CN1796825A - Multi-speed transmission for vehicle - Google Patents

Multi-speed transmission for vehicle Download PDF

Info

Publication number
CN1796825A
CN1796825A CN 200510097408 CN200510097408A CN1796825A CN 1796825 A CN1796825 A CN 1796825A CN 200510097408 CN200510097408 CN 200510097408 CN 200510097408 A CN200510097408 A CN 200510097408A CN 1796825 A CN1796825 A CN 1796825A
Authority
CN
China
Prior art keywords
planetary gear
grade
gear set
clutch
engaging
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN 200510097408
Other languages
Chinese (zh)
Other versions
CN100540943C (en
Inventor
镰田淳史
本多敦
安倍晶治
田端淳
野崎和俊
井上雄二
太田博文
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Motor Corp
Original Assignee
Toyota Motor Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Toyota Motor Corp filed Critical Toyota Motor Corp
Publication of CN1796825A publication Critical patent/CN1796825A/en
Application granted granted Critical
Publication of CN100540943C publication Critical patent/CN100540943C/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0073—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eleven forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
    • F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
    • F16H2200/2023—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 4 connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2048—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with seven engaging means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

A transmission can be provided which achieves multiple speeds while maintaining good balance of gear ratio steps between gears by having a first clutch which selectively connects a first intermediate output member and a fourth rotating element RE 4 together, a second clutch which selectively connects an input shaft and a second rotating element RE 2 together, a third clutch which selectively connects the first intermediate output member and a first rotating element RE 1 together, a fourth clutch which selectively connects the input shaft and the first rotating element RE 1 together, a fifth clutch which selectively connects a second intermediate output member and the first rotating element RE 1 together, a first brake which selectively holds the first rotating element RE 1 to a transmission case, and a second brake which selectively holds the second rotating element RE 2 to the transmission case.

Description

The multi-speed transmission that is used for vehicle
Technical field
The present invention relates to be used for the multi-speed transmission (multiple-speed gear-box, multistage speed changer) of vehicle, this multi-speed transmission is arranged on such as between prime mover and driving wheel in the vehicle of automobile.
Background technique
Vehicle is provided with speed changer usually between prime mover and driving wheel.A kind of so known speed changer is the multi-speed transmission that is used to realize a plurality of predetermined speed ratios or shelves.Use a plurality of planetary gear set and be used for to form that the element of those planetary gear set is bonded together is widely used such as the multi-speed transmission of the planetary gear type of the joint element of clutch and break.For example, disclosed Japanese national phase application No.2003-514195, JP (A) 2002-206601, JP (A) 2002-213545, JP (A) 2002-227940, JP (A) 2002-266956 and JP (A) 2002-295609 have proposed a kind of multi-speed transmission, and described multi-speed transmission has first speed changing portion that comprises two preposition planetary gear set and comprises second speed changing portion of two rearmounted planetary gear set and can realize a plurality of gears of seven or more a plurality of forward gearss.Particularly, the multi-speed transmission that discloses in disclosed Japanese national phase application No.2003-514195 has two not changeable preposition planetary gear set and a plurality of joint element, and can realize at least seven gears that advance (that is shelves) by optionally engaging those joint elements.
When being used for the quantity of gear (that is, shelves) of the multi-speed transmission of vehicle when further increase, preferably speed ratio level (that is, the variance ratio of the speed ratio of shelves) continuously equates or is approaching with it.Yet under the situation of this traditional multi-speed transmission, the speed ratio level of shelves is always not good yet.For example, as shown in Fig. 1 (B) of disclosed Japanese national phase application No.2003-514195, the speed ratio level between first grade and second grade is 1.86, this is a bigger level.Also have the change of a great deal of in the big small-scale of speed ratio level, this is undesirable.Therefore the demand that has the multi-speed transmission of a kind of like this vehicle of exploitation, described multi-speed transmission can realize that a plurality of gears (that is shelves) keep good balance simultaneously among the speed ratio level between the shelves.
Summary of the invention
Consider afore-mentioned, therefore the invention provides a kind of multi-speed transmission that is used for vehicle, described multi-speed transmission can realize that a plurality of gears (speed) (also being referred to as " shelves " hereinafter (gear)) keep good balance simultaneously among the speed ratio level between the shelves.
Therefore, the invention is characterized in and comprise: first speed changing portion, described first speed changing portion have slow down and transmit come from the rotation of importing rotating element first in the middle of output element, and make come from import rotating element rotation oppositely and transmit the second centre output element of this rotation; Second speed changing portion, described second speed changing portion comprise four rotating elements that some sun gears, planet carrier and the gear ring by two planetary gear set that link together constitutes; And when on the nomogram of the rotating speed that can represent four rotating elements by straight line, by the order that passes through, with described four rotating elements during as first rotating element, second rotating element, the 3rd rotating element and the 4th rotating element, have: first clutch element, described first clutch element optionally link together the first middle output element and the 4th rotating element; The second clutch element, described second clutch element optionally will import rotating element and second rotating element links together; Three-clutch element, described three-clutch element optionally link together the first middle output element and first rotating element; The four clutches element, described four clutches element optionally will import rotating element and first rotating element links together; The 5th clutch element, described the 5th clutch element optionally link together the second middle output element and first rotating element; First brake component, described first brake component optionally remains in nonrotational element with first rotating element; And second brake component, described second brake component optionally remains in nonrotational element with second rotating element.
Therefore, provide first speed changing portion and second speed changing portion that a kind of multi-speed transmission that is used for vehicle can be provided, described multi-speed transmission can realize that a plurality of gears (that is shelves) keep good balance simultaneously among the speed ratio level between the shelves.
Here, preferably set up first grade by engaging the first clutch element and second brake component; Set up second grade by engaging the first clutch element and first brake component; Set up third gear by engaging first clutch element and three-clutch element; Set up fourth speed by engaging first clutch element and four clutches element; Set up the 5th grade by engaging first clutch element and second clutch element; Set up the 6th grade by engaging second clutch element and four clutches element; Set up the 7th grade by engaging second clutch element and three-clutch element; Set up the 8th grade by engaging the second clutch element and first brake component; And set up the 9th grade by engaging second clutch element and the 5th clutch element.Therefore, except that can realizing nine forward gearss, the level between the 8th grade and the 9th grade can preferably be set lessly with intensive speed ratio.
In addition, preferably set up first grade by engaging first clutch element and the 5th clutch element; Set up second grade by engaging the first clutch element and first brake component; Set up third gear by engaging first clutch element and three-clutch element; Set up fourth speed by engaging first clutch element and four clutches element; Set up the 5th grade by engaging first clutch element and second clutch element; Set up the 6th grade by engaging second clutch element and four clutches element; Set up the 7th grade by engaging second clutch element and three-clutch element; Set up the 8th grade by engaging the second clutch element and first brake component; And set up the 9th grade by engaging second clutch element and the 5th clutch element.Therefore, except that can realizing nine forward gearss, the level between the 8th grade and the 9th grade can preferably be set lessly with intensive speed ratio.
In addition, preferably set up first grade by engaging the 5th clutch element and second brake component; Set up second grade by engaging the first clutch element and first brake component; Set up third gear by engaging first clutch element and three-clutch element; Set up fourth speed by engaging first clutch element and four clutches element; Set up the 5th grade by engaging first clutch element and second clutch element; Set up the 6th grade by engaging second clutch element and four clutches element; Set up the 7th grade by engaging second clutch element and three-clutch element; Set up the 8th grade by engaging the second clutch element and first brake component; And set up the 9th grade by engaging second clutch element and the 5th clutch element.Therefore, except that can realizing nine forward gearss, the level between the 8th grade and the 9th grade can preferably be set lessly with intensive speed ratio.
In addition, preferably set up first grade by engaging the 5th clutch element and second brake component; Set up second grade by engaging the first clutch element and second brake component; Set up third gear by engaging the first clutch element and first brake component; Set up fourth speed by engaging first clutch element and three-clutch element; Set up the 5th grade by engaging first clutch element and four clutches element; Set up the 6th grade by engaging first clutch element and second clutch element; Set up the 7th grade by engaging second clutch element and four clutches element; Set up the 8th grade by engaging second clutch element and three-clutch element; And set up the 9th grade by engaging the second clutch element and first brake component.Therefore, except that can realizing nine forward gearss, the level between the 8th grade and the 9th grade can preferably be set lessly with intensive speed ratio.
In addition, preferably set up first grade by engaging the first clutch element and second brake component; Set up second grade by engaging first clutch element and the 5th clutch element; Set up third gear by engaging the first clutch element and first brake component; Set up fourth speed by engaging first clutch element and three-clutch element; Set up the 5th grade by engaging first clutch element and four clutches element; Set up the 6th grade by engaging first clutch element and second clutch element; Set up the 7th grade by engaging second clutch element and four clutches element; Set up the 8th grade by engaging second clutch element and three-clutch element; And set up the 9th grade by engaging the second clutch element and first brake component.Therefore, except that can realizing nine forward gearss, the level between the 8th grade and the 9th grade can preferably be set lessly with intensive speed ratio.
In addition, preferably set up first grade by engaging the 5th clutch element and second brake component; Set up second grade by engaging first clutch element and the 5th clutch element; Set up third gear by engaging the first clutch element and first brake component; Set up fourth speed by engaging first clutch element and three-clutch element; Set up the 5th grade by engaging first clutch element and four clutches element; Set up the 6th grade by engaging first clutch element and second clutch element; Set up the 7th grade by engaging second clutch element and four clutches element; Set up the 8th grade by engaging second clutch element and three-clutch element; And set up the 9th grade by engaging the second clutch element and first brake component.Therefore, except that can realizing nine forward gearss, the level between the 8th grade and the 9th grade can preferably be set lessly with intensive speed ratio.
In addition, preferably set up first grade by engaging first clutch element and the 5th clutch element; Set up second grade by engaging the first clutch element and second brake component; Set up third gear by engaging the first clutch element and first brake component; Set up fourth speed by engaging first clutch element and three-clutch element; Set up the 5th grade by engaging first clutch element and four clutches element; Set up the 6th grade by engaging first clutch element and second clutch element; Set up the 7th grade by engaging second clutch element and four clutches element; Set up the 8th grade by engaging second clutch element and three-clutch element; Set up the 9th grade by engaging the second clutch element and first brake component; And set up the tenth grade by engaging second clutch element and the 5th clutch element.Therefore, except that can realizing ten forward gearss, the level between the 9th grade and the tenth grade can preferably be set lessly with intensive speed ratio.
In addition, preferably set up first grade by engaging the 5th clutch element and second brake component; Set up second grade by engaging the first clutch element and second brake component; Set up third gear by engaging the first clutch element and first brake component; Set up fourth speed by engaging first clutch element and three-clutch element; Set up the 5th grade by engaging first clutch element and four clutches element; Set up the 6th grade by engaging first clutch element and second clutch element; Set up the 7th grade by engaging second clutch element and four clutches element; Set up the 8th grade by engaging second clutch element and three-clutch element; Set up the 9th grade by engaging the second clutch element and first brake component; And set up the tenth grade by engaging second clutch element and the 5th clutch element.Therefore, except that can realizing ten forward gearss, the level between the 9th grade and the tenth grade can preferably be set lessly with intensive speed ratio.
In addition, preferably set up first grade by engaging the first clutch element and second brake component; Set up second grade by engaging first clutch element and the 5th clutch element; Set up third gear by engaging the first clutch element and first brake component; Set up fourth speed by engaging first clutch element and three-clutch element; Set up the 5th grade by engaging first clutch element and four clutches element; Set up the 6th grade by engaging first clutch element and second clutch element; Set up the 7th grade by engaging second clutch element and four clutches element; Set up the 8th grade by engaging second clutch element and three-clutch element; Set up the 9th grade by engaging the second clutch element and first brake component; And set up the tenth grade by engaging second clutch element and the 5th clutch element.Therefore, except that can realizing ten forward gearss, the level between the 9th grade and the tenth grade can preferably be set lessly with intensive speed ratio.
In addition, preferably set up first grade by engaging the first clutch element and second brake component; Set up second grade by engaging first clutch element and the 5th clutch element; Set up third gear by engaging the first clutch element and first brake component; Set up fourth speed by engaging first clutch element and three-clutch element; Set up the 5th grade by engaging first clutch element and four clutches element; Set up the 6th grade by engaging first clutch element and second clutch element; Set up the 7th grade by engaging second clutch element and four clutches element; Set up the 8th grade by engaging second clutch element and three-clutch element; Set up the 9th grade by engaging the second clutch element and first brake component; And set up the tenth grade by engaging second clutch element and the 5th clutch element.Therefore, except that can realizing ten forward gearss, the level between the 9th grade and the tenth grade can preferably be set lessly with intensive speed ratio.
In addition, preferably set up first grade by engaging the 5th clutch element and second brake component; Set up second grade by engaging the first clutch element and second brake component; Set up third gear by engaging first clutch element and the 5th clutch element; Set up fourth speed by engaging the first clutch element and first brake component; Set up the 5th grade by engaging first clutch element and three-clutch element; Set up the 6th grade by engaging first clutch element and four clutches element; Set up the 7th grade by engaging first clutch element and second clutch element; Set up the 8th grade by engaging second clutch element and four clutches element; Set up the 9th grade by engaging second clutch element and three-clutch element; Set up the tenth grade by engaging the second clutch element and first brake component; And set up the 11 grade by engaging second clutch element and the 5th clutch element.Therefore, except that can realizing 11 forward gearss, the level between the 8th grade and the 11 grade can preferably be set lessly with intensive speed ratio.In addition, first grade can be set extremely lowly.
In addition, first speed changing portion preferably includes first preposition planetary gear set of single small gear type and the second preposition planetary gear set of double pinion type, wherein the sun gear of the planet carrier of the first preposition planetary gear set and the second preposition planetary gear set always is connected in nonrotational element, and the planet carrier of the sun gear of the first preposition planetary gear set and the second preposition planetary gear set is connected in the input rotating element, so that the gear ring of the second preposition planetary gear set as the first middle output element, makes the gear ring of the preposition planetary gear set of winning as the second middle output element simultaneously.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, first speed changing portion preferably includes first preposition planetary gear set of double pinion type and the second preposition planetary gear set of single small gear type, wherein the planet carrier of the first preposition planetary gear set always is connected in nonrotational element, the planet carrier of the gear ring of the first preposition planetary gear set and the second preposition planetary gear set links together, and the gear ring of the sun gear of the first preposition planetary gear set and the second preposition planetary gear set is connected in the input rotating element, so that the planet carrier of the gear ring of the first preposition planetary gear set or the second preposition planetary gear set as the first middle output element, makes the sun gear of the second preposition planetary gear set be used as the second middle output element simultaneously.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, first speed changing portion preferably includes first preposition planetary gear set of double pinion type and the second preposition planetary gear set of single small gear type, wherein the sun gear of the first preposition planetary gear set always is connected in nonrotational element, the planet carrier of the gear ring of the first preposition planetary gear set and the second preposition planetary gear set links together, and the gear ring of the planet carrier of the first preposition planetary gear set and the second preposition planetary gear set is connected in the input rotating element, so that the planet carrier of the gear ring of the first preposition planetary gear set or the second preposition planetary gear set as the first middle output element, makes the sun gear of the second preposition planetary gear set be used as the second middle output element simultaneously.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, first speed changing portion preferably includes first preposition planetary gear set of single small gear type and the second preposition planetary gear set of double pinion type, wherein the gear ring of the second preposition planetary gear set always is connected in nonrotational element, the sun gear of the sun gear of the first preposition planetary gear set and the second preposition planetary gear set links together, the planet carrier of the planet carrier of the first preposition planetary gear set and the second preposition planetary gear set links together, and the gear ring of the first preposition planetary gear set is connected in the input rotating element, so that the planet carrier of the planet carrier of the first preposition planetary gear set or the second preposition planetary gear set as the first middle output element, makes the sun gear of the preposition planetary gear set of winning or the sun gear of the second preposition planetary gear set be used as the second middle output element simultaneously.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, first speed changing portion preferably includes first preposition planetary gear set of single small gear type and the second preposition planetary gear set of double pinion type, wherein the gear ring of the planet carrier of the first preposition planetary gear set and the second preposition planetary gear set always is connected in nonrotational element, the planet carrier of the gear ring of the first preposition planetary gear set and the second preposition planetary gear set links together, and the sun gear of the first preposition planetary gear set is connected in the input rotating element, so that the sun gear of the second preposition planetary gear set as the first middle output element, makes the gear ring of the preposition planetary gear set of winning or the planet carrier of the second preposition planetary gear set be used as the second middle output element simultaneously.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, first speed changing portion preferably includes first preposition planetary gear set of single small gear type and the second preposition planetary gear set of single small gear type, wherein the planet carrier of the planet carrier of the first preposition planetary gear set and the second preposition planetary gear set always is connected in nonrotational element, and the sun gear of the first preposition planetary gear set is connected in the input rotating element, so that the sun gear of the second preposition planetary gear set as the first middle output element, makes the gear ring of the preposition planetary gear set of winning as the second middle output element simultaneously.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, first speed changing portion preferably includes first preposition planetary gear set of single small gear type and the second preposition planetary gear set of single small gear type, wherein the planet carrier of the planet carrier of the first preposition planetary gear set and the second preposition planetary gear set always is connected in nonrotational element, and the sun gear of the first preposition planetary gear set is connected in the input rotating element, so that the sun gear of the second preposition planetary gear set as the first middle output element, makes the gear ring of the second preposition planetary gear set be used as the second middle output element simultaneously.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, first speed changing portion preferably includes first preposition planetary gear set of single small gear type and the second preposition planetary gear set of single small gear type, wherein the sun gear of the second preposition planetary gear set always is connected in nonrotational element, the planet carrier of the planet carrier of the first preposition planetary gear set and the second preposition planetary gear set is joined together to form single rotating element, and the gear ring of the second preposition planetary gear set is connected in the input rotating element, so that single rotating element as the first middle output element, makes the sun gear of the preposition planetary gear set of winning as the second middle output element simultaneously.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, first speed changing portion preferably includes first preposition planetary gear set of single small gear type and the second preposition planetary gear set of single small gear type, wherein the sun gear of the second preposition planetary gear set always is connected in nonrotational element, the planet carrier of the planet carrier of the first preposition planetary gear set and the second preposition planetary gear set is joined together to form single rotating element, and the gear ring of the first preposition planetary gear set is connected in the input rotating element, so that single rotating element as the first middle output element, makes the sun gear of the preposition planetary gear set of winning as the second middle output element simultaneously.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, first speed changing portion preferably includes first preposition planetary gear set of single small gear type and the second preposition planetary gear set of double pinion type, wherein the gear ring of the second preposition planetary gear set always is connected in nonrotational element, the sun gear of the planet carrier of the first preposition planetary gear set and the second preposition planetary gear set links together, the planet carrier of the sun gear of the first preposition planetary gear set and the second preposition planetary gear set links together, and the gear ring of the first preposition planetary gear set is connected in the input rotating element, so that the sun gear of the planet carrier of the first preposition planetary gear set that links together and the second preposition planetary gear set is used as the first middle output element, the planet carrier of the sun gear of the feasible first preposition planetary gear set that links together and the second preposition planetary gear set is as the second middle output element simultaneously.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, first speed changing portion preferably includes first preposition planetary gear set of single small gear type and the second preposition planetary gear set of double pinion type, wherein the gear ring of the second preposition planetary gear set always is connected in nonrotational element, the sun gear of the sun gear of the first preposition planetary gear set and the second preposition planetary gear set links together, and the planet carrier of the gear ring of the first preposition planetary gear set and the second preposition planetary gear set links together and is connected in the input rotating element, so that the planet carrier of the first preposition planetary gear set is used as the first middle output element, the sun gear of the sun gear of the feasible first preposition planetary gear set that links together and the second preposition planetary gear set is as the second middle output element simultaneously.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, first speed changing portion preferably includes first preposition planetary gear set of single small gear type and the second preposition planetary gear set of double pinion type, wherein the gear ring of the planet carrier of the first preposition planetary gear set and the second preposition planetary gear set always is connected in nonrotational element, the sun gear of the gear ring of the first preposition planetary gear set and the second preposition planetary gear set links together, and the sun gear of the first preposition planetary gear set is connected in the input rotating element, so that the planet carrier of the second preposition planetary gear set is used as the first middle output element, the sun gear of the gear ring of the feasible first preposition planetary gear set that links together and the second preposition planetary gear set is as the second middle output element simultaneously.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, first speed changing portion preferably includes first preposition planetary gear set of double pinion type and the second preposition planetary gear set of single small gear type, wherein the gear ring of the first preposition planetary gear set always is connected in nonrotational element, the sun gear of the planet carrier of the first preposition planetary gear set and the second preposition planetary gear set links together, and the gear ring of the sun gear of the first preposition planetary gear set and the second preposition planetary gear set is connected in the input rotating element, so that the planet carrier of the second preposition planetary gear set is used as the first middle output element, the sun gear of the planet carrier of the feasible first preposition planetary gear set that links together and the second preposition planetary gear set is as the second middle output element simultaneously.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, first speed changing portion preferably includes first preposition planetary gear set of single small gear type and the second preposition planetary gear set of single small gear type, wherein the planet carrier of the first preposition planetary gear set always is connected in nonrotational element, the sun gear of the gear ring of the first preposition planetary gear set and the second preposition planetary gear set links together, and the gear ring of the sun gear of the first preposition planetary gear set and the second preposition planetary gear set is connected in the input rotating element, so that the planet carrier of the second preposition planetary gear set is used as the first middle output element, the sun gear of the gear ring of the feasible first preposition planetary gear set that links together and the second preposition planetary gear set is as the second middle output element simultaneously.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, second speed changing portion preferably includes first rearmounted planetary gear set of single small gear type and the second rearmounted planetary gear set of double pinion type, wherein first rotating element is that sun gear by the first rearmounted planetary gear set constitutes, second rotating element is that the planet carrier by the planet carrier of the first rearmounted planetary gear set that links together and the second rearmounted planetary gear set constitutes, the 3rd rotating element is that the gear ring by the gear ring of the first rearmounted planetary gear set that links together and the second rearmounted planetary gear set constitutes, and the 4th rotating element is that sun gear by the second rearmounted planetary gear set constitutes.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, second speed changing portion preferably includes first rearmounted planetary gear set of single small gear type and the second rearmounted planetary gear set of double pinion type, wherein first rotating element is to be made of the sun gear of the first rearmounted planetary gear set that links together and the planet carrier of the second rearmounted planetary gear set, second rotating element is that the gear ring by the planet carrier of the first rearmounted planetary gear set that links together and the second rearmounted planetary gear set constitutes, the 3rd rotating element is that the gear ring by the first rearmounted planetary gear set constitutes, and the 4th rotating element is that sun gear by the second rearmounted planetary gear set constitutes.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, second speed changing portion preferably includes first rearmounted planetary gear set of single small gear type and the second rearmounted planetary gear set of double pinion type, wherein first rotating element is that sun gear by the first rearmounted planetary gear set constitutes, second rotating element is that the planet carrier by the planet carrier of the first rearmounted planetary gear set that links together and the second rearmounted planetary gear set constitutes, the 3rd rotating element is that the gear ring by the second rearmounted planetary gear set constitutes, and the 4th rotating element is to be made of the gear ring of the first rearmounted planetary gear set that links together and the sun gear of the second rearmounted planetary gear set.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, second speed changing portion preferably includes first rearmounted planetary gear set of double pinion type and the second rearmounted planetary gear set of double pinion type, wherein first rotating element is that sun gear by the first rearmounted planetary gear set constitutes, second rotating element is that the planet carrier by the gear ring of the first rearmounted planetary gear set that links together and the second rearmounted planetary gear set constitutes, the 3rd rotating element is that the gear ring by the second rearmounted planetary gear set constitutes, and the 4th rotating element is to be made of the planet carrier of the first rearmounted planetary gear set that links together and the sun gear of the second rearmounted planetary gear set.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, second speed changing portion preferably includes first rearmounted planetary gear set of double pinion type and the second rearmounted planetary gear set of double pinion type, wherein first rotating element is that planet carrier by the first rearmounted planetary gear set constitutes, second rotating element is that the planet carrier by the gear ring of the first rearmounted planetary gear set that links together and the second rearmounted planetary gear set constitutes, the 3rd rotating element is that the gear ring by the second rearmounted planetary gear set constitutes, and the 4th rotating element is to be made of the sun gear of the first rearmounted planetary gear set that links together and the sun gear of the second rearmounted planetary gear set.Therefore, can be provided for the practical multi-speed transmission of vehicle.
Description of drawings
Read following detailed description of preferred embodiment in conjunction with the drawings, will understand its feature, advantage and technology and the industrial significance of the embodiment of the invention better, wherein:
Fig. 1 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's first exemplary embodiment;
Fig. 2 is clutch and brake engages figure, shows in the speed changer shown in Fig. 1 default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those (presetting) grade;
Fig. 3 shows the signal that is input to the ECU that is used for the speed changer shown in the control graph 1 and the view of the example of the signal exported from described ECU;
Fig. 4 is the nomogram that can enough straight lines be illustrated in the relativeness between the rotational velocity of the various rotating elements that differently connect in the speed changer shown in Fig. 1 in each grade;
Fig. 5 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's second exemplary embodiment;
Fig. 6 is clutch and brake engages figure, shows in the speed changer shown in Fig. 5 default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Fig. 7 is the nomogram that can enough straight lines be illustrated in the relativeness between the rotational velocity of the various rotating elements that differently connect in the speed changer shown in Fig. 5 in each grade;
Fig. 8 is clutch and brake engages figure, shows first of the present invention's second exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Fig. 9 is and the corresponding nomogram of Fig. 8, and described nomogram can enough straight lines be illustrated in first of the present invention's second exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 10 is clutch and brake engages figure, shows second of the present invention's second exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 11 is and the corresponding nomogram of Figure 10, and described nomogram can enough straight lines be illustrated in second of the present invention's second exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 12 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's the 3rd exemplary embodiment;
Figure 13 is clutch and brake engages figure, shows in the speed changer shown in Figure 12 default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 14 is the nomogram that can enough straight lines be illustrated in the relativeness between the rotational velocity of the various rotating elements that differently connect in the speed changer shown in Figure 12 in each grade;
Figure 15 is clutch and brake engages figure, shows first of the present invention's the 3rd exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 16 is and the corresponding nomogram of Figure 15, and described nomogram can enough straight lines be illustrated in first of the present invention's the 3rd exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 17 is clutch and brake engages figure, shows second of the present invention's the 3rd exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 18 is and the corresponding nomogram of Figure 17, and described nomogram can enough straight lines be illustrated in second of the present invention's the 3rd exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 19 is clutch and brake engages figure, shows the 3rd of the present invention's the 3rd exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 20 is and the corresponding nomogram of Figure 19, and described nomogram can enough straight lines be illustrated in the 3rd of the present invention's the 3rd exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 21 is clutch and brake engages figure, shows the 4th of the present invention's the 3rd exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 22 is and the corresponding nomogram of Figure 21, and described nomogram can enough straight lines be illustrated in the 4th of the present invention's the 3rd exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 23 is clutch and brake engages figure, shows the 5th of the present invention's the 3rd exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 24 is and the corresponding nomogram of Figure 23, and described nomogram can enough straight lines be illustrated in the 5th of the present invention's the 3rd exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 25 is clutch and brake engages figure, shows the 6th of the present invention's the 3rd exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 26 is and the corresponding nomogram of Figure 25, and described nomogram can enough straight lines be illustrated in the 6th of the present invention's the 3rd exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 27 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's the 4th exemplary embodiment;
Figure 28 is clutch and brake engages figure, shows in the speed changer shown in Figure 27 default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 29 is clutch and brake engages figure, shows first of the present invention's the 4th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 30 can enough straight lines be illustrated in the related speed changer of the present invention's the 4th exemplary embodiment and first nomogram of revising the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade of the present invention's the 4th exemplary embodiment;
Figure 31 is clutch and brake engages figure, shows second of the present invention's the 4th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 32 is and the corresponding nomogram of Figure 31, and described nomogram can enough straight lines be illustrated in second of the present invention's the 4th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 33 is clutch and brake engages figure, shows the 3rd of the present invention's the 4th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 34 is and the corresponding nomogram of Figure 33, and described nomogram can enough straight lines be illustrated in the 3rd of the present invention's the 4th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 35 is clutch and brake engages figure, shows the 4th of the present invention's the 4th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 36 is and the corresponding nomogram of Figure 35, and described nomogram can enough straight lines be illustrated in the 4th of the present invention's the 4th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 37 is clutch and brake engages figure, shows the 5th of the present invention's the 4th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 38 is and the corresponding nomogram of Figure 37, and described nomogram can enough straight lines be illustrated in the 5th of the present invention's the 4th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 39 is clutch and brake engages figure, shows the 6th of the present invention's the 4th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 40 is and the corresponding nomogram of Figure 39, and described nomogram can enough straight lines be illustrated in the 6th of the present invention's the 4th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 41 is clutch and brake engages figure, shows the 7th of the present invention's the 4th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 42 is and the corresponding nomogram of Figure 41, and described nomogram can enough straight lines be illustrated in the 7th of the present invention's the 4th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 43 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's the 5th exemplary embodiment;
Figure 44 is clutch and brake engages figure, shows in the speed changer shown in Figure 43 default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 45 is clutch and brake engages figure, shows first of the present invention's the 5th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 46 can enough straight lines be illustrated in the related speed changer of the present invention's the 5th exemplary embodiment and first nomogram of revising the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade of the present invention's the 5th exemplary embodiment;
Figure 47 is clutch and brake engages figure, shows second of the present invention's the 5th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 48 is and the corresponding nomogram of Figure 47, and described nomogram can enough straight lines be illustrated in second of the present invention's the 5th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 49 is clutch and brake engages figure, shows the 3rd of the present invention's the 5th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 50 is and the corresponding nomogram of Figure 49, and described nomogram can enough straight lines be illustrated in the 3rd of the present invention's the 5th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 51 is clutch and brake engages figure, shows the 4th of the present invention's the 5th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 52 is and the corresponding nomogram of Figure 51, and described nomogram can enough straight lines be illustrated in the 4th of the present invention's the 5th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 53 is clutch and brake engages figure, shows the 5th of the present invention's the 5th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 54 is and the corresponding nomogram of Figure 53, and described nomogram can enough straight lines be illustrated in the 5th of the present invention's the 5th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 55 is clutch and brake engages figure, shows the 6th of the present invention's the 5th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 56 is and the corresponding nomogram of Figure 55, and described nomogram can enough straight lines be illustrated in the 6th of the present invention's the 5th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 57 is clutch and brake engages figure, shows the 7th of the present invention's the 5th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 58 is and the corresponding nomogram of Figure 57, and described nomogram can enough straight lines be illustrated in the 7th of the present invention's the 5th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 59 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's the 6th exemplary embodiment;
Figure 60 is clutch and brake engages figure, shows in the speed changer shown in Figure 59 default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 61 is the nomogram that can enough straight lines be illustrated in the relativeness between the rotational velocity of the various rotating elements that differently connect in the speed changer shown in Figure 59 in each grade;
Figure 62 is clutch and brake engages figure, shows first of the present invention's the 6th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 63 is and physical culture 62 corresponding nomograms, and described nomogram can enough straight lines be illustrated in first of the present invention's the 6th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 64 is clutch and brake engages figure, shows second of the present invention's the 6th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 65 is and the corresponding nomogram of Figure 64, and described nomogram can enough straight lines be illustrated in second of the present invention's the 6th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 66 is clutch and brake engages figure, shows the 3rd of the present invention's the 6th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 67 is and the corresponding nomogram of Figure 66, and described nomogram can enough straight lines be illustrated in the 3rd of the present invention's the 6th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 68 is clutch and brake engages figure, shows the 4th of the present invention's the 6th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 69 is and the corresponding nomogram of Figure 68, and described nomogram can enough straight lines be illustrated in the 4th of the present invention's the 6th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 70 is clutch and brake engages figure, shows the 5th of the present invention's the 6th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 71 is and the corresponding nomogram of Figure 70, and described nomogram can enough straight lines be illustrated in the 5th of the present invention's the 6th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 72 is clutch and brake engages figure, shows the 6th of the present invention's the 6th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 73 is and the corresponding nomogram of Figure 72, and described nomogram can enough straight lines be illustrated in the 6th of the present invention's the 6th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 74 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's the 7th exemplary embodiment;
Figure 75 is clutch and brake engages figure, shows in the speed changer shown in Figure 74 default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 76 is clutch and brake engages figure, shows first of the present invention's the 7th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 77 is clutch and brake engages figure, shows second of the present invention's the 7th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 78 can enough straight lines be illustrated in the related speed changer of the present invention's the 7th exemplary embodiment and first and second nomograms of revising the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of examples in each grade of the present invention's the 7th exemplary embodiment;
Figure 79 is clutch and brake engages figure, shows the 3rd of the present invention's the 7th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 80 can be illustrated in the 3rd of the present invention's the 7th exemplary embodiment is revised the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade nomogram by enough straight lines;
Figure 81 is clutch and brake engages figure, shows the 4th of the present invention's the 7th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 82 can be illustrated in the 4th of the present invention's the 7th exemplary embodiment is revised the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade nomogram by enough straight lines;
Figure 83 is clutch and brake engages figure, shows the 5th of the present invention's the 7th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 84 can be illustrated in the 5th of the present invention's the 7th exemplary embodiment is revised the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade nomogram by enough straight lines;
Figure 85 is clutch and brake engages figure, shows the 6th of the present invention's the 7th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 86 can be illustrated in the 6th of the present invention's the 7th exemplary embodiment is revised the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade nomogram by enough straight lines;
Figure 87 is clutch and brake engages figure, shows the 7th of the present invention's the 7th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 88 can be illustrated in the 7th of the present invention's the 7th exemplary embodiment is revised the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade nomogram by enough straight lines;
Figure 89 is clutch and brake engages figure, shows the 8th of the present invention's the 7th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 90 can be illustrated in the 8th of the present invention's the 7th exemplary embodiment is revised the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade nomogram by enough straight lines;
Figure 91 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's the 8th exemplary embodiment;
Figure 92 is clutch and brake engages figure, shows in the related speed changer of the present invention's the 8th exemplary embodiment default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 93 is clutch and brake engages figure, shows first of the present invention's the 8th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 94 can enough straight lines be illustrated in the related speed changer of the present invention's the 8th exemplary embodiment and first nomogram of revising the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade of the present invention's the 8th exemplary embodiment;
Figure 95 is clutch and brake engages figure, shows second of the present invention's the 8th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 96 is and the corresponding nomogram of Figure 91, and described nomogram can enough straight lines be illustrated in second of the present invention's the 8th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 97 is clutch and brake engages figure, shows the 3rd of the present invention's the 8th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 98 is and the corresponding nomogram of Figure 97, and described nomogram can enough straight lines be illustrated in the 3rd of the present invention's the 8th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 99 is clutch and brake engages figure, shows the 4th of the present invention's the 8th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 100 is and the corresponding nomogram of Figure 99, and described nomogram can enough straight lines be illustrated in the 4th of the present invention's the 8th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 101 is clutch and brake engages figure, shows the 5th of the present invention's the 8th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 102 is and the corresponding nomogram of Figure 101, and described nomogram can enough straight lines be illustrated in the 5th of the present invention's the 8th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 103 is clutch and brake engages figure, shows the 6th of the present invention's the 8th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 104 is and the corresponding nomogram of Figure 103, and described nomogram can enough straight lines be illustrated in the 6th of the present invention's the 8th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 105 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's the 9th exemplary embodiment;
Figure 106 is clutch and brake engages figure, shows in the related speed changer of the present invention's the 9th exemplary embodiment default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 107 is clutch and brake engages figure, shows first of the present invention's the 9th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 108 can enough straight lines be illustrated in the related speed changer of the present invention's the 9th exemplary embodiment and first nomogram of revising the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade of the present invention's the 9th exemplary embodiment;
Figure 109 is clutch and brake engages figure, shows second of the present invention's the 9th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 110 is and the corresponding nomogram of Figure 109, and described nomogram can enough straight lines be illustrated in second of the present invention's the 9th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 111 is clutch and brake engages figure, shows the 3rd of the present invention's the 9th exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 112 is and the corresponding nomogram of Figure 111, and described nomogram can enough straight lines be illustrated in the 3rd of the present invention's the 9th exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 113 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's the tenth exemplary embodiment;
Figure 114 is clutch and brake engages figure, shows in the related speed changer of the present invention's the tenth exemplary embodiment default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 115 is clutch and brake engages figure, shows first of the present invention's the tenth exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 116 can enough straight lines be illustrated in the related speed changer of the present invention's the tenth exemplary embodiment and first nomogram of revising the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade of the present invention's the tenth exemplary embodiment;
Figure 117 is clutch and brake engages figure, shows second of the present invention's the tenth exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 118 is and the corresponding nomogram of Figure 117, and described nomogram can enough straight lines be illustrated in second of the present invention's the tenth exemplary embodiment and revises relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade;
Figure 119 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's the 11 exemplary embodiment;
Figure 120 is clutch and brake engages figure, shows in the related speed changer of the present invention's the 11 exemplary embodiment default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 121 is the nomogram that can enough straight lines be illustrated in the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of the present invention's the 11 exemplary embodiment in each grade;
Figure 122 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's the 12 exemplary embodiment;
Figure 123 is clutch and brake engages figure, shows in the related speed changer of the present invention's the 12 exemplary embodiment default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 124 is the nomogram that can enough straight lines be illustrated in the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of the present invention's the 12 exemplary embodiment in each grade;
Figure 125 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's the 13 exemplary embodiment;
Figure 126 is clutch and brake engages figure, shows in the related speed changer of the present invention's the 13 exemplary embodiment default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 127 is the nomogram that can enough straight lines be illustrated in the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of the present invention's the 13 exemplary embodiment in each grade;
Figure 128 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's the 14 exemplary embodiment;
Figure 129 is clutch and brake engages figure, shows in the related speed changer of the present invention's the 14 exemplary embodiment default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 130 is the nomogram that can enough straight lines be illustrated in the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of the present invention's the 14 exemplary embodiment in each grade;
Figure 131 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's the 15 exemplary embodiment;
Figure 132 is clutch and brake engages figure, shows in the related speed changer of the present invention's the 15 exemplary embodiment default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 133 is the nomogram that can enough straight lines be illustrated in the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of the present invention's the 15 exemplary embodiment in each grade;
Figure 134 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's the 16 exemplary embodiment;
Figure 135 is clutch and brake engages figure, shows in the related speed changer of the present invention's the 16 exemplary embodiment default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 136 is the nomogram that can enough straight lines be illustrated in the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of the present invention's the 16 exemplary embodiment in each grade;
Figure 137 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's the 17 exemplary embodiment;
Figure 138 is clutch and brake engages figure, shows in the related speed changer of the present invention's the 17 exemplary embodiment default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 139 is the nomogram that can enough straight lines be illustrated in the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of the present invention's the 17 exemplary embodiment in each grade;
Figure 140 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's the 18 exemplary embodiment;
Figure 141 is clutch and brake engages figure, shows in the related speed changer of the present invention's the 18 exemplary embodiment default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 142 is the nomogram that can enough straight lines be illustrated in the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of the present invention's the 18 exemplary embodiment in each grade;
Figure 143 is clutch and brake engages figure, shows first of the present invention's the 18 exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 144 can be illustrated in first of the present invention's the 18 exemplary embodiment is revised the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade nomogram by enough straight lines;
Figure 145 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's the 19 exemplary embodiment;
Figure 146 is clutch and brake engages figure, shows in the related speed changer of the present invention's the 19 exemplary embodiment default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 147 is the nomogram that can enough straight lines be illustrated in the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of the present invention's the 19 exemplary embodiment in each grade;
Figure 148 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's the 20 exemplary embodiment;
Figure 149 is clutch and brake engages figure, shows in the related speed changer of the present invention's the 20 exemplary embodiment default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 150 is the nomogram that can enough straight lines be illustrated in the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of the present invention's the 20 exemplary embodiment in each grade;
Figure 151 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's the 21 exemplary embodiment;
Figure 152 is clutch and brake engages figure, shows in the related speed changer of the present invention's the 21 exemplary embodiment default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 153 is the nomogram that can enough straight lines be illustrated in the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of the present invention's 21 exemplary embodiments in each grade;
Figure 154 is clutch and brake engages figure, shows first of the present invention's the 21 exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 155 can be illustrated in first of the present invention's the 21 exemplary embodiment is revised the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade nomogram by enough straight lines;
Figure 156 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's the 22 exemplary embodiment;
Figure 157 is clutch and brake engages figure, shows in the related speed changer of the present invention's the 22 exemplary embodiment default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 158 is the nomogram that can enough straight lines be illustrated in the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of the present invention's the 22 exemplary embodiment in each grade;
Figure 159 is clutch and brake engages figure, shows first of the present invention's the 22 exemplary embodiment and revises default shelves in the related speed changer of example and be used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades;
Figure 160 can be illustrated in first of the present invention's the 22 exemplary embodiment is revised the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of example in each grade nomogram by enough straight lines;
Figure 161 is the perspective view of structure of the multi-speed transmission that is used for vehicle of the present invention's the 23 exemplary embodiment;
Figure 162 is clutch and brake engages figure, shows in the related speed changer of the present invention's the 23 exemplary embodiment default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades; And
Figure 163 is the nomogram that can enough straight lines be illustrated in the relativeness between the rotational velocity of the various rotating elements that differently connect in the related speed changer of the present invention's the 23 exemplary embodiment in each grade.
Embodiment
In the following description and drawings, will the present invention be described in more detail in conjunction with exemplary embodiment.
Fig. 1 is the perspective view as the structure of the related multi-speed transmission that is used for vehicle (being simply referred to as hereinafter, " speed changer ") 14 of first exemplary embodiment of an example of the automatic transmission that can be used as vehicle.As shown in fig. 1, the related speed changer 14 of this exemplary embodiment comprises: the fluid torque converter 20 with lock-up clutch 18, input shaft 22 as the input rotating element that is connected in fluid torque converter 20, comprise as first preposition planetary gear set 24 of its primary clustering and first speed changing portion 38 of the second preposition planetary gear set 26, comprise as first rearmounted planetary gear set 28 of its primary clustering and second speed changing portion 40 of the second rearmounted planetary gear set 30, be used for from first speed changing portion 38 output element 34 in the middle of the first middle output element 32 and second of second speed changing portion, 40 transmission power, and as the output shaft 36 of exporting rotating element.These assemblies all are disposed on the common shaft by the order of starting pusher side to begin from gearbox 16, and described gearbox 16 is the nonrotational elements that are installed on car body.
Speed changer 14 preferably is used as the automatic transmission that is used for FF (front-mounted engine and front-wheel drive) vehicle that for example vertically is installed in the automatic transmission that is used for FR (front-mounted engine and rear wheel drive) vehicle in the vehicle or laterally is installed in vehicle.Speed changer 14 is disposed between motor 10 (as prime mover) and the driving wheel (not shown).Speed changer 14 changes from the speed and/or the direction of the rotation of motor 10 outputs, afterwards the rotation that is changed is delivered to driving wheel.Fluid torque converter 20 is operably connected to the bent axle 12 of motor 10 and will be outputs to input shaft 22 from the power of motor 10 outputs.That is to say that the input shaft 22 that is connected in as the turbine shaft of the outlet side rotating element of fluid torque converter 20 is driven rotationally by motor 10.The turbine shaft of fluid torque converter 20 also is equivalent to import rotating element (as input shaft 22).In addition, output shaft 36 drives a pair of left and right sidesing driving wheel rotationally by (not shown) such as for example differential gear unit.Speed changer 14 is about its axis symmetry, therefore will omit its underpart part from the perspective view shown in Fig. 1, and omission its underpart part in the mentioned perspective view in the description hereinafter.
The first preposition planetary gear set 24 that constitutes the part of first speed changing portion 38 be comprise sun gear S1, small gear (planetary pinion) P1, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA1 of support small gear P1 and the gear ring R1 that is meshed with sun gear S1 by small gear P1.The same second preposition planetary gear set 26 that constitutes the part of first speed changing portion 38 be many groups small gear P2 of comprising sun gear S2, being engaged with each other, can rotation and can revolve round the sun the planetary gear set of double pinion type of the planet carrier CA2 of support small gear P2 and the gear ring R2 that is meshed with sun gear S2 by small gear P2.
In first speed changing portion 38, the sun gear S2 of the planet carrier CA1 of the first preposition planetary gear set 24 and the second preposition planetary gear set 26 is connected in the gearbox 16 as nonrotational element integratedly, thereby prevents that planet carrier CA1 and sun gear S2 from rotating with respect to gearbox 16.In addition, the planet carrier CA2 of the sun gear S1 of the first preposition planetary gear set 24 and the second preposition planetary gear set 26 is connected in the input shaft 22 as the input rotating element integratedly.In addition, output element 32 in the middle of the gear ring R2 of the second preposition planetary gear set 26 is connected in first integratedly, and the gear ring R1 of the first preposition planetary gear set 24 is connected in the second middle output element 34 integratedly.This structure causes first speed changing portion 38 by the slow down rotation that comes from the input shaft 22 and rotation of being slowed down is delivered to second speed changing portion 40 of output element 32 in the middle of first, and makes the rotations that come from input shaft 22 oppositely and with described backward rotation be delivered to second speed changing portion 40 by output element 34 in the middle of second.
The first rearmounted planetary gear set 28 that constitutes the part of second speed changing portion 40 be comprise sun gear S3, small gear P3, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA3 of support small gear P3 and the gear ring R3 that is meshed with sun gear S3 by small gear P3.The same second rearmounted planetary gear set 30 that constitutes the part of second speed changing portion 40 be many groups small gear P4 of comprising sun gear S4, being engaged with each other, can rotation and can revolve round the sun the planetary gear set of double pinion type of the planet carrier CA4 of support small gear P4 and the gear ring R4 that is meshed with sun gear S4 by small gear P4.
In second speed changing portion 40, the planet carrier CA4 of the sun gear S3 of the first rearmounted planetary gear set 28 and the second rearmounted planetary gear set 30 is joined together to form the first rotating element RE1.The gear ring R4 of the planet carrier CA3 of the first rearmounted planetary gear set 28 and the second rearmounted planetary gear set 30 is joined together to form the second rotating element RE2.The gear ring R3 of the first rearmounted planetary gear set 28 forms the 3rd rotating element RE3, and the sun gear S4 of the second rearmounted planetary gear set 30 forms the 4th rotating element RE4.Speed changer 14 also comprises first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, the first break B1 and the second break B2.First clutch C1 is the first clutch element that optionally the first middle output element 32 is connected with the 4th rotating element RE4.Second clutch C2 is the second clutch element that optionally input shaft 22 is connected with the second rotating element RE2.Three-clutch C3 is the three-clutch element that optionally the first middle output element 32 is connected with the first rotating element RE1.Four clutches C4 is the four clutches element that optionally input shaft 22 and the first rotating element RE1 is linked together.The 5th clutch C5 is the 5th clutch element that optionally output element 34 in the middle of second and the first rotating element RE1 is linked together.The first break B1 is first brake component that optionally the first rotating element RE1 is remained in as the gearbox 16 of nonrotational element, and the second break B2 is second brake component that optionally the second rotating element RE2 is remained in gearbox 16.
First clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, the first break B1 and the second break B2 for example are the hydraulic frictional bonding apparatuss that is used in the traditional automatic transmission that is used for vehicle usually.These clutches and break are to be used for optionally they being inserted in the device that resolution element wherein links together, and can be, for example, wherein a plurality of overlapping friction plates are pressed against together wet multi-disc device by hydraulic actuating unit, and wherein are wrapped in the band brake of an end of one or two band around the barrel tumbler outer surface by the hydraulic actuating unit tension.
Fig. 3 shows signal that is input to the electronic control unit (ECU) 42 that is used for controlling speed changer 14 and the signal of exporting from described ECU.ECU42 comprises so-called micro computer, and described micro computer comprises CPU, ROM, RAM and input/output interface etc.ECU42 is by using the interim storing function execution signal processing of RAM to carry out drive controlling simultaneously according to the program that is stored in advance among the ROM, such as the speed Control in the speed changer 14.
The various signals of exporting from various sensors and switch (not shown) are imported among the ECU42.The example of these signals comprises: the signal of expression engineer coolant temperature, the signal of expression MLP, the signal of expression engine speed NE is the signal of the rotational velocity of motor 10, the air conditioner signal of the operation of expression air conditioner, with the corresponding vehicle velocity signal of the rotational velocity of output shaft 36, the AT fluid temperature signal of the temperature of hydraulic fluid in the expression speed changer 14, the signal of expression emergency stopper operation, the signal of expression foot brake operation, the catalyst temperature signal of expression catalyst temperature, the accelerator opening signal Acc of the operation amount of expression accelerator pedal, the cam angle signal, the snowfield mode initialization signal of expression snowfield mode initialization, the vehicle acceleration signal of the forward/backward acceleration of expression vehicle, and the signal of representing the rotational velocity of the first motor MG1 (not shown).In addition, also from ECU42, export various signals.The example of these signals comprises: the drive signal that outputs to the throttle actuator of the aperture that is used to control the electronic throttle (not shown); Be used to regulate the boost pressure regulated signal of boost pressure; Be used to handle the electric air-conditioning device drive signal of electric air-conditioning device; The fire signal of the ignition timing of instruction motor 10; Instruct the command signal of operation of the first motor MG1 and the second motor MG2 (not shown); Be used to indicate the speed ratio index signal of speed ratio; Be used to indicate the snowfield mode indication signal of setting the snowfield pattern when; Be used to activate the ABS activation signal of ABS actuator, described ABS actuator is used to prevent that the wheel of vehicle from sliding during braking; AT solenoid command signal, described signal are used for activating the solenoid valve of the hydraulic actuator device that is used to control the hydraulic frictional bonding apparatus that is located at speed changer 14; Be used to activate the drive instruction signal of electric hydraulic pump (not shown); Be used to drive the signal of electric heater; And the signal that outputs to Ruiss Controll usefulness control computer.
Fig. 2 is clutch and brake engages figure, shows in the speed changer 14 default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades.In the speed changer 14 that constitutes as mentioned above, in response to instruction from ECU42, as shown in Figure 2, can be by for example engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10st " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
That is to say, as shown in Figure 2, first clutch C1 is engaged with the 4th rotating element RE4, the i.e. sun gear S4 of the second rearmounted planetary gear set 30, be connected with output element 32 in the middle of first, and the 5th clutch C5 is engaged with the first rotating element RE1, the sun gear S3 of the first rearmounted planetary gear set 28 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 30, be connected with output element 34 in the middle of second, thereby set up first grade, described first grade has slowest ratio γ 1, for example, is approximately 4.648.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the i.e. sun gear S4 of the second rearmounted planetary gear set 30, be connected with output element 32 in the middle of first, and the second break B2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 28 that promptly links together and the gear ring R4 of the second rearmounted planetary gear set 30, remain in gearbox 16, thereby set up second grade, described second grade of speed ratio γ 2 that has less than first grade speed ratio γ 1, for example, be approximately 4.100.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the i.e. sun gear S4 of the second rearmounted planetary gear set 30, be connected with output element 32 in the middle of first, and the first break B1 is engaged with the first rotating element RE1, the sun gear S3 of the first rearmounted planetary gear set 28 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 30, remain in gearbox 16, thereby the third gear of foundation, described third gear has the speed ratio γ 3 less than second grade speed ratio γ 2, for example, be approximately 2.578.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the i.e. sun gear S4 of the second rearmounted planetary gear set 30, be connected with output element 32 in the middle of first, and three-clutch C3 is engaged with the first rotating element RE1, the sun gear S3 of the first rearmounted planetary gear set 28 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 30, be connected with output element 32 in the middle of first, thereby set up fourth speed, described fourth speed has the speed ratio γ 4 less than the speed ratio γ 3 of third gear, for example, be approximately 1.786.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the i.e. sun gear S4 of the second rearmounted planetary gear set 30, be connected with output element 32 in the middle of first, and four clutches C4 is engaged with the first rotating element RE1, the sun gear S3 of the first rearmounted planetary gear set 28 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 30, be connected with input shaft 22, thereby set up the 5th grade, described the 5th grade of speed ratio γ 5 that has less than fourth speed speed ratio γ 4, for example, be approximately 1.438.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the i.e. sun gear S4 of the second rearmounted planetary gear set 30, be connected with output element 32 in the middle of first, and second clutch C2 is engaged with the second rotating element RE12, the gear ring R4 of the CA3 of the first rearmounted planetary gear set 28 that promptly links together and the second rearmounted planetary gear set 30, be connected with input shaft 22, thereby set up the 6th grade, described the 6th grade of speed ratio γ 6 that has less than the 5th grade of speed ratio γ 5, for example, be approximately 1.237.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 28 that promptly links together and the gear ring R4 of the second rearmounted planetary gear set 30, be connected with input shaft 22, and four clutches C4 is engaged with the first rotating element RE1, the sun gear S3 of the first rearmounted planetary gear set 28 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 30, be connected with input shaft 22, thereby set up the 7th grade, described the 7th grade of speed ratio γ 7 that has less than the 6th grade of speed ratio γ 6, for example, be approximately 1.000.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 28 that promptly links together and the gear ring R4 of the second rearmounted planetary gear set 30, be connected with input shaft 22, and three-clutch C3 is engaged with the first rotating element RE1, the sun gear S3 of the first rearmounted planetary gear set 28 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 30, be connected with output element 32 in the middle of first, thereby set up the 8th grade, described the 8th grade of speed ratio γ 8 that has less than the 7th grade of speed ratio γ 7, for example, be approximately 0.814.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 28 that promptly links together and the gear ring R4 of the second rearmounted planetary gear set 30, be connected with input shaft 22, and the first break B1 is engaged with the first rotating element RE1, the sun gear S3 of the first rearmounted planetary gear set 28 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 30, remain in gear-box 16, thereby set up the 9th grade, described the 9th grade of speed ratio γ 9 that has less than the 8th grade of speed ratio γ 8, for example, be approximately 0.658.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 28 that promptly links together and the gear ring R4 of the second rearmounted planetary gear set 30, be connected with input shaft 22, and the 5th clutch C5 is engaged with the first rotating element RE1, the sun gear S3 of the first rearmounted planetary gear set 28 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 30, be connected with output element 34 in the middle of second, thereby set up the tenth grade, the described ten grade has minimum speed ratio γ 10, for example, be approximately 0.552.
In addition, three-clutch C3 is engaged with the first rotating element RE1, the sun gear S3 of the first rearmounted planetary gear set 28 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 30, be connected with output element 32 in the middle of first, and the second break B2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 28 that promptly links together and the gear ring R4 of the second rearmounted planetary gear set 30, remain in gear-box 16, thereby set up first reverse gear " R1 ", described reverse gear " R1 " has and is approximately 3.434 speed ratio γ R1.
In addition, four clutches C4 is engaged with the first rotating element RE1, the sun gear S3 of the first rearmounted planetary gear set 28 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 30, be connected with input shaft 22, and the second break B2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 28 that promptly links together and the gear ring R4 of the second rearmounted planetary gear set 30, remain in gear-box 16, thereby set up second reverse gear " R2 ", described reverse gear " R2 " has the speed ratio γ R2 less than the speed ratio γ R1 of first reverse gear, for example, 1.923.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 28 of gear ratio ρ 1, the second preposition planetary gear set 26 of the first preposition planetary gear set 24 and the gear ratio ρ 4 of the second rearmounted planetary gear set 30 are designed to be and can realize aforementioned speed ratio.
Setting up in the speed changer 14 of gear according to clutch shown in Fig. 2 and brake engages figure, level (step), promptly the ratio (=γ 1/ γ 2) of the speed ratio γ 2 of first grade speed ratio γ 1 and second grade is 1.133, second grade speed ratio γ 2 is 1.591 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.443 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.241, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.163, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.237, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is 1.229, the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of the 8th grade speed ratio γ 8 and the 9th grade is 1.237, and the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.192.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 10) of the speed ratio γ 10 of first grade speed ratio γ 1 and the tenth grade is 8.420, this is bigger numerical value.
Fig. 4 is the nomogram that can enough straight lines be illustrated in the relativeness between the rotational velocity of the various rotating elements that differently connect in the speed changer 14 in each grade.Nomogram among Fig. 4 is two-dimentional coordinate system, and this two dimension coordinate system shows the relation of the gear ratio ρ of each planetary gear set 24,26,28 and 30 along transverse axis, and shows the speed of relatively rotating along the longitudinal axis.In five horizontal lines, nethermost horizontal line (that is, dotted line) X1 represents the rotational velocity of output element 34 in the middle of second, that is, and and the output of first speed changing portion 38.Horizontal line XZ directly over the bottom horizontal line X1 is expressed as zero rotational velocity.Horizontal line directly over the horizontal line XZ (that is, dotted line) X2 represents the rotational velocity of output element 32 in the middle of first, that is, and and the output of first speed changing portion 38.Horizontal line X3 directly over the horizontal line X2 is expressed as the rotational velocity of " 1.0 ", that is, and and as the rotational velocity of the input shaft 22 of importing rotating element.The horizontal line X4 of the top is expressed as the rotational velocity of " 2.0 ",, doubles the rotational velocity of input shaft 22 that is.Six vertical curve Y1 of first speed changing portion 38 shown in this nomographic left half represent sun gear S1, the planet carrier CA1 of the first preposition planetary gear set 24, gear ring R1, the sun gear S2 of the second preposition planetary gear set 26 of the first preposition planetary gear set 24, the gear ring R2 of the second preposition planetary gear set 26, the planet carrier CA2 of the second preposition planetary gear set 26 of the first preposition planetary gear set 24 respectively by order from left to right to Y6.The distance of setting between these vertical curves according to the gear ratio ρ 2 of the gear ratio ρ 1 of the first preposition planetary gear set 24 and the second preposition planetary gear set 26.Similarly, four vertical curve Y7 shown in this nomographic right half represent the assembly of second speed changing portion 40 to Y10.In the drawings from left to right, line Y7 represents to link together and is equivalent to the sun gear S3 of the first rearmounted planetary gear set 28 of the first rotating element RE1 and the planet carrier CA4 of the second rearmounted planetary gear set 30, line Y8 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 28 of the second rotating element RE2 and the gear ring R4 of the second rearmounted planetary gear set 30, and line Y9 represents to be equivalent to the gear ring R3 of first speed changing portion 38 of the 3rd rotating element RE3, and line Y10 represents to be equivalent to the sun gear S4 of the second rearmounted planetary gear set 30 of the 4th rotating element RE4.The distance of setting between these vertical curves according to the gear ratio ρ 4 of the gear ratio ρ 3 of the first rearmounted planetary gear set 28 and the second rearmounted planetary gear set 30.
When using nomographing, in first speed changing portion 38 of the related speed changer 14 of this exemplary embodiment, as the sun gear S1 of one of three rotating elements of the first preposition planetary gear set 24 be connected as the input shaft 22 of importing rotating element.Be held in the gearbox 16 of the nonrotational element of conduct as another planet carrier CA1 in three rotating elements, thereby can not rotate to it.Be provided with integratedly as output element 34 in the middle of the gear ring R1 and second of residue the 3rd rotating element of the first preposition planetary gear set 24, therefore play with the second middle output element similarly acting on, optionally be connected in the first rotating element RE1 (S3, CA4) by the 5th clutch C5 simultaneously.In addition, be held in gearbox 16 as the sun gear S2 of one of three rotating elements of the second preposition planetary gear set 26, thereby can not rotate with respect to it as nonrotational element.Be provided with integratedly as another the gear ring R2 and the first middle output element 32 in three rotating elements, therefore play with the first middle output element similarly acting on, optionally be connected in the first rotating element RE1 (S3, CA4) and optionally be connected in the 4th rotating element RE4 (S4) by three-clutch C3 simultaneously by first clutch C1.Be connected with input shaft 22 as the planet carrier CA2 of residue the 3rd rotating element of the second preposition planetary gear set 26 as the input rotating element.In addition, in second speed changing portion 40 of speed changer 14, the first rotating element RE1 (S3, CA4) by three-clutch C3 optionally be connected in output element 32 in the middle of first, by four clutches C4 optionally be connected in optionally be connected in second as the input shaft 22 of input rotating element and by the 5th clutch C5 in the middle of output element 34, and optionally remained in gearbox 16 as nonrotational element by the first break B1.In addition, the second rotating element RE2 (CA3, R4) optionally is connected in as the input shaft 22 of input rotating element and by the second break B2 by second clutch C2 and is optionally remained in the nonrotationally gearbox 16 of element of conduct.In addition, the 3rd rotating element RE3 (R3) is provided with integratedly with the output shaft 36 of conduct output rotating element, therefore plays the effect similar to exporting rotating element.In addition, output element 32 in the middle of the 4th rotating element RE4 (S4) optionally is connected in first by first clutch C1.
In the nomogram in Fig. 4, in first grade, the 5th clutch C5 is engaged the first rotating element RE1 being connected in output element 34 in the middle of second, and this causes rotating under the identical speed of first rotating element RE1 output element 34 in the middle of with second.Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (1st) expression, and (1st) locates at point, and the straight line and the vertical curve Y9 of the point of intersection of connection vertical curve Y7 and horizontal line X1 and the point of intersection of vertical curve Y10 and horizontal line X2 intersect.
In second grade, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (2nd) expression, and (2nd) locates at point, and the straight line and the vertical curve Y9 of the point of intersection of connection vertical curve Y8 and horizontal line XZ and the point of intersection of vertical curve Y10 and horizontal line X2 intersect.
In third gear, the first break B1 is engaged so that the first rotating element RE1 is remained in gearbox 16, and this causes the rotational velocity of the first rotating element RE1 to be " 0 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (3rd) expression, and (3rd) locates at point, and the straight line and the vertical curve Y9 of the point of intersection of connection vertical curve Y7 and horizontal line XZ and the point of intersection of vertical curve Y10 and horizontal line X2 intersect.
In fourth speed, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (4th) expression, and (4th) locates at point, and horizontal line X2 and vertical curve Y9 intersect.
In the 5th grade, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (5th) expression, and (5th) locates at point, and the straight line and the vertical curve Y9 of the point of intersection of connection vertical curve Y7 and horizontal line X3 and the point of intersection of vertical curve Y10 and horizontal line X2 intersect.
In the 6th grade, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (6th) expression, and (6th) locates at point, and the straight line and the vertical curve Y9 of the point of intersection of connection vertical curve Y8 and horizontal line X3 and the point of intersection of vertical curve Y10 and horizontal line X2 intersect.
In the 7th grade, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (7th) expression, and (7th) locates at point, and horizontal line X3 and vertical curve Y9 intersect.
In the 8th grade, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (8th) expression, and (8th) locates at point, and the straight line and the vertical curve Y9 of the point of intersection of connection vertical curve Y7 and horizontal line X2 and the point of intersection of vertical curve Y8 and horizontal line X3 intersect.
In the 9th grade, the first break B1 is engaged so that the first rotating element RE1 is remained in gearbox 16, and this causes the rotational velocity of the first rotating element RE1 to be " 0 ".Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (9th) expression, and (9th) locates at point, and the straight line and the vertical curve Y9 of the point of intersection of connection vertical curve Y7 and horizontal line XZ and the point of intersection of vertical curve Y8 and horizontal line X3 intersect.
In the tenth grade, the 5th clutch C5 is engaged the first rotating element RE1 being connected in output element 34 in the middle of second, and this causes rotating under the identical speed of first rotating element RE1 output element 34 in the middle of with second.Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (10th) expression, and (10th) locates at point, and the straight line and the vertical curve Y9 of the point of intersection of connection vertical curve Y7 and horizontal line X1 and the point of intersection of vertical curve Y8 and horizontal line X3 intersect.
In first reverse gear, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (Rev1) expression, and (Rev1) locates at point, and the straight line and the vertical curve Y9 of the point of intersection of connection vertical curve Y7 and horizontal line X2 and the point of intersection of vertical curve Y8 and horizontal line XZ intersect.
In second reverse gear, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (Rev2) expression, and (Rev2) locates at point, and the straight line and the vertical curve Y9 of the point of intersection of connection vertical curve Y7 and horizontal line X3 and the point of intersection of vertical curve Y8 and horizontal line XZ intersect.
By this way, according to this exemplary embodiment, the present invention can provide speed changer 14, and this speed changer 14 can realize that a plurality of gears keep good balance simultaneously among the speed ratio level between the shelves.Because speed changer 14 has the above various assembly, therefore can accomplish this point.More particularly, these assemblies comprise first speed changing portion 38 and second speed changing portion 40, wherein first speed changing portion 38 comprise be used to slow down and transmit come from as the rotation of the input shaft 22 of input rotating element first in the middle of output element 32 and make come from input shaft 22 rotation oppositely and transmit this rotation second in the middle of output element 34 both, second speed changing portion 40 comprises four rotating elements that link together and constitute by some sun gears, planet carrier and gear ring with two planetary gear set.When in the nomogram of the rotational velocity of can enough straight lines representing four rotating elements, these four rotating elements being expressed as the first rotating element RE1, the second rotating element RE2, the 3rd rotating element RE3 and the 4th rotating element RE4 by the order that passes through, the assembly of speed changer 14 also comprises: first clutch C1, the first clutch element of described first clutch C1 for optionally output element 32 in the middle of first and the 4th rotating element RE4 being linked together; Second clutch C2, the second clutch element of described second clutch C2 for optionally input shaft 22 and the second rotating element RE2 being linked together; Three-clutch C3, the three-clutch element of described three-clutch C3 for optionally output element 32 in the middle of first and the first rotating element RE1 being linked together; Four clutches C4, the four clutches element of described four clutches C4 for optionally input shaft 22 and the first rotating element RE1 being linked together; The 5th clutch C5, five clutch element of described the 5th clutch C5 for optionally output element 34 in the middle of second and the first rotating element RE1 being linked together; The first break B1, the described first break B1 is for optionally remaining in the first rotating element RE1 first brake component as the gearbox 16 of nonrotational element; And the second break B2, the described second break B2 is for optionally remaining in the second rotating element RE2 second brake component of gearbox 16.
And, set up first grade by engaging first clutch C1 and the 5th clutch C5.Set up second grade by engaging the first clutch C1 and the second break B2.Set up third gear by engaging the first clutch C1 and the first break B1.Set up fourth speed by engaging first clutch C1 and three-clutch C3.Set up the 5th grade by engaging first clutch C1 and four clutches C4.Set up the 6th grade by engaging first clutch C1 and second clutch C2.Set up the 7th grade by engaging second clutch C2 and four clutches C4.Set up the 8th grade by engaging second clutch C2 and three-clutch C3, and set up the 9th grade by engaging the second clutch C2 and the first break B1.Therefore, speed changer 14 can be realized nine forward gearss.
Speed changer 14 can also be realized the tenth grade by engaging second clutch C2 and the 5th clutch C5.Therefore, except that can realizing ten forward gearss, preferably can set the level between the 9th grade and the tenth grade less with intensive speed ratio (speed ratio that is more or less the same, close ratio).
And first speed changing portion 38 comprises first preposition planetary gear set 24 of single small gear type and the second preposition planetary gear set 26 of double pinion type.The sun gear S2 of the planet carrier CA1 of the first preposition planetary gear set 24 and the second preposition planetary gear set 26 always is connected in the gearbox 16 as nonrotational element, and the planet carrier CA2 of the sun gear S1 of the first preposition planetary gear set 24 and the second preposition planetary gear set 26 is connected in the input shaft 22 as the input rotating element.Therefore, the gear ring R2 of the second preposition planetary gear set 26 is as the first middle output element 32, and the gear ring R1 that makes the preposition planetary gear set 24 of winning simultaneously is as the second middle output element 34.Therefore, can provide practical speed changer 14.
In addition, second speed changing portion 40 comprises first rearmounted planetary gear set 28 of single small gear type and the second rearmounted planetary gear set 30 of double pinion type.The first rotating element RE1 is that the planet carrier CA4 by the sun gear S3 of the first rearmounted planetary gear set 28 that links together and the second rearmounted planetary gear set 30 constitutes.The second rotating element RE2 is that the gear ring R4 by the planet carrier CA3 of the first rearmounted planetary gear set 28 that links together and the second rearmounted planetary gear set 30 constitutes.The 3rd rotating element RE3 is that the gear ring R3 of the first rearmounted planetary gear set 28 constitutes.The 4th rotating element RE4 is that the sun gear S4 by the second rearmounted planetary gear set 30 constitutes.Therefore, can provide practical speed changer 14.
In addition, speed changer 14 by this exemplary embodiment, also exist well balanced in the quantity of clutch and the quantitative aspects of break, and the position of those clutches and break is by on the relative axial direction that is dispersed in speed changer 14, and this helps the oil circuit of described clutch and break to arrange.
In addition, speed changer 14 also can be used for realizing nine forward gearss second grade in clutch shown in above-mentioned Fig. 2 and brake engages figure.That is to say, in speed changer 14, set up first grade by engaging first clutch C1 and the 5th clutch C5.Set up second grade by engaging the first clutch C1 and the first break B1.Set up third gear by engaging first clutch C1 and three-clutch C3.Set up fourth speed by engaging first clutch C1 and four clutches C4.Set up the 5th grade by engaging first clutch C1 and second clutch C2.Set up the 6th grade by engaging second clutch C2 and four clutches C4.Set up the 7th grade by engaging second clutch C2 and three-clutch C3.Set up the 8th grade by engaging the second clutch C2 and the first break B1, and realize the 9th grade by engaging second clutch C2 and the 5th clutch C5.And speed changer 14 also can be used for realizing nine forward gearss first grade in clutch shown in above-mentioned Fig. 2 and brake engages figure.
Next, describe second exemplary embodiment of the present invention with reference to the accompanying drawings in detail.In the following description, the part in second exemplary embodiment identical with part in above-mentioned first exemplary embodiment will represent with identical reference character, and will omit the description to it.
Fig. 5 is the perspective view of the structure of the related speed changer 44 of the present invention's second exemplary embodiment.Fig. 6 is clutch and brake engages figure, shows in the speed changer 44 default shelves and is used to realize relation between the operation of hydraulic frictional bonding apparatus of those grades; Fig. 7 shows the nomogram of the rotational velocity of the rotating element in each grade.Except that the structure of second speed changing portion 50, the speed changer 44 of this exemplary embodiment is similar to the speed changer 14 shown in Fig. 1 in configuration aspects, the effect of the equivalence that therefore can obtain by this exemplary embodiment and be obtained from previous embodiment.Hereinafter, will the part of the speed changer 44 of this exemplary embodiment different with the part of speed changer 14 be described.
As shown in Figure 5, the first rearmounted planetary gear set 46 that constitutes the part of second speed changing portion 50 is to comprise sun gear S3, small gear P3, rotatable and can support the planet carrier CA3 of small gear P3 and the planetary gear set of single small gear type of the gear ring R3 that is meshed with sun gear S3 by small gear P3 with revolving round the sun.The same second rearmounted planetary gear set 48 that constitutes the part of second speed changing portion 50 is many groups small gear P4 of comprising sun gear S4, being engaged with each other, rotatable and can support the planet carrier CA4 of small gear P4 and the planetary gear set of the double pinion type of the gear ring R4 that is meshed with sun gear S4 by small gear P4 with revolving round the sun.The first rearmounted planetary gear set 46 and the second rearmounted planetary gear set 48 constitute the epicyclic train of La Weilie AUX (Ravigneaux) type, wherein planet carrier CA3 and planet carrier CA4 are common elements, gear ring R3 and gear ring R4 are common elements, and the small gear of the first rearmounted planetary gear set 46 also is used as second small gear of the second rearmounted planetary gear set 48.
In second speed changing portion 50 of speed changer 44, the first rotating element RE1 is that the sun gear S3 by the first rearmounted planetary gear set 46 constitutes.The second rotating element RE2 is that the planet carrier CA4 by the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the second rearmounted planetary gear set 48 constitutes.The 3rd rotating element RE3 is that the gear ring R4 by the gear ring R3 of the first rearmounted planetary gear set 46 that links together and the second rearmounted planetary gear set 48 constitutes, and the 4th rotating element RE4 is that sun gear S4 by the second rearmounted planetary gear set 48 constitutes.
In the speed changer 44 that constitutes as mentioned above, in response to the instruction that comes from ECU42, for example, as shown in Figure 6, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
In the nomogram of Fig. 7, four vertical curve Y7 represent the assembly of second speed changing portion 50 to Y10.In the drawings from left to right, line Y7 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 46 of the first rotating element RE1, line Y8 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 46 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 48, and line Y9 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 46 of the 3rd rotating element RE3 and the gear ring R4 of the second rearmounted planetary gear set 48, and line Y10 represents to be equivalent to the sun gear S4 of the second rearmounted planetary gear set 48 of the 4th rotating element RE4.Therefore, according to these rotating elements, the nomogram shown in Fig. 7 is similar to the nomogram shown in above-mentioned Fig. 4, therefore will omit the description to it.
By this way, according to this exemplary embodiment, second speed changing portion 50 comprises first rearmounted planetary gear set 46 of single small gear type and the second rearmounted planetary gear set 48 of double pinion type.The first rotating element RE1 is that the sun gear S3 by the first rearmounted planetary gear set 46 constitutes.The second rotating element RE2 is that the planet carrier CA4 by the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the second rearmounted planetary gear set 48 constitutes.The 3rd rotating element RE3 is that the gear ring R4 by the gear ring R3 of the first rearmounted planetary gear set 46 that links together and the second rearmounted planetary gear set 48 constitutes, and the 4th rotating element RE4 is that sun gear S4 by the second rearmounted planetary gear set 48 constitutes.Therefore, can provide practical speed changer 44.
Here, revise example as second embodiment's first, as shown in Figure 8, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, speed changer 44 can obtain nine forward gearss and two reverse gears, and suitably sets the gear ratio of each planetary gear set.Fig. 9 is and the corresponding nomogram of Fig. 8 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the first correction example of Fig. 8 different with aforementioned exemplary embodiment and second exemplary embodiment shown in Fig. 9 be described.
As shown in clutch among Fig. 8 and brake engages figure, by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
As shown in Figure 8, first clutch C1 is engaged with the 4th rotating element RE4, the i.e. sun gear S4 of the second rearmounted planetary gear set 48, be connected with output element 32 in the middle of first, and the second break B2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 46 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gearbox 16, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, be approximately 4.776.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, promptly the sun gear S4 of the second rearmounted planetary gear set 48 is connected with output element 32 in the middle of first, and the first break B1 is engaged with the first rotating element RE1, and promptly the sun gear S3 of the first rearmounted planetary gear set 46 remains in gearbox 16, thereby set up second grade, described second grade of speed ratio γ 2 that has less than first grade of speed ratio γ 1 for example, is approximately 2.925.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the i.e. sun gear S4 of the second rearmounted planetary gear set 48 is connected with output element 32 in the middle of first, and three-clutch C3 is engaged with the first rotating element RE1, the i.e. sun gear S3 of the first rearmounted planetary gear set 46, be connected with output element 32 in the middle of first, thus the third gear of foundation, and described third gear has the speed ratio γ 3 less than second grade of speed ratio γ 2, for example, be approximately 2.000.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and four clutches C4 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with input shaft 22, thereby set up fourth speed, described fourth speed has the speed ratio γ 4 less than third gear speed ratio γ 3, for example, be approximately 1.519.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 46 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, be connected with input shaft 22, thereby set up the 5th grade, described the 5th grade of speed ratio γ 5 that has less than fourth speed speed ratio γ 4, for example, be approximately 1.265.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 46 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, be connected with input shaft 22, and four clutches C4 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with input shaft 22, thereby set up the 6th grade, described the 6th grade of speed ratio γ 6 that has less than the 5th grade of speed ratio γ 5, for example, be approximately 1.000.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 46 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, be connected with input shaft 22, and three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the first centre output element 32, thereby set up the 7th grade, described the 7th grade of speed ratio γ 7 that has less than the 6th grade of speed ratio γ 6, for example, be approximately 0.800.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 46 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, be connected with input shaft 22, and the first break B1 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 remain in gear-box 16, thereby set up the 8th grade, described the 8th grade of speed ratio γ 8 that has less than the 7th grade of speed ratio γ 7, for example, be approximately 0.667.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 46 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, be connected with input shaft 22, and the 5th clutch C5 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the second centre output element 34, thereby set up the 9th grade, described the 9th grade has minimum speed ratio γ 9, for example, be approximately 0.588.
In addition, three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 46 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gear-box 16, thereby set up first reverse gear " R1 ", described reverse gear " R1 " has and is approximately 4.000 speed ratio γ R1.
In addition, four clutches C4 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with input shaft 22, and the second break B2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 46 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gear-box 16, thereby set up second reverse gear " R2 ", described reverse gear " R2 " has the speed ratio γ R2 less than the speed ratio γ R1 of first reverse gear, for example, 2.000.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 46 of gear ratio ρ 1, the second preposition planetary gear set 26 of the first preposition planetary gear set 24 and the gear ratio ρ 4 of the second rearmounted planetary gear set 48 are designed to be and can realize aforementioned speed ratio.
Setting up in the speed changer 44 of gear according to clutch shown in Fig. 8 and brake engages figure, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.633, second grade speed ratio γ 2 is 1.463 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.316 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.201, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.265, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.250, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is 1.200, and the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of the 8th grade speed ratio γ 8 and the 9th grade is 1.133.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 9) of the speed ratio γ 9 of first grade speed ratio γ 1 and the 9th grade is 8.119, this is bigger numerical value.
In the nomogram of Fig. 9, four vertical curve Y1 represent the assembly of first speed changing portion 38 to Y4.In the drawings from left to right, line Y1 represents that gear ring R1, the line Y2 of the first preposition planetary gear set 24 represent that sun gear S2, the line Y3 of the planet carrier CA1 of the first preposition planetary gear set 24 that links together and the second preposition planetary gear set 26 represent that the gear ring R2 of the second preposition planetary gear set 26 and line Y4 represent the sun gear S1 of the first preposition planetary gear set 24 that links together and the planet carrier CA2 of the second preposition planetary gear set 26.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 50 to Y8.In the drawings from left to right, line Y5 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 48 of the first rotating element RE1, line Y6 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 46 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 48, line Y7 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 46 of the 3rd rotating element RE3 and the gear ring R4 of the second rearmounted planetary gear set 48, and line Y8 represents to be equivalent to the sun gear S4 of the second rearmounted planetary gear set 48 of the 4th rotating element RE4.
In the nomogram of Fig. 9, in first grade, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (1st) expression, and (1st) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y6 and horizontal line XZ and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In second grade, the first break B1 is engaged so that the first rotating element RE1 is remained in gearbox 16, and this causes the rotational velocity of the first rotating element RE1 to be " 0 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (2nd) expression, and (2nd) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line XZ and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In third gear, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (3rd) expression, and (3rd) locates at point, and horizontal line X2 and vertical curve Y7 intersect.
In fourth speed, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (4th) expression, and (4th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X3 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In the 5th grade, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (5th) expression, and (5th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y6 and horizontal line X3 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In the 6th grade, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (6th) expression, and (6th) locates at point, and horizontal line X3 and vertical curve Y7 intersect.
In the 7th grade, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (7th) expression, and (7th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X2 and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In the 8th grade, the first break B1 is engaged so that the first rotating element RE1 is remained in gearbox 16, and this causes the rotational velocity of the first rotating element RE1 to be " 0 ".Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (8th) expression, and (8th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line XZ and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In the 9th grade, the 5th clutch C5 is engaged the first rotating element RE1 being connected in output element 34 in the middle of second, and this causes rotating under the identical speed of first rotating element RE1 output element 34 in the middle of with second.Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (9th) expression, and (9th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X1 and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In first reverse gear, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (Rev1) expression, and (Rev1) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X2 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
In second reverse gear, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (Rev2) expression, and (Rev2) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X3 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
By this way, revise example, set up first grade by engaging the first clutch C1 and the second break B2 according to first of second exemplary embodiment.Set up second grade by engaging the first clutch C1 and the first break B1.Set up third gear by engaging first clutch C1 and three-clutch C3.Set up fourth speed by engaging first clutch C1 and four clutches C4.Set up the 5th grade by engaging first clutch C1 and second clutch C2.Set up the 6th grade by engaging second clutch C2 and four clutches C4.Set up the 7th grade by engaging second clutch C2 and three-clutch C3, and set up the 8th grade by engaging the second clutch C2 and the first break B1.Therefore, first of second exemplary embodiment speed changer 44 of revising example can be realized eight forward gearss.
First of second exemplary embodiment is revised the speed changer 44 of example can also realize the 9th grade by engaging second clutch C2 and the 5th clutch C5.Therefore, except that can realizing nine forward gearss, preferably can be by setting the level between the 8th grade and the 9th grade less with intensive speed ratio.
Here, revise example as second of second exemplary embodiment, speed changer 44 also can be as shown in Figure 10, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, obtain nine forward gearss and two reverse gears, and suitably set the gear ratio of each planetary gear set.Figure 11 is and the corresponding nomogram of Figure 10 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the second correction example of Figure 10 different with aforementioned exemplary embodiment and second exemplary embodiment shown in Figure 11 be described.
As shown in clutch among Figure 10 and brake engages figure, by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
As shown in Figure 10, the 5th clutch C5 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the second centre output element 34, and the second break B2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 46 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gearbox 16, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, be approximately 4.971.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 46 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 48 remain in gearbox 16, thereby set up second grade, described second grade of speed ratio γ 2 that has less than first grade of speed ratio γ 1, for example, be approximately 3.290.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and the first break B1 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 remain in gearbox 16, thereby the third gear of foundation, described third gear has the speed ratio γ 3 less than second grade of speed ratio γ 2, for example, be approximately 2.222.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the first centre output element 32, thereby set up fourth speed, described fourth speed has the speed ratio γ 4 less than third gear speed ratio γ 3, for example, be approximately 1.645.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and four clutches C4 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with input shaft 22, thereby set up the 5th grade, described the 5th grade of speed ratio γ 5 that has less than fourth speed speed ratio γ 4, for example, be approximately 1.409.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 46 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, be connected with input shaft 22, thereby set up the 6th grade, described the 6th grade of speed ratio γ 6 that has less than the 5th grade of speed ratio γ 5, for example, be approximately 1.244.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 46 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, be connected with input shaft 22, and four clutches C4 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with input shaft 22, thereby set up the 7th grade, described the 7th grade of speed ratio γ 7 that has less than the 6th grade of speed ratio γ 6, for example, be approximately 1.000.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 46 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, be connected with input shaft 22, and three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the first centre output element 32, thereby set up the 8th grade, described the 8th grade of speed ratio γ 8 that has less than the 7th grade of speed ratio γ 7, for example, be approximately 0.825.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 46 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, be connected with input shaft 22, and the first break B1 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 remain in gearbox 16, thereby set up the 9th grade, described the 9th grade has minimum speed ratio γ 9, for example, be approximately 0.649.
In addition, three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 46 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gear-box 16, thereby set up first reverse gear " R1 ", described reverse gear " R1 " has and is approximately 3.047 speed ratio γ R1.
In addition, four clutches C4 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with input shaft 22, and the second break B2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 46 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gear-box 16, thereby set up second reverse gear " R2 ", described reverse gear " R2 " has the speed ratio γ R2 less than the speed ratio γ R1 of first reverse gear, for example, 1.852.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 46 of gear ratio ρ 1, the second preposition planetary gear set 26 of the first preposition planetary gear set 24 and the gear ratio ρ 4 of the second rearmounted planetary gear set 48 are designed to be and can realize aforementioned speed ratio.
Setting up in the speed changer 44 of gear according to clutch shown in Figure 10 and brake engages figure, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.511, second grade speed ratio γ 2 is 1.481 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.351 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.167, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.133, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.244, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is 1.212, and the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of the 8th grade speed ratio γ 8 and the 9th grade is 1.271.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 9) of the speed ratio γ 9 of first grade speed ratio γ 1 and the 9th grade is 7.655, this is bigger numerical value.
In the nomogram of Figure 11, four vertical curve Y1 represent the assembly of first speed changing portion 38 to Y4.In the drawings from left to right, line Y1 represents that gear ring R1, the line Y2 of the first preposition planetary gear set 24 represent that sun gear S2, the line Y3 of the planet carrier CA1 of the first preposition planetary gear set 24 that links together and the second preposition planetary gear set 26 represent that the gear ring R2 of the second preposition planetary gear set 26 and line Y4 represent the sun gear S1 of the first preposition planetary gear set 24 that links together and the planet carrier CA2 of the second preposition planetary gear set 26.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 50 to Y8.In the drawings from left to right, line Y5 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 46 of the first rotating element RE1, line Y6 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 46 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 48, line Y7 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 46 of the 3rd rotating element RE3 and the gear ring R4 of the second rearmounted planetary gear set 48, and line Y8 represents to be equivalent to the sun gear S4 of the second rearmounted planetary gear set 48 of the 4th rotating element RE4.
In the nomogram of Figure 11, in first grade, the 5th clutch C5 is engaged so that the first rotating element RE1 is connected with output element 34 in the middle of second, and this causes the first rotating element RE1 to rotate under the speed identical with output element 34 in the middle of second.Simultaneously, the second break B2 is engaged the second rotating element RE2 is remained in the gearbox 16 as nonrotational element, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (1st) expression, and (1st) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X1 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
In second grade, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (2nd) expression, and (2nd) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y6 and horizontal line XZ and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In third gear, the first break B1 is engaged so that the first rotating element RE1 is remained in gearbox 16, and this causes the rotational velocity of the first rotating element RE1 to be " 0 ".Simultaneously, first clutch C1 is engaged the 4th rotating element RE4 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of the 4th rotating element RE4 output element 32 in the middle of with first.Therefore, the rotational velocity of output shaft 36 is by point (3rd) expression, and (3rd) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line XZ and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In fourth speed, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (4th) expression, and (4th) locates at point, and horizontal line X2 and vertical curve Y7 intersect.
In the 5th grade, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (5th) expression, and (5th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X3 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In the 6th grade, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Simultaneously, first clutch C1 is engaged the 4th rotating element RE4 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of the 4th rotating element RE4 output element 32 in the middle of with first.Therefore, the rotational velocity of output shaft 36 is by point (6th) expression, and (6th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y6 and horizontal line X3 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In the 7th grade, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (7th) expression, and (7th) locates at point, and horizontal line X3 and vertical curve Y7 intersect.
In the 8th grade, three-clutch is engaged so that the first rotating element RE1 is connected in first output element 32, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (8th) expression, and (8th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X2 and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In the 9th grade, the first break B1 is engaged so that the first rotating element RE1 is remained in gearbox 16, and this causes the rotational velocity of the first rotating element RE1 to be " 0 ".Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (9th) expression, and (9th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line XZ and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In first reverse gear, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (Rev1) expression, and (Rev1) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X2 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
In second reverse gear, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (Rev2) expression, and (Rev2) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X3 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
By this way, revise example, by engaging the 5th clutch C5 and the second break B2 sets up first grade according to second of second exemplary embodiment.Set up second grade by engaging the first clutch C1 and the second break B2.Set up third gear by engaging the first clutch C1 and the first break B1.Set up fourth speed by engaging first clutch C1 and three-clutch C3.Set up the 5th grade by engaging first clutch C1 and four clutches C4.Set up the 6th grade by engaging first clutch C1 and second clutch C2.Set up the 7th grade by engaging second clutch C2 and four clutches C4, and set up the 8th grade by engaging second clutch C2 and three-clutch C3.Therefore, second of this second exemplary embodiment speed changer 44 of revising example can be realized eight forward gearss.
This second speed changer 44 of revising example of second exemplary embodiment can also be realized the 9th grade by engaging the second clutch C2 and the first break B1.Therefore, except that can realizing nine forward gearss, preferably can set the level between the 8th grade and the 9th grade less with intensive speed ratio.
Figure 12 is the perspective view of structure of the speed changer 66 of the present invention's the 3rd exemplary embodiment.Figure 13 shows in the speed changer 66 default shelves and is used to realize the figure of the relation between the operation of friction engagement device of those grades.Figure 14 shows the nomogram of the rotational velocity of the rotating element in each grade.Except that the structure of first speed changing portion 72 and second speed changing portion 64, the speed changer 66 of this exemplary embodiment is similar to the speed changer 14 shown in Fig. 1 in configuration aspects, the effect of the equivalence that therefore can obtain by this exemplary embodiment and be obtained from previous embodiment.Hereinafter, will the part of the speed changer 66 of this exemplary embodiment different with the part of speed changer 14 be described.
As shown in Figure 12, the first preposition planetary gear set 68 that constitutes the part of first speed changing portion 72 be comprise sun gear S1, intermeshing many group small gear P1, can rotation and can revolve round the sun the planetary gear set of double pinion type of the planet carrier CA1 of support small gear P1 and the gear ring R1 that is meshed with sun gear S1 by small gear P1.The same second preposition planetary gear set 70 that constitutes the part of first speed changing portion 72 be comprise sun gear S2, small gear P2, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA2 of support small gear P2 and the gear ring R2 that is meshed with sun gear S2 by small gear P2.
In first speed changing portion 72, the planet carrier CA1 of the first preposition planetary gear set 68 is connected in the gearbox 16 as nonrotational element integratedly, thereby prevents that planet carrier CA1 from rotating with respect to gearbox 16.In addition, the gear ring R2 of the sun gear S1 of the first preposition planetary gear set 68 and the second preposition planetary gear set 70 is connected in the input shaft 22 as the input rotating element integratedly.And the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 68 and the second preposition planetary gear set 70 links together and is connected in the first middle output element 32 integratedly.In addition, output element 34 in the middle of the sun gear S2 of the second preposition planetary gear set 70 is connected in second integratedly.This structure causes first speed changing portion 72 by the slow down rotation that comes from the input shaft 22 and rotation of being slowed down is delivered to second speed changing portion 64 of output element 32 in the middle of first, and makes the rotations that come from input shaft 22 oppositely and with described backward rotation be delivered to second speed changing portion 64 by output element 34 in the middle of second.
The first rearmounted planetary gear set 58 that constitutes the part of second speed changing portion 64 be many groups small gear P3 of comprising sun gear S3, being engaged with each other, can rotation and can revolve round the sun the planetary gear set of double pinion type of the planet carrier CA3 of support small gear P3 and the gear ring R3 that is meshed with sun gear S3 by small gear P3.The same second rearmounted planetary gear set 60 that constitutes the part of second speed changing portion 64 be comprise sun gear S4, small gear P4, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA4 of support small gear P4 and the gear ring R4 that is meshed with sun gear S4 by small gear P4.
In second speed changing portion 64, the sun gear S4 of the planet carrier CA3 of the first rearmounted planetary gear set 58 and the second rearmounted planetary gear set 60 links together to constitute the first rotating element RE1.The planet carrier CA4 of the gear ring R3 of the first rearmounted planetary gear set 58 and the second rearmounted planetary gear set 60 links together to constitute the second rotating element RE2.The gear ring R4 of the second rearmounted planetary gear set 60 constitutes the 3rd rotating element RE3, and the sun gear S3 of the first rearmounted planetary gear set 58 constitutes the 4th rotating element RE4.Speed changer 66 also comprises first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, the first break B1 and the second break B2.First clutch C1 is the first clutch element that optionally the first middle output element 32 is connected with the 4th rotating element RE4.Second clutch C2 is the second clutch element that optionally input shaft 22 is connected with the second rotating element RE2.Three-clutch C3 is the three-clutch element that optionally the first middle output element 32 is connected with the first rotating element RE1.Four clutches C4 is the four clutches element that optionally input shaft 22 and the first rotating element RE1 is linked together.The 5th clutch C5 is the 5th clutch element that optionally output element 34 in the middle of second and the first rotating element RE1 is linked together.The first break B1 is first brake component that optionally the first rotating element RE1 is remained in as the gearbox 16 of nonrotational element, and the second break B2 is second brake component that optionally the second rotating element RE2 is remained in gearbox 16.
In the speed changer 66 that constitutes as mentioned above, can be by in response to the instruction that comes from ECU42, for example, as shown in Figure 13, engage simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
That is to say, as shown in Figure 13, the 5th clutch C5 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 34 in the middle of second, and the second break B2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16 as nonrotational element, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, is approximately 4.762.
In clutch shown in Figure 13 and brake engages figure, it is described identical with use Fig. 2 to the operation of the friction engagement device of the tenth grade " 10th " to be used to set up second grade " 2nd ", therefore will omit giving unnecessary details it.In addition, setting up in the speed changer 66 of gear according to clutch shown in Figure 13 and brake engages figure, second grade speed ratio γ 2 is approximately 4.110, the speed ratio γ 3 of third gear is approximately 2.603, the speed ratio γ 4 of fourth speed is approximately 2.000, the 5th grade speed ratio γ 5 is approximately 1.624, the 6th grade speed ratio γ 6 is approximately 1.322, the 7th grade speed ratio γ 7 is approximately 1.000, the 8th grade speed ratio γ 8 is approximately 0.833, the 9th grade speed ratio γ 9 is approximately 0.714, the tenth grade speed ratio γ 10 is approximately 0.621, the speed ratio γ R2 that the speed ratio γ R1 of first reverse gear is approximately 5.000 and second reverse gear is approximately 2.500.In addition, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.159, second grade speed ratio γ 2 is 1.579 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.301 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.232, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.229, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.322, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is that the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of 1.200, the eight grades speed ratio γ 8 and the 9th grade is 1.167, and the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.150.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 10) of the speed ratio γ 10 of first grade speed ratio γ 1 and the tenth grade is 7.667, this is bigger numerical value.
In the nomogram shown in Figure 14, four vertical curve Y1 represent the assembly of first speed changing portion 72 to Y4.In the drawings from left to right, line Y1 represents that gear ring R2, the line Y2 of the sun gear S1 of the first preposition planetary gear set 68 that links together and the second preposition planetary gear set 70 represent that the gear ring R1 of the first preposition planetary gear set 68 that links together and planet carrier CA2, the line Y3 of the second preposition planetary gear set 70 represent the planet carrier CA1 of the first preposition planetary gear set 68 and the sun gear S2 that line Y4 represents the second preposition planetary gear set 70.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 64 to Y8.In the drawings from left to right, line Y5 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 58 of the first rotating element RE1 and the sun gear S4 of the second rearmounted planetary gear set 60, line Y6 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 58 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 60, line Y7 represents to be equivalent to the gear ring R4 of the second rearmounted planetary gear set 60 of the 3rd rotating element RE3, and line Y8 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 58 of the 4th rotating element RE4.Therefore, based on these rotating elements, the nomogram shown in Figure 14 is similar to for example nomogram shown in above-mentioned Fig. 4, therefore omits the description to it.
When using nomographing, in first speed changing portion 72 of the related speed changer 66 of the 3rd exemplary embodiment, link together and be connected with input shaft 22 as the input rotating element as the gear ring R2 of the sun gear S1 of the first preposition planetary gear set 68 one of in four rotating elements and the second preposition planetary gear set 70.Link together and is provided with integratedly, therefore play and the similar effect of the first centre output element as output element 32 in the middle of the planet carrier CA2 and first of the gear ring R1 of another the first preposition planetary gear set 68 in four rotating elements and the second preposition planetary gear set 70.Planet carrier CA1 as another the first preposition planetary gear set 68 in four rotating elements is held in the nonrotationally gearbox 16 of element of conduct, so that can not rotate with respect to it.Therefore in addition, is provided with integratedly, plays with the second centre output element similarly acting on as output element 34 in the middle of another the sun gear S2 and second of the second preposition planetary gear set 70 of four rotating elements.In addition, in second speed changing portion 64 of speed changer 66, the first rotating element RE1 (CA3, S4) optionally is connected in output element 32 in the middle of first, optionally is connected in as the input shaft 22 of input rotating element and by the 5th clutch C5 by four clutches C4 and optionally is connected in output element 34 in the middle of second and is optionally remained in gearbox 16 as nonrotational element by the first break B1 by three-clutch C3.In addition, the second rotating element RE2 (R3, CA4) optionally is connected in as the input shaft 22 of input rotating element and by the second break B2 by second clutch C2 and is optionally remained in the nonrotationally gearbox 16 of element of conduct.In addition, the 3rd rotating element RE3 (R4) is provided with integratedly with the output shaft 36 of conduct output rotating element, therefore plays the effect similar to exporting rotating element.In addition, output element 32 in the middle of the 4th rotating element RE4 (S3) optionally is connected in first by first clutch C1.
In the nomogram in Figure 14, in first grade, the 5th clutch C5 is engaged the first rotating element RE1 being connected in output element 34 in the middle of second, and this causes rotating under the identical speed of first rotating element RE1 output element 34 in the middle of with second.Simultaneously, the second break B2 is engaged the second rotating element RE2 is remained in the gearbox 16 as nonrotational element, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (1st) expression, and (1st) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X1 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
In second grade, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (2nd) expression, and (2nd) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y6 and horizontal line XZ and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In third gear, the first break B1 is engaged so that the first rotating element RE1 is remained in gearbox 16, and this causes the rotational velocity of the first rotating element RE1 to be " 0 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (3rd) expression, and (3rd) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line XZ and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In fourth speed, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (4th) expression, and (4th) locates at point, and horizontal line X2 and vertical curve Y7 intersect.
In the 5th grade, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (5th) expression, and (5th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X3 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In the 6th grade, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (6th) expression, and (6th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y6 and horizontal line X3 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In the 7th grade, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (7th) expression, and (7th) locates at point, and horizontal line X3 and vertical curve Y7 intersect.
In the 8th grade, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (8th) expression, and (8th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X2 and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In the 9th grade, the first break B1 is engaged so that the first rotating element RE1 is remained in gearbox 16, and this causes the rotational velocity of the first rotating element RE1 to be " 0 ".Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (9th) expression, and (9th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line XZ and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In the tenth grade, the 5th clutch C5 is engaged the first rotating element RE1 being connected in output element 34 in the middle of second, and this causes rotating under the identical speed of first rotating element RE1 output element 34 in the middle of with second.Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (10th) expression, and (10th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X1 and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In first reverse gear, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (Rev1) expression, and (Rev1) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X2 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
In second reverse gear, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (Rev2) expression, and (Rev2) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X3 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
By this way, according to the 3rd exemplary embodiment, by engaging the 5th clutch C5 and the second break B2 sets up first grade.Set up second grade by engaging the first clutch C1 and the second break B2.Set up third gear by engaging the first clutch C1 and the first break B1.Set up fourth speed by engaging first clutch C1 and three-clutch C3.Set up the 5th grade by engaging first clutch C1 and four clutches C4.Set up the 6th grade by engaging first clutch C1 and second clutch C2.Set up the 7th grade by engaging second clutch C2 and four clutches C4.Set up the 8th grade by engaging second clutch C2 and three-clutch C3, and set up the 9th grade by engaging the second clutch C2 and the first break B1.Therefore, the speed changer 66 of the 3rd exemplary embodiment can be realized nine forward gearss.
The speed changer 66 of the 3rd exemplary embodiment can also be realized the tenth grade by engaging second clutch C2 and the 5th clutch C5.Therefore, except that can realizing ten forward gearss, preferably can set the level between the 9th grade and the tenth grade less with intensive speed ratio.
And first speed changing portion 72 comprises first preposition planetary gear set 68 of double pinion type and the second preposition planetary gear set 70 of single small gear type.The planet carrier CA1 of the first preposition planetary gear set 68 always is connected in the gearbox 16 as nonrotational element, and the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 68 and the second preposition planetary gear set 70 links together, and the gear ring R2 of the sun gear S1 of the first preposition planetary gear set 68 and the second preposition planetary gear set 70 is connected in the input shaft 22 as the input rotating element simultaneously.Therefore, the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 68 or the second preposition planetary gear set 70 is as the first middle output element 32, and the sun gear S2 of the second preposition planetary gear set 70 is as the second middle output element 34 simultaneously.Therefore, can provide practical speed changer 66.
In addition, second speed changing portion 64 comprises first rearmounted planetary gear set 58 of double pinion type and the second rearmounted planetary gear set 60 of single small gear type.The first rotating element RE1 is that the sun gear S4 by the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the second rearmounted planetary gear set 60 constitutes.The second rotating element RE2 is that the planet carrier CA4 by the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the second rearmounted planetary gear set 60 constitutes.The 3rd rotating element RE3 is that the gear ring R4 by the second rearmounted planetary gear set 60 constitutes.The 4th rotating element RE4 is that the sun gear S3 by the first rearmounted planetary gear set 58 constitutes.Therefore, can provide practical speed changer 66.
In addition, speed changer 66 also can be used for realizing nine forward gearss second grade in clutch shown in above-mentioned Figure 13 and brake engages figure.That is to say, in speed changer 66, by engaging the 5th clutch C5 and the second break B2 sets up first grade.Set up second grade by engaging the first clutch C1 and the first break B1.Set up third gear by engaging first clutch C1 and three-clutch C3.Set up fourth speed by engaging first clutch C1 and four clutches C4.Set up the 5th grade by engaging first clutch C1 and second clutch C2.Set up the 6th grade by engaging second clutch C2 and four clutches C4.Set up the 7th grade by engaging second clutch C2 and three-clutch C3.Set up the 8th grade by engaging the second clutch C2 and the first break B1, and realize the 9th grade by engaging second clutch C2 and the 5th clutch C5.
Here, revise example as the 3rd embodiment's first, as shown in Figure 15, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 66 can obtain ten forward gearss and two reverse gears.Figure 16 is and the corresponding nomogram of Figure 15 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, with clutch and brake engages figure and the nomogram described as the first correction example of the Figure 15 of the part different and the 3rd exemplary embodiment shown in Figure 16 with aforementioned exemplary embodiment.
As shown in clutch among Figure 15 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, first grade " 1st " is to the tenth grade of 10th " in any one; perhaps two reverse gears; promptly; first reverse gear " R1 " or second reverse gear " R2 ", and can obtain the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that for each grade, changes with basic identical ratio.
As shown in Figure 15, first clutch C1 is engaged with the 4th rotating element RE4, the i.e. sun gear S3 of the first rearmounted planetary gear set 58, be connected with output element 32 in the middle of first, and the 5th clutch C5 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, output element 34 in the middle of being connected in second, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, be approximately 5.971.
In clutch shown in Figure 15 and brake engages figure, it is described identical with use Figure 13 to the operation of the friction engagement device of the tenth grade " 10th " to be used to set up second grade " 2d ", therefore will omit giving unnecessary details it.In addition, setting up in the speed changer 66 of shelves according to clutch shown in Figure 15 and brake engages figure, second grade speed ratio γ 2 is approximately 3.783, the speed ratio γ 3 of third gear is approximately 2.509, the speed ratio γ 4 of fourth speed is approximately 1.782, the 5th grade speed ratio γ 5 is approximately 1.452, the 6th grade speed ratio γ 6 is approximately 1.260, the 7th grade speed ratio γ 7 is approximately 1.000, the 8th grade speed ratio γ 8 is approximately 0.800, the 9th grade speed ratio γ 9 is approximately 0.636, the tenth grade speed ratio γ 10 is approximately 0.493, the speed ratio γ R2 that the speed ratio γ R1 of first reverse gear is approximately 3.118 and second reverse gear is approximately 1.750.In addition, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.578, second grade speed ratio γ 2 is 1.508 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.408 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.227, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.152, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.260, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is that the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of 1.251, the eight grades speed ratio γ 8 and the 9th grade is 1.256, and the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.290.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 10) of the speed ratio γ 10 of first grade speed ratio γ 1 and the tenth grade is 12.101, this is bigger numerical value.
In the nomogram shown in Figure 16, four vertical curve Y1 represent the assembly of first speed changing portion 72 to Y4.In the drawings from left to right, line Y1 represents that sun gear S2, the line Y2 of the second preposition planetary gear set 70 represent that planet carrier CA1, the line Y3 of the first preposition planetary gear set 68 represent that the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 68 that links together and the second preposition planetary gear set 70 and line Y4 represent the sun gear S1 of the first preposition planetary gear set 68 that links together and the gear ring R2 of the second preposition planetary gear set 70.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 64 to Y8.In the drawings from left to right, line Y5 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 58 of the first rotating element RE1 and the sun gear S4 of the second rearmounted planetary gear set 60, line Y6 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 58 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 60, line Y7 represents to be equivalent to the gear ring R4 of the second rearmounted planetary gear set 60 of the 3rd rotating element RE3, and line Y8 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 58 of the 4th rotating element RE4.Nomogram shown in Figure 16 is similar to the nomogram shown in above-mentioned Fig. 4, therefore omits the description to it.
By this way, revise example according to first of the 3rd exemplary embodiment, clutch by each grade and the combination of the joint of break and suitably set the gear ratio of each planetary gear set can obtain to realize ten forward gearss and two reverse gears and its middle-grade level speed changer 66 for the speed ratio of comparatively dense.
Here, revise example as the 3rd embodiment's first, as shown in Figure 17, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 66 can obtain ten forward gearss and two reverse gears.Figure 18 is and the corresponding nomogram of Figure 17 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the second correction example of Figure 17 different with aforementioned exemplary embodiment and the 3rd exemplary embodiment shown in Figure 18 be described.
As shown in clutch among Figure 17 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, first grade " 1st " is to the tenth grade of 10th " in any one; perhaps two reverse gears; promptly; first reverse gear " R1 " or second reverse gear " R2 ", and can obtain the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that for each grade, changes with basic identical ratio.
As shown in Figure 17, first clutch C1 is engaged with the 4th rotating element RE4, the i.e. sun gear S3 of the first rearmounted planetary gear set 58, be connected with output element 32 in the middle of first, and the 5th clutch C5 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, output element 34 in the middle of being connected in second, thereby set up second grade, described second grade has and for example is approximately 2.924 speed ratio γ 2.
Simultaneously, in clutch shown in Figure 17 and brake engages figure, it is described identical with use Figure 13 to the operation of the friction engagement device of the tenth grade " 10th " with third gear " 3rd " to be used to set up first grade " 1st ", therefore will omit giving unnecessary details it.In addition, setting up in the speed changer 66 of shelves according to clutch shown in Figure 17 and brake engages figure, first grade speed ratio γ 1 is approximately 4.549, the speed ratio γ 3 of third gear is approximately 2.233, the speed ratio γ 4 of fourth speed is approximately 1.645, the 5th grade speed ratio γ 5 is approximately 1.414, the 6th grade speed ratio γ 6 is approximately 1.246, the 7th grade speed ratio γ 7 is approximately 1.000, the 8th grade speed ratio γ 8 is approximately 0.824, the 9th grade speed ratio γ 9 is approximately 0.649, the tenth grade speed ratio γ 10 is approximately 0.568, the speed ratio γ R2 that the speed ratio γ R1 of first reverse gear is approximately 3.062 and second reverse gear is approximately 1.852.In addition, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.556, second grade speed ratio γ 2 is 1.309 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.351 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.170, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.134, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.246, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is that the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of 1.213, the eight grades speed ratio γ 8 and the 9th grade is 1.246, and the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.143.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 10) of the speed ratio γ 10 of first grade speed ratio γ 1 and the tenth grade is 8.005, this is bigger numerical value.
In the nomogram shown in Figure 18, because therefore identical in perspective view and the previous embodiment represent that four vertical curve Y1 of the assembly of first speed changing portion 72 represent and the identical rotating element shown in Figure 16 to Y8 with four vertical curve Y5 of the assembly of representing second speed changing portion 64 to Y4.In addition, in clutch shown in Figure 17 and brake engages figure, it is described identical with use Figure 13 to the operation of the friction engagement device of the tenth grade " 10th " with third gear " 3rd " to be used to set up first grade " 1st ".Therefore, nomogram is also corresponding with it.Therefore, first grade " 1st " among Figure 18 and third gear " 3rd " be to the tenth grade " 10th " identical with shown in Figure 14, therefore will the descriptions thereof are omitted.
Simultaneously, in second grade, the 5th clutch C5 is engaged the first rotating element RE1 being connected in output element 34 in the middle of second, and this causes rotating under the identical speed of first rotating element RE1 output element 34 in the middle of with second.Simultaneously, first clutch C1 is engaged the 4th rotating element RE4 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of the 4th rotating element RE4 output element 32 in the middle of with first.Therefore, the rotational velocity of output shaft 36 is by point (2nd) expression, and (2nd) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X1 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
By this way, second revise example, by engaging the 5th clutch C5 and the second break B2 sets up first grade according to this of the 3rd exemplary embodiment.Set up second grade by engaging first clutch C1 and the 5th clutch C5.Set up third gear by engaging the first clutch C1 and the first break B1.Set up fourth speed by engaging first clutch C1 and three-clutch C3.Set up the 5th grade by engaging first clutch C1 and four clutches C4.Set up the 6th grade by engaging first clutch C1 and second clutch C2.Set up the 7th grade by engaging second clutch C2 and four clutches C4.Set up the 8th grade by engaging second clutch C2 and three-clutch C3.Set up the 9th grade by engaging the second clutch C2 and the first break B1, and set up the tenth grade by engaging second clutch C2 and the 5th clutch C5.Therefore, except that can obtaining ten forward gearss, the level between the 9th grade and the tenth grade can preferably be set lessly with intensive speed ratio.
Here, revise example as the 3rd of the 3rd embodiment, as shown in Figure 19, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 66 can obtain nine forward gearss and two reverse gears.Figure 20 is and the corresponding nomogram of Figure 19 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 3rd correction example of Figure 19 different with aforementioned exemplary embodiment and the 3rd exemplary embodiment shown in Figure 20 be described.
As shown in clutch among Figure 19 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
As shown in Figure 19, first clutch C1 is engaged with the 4th rotating element RE4, the i.e. sun gear S3 of the first rearmounted planetary gear set 58, be connected with output element 32 in the middle of first, and the second break B2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, be approximately 4.776.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and the first break B1 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up second grade, described second grade of speed ratio γ 2 that has less than first grade of speed ratio γ 1, for example, be approximately 2.925.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and three-clutch C3 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 32 in the middle of first, thereby the third gear of foundation, described third gear has the speed ratio γ 3 less than second grade of speed ratio γ 2, for example, be approximately 2.000.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and four clutches C4 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up fourth speed, described fourth speed has the speed ratio γ 4 less than third gear speed ratio γ 3, for example, be approximately 1.519.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and second clutch C2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up the 5th grade, described the 5th grade of speed ratio γ 5 that has less than fourth speed speed ratio γ 4, for example, be approximately 1.265.
In addition, second clutch C2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and four clutches C4 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up the 6th grade, described the 6th grade of speed ratio γ 6 that has less than the 5th grade of speed ratio γ 5, for example, be approximately 1.000.
In addition, second clutch C2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and three-clutch C3 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 32 in the middle of first, thereby set up the 7th grade, described the 7th grade of speed ratio γ 7 that has less than the 6th grade of speed ratio γ 6, for example, be approximately 0.800.
In addition, second clutch C2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and the first break B1 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up the 8th grade, described the 8th grade of speed ratio γ 8 that has less than the 7th grade of speed ratio γ 7, for example, be approximately 0.667.
In addition, second clutch C2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and the 5th clutch C5 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 34 in the middle of second, thereby set up the 9th grade, described the 9th grade has minimum speed ratio γ 9, for example, be approximately 0.588.
In addition, three-clutch C3 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 32 in the middle of first, and the second break B2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up first reverse gear " R1 ", described reverse gear " R1 " has and is approximately 4.000 speed ratio γ R1.
In addition, four clutches C4 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and the second break B2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up second reverse gear " R2 ", described reverse gear " R2 " has the speed ratio γ R2 less than the speed ratio γ R1 of first reverse gear, for example, 2.000.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 58 of gear ratio ρ 1, the second preposition planetary gear set 70 of the first preposition planetary gear set 68 and the gear ratio ρ 4 of the second rearmounted planetary gear set 60 are designed to be and can realize aforementioned speed ratio.
Obtaining in the speed changer 66 of shelves according to clutch shown in Figure 19 and brake engages figure, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.633, second grade speed ratio γ 2 is 1.463 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.316 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.201, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.265, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.250, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is 1.200, and the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of the 8th grade speed ratio γ 8 and the 9th grade is 1.133.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 9) of the speed ratio γ 9 of first grade speed ratio γ 1 and the 9th grade is 8.119, this is bigger numerical value.
In the nomogram of Figure 20, four vertical curve Y1 represent the assembly of first speed changing portion 72 to Y4.In the drawings from left to right, line Y1 represents that sun gear S2, the line Y2 of the second preposition planetary gear set 70 represent that planet carrier CA1, the line Y3 of the first preposition planetary gear set 68 represent that the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 68 that links together and the second preposition planetary gear set 70 and line Y4 represent the sun gear S1 of the first preposition planetary gear set 68 that links together and the gear ring R2 of the second preposition planetary gear set 70.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 64 to Y8.In the drawings from left to right, line Y5 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 58 of the first rotating element RE1 and the sun gear S4 of the second rearmounted planetary gear set 60, line Y6 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 58 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 60, line Y7 represents to be equivalent to the gear ring R4 of the second rearmounted planetary gear set 60 of the 3rd rotating element RE3, and line Y8 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 58 of the 4th rotating element RE4.Therefore nomogram shown in Figure 20 similar to shown in Fig. 9 will omit the description to it.
By this way, revise example, set up first grade by engaging the first clutch C1 and the second break B2 according to the 3rd of the 3rd exemplary embodiment.Set up second grade by engaging the first clutch C1 and the first break B1.Set up third gear by engaging first clutch C1 and three-clutch C3.Set up fourth speed by engaging first clutch C1 and four clutches C4.Set up the 5th grade by engaging first clutch C1 and second clutch C2.Set up the 6th grade by engaging second clutch C2 and four clutches C4.Set up the 7th grade by engaging second clutch C2 and three-clutch C3, and set up the 8th grade by engaging the second clutch C2 and the first break B1.Therefore, the 3rd of the 3rd exemplary embodiment the speed changer 66 of revising example can be realized eight forward gearss.
The 3rd of the 3rd exemplary embodiment is revised the speed changer 66 of example can also realize the 9th grade by engaging second clutch C2 and the 5th clutch C5.Therefore, except that can realizing nine forward gearss, can be with intensive speed ratio preferably set the level between the 8th grade and the 9th grade less.
Here, revise example as the 4th of the 3rd embodiment, as shown in Figure 21, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 66 can obtain nine forward gearss and two reverse gears.Figure 22 is and the corresponding nomogram of Figure 21.Hereinafter, will clutch and the brake engages figure and the nomogram of the 4th correction example of Figure 21 different with aforementioned exemplary embodiment and the 3rd exemplary embodiment shown in Figure 22 be described.
As shown in clutch among Figure 21 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
As shown in Figure 21, the 5th clutch C5 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 34 in the middle of second, and the second break B2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, be approximately 4.971.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up second grade, described second grade of speed ratio γ 2 that has less than first grade of speed ratio γ 1, for example, be approximately 3.290.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and the first break B1 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby the third gear of foundation, described third gear has the speed ratio γ 3 less than second grade of speed ratio γ 2, for example, be approximately 2.222.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and three-clutch C3 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 32 in the middle of first, thereby set up fourth speed, described fourth speed has the speed ratio γ 4 less than third gear speed ratio γ 3, for example, be approximately 1.645.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and four clutches C4 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up the 5th grade, described the 5th grade of speed ratio γ 5 that has less than fourth speed speed ratio γ 4, for example, be approximately 1.409.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and second clutch C2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up the 6th grade, described the 6th grade of speed ratio γ 6 that has less than the 5th grade of speed ratio γ 5, for example, be approximately 1.244.
In addition, second clutch C2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and four clutches C4 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up the 7th grade, described the 7th grade of speed ratio γ 7 that has less than the 6th grade of speed ratio γ 6, for example, be approximately 1.000.
In addition, second clutch C2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and three-clutch C3 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, output element 32 in the middle of being connected in first, thereby set up the 8th grade, described the 8th grade of speed ratio γ 8 that has less than the 7th grade of speed ratio γ 7, for example, be approximately 0.825.
In addition, second clutch C2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and the first break B1 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up the 9th grade, described the 9th grade has minimum speed ratio γ 9, for example, be approximately 0.649.
In addition, three-clutch C3 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 32 in the middle of first, and the second break B2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up first reverse gear " R1 ", described reverse gear " R1 " has and is approximately 3.047 speed ratio γ R1.
In addition, four clutches C4 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and the second break B2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up second reverse gear " R2 ", described reverse gear " R2 " has the speed ratio γ R2 less than the speed ratio γ R1 of first reverse gear, for example, 1.852.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 58 of gear ratio ρ 1, the second preposition planetary gear set 70 of the first preposition planetary gear set 68 and the gear ratio ρ 4 of the second rearmounted planetary gear set 60 are designed to be and can realize aforementioned speed ratio.
Obtaining in the speed changer 66 of shelves according to clutch shown in Figure 21 and brake engages figure, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.511, second grade speed ratio γ 2 is 1.481 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.351 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.167, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.133, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.244, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is 1.212, and the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of the 8th grade speed ratio γ 8 and the 9th grade is 1.271.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 9) of the speed ratio γ 9 of first grade speed ratio γ 1 and the 9th grade is 7.655, this is bigger numerical value.
In the nomogram of Figure 22, four vertical curve Y1 represent the assembly of first speed changing portion 72 to Y4.In the drawings from left to right, line Y1 represents that sun gear S2, the line Y2 of the second preposition planetary gear set 70 represent that planet carrier CA1, the line Y3 of the first preposition planetary gear set 68 represent that the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 68 that links together and the second preposition planetary gear set 70 and line Y4 represent the sun gear S1 of the first preposition planetary gear set 68 that links together and the gear ring R2 of the second preposition planetary gear set 70.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 64 to Y8.In the drawings from left to right, line Y5 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 58 of the first rotating element RE1 and the sun gear S4 of the second rearmounted planetary gear set 60, line Y6 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 58 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 60, line Y7 represents to be equivalent to the gear ring R4 of the second rearmounted planetary gear set 60 of the 3rd rotating element RE3, and line Y8 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 58 of the 4th rotating element RE4.Therefore nomogram shown in Figure 22 similar to shown in Figure 11 will omit the description to it.
By this way, revise example, by engaging the 5th clutch C5 and the second break B2 sets up first grade according to the 4th of the 3rd exemplary embodiment.Set up second grade by engaging the first clutch C1 and the second break B2.Set up third gear by engaging the first clutch C1 and the first break B1.Set up fourth speed by engaging first clutch C1 and three-clutch C3.Set up the 5th grade by engaging first clutch C1 and four clutches C4.Set up the 6th grade by engaging first clutch C1 and second clutch C2.Set up the 7th grade by engaging second clutch C2 and four clutches C4, and set up the 8th grade by engaging second clutch C2 and three-clutch C3.Therefore, the 4th of the 3rd exemplary embodiment the speed changer 66 of revising example can be realized eight forward gearss.
The 4th of the 3rd exemplary embodiment is revised the speed changer 66 of example can also realize the 9th grade by engaging the second clutch C2 and the first break B1.Therefore, except that can realizing nine forward gearss, can be with intensive speed ratio preferably set the level between the 8th grade and the 9th grade less.
Here, revise example as the 5th of the 3rd embodiment, as shown in Figure 23, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 66 can obtain nine forward gearss and two reverse gears, and can obtain the effect that is equal to aforementioned exemplary embodiment.In addition, Figure 24 is and the corresponding nomogram of Figure 23.Hereinafter, will clutch and the brake engages figure and the nomogram of the 5th correction example of Figure 23 different with aforementioned exemplary embodiment and the 3rd exemplary embodiment shown in Figure 24 be described.
As shown in clutch among Figure 23 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
In clutch shown in Figure 23 and brake engages figure, it is described identical with use Figure 21 to the operation of the friction engagement device of the 9th grade " 9th " with third gear " 3rd " to be used to set up first grade " 1st ", therefore will omit giving unnecessary details it.
On the other hand, by engaging first clutch C1 with the 4th rotating element RE4, the i.e. sun gear S3 of the first rearmounted planetary gear set 58, be connected with output element 32 in the middle of first, and engage the 5th clutch C5 with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60 are connected in the second middle output element 34, and set up second grade.
Obtaining in the speed changer 66 of shelves according to clutch shown in Figure 23 and brake engages figure, first grade speed ratio γ 1 is approximately 4.549, second grade speed ratio γ 2 is approximately 2.924, the speed ratio γ 3 of third gear is approximately 2.233, the speed ratio γ 4 of fourth speed is approximately 1.645, the 5th grade speed ratio γ 5 is approximately 1.414, the 6th grade speed ratio γ 6 is approximately 1.246, the 7th grade speed ratio γ 7 is approximately 1.000, the 8th grade speed ratio γ 8 is approximately 0.824, the 9th grade speed ratio γ 9 is approximately 0.649, the speed ratio γ R2 that the speed ratio γ R1 of first reverse gear is approximately 3.062 and second reverse gear is approximately 1.852.In addition, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.556, second grade speed ratio γ 2 is 1.309 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.351 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.170, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.134, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.246, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is that the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of 1.213, the eight grades speed ratio γ 8 and the 9th grade is 1.246.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 9) of the speed ratio γ 9 of first grade speed ratio γ 1 and the 9th grade is 7.005, this is bigger numerical value.
In the nomogram shown in Figure 24, because the structure shown in the perspective view is identical, represent that therefore four vertical curve Y1 of the assembly of first speed changing portion 72 represent and the identical rotating element shown in Figure 16 to Y8 with four vertical curve Y5 of the assembly of expression second speed changing portion 64 to Y4.In addition, in clutch shown in Figure 23 and brake engages figure, it is described identical with use Figure 21 to the operation of the friction engagement device of the 9th grade " 9th " with third gear " 3rd " to be used to set up first grade " 1st ".Therefore, nomogram is also corresponding with it.Therefore, except that second grade " 2nd ", the nomogram shown in Figure 24 is identical with nomogram among Figure 22.
On the other hand, in second grade, the 5th clutch C5 is engaged the first rotating element RE1 being connected in output element 34 in the middle of second, and this causes rotating under the identical speed of first rotating element RE1 output element 34 in the middle of with second.Simultaneously, first clutch C1 is engaged the 4th rotating element RE4 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of the 4th rotating element RE4 output element 32 in the middle of with first.Therefore, the rotational velocity of output shaft 36 is by point (2nd) expression, and (2nd) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X1 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
By this way, revise example, by engaging the 5th clutch C5 and the second break B2 sets up first grade according to the 5th of the 3rd exemplary embodiment.Set up second grade by engaging first clutch C1 and the 5th clutch C5.Set up third gear by engaging the first clutch C1 and the first break B1.Set up fourth speed by engaging first clutch C1 and three-clutch C3.Set up the 5th grade by engaging first clutch C1 and four clutches C4.Set up the 6th grade by engaging first clutch C1 and second clutch C2.Set up the 7th grade by engaging second clutch C2 and four clutches C4.Set up the 8th grade by engaging second clutch C2 and three-clutch C3, and set up the 9th grade by engaging the second clutch C2 and the first break B1.Therefore, except that can obtaining nine forward gearss, the level between the 8th grade and the 9th grade can preferably be set lessly with intensive speed ratio.
Here, revise example as the 6th of the 3rd embodiment, as shown in Figure 25, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 66 can obtain nine forward gearss and two reverse gears.In addition, Figure 26 is and the corresponding nomogram of Figure 25 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 6th correction example of Figure 25 different with aforementioned exemplary embodiment and the 3rd exemplary embodiment shown in Figure 26 be described.
As shown in clutch among Figure 25 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
As shown in Figure 25, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and the 5th clutch C5 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, output element 34 in the middle of being connected in second, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, be approximately 4.503.
Simultaneously, in clutch shown in Figure 25 and brake engages figure, it is described identical with use Figure 19 to the operation of the friction engagement device of the 9th grade " 9th " to be used to set up second grade " 2nd ", therefore will omit giving unnecessary details it.In addition, obtaining in the speed changer 66 of shelves according to clutch shown in Figure 25 and brake engages figure, second grade speed ratio γ 2 is approximately 2.720, the speed ratio γ 3 of third gear is approximately 2.000, the speed ratio γ 4 of fourth speed is approximately 1.581, the 5th grade speed ratio γ 5 is approximately 1.316, the 6th grade speed ratio γ 6 is approximately 1.000, the 7th grade speed ratio γ 7 is approximately 0.800, the 8th grade speed ratio γ 8 is approximately 0.667, the 9th grade speed ratio γ 9 is approximately 0.563, the speed ratio γ R2 that the speed ratio γ R1 of first reverse gear is approximately 4.000 and second reverse gear is approximately 2.000.In addition, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.656, second grade speed ratio γ 2 is 1.360 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.265 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.201, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.316, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.250, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is 1.200, and the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of the 8th grade speed ratio γ 8 and the 9th grade is 1.183.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 9) of the speed ratio γ 9 of first grade speed ratio γ 1 and the 9th grade is 7.993, this is bigger numerical value.
In the nomogram shown in Figure 26, because therefore identical in perspective view and the previous embodiment represent that four vertical curve Y1 of the assembly of first speed changing portion 72 represent and the identical rotating element shown in Figure 16 to Y8 with four vertical curve Y5 of the assembly of representing second speed changing portion 64 to Y4.In addition, in clutch shown in Figure 25 and brake engages figure, it is described identical with use Figure 19 to the operation of the friction engagement device of the 9th grade " 9th " to be used to set up second grade " 2nd ".Therefore, nomogram is also corresponding with it.Therefore, second grade " 2nd " among Figure 26 be to the 9th grade " 9th " identical with shown in Figure 20, therefore will the descriptions thereof are omitted.
On the other hand, in first grade, the 5th clutch C5 is engaged the first rotating element RE1 being connected in output element 34 in the middle of second, and this causes rotating under the identical speed of first rotating element RE1 output element 34 in the middle of with second.Simultaneously, first clutch C1 is engaged the 4th rotating element RE4 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of the 4th rotating element RE4 output element 32 in the middle of with first.Therefore, the rotational velocity of output shaft 36 is by point (2nd) expression, and (2nd) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X1 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
By this way, revise example, set up first grade by engaging first clutch C1 and the 5th clutch C5 according to the 6th of the 3rd exemplary embodiment.Set up second grade by engaging the first clutch C1 and the first break B1.Set up third gear by engaging first clutch C1 and three-clutch C3.Set up fourth speed by engaging first clutch C1 and four clutches C4.Set up the 5th grade by engaging first clutch C1 and second clutch C2.Set up the 6th grade by engaging second clutch C2 and four clutches C4.Set up the 7th grade by engaging second clutch C2 and three-clutch C3.Set up the 8th grade by engaging the second clutch C2 and the first break B1, and set up the 9th grade by engaging second clutch C2 and the 5th clutch C5.Therefore, except that can obtaining nine forward gearss, the level between the 8th grade and the 9th grade can preferably be set lessly with intensive speed ratio.
Figure 27 is the perspective view of the structure of the related speed changer 74 of the present invention's the 4th exemplary embodiment.It is middle-grade and be used to set up the figure of the relation between the operation of the required friction engagement device of those grades that Figure 28 shows speed changer 74.Figure 30 shows the nomogram of the rotational velocity of rotating element in each grade.Except that the structure of first speed changing portion 80, the speed changer 74 of this exemplary embodiment is similar to the speed changer 66 shown in Figure 12 in configuration aspects, the effect of the equivalence that therefore can obtain by this exemplary embodiment and be obtained from previous embodiment.Hereinafter, will the part of the speed changer 74 of this exemplary embodiment different with the part of speed changer 66 be described.
As shown in Figure 27, the first preposition planetary gear set 76 that constitutes the part of first speed changing portion 80 be comprise sun gear S1, intermeshing many group small gear P1, can rotation and can revolve round the sun the planetary gear set of double pinion type of the planet carrier CA1 of support small gear P1 and the gear ring R1 that is meshed with sun gear S1 by small gear P1.The same second preposition planetary gear set 78 that constitutes the part of first speed changing portion 80 be comprise sun gear S2, small gear P2, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA2 of support small gear P2 and the gear ring R2 that is meshed with sun gear S2 by small gear P2.
In first speed changing portion 80, the sun gear S1 of the first preposition planetary gear set 76 is connected in the gearbox 16 as nonrotational element integratedly, thereby prevents that sun gear S1 from rotating with respect to gearbox 16.In addition, the gear ring R2 of the planet carrier CA1 of the first preposition planetary gear set 76 and the second preposition planetary gear set 78 links together and is connected in integratedly as the input shaft 22 of importing rotating element.In addition, the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 76 and the second preposition planetary gear set 78 links together and is connected in the first middle output element 32 integratedly.Output element 34 in the middle of the sun gear S2 of the second preposition planetary gear set 78 is connected in second integratedly.This structure causes first speed changing portion 80 by the slow down rotation that comes from the input shaft 22 and rotation of being slowed down is delivered to second speed changing portion 64 of output element 32 in the middle of first, and makes the rotations that come from input shaft 22 oppositely and with described backward rotation be delivered to second speed changing portion 64 by output element 34 in the middle of second.
In the speed changer 74 that constitutes as mentioned above, as shown in Figure 28, for example can be by engaging simultaneously from first clutch C1 in response to the instruction that comes from ECU42, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with essentially identical ratio.
Obtaining in the speed changer 74 of shelves according to clutch shown in Figure 28 and brake engages figure, first grade speed ratio γ 1 is approximately 4.762, second grade speed ratio γ 2 is approximately 4.110, the speed ratio γ 3 of third gear is approximately 2.603, the speed ratio γ 4 of fourth speed is approximately 2.000, the 5th grade speed ratio γ 5 is approximately 1.624, the 6th grade speed ratio γ 6 is approximately 1.322, the 7th grade speed ratio γ 7 is approximately 1.000, the 8th grade speed ratio γ 8 is approximately 0.833, the 9th grade speed ratio γ 9 is approximately 0.714, the tenth grade speed ratio γ 10 is approximately 0.621, the speed ratio γ R2 that the speed ratio γ R1 of first reverse gear is approximately 5.000 and second reverse gear is approximately 2.500.In addition, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.159, second grade speed ratio γ 2 is 1.579 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.301 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.232, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.229, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.322, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is that the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of 1.200, the eight grades speed ratio γ 8 and the 9th grade is 1.167, and the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.150.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 10) of the speed ratio γ 10 of first grade speed ratio γ 1 and the tenth grade is 7.667, this is bigger numerical value.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 58 of gear ratio ρ 1, the second preposition planetary gear set 78 of the first preposition planetary gear set 76 and the gear ratio ρ 4 of the second rearmounted planetary gear set 60 are designed to be and can realize aforementioned speed ratio.
Revise example as first of the 4th exemplary embodiment,, can obtain those grades shown in Figure 29 by the gear ratio ρ 1 to ρ 4 that suitably sets planetary gear set although the bonding operation of each grade of speed changer 74 does not change.Obtaining in the speed changer 74 of shelves according to clutch shown in Figure 29 and brake engages figure, first grade speed ratio γ 1 is approximately 4.971, second grade speed ratio γ 2 is approximately 3.290, the speed ratio γ 3 of third gear is approximately 2.222, the speed ratio γ 4 of fourth speed is approximately 1.645, the 5th grade speed ratio γ 5 is approximately 1.409, the 6th grade speed ratio γ 6 is approximately 1.244, the 7th grade speed ratio γ 7 is approximately 1.000, the 8th grade speed ratio γ 8 is approximately 0.825, the 9th grade speed ratio γ 9 is approximately 0.649, the tenth grade speed ratio γ 10 is approximately 0.574, the speed ratio γ R2 that the speed ratio γ R1 of first reverse gear is approximately 3.047 and second reverse gear is approximately 1.852.In addition, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.511, second grade speed ratio γ 2 is 1.481 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.351 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.167, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.133, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.244, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is that the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of 1.212, the eight grades speed ratio γ 8 and the 9th grade is 1.271, and the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.131.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 10) of the speed ratio γ 10 of first grade speed ratio γ 1 and the tenth grade is 8.655, this is bigger numerical value.By suitably setting the gear ratio of each planetary gear set by this way, the overall ratio scope can be set widelyer than the overall ratio scope shown in Figure 28.
In the nomogram shown in Figure 30, four vertical curve Y1 represent the assembly of first speed changing portion 80 to Y4.In the drawings from left to right, line Y1 gear ring R2, line Y2 with the planet carrier CA1 of the first preposition planetary gear set 76 that constitutes a rotating element and the second preposition planetary gear set 78 represent to link together planet carrier CA2, the line Y3 with the gear ring R1 of the first preposition planetary gear set 76 that constitutes another rotating element and the second preposition planetary gear set 78 that represent to link together represents to represent sun gear S2 as the second preposition planetary gear set 78 of another rotating element as the sun gear S1 of the first preposition planetary gear set 76 of another rotating element and line Y4.Therefore, based on these rotating elements, the nomogram shown in Figure 30 is similar to the nomogram shown in above-mentioned Fig. 4, therefore omits the description to it.
By this way, revise example according to first of the 4th exemplary embodiment, first speed changing portion 80 comprises first preposition planetary gear set 76 of double pinion type and the second preposition planetary gear set 78 of single small gear type.The sun gear S1 of the first preposition planetary gear set 76 always is connected in the gearbox 16 as nonrotational element, and the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 76 and the second preposition planetary gear set 78 links together, and the gear ring R2 of the planet carrier CA1 of the first preposition planetary gear set 76 and the second preposition planetary gear set 78 is connected in the input shaft 22 as the input rotating element simultaneously.Therefore, the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 76 or the second preposition planetary gear set 78 is as the first middle output element 32, and the sun gear S1 of the first preposition planetary gear set 76 is as the second middle output element 34 simultaneously.Therefore, can provide practical speed changer 74.
Here, revise example as second of the 4th exemplary embodiment, as shown in Figure 31, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 74 can obtain ten forward gearss and two reverse gears.In addition, Figure 32 is and the corresponding nomogram of Figure 31 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the second correction example of the 4th exemplary embodiment shown in Figure 31 and 32 different with aforementioned exemplary embodiment be described.
As shown in clutch among Figure 31 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
In clutch shown in Figure 31 and brake engages figure, it is described identical with use Figure 15 to the operation of the friction engagement device of the tenth grade " 10th " to be used to set up first grade " 1st ", therefore with the descriptions thereof are omitted.In addition, also identical by the speed ratio that joint obtained of those friction engagement devices in each grade with the speed ratio shown in Figure 15, therefore with the descriptions thereof are omitted.
In the nomogram shown in Figure 32, four vertical curve Y1 represent the assembly of first speed changing portion 80 to Y4.In the drawings from left to right, line Y1 represents that sun gear S2, the line Y2 of the second preposition planetary gear set 78 represent that sun gear S1, the line Y3 of the first preposition planetary gear set 76 represent that the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 76 that links together and the second preposition planetary gear set 78 and line Y4 represent the planet carrier CA1 of the first preposition planetary gear set 76 that links together and the gear ring R2 of the second preposition planetary gear set 78.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 64 to Y8.In the drawings from left to right, line Y5 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 58 of the first rotating element RE1 and the sun gear S4 of the second rearmounted planetary gear set 60, line Y6 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 58 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 60, line Y7 represents to be equivalent to the gear ring R4 of the second rearmounted planetary gear set 60 of the 3rd rotating element RE3, and line Y8 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 58 of the 4th rotating element RE4.Nomogram shown in Figure 32 is similar to the nomogram shown in Figure 16, therefore omits the description to it.
By this way, revise example according to second of the 4th exemplary embodiment, clutch by each grade and the combination of the joint of break and suitably set the gear ratio of each planetary gear set can obtain to realize ten forward gearss and two reverse gears and its middle-grade level speed changer 74 for the speed ratio of comparatively dense.
Here, revise example as the 3rd of the 4th embodiment, as shown in Figure 33, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 74 can obtain ten forward gearss and two reverse gears.Figure 34 is and the corresponding nomogram of Figure 33 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 3rd correction example of Figure 33 different with aforementioned exemplary embodiment and the 4th exemplary embodiment shown in Figure 34 be described.
As shown in clutch among Figure 33 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, first grade " 1st " is to the tenth grade of 10th " in any one; perhaps two reverse gears; promptly; first reverse gear " R1 " or second reverse gear " R2 ", and can obtain the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that for each grade, changes with basic identical ratio.
In clutch shown in Figure 33 and brake engages figure, it is described identical with use Figure 17 to the operation of the friction engagement device of the tenth grade " 10th " to be used to set up first grade " 1st ", therefore with the descriptions thereof are omitted.In addition, also identical by the speed ratio that joint obtained of those friction engagement devices in each grade with the speed ratio shown in Figure 17, therefore with the descriptions thereof are omitted.
In the nomogram shown in Figure 34, four vertical curve Y1 represent the assembly of first speed changing portion 80 to Y4.In the drawings from left to right, line Y1 represents that sun gear S2, the line Y2 of the second preposition planetary gear set 78 represent that sun gear S1, the line Y3 of the first preposition planetary gear set 76 represent that the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 76 that links together and the second preposition planetary gear set 78 and line Y4 represent the planet carrier CA1 of the first preposition planetary gear set 76 that links together and the gear ring R2 of the second preposition planetary gear set 78.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 64 to Y8.In the drawings from left to right, line Y5 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 58 of the first rotating element RE1 and the sun gear S4 of the second rearmounted planetary gear set 60, line Y6 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 58 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 60, line Y7 represents to be equivalent to the gear ring R4 of the second rearmounted planetary gear set 60 of the 3rd rotating element RE3, and line Y8 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 58 of the 4th rotating element RE4.Nomogram shown in Figure 34 is similar to the nomogram shown in Figure 18, therefore omits the description to it.
By this way, revise example according to the 3rd of the 4th exemplary embodiment, as mentioned above, clutch by each grade and the combination of the joint of break and suitably set the gear ratio of each planetary gear set can obtain to realize ten forward gearss and two reverse gears and its middle-grade level speed changer 74 for the speed ratio of comparatively dense.
Here, revise example as the 4th of the 4th embodiment, as shown in Figure 35, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 74 can obtain nine forward gearss and two reverse gears.Figure 36 is and the corresponding nomogram of Figure 35 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 4th correction example of Figure 35 different with aforementioned exemplary embodiment and the 4th exemplary embodiment shown in Figure 36 be described.
As shown in clutch among Figure 35 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
As shown in Figure 35, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, be approximately 4.776.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and the first break B1 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up second grade, described second grade of speed ratio γ 2 that has less than first grade of speed ratio γ 1, for example, be approximately 2.925.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and three-clutch C3 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 32 in the middle of first, thereby the third gear of foundation, described third gear has the speed ratio γ 3 less than second grade of speed ratio γ 2, for example, be approximately 2.000.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and four clutches C4 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up fourth speed, described fourth speed has the speed ratio γ 4 less than third gear speed ratio γ 3, for example, be approximately 1.519.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and second clutch C2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up the 5th grade, described the 5th grade of speed ratio γ 5 that has less than fourth speed speed ratio γ 4, for example, be approximately 1.265.
In addition, second clutch C2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and four clutches C4 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up the 6th grade, described the 6th grade of speed ratio γ 6 that has less than the 5th grade of speed ratio γ 5, for example, be approximately 1.000.
In addition, second clutch C2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and three-clutch C3 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 32 in the middle of first, thereby set up the 7th grade, described the 7th grade of speed ratio γ 7 that has less than the 6th grade of speed ratio γ 6, for example, be approximately 0.800.
In addition, second clutch C2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and the first break B1 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up the 8th grade, described the 8th grade of speed ratio γ 8 that has less than the 7th grade of speed ratio γ 7, for example, be approximately 0.667.
In addition, second clutch C2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and the 5th clutch C5 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 34 in the middle of second, thereby set up the 9th grade, described the 9th grade has minimum speed ratio γ 9, for example, be approximately 0.588.
In addition, three-clutch C3 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 32 in the middle of first, and the second break B2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up first reverse gear " R1 ", described reverse gear " R1 " has and is approximately 4.000 speed ratio γ R1.
In addition, four clutches C4 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and the second break B2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up second reverse gear " R2 ", described reverse gear " R2 " has the speed ratio γ R2 less than the speed ratio γ R1 of first reverse gear, for example, 2.000.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 58 of gear ratio ρ 1, the second preposition planetary gear set 78 of the first preposition planetary gear set 76 and the gear ratio ρ 4 of the second rearmounted planetary gear set 60 are designed to be and can realize aforementioned speed ratio.
Obtaining in the speed changer 74 of shelves according to clutch shown in Figure 35 and brake engages figure, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.633, second grade speed ratio γ 2 is 1.463 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.316 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.201, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.265, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.250, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is 1.200, and the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of the 8th grade speed ratio γ 8 and the 9th grade is 1.133.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 9) of the speed ratio γ 9 of first grade speed ratio γ 1 and the 9th grade is 8.119, this is bigger numerical value.
In the nomogram of Figure 36, four vertical curve Y1 represent the assembly of first speed changing portion 80 to Y4.In the drawings from left to right, line Y1 represents that sun gear S2, the line Y2 of the second preposition planetary gear set 78 represent that sun gear S1, the line Y3 of the first preposition planetary gear set 76 represent that the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 76 that links together and the second preposition planetary gear set 78 and line Y4 represent the planet carrier CA1 of the first preposition planetary gear set 76 that links together and the gear ring R2 of the second preposition planetary gear set 78.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 64 to Y8.In the drawings from left to right, line Y5 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 58 of the first rotating element RE1 and the sun gear S4 of the second rearmounted planetary gear set 60, line Y6 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 58 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 60, line Y7 represents to be equivalent to the gear ring R4 of the second rearmounted planetary gear set 60 of the 3rd rotating element RE3, and line Y8 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 58 of the 4th rotating element RE4.Therefore, based on these rotating elements, therefore similar to shown in Fig. 9 of the nomogram shown in Figure 36 will omit the description to it.
By this way, revise example, set up first grade by engaging the first clutch C1 and the second break B2 according to the 4th of the 4th exemplary embodiment.Set up second grade by engaging the first clutch C1 and the first break B1.Set up third gear by engaging first clutch C1 and three-clutch C3.Set up fourth speed by engaging first clutch C1 and four clutches C4.Set up the 5th grade by engaging first clutch C1 and second clutch C2.Set up the 6th grade by engaging second clutch C2 and four clutches C4.Set up the 7th grade by engaging second clutch C2 and three-clutch C3, and set up the 8th grade by engaging the second clutch C2 and the first break B1.Therefore, the 4th of the 4th exemplary embodiment the speed changer 74 of revising example can be realized eight forward gearss.
The 4th of the 4th exemplary embodiment is revised the speed changer 74 of example can also realize the 9th grade by engaging second clutch C2 and the 5th clutch C5.Therefore, except that can realizing nine forward gearss, can be with intensive speed ratio preferably set the level between the 8th grade and the 9th grade less.
Here, revise example as the 5th of the 4th embodiment, as shown in Figure 37, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 74 can obtain nine forward gearss and two reverse gears.In addition, Figure 38 is and the corresponding nomogram of Figure 37 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 5th correction example of Figure 37 different with aforementioned exemplary embodiment and the 4th exemplary embodiment shown in Figure 38 be described.
As shown in clutch among Figure 37 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
As shown in Figure 37, the 5th clutch C5 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 34 in the middle of second, and the second break B2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, be approximately 4.971.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up second grade, described second grade of speed ratio γ 2 that has less than first grade of speed ratio γ 1, for example, be approximately 3.290.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and the first break B1 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby the third gear of foundation, described third gear has the speed ratio γ 3 less than second grade of speed ratio γ 2, for example, be approximately 2.222.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and three-clutch C3 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 32 in the middle of first, thereby set up fourth speed, described fourth speed has the speed ratio γ 4 less than third gear speed ratio γ 3, for example, be approximately 1.645.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and four clutches C4 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up the 5th grade, described the 5th grade of speed ratio γ 5 that has less than fourth speed speed ratio γ 4, for example, be approximately 1.409.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up the 6th grade, described the 6th grade of speed ratio γ 6 that has less than the 5th grade of speed ratio γ 5, for example, be approximately 1.244.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and four clutches C4 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up the 7th grade, described the 7th grade of speed ratio γ 7 that has less than the 6th grade of speed ratio γ 6, for example, be approximately 1.000.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and three-clutch C3 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, output element 32 in the middle of being connected in first, thus set up the 8th grade, described the 8th grade of speed ratio γ 8 that has less than the 7th grade of speed ratio γ 7, for example, be approximately 0.825.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and the first break B1 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up the 9th grade, described the 9th grade has minimum speed ratio γ 9, for example, be approximately 0.649.
In addition, three-clutch C3 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 32 in the middle of first, and the second break B2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up first reverse gear " R1 ", described reverse gear " R1 " has and is approximately 3.047 speed ratio γ R1.
In addition, four clutches C4 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and the second break B2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up second reverse gear " R2 ", described reverse gear " R2 " has the speed ratio γ R2 less than the speed ratio γ R1 of first reverse gear, for example, 1.852.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 58 of gear ratio ρ 1, the second preposition planetary gear set 78 of the first preposition planetary gear set 76 and the gear ratio ρ 4 of the second rearmounted planetary gear set 60 are designed to be and can realize aforementioned speed ratio.
Obtaining in the speed changer 74 of shelves according to clutch shown in Figure 37 and brake engages figure, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.511, second grade speed ratio γ 2 is 1.481 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.351 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.167, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.133, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.244, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is 1.212, and the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of the 8th grade speed ratio γ 8 and the 9th grade is 1.271.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 9) of the speed ratio γ 9 of first grade speed ratio γ 1 and the 9th grade is 7.655, this is bigger numerical value.
In the nomogram of Figure 38, four vertical curve Y1 represent the assembly of first speed changing portion 80 to Y4.In the drawings from left to right, line Y1 represents that sun gear S2, the line Y2 of the second preposition planetary gear set 78 represent that sun gear S1, the line Y3 of the first preposition planetary gear set 76 represent that the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 76 that links together and the second preposition planetary gear set 78 and line Y4 represent the planet carrier CA1 of the first preposition planetary gear set 76 that links together and the gear ring R2 of the second preposition planetary gear set 78.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 64 to Y8.In the drawings from left to right, line Y5 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 58 of the first rotating element RE1 and the sun gear S4 of the second rearmounted planetary gear set 60, line Y6 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 58 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 60, line Y7 represents to be equivalent to the gear ring R4 of the second rearmounted planetary gear set 60 of the 3rd rotating element RE3, and line Y8 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 58 of the 4th rotating element RE4.Therefore, based on these rotating elements, therefore similar to shown in Figure 11 of the nomogram shown in Figure 38 will omit the description to it.
By this way, revise example, by engaging the 5th clutch C5 and the second break B2 sets up first grade according to the 5th of the 4th exemplary embodiment.Set up second grade by engaging the first clutch C1 and the second break B2.Set up third gear by engaging the first clutch C1 and the first break B1.Set up fourth speed by engaging first clutch C1 and three-clutch C3.Set up the 5th grade by engaging first clutch C1 and four clutches C4.Set up the 6th grade by engaging first clutch C1 and second clutch C2.Set up the 7th grade by engaging second clutch C2 and four clutches C4, and set up the 8th grade by engaging second clutch C2 and three-clutch C3.Therefore, the 5th of the 4th exemplary embodiment the speed changer 74 of revising example can be realized eight forward gearss.
The 5th of the 4th exemplary embodiment is revised the speed changer 74 of example can also realize the 9th grade by engaging the second clutch C2 and the first break B1.Therefore, except that can realizing nine forward gearss, can be with intensive speed ratio preferably set the level between the 8th grade and the 9th grade less.
Here, revise example as the 6th of the 4th exemplary embodiment, as shown in Figure 39, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 74 can obtain nine forward gearss and two reverse gears, and can obtain the effect that is equal to aforementioned exemplary embodiment.In addition, Figure 40 is and the corresponding nomogram of Figure 39 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 6th correction example of Figure 39 different with aforementioned exemplary embodiment and the 4th exemplary embodiment shown in Figure 40 be described.
As shown in clutch among Figure 39 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.The speed ratio that is used to set up the operation of friction engagement device of described shelves and described shelves with use Figure 23 described identical, so will omit giving unnecessary details to it.
In the nomogram shown in Figure 40, because the structure shown in the perspective view is identical, represent that therefore four vertical curve Y1 of the assembly of first speed changing portion 80 represent and the identical rotating element shown in above-mentioned Figure 32 to Y8 with four vertical curve Y5 of the assembly of expression second speed changing portion 64 to Y4.In addition, in clutch shown in Figure 39 and brake engages figure, it is described identical with above-mentioned use Figure 23 to the operation of the friction engagement device of the 9th grade " 9th " to be used to set up first grade " 1st ".Therefore, nomogram is also corresponding with it.Therefore, the nomogram shown in Figure 40 is identical with the nomogram shown in Figure 24.
Therefore, revise example according to the 6th of the 4th exemplary embodiment, by with different compound mode engaging clutches and break and suitably set the gear ratio of each planetary gear set, also can obtain nine forward gearss and two reverse gears, and more particularly, the level between the 8th grade and the 9th grade can be set lessly with intensive speed ratio.
Here, revise example as the 7th of the 4th exemplary embodiment, as shown in Figure 41, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 74 can obtain nine forward gearss and two reverse gears.In addition, Figure 42 is and the corresponding nomogram of Figure 41 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 7th correction example of Figure 41 different with aforementioned exemplary embodiment and the 4th exemplary embodiment shown in Figure 42 be described.
As shown in clutch among Figure 41 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
In clutch shown in Figure 41 and brake engages figure, it is described identical with the above-mentioned Figure 25 of use to the operation of the friction engagement device of the 9th grade " 9th " to be used to set up first grade " 1st ", therefore with the descriptions thereof are omitted.In addition, also identical by the speed ratio that joint obtained of those friction engagement devices in each grade with the speed ratio shown in Figure 25, therefore with the descriptions thereof are omitted.
In the nomogram shown in Figure 42, four vertical curve Y1 represent the assembly of first speed changing portion 80 to Y4.In the drawings from left to right, line Y1 represents that sun gear S2, the line Y2 of the second preposition planetary gear set 78 represent that sun gear S1, the line Y3 of the first preposition planetary gear set 76 represent that the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 76 that links together and the second preposition planetary gear set 78 and line Y4 represent the planet carrier CA1 of the first preposition planetary gear set 76 that links together and the gear ring R2 of the second preposition planetary gear set 78.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 64 to Y8.In the drawings from left to right, line Y5 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 58 of the first rotating element RE1 and the sun gear S4 of the second rearmounted planetary gear set 60, line Y6 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 58 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 60, line Y7 represents to be equivalent to the gear ring R4 of the second rearmounted planetary gear set 60 of the 3rd rotating element RE3, and line Y8 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 58 of the 4th rotating element RE4.Nomogram shown in Figure 42 is similar to the nomogram shown in Figure 26, therefore omits the description to it.
By this way, revise example according to the 7th of the 4th exemplary embodiment, clutch by each grade and the combination of the joint of break (such as above-described those) and suitably set the gear ratio of each planetary gear set, can obtain to realize nine forward gearss and two reverse gears and its middle-grade level speed changer 74 for the speed ratio of comparatively dense.
Figure 43 is the perspective view of the structure of the related speed changer 98 of the present invention's the 5th exemplary embodiment.It is middle-grade and be used to set up the figure of the relation between the operation of the required friction engagement device of those grades that Figure 44 shows speed changer 98.Figure 46 shows the nomogram of the rotational velocity of rotating element in each grade.Except that the structure of first speed changing portion 104, the speed changer 98 of this exemplary embodiment is similar to the speed changer 66 shown in Figure 12 in configuration aspects, the effect of the equivalence that therefore can obtain by this exemplary embodiment and be obtained from previous embodiment.Hereinafter, will the part of the speed changer 98 of this exemplary embodiment different with the part of speed changer 66 be described.
As shown in Figure 43, the first preposition planetary gear set 100 that constitutes the part of first speed changing portion 104 be comprise sun gear S1, small gear P1, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA1 of support small gear P1 and the gear ring R1 that is meshed with sun gear S1 by small gear P1.The same second preposition planetary gear set 102 that constitutes the part of first speed changing portion 104 be comprise sun gear S2, intermeshing many group small gear P2, can rotation and can revolve round the sun the planetary gear set of double pinion type of the planet carrier CA2 of support small gear P2 and the gear ring R2 that is meshed with sun gear S2 by small gear P2.
In first speed changing portion 104, the gear ring R2 of the second preposition planetary gear set 102 is connected in the gearbox 16 as nonrotational element integratedly, thereby prevents that gear ring R2 from rotating with respect to gearbox 16.In addition, the gear ring R1 of the first preposition planetary gear set 100 is connected in the input shaft 22 as the input rotating element integratedly.In addition, the planet carrier CA2 of the planet carrier CA1 of the first preposition planetary gear set 100 and the second preposition planetary gear set 102 links together and is connected in the first middle output element 32 integratedly.In addition, the sun gear S2 of the sun gear S1 of the first preposition planetary gear set 100 and the second preposition planetary gear set 102 links together and is connected in the second middle output element 34 integratedly.This structure causes first speed changing portion 104 by the slow down rotation that comes from the input shaft 22 and rotation of being slowed down is delivered to second speed changing portion 64 of output element 32 in the middle of first, and makes the rotations that come from input shaft 22 oppositely and with described backward rotation be delivered to second speed changing portion 64 by output element 34 in the middle of second.
In the speed changer 98 that constitutes as mentioned above, as shown in Figure 44, for example can be by engaging simultaneously from first clutch C1 in response to the instruction that comes from ECU42, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
Obtaining in the speed changer 98 of shelves according to clutch shown in Figure 44 and brake engages figure, first grade speed ratio γ 1 is approximately 4.762, second grade speed ratio γ 2 is approximately 4.110, the speed ratio γ 3 of third gear is approximately 2.603, the speed ratio γ 4 of fourth speed is approximately 2.000, the 5th grade speed ratio γ 5 is approximately 1.624, the 6th grade speed ratio γ 6 is approximately 1.322, the 7th grade speed ratio γ 7 is approximately 1.000, the 8th grade speed ratio γ 8 is approximately 0.833, the 9th grade speed ratio γ 9 is approximately 0.714, the tenth grade speed ratio γ 10 is approximately 0.621, the speed ratio γ R2 that the speed ratio γ R1 of first reverse gear is approximately 5.000 and second reverse gear is approximately 2.500.In addition, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.159, second grade speed ratio γ 2 is 1.579 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.301 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.232, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.229, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.322, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is that the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of 1.200, the eight grades speed ratio γ 8 and the 9th grade is 1.167, and the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.150.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 10) of the speed ratio γ 10 of first grade speed ratio γ 1 and the tenth grade is 7.667, this is bigger numerical value.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 58 of gear ratio ρ 1, the second preposition planetary gear set 102 of the first preposition planetary gear set 100 and the gear ratio ρ 4 of the second rearmounted planetary gear set 60 are designed to be and can realize aforementioned speed ratio.
Revise example as first of the 5th exemplary embodiment,, can obtain those grades shown in Figure 45 by the gear ratio ρ 1 to ρ 4 that suitably sets planetary gear set although the bonding operation of each grade does not change.Obtaining in the speed changer 98 of shelves according to clutch shown in Figure 45 and brake engages figure, first grade speed ratio γ 1 is approximately 4.971, second grade speed ratio γ 2 is approximately 3.290, the speed ratio γ 3 of third gear is approximately 2.222, the speed ratio γ 4 of fourth speed is approximately 1.645, the 5th grade speed ratio γ 5 is approximately 1.409, the 6th grade speed ratio γ 6 is approximately 1.244, the 7th grade speed ratio γ 7 is approximately 1.000, the 8th grade speed ratio γ 8 is approximately 0.825, the 9th grade speed ratio γ 9 is approximately 0.649, the tenth grade speed ratio γ 10 is approximately 0.574, the speed ratio γ R2 that the speed ratio γ R1 of first reverse gear is approximately 3.047 and second reverse gear is approximately 1.852.In addition, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.511, second grade speed ratio γ 2 is 1.481 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.351 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.167, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.133, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.244, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is that the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of 1.212, the eight grades speed ratio γ 8 and the 9th grade is 1.271, and the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.131.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 10) of the speed ratio γ 10 of first grade speed ratio γ 1 and the tenth grade is 8.655, this is bigger numerical value.By suitably setting the gear ratio of each planetary gear set by this way, the overall ratio scope can be set than the overall ratio wide ranges shown in Figure 44.
In the nomogram shown in Figure 46, four vertical curve Y1 represent the assembly of first speed changing portion 104 to Y4.In the drawings from left to right, line Y1 represents the gear ring R1 as the first preposition planetary gear set 100 of a rotating element, line Y2 represents to link together with the planet carrier CA1 of the first preposition planetary gear set 100 that constitutes another rotating element and the planet carrier CA2 of the second preposition planetary gear set 102, line Y3 represents the gear ring R2 as the second preposition planetary gear set 102 of another rotating element, and line Y4 represents to link together with the sun gear S1 of the first preposition planetary gear set 100 that constitutes another rotating element and the sun gear S2 of the second preposition planetary gear set 102.Therefore, based on these rotating elements, the nomogram shown in Figure 46 is similar to the nomogram shown in above-mentioned Figure 14, therefore omits the description to it.
By this way, revise example according to first of the 5th exemplary embodiment, first speed changing portion 104 comprises first preposition planetary gear set 100 of single small gear type and the second preposition planetary gear set 102 of double pinion type.The gear ring R2 of the second preposition planetary gear set 102 always is connected in the gearbox 16 as nonrotational element, and the sun gear S2 of the sun gear S1 of the first preposition planetary gear set 100 and the second preposition planetary gear set 102 links together.In addition, the planet carrier CA2 of the planet carrier CA1 of the first preposition planetary gear set 100 and the second preposition planetary gear set 102 links together, and the gear ring R1 of the first preposition planetary gear set 100 is connected in the input shaft 22 as the input rotating element.Therefore, the planet carrier CA2 of the planet carrier CA1 of the first preposition planetary gear set 100 or the second preposition planetary gear set 102 is as the first middle output element 32, and the sun gear S2 of the sun gear S1 of the first preposition planetary gear set 100 or the second preposition planetary gear set 102 is as the second middle output element 34 simultaneously.Therefore, can provide practical speed changer 98.
Here, revise example as second of the 5th exemplary embodiment, as shown in Figure 47, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 98 can obtain ten forward gearss and two reverse gears.In addition, Figure 48 is and the corresponding nomogram of Figure 47 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the second correction example of the 5th exemplary embodiment shown in Figure 47 and 48 different with aforementioned exemplary embodiment be described.
As shown in clutch among Figure 47 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
In clutch shown in Figure 47 and brake engages figure, it is described identical with use Figure 15 to the operation of the friction engagement device of the tenth grade " 10th " to be used to set up first grade " 1st ", therefore with the descriptions thereof are omitted.In addition, the speed ratio that joint obtained by those friction engagement devices in each grade is identical with shown in Figure 15 also, therefore will the descriptions thereof are omitted.
In the nomogram shown in Figure 48, four vertical curve Y1 represent the assembly of first speed changing portion 104 to Y4.In the drawings from left to right, line Y1 represents that sun gear S2, the line Y2 of the sun gear S1 of the first preposition planetary gear set 100 that links together and the second preposition planetary gear set 102 represent that gear ring R2, the line Y3 of the second preposition planetary gear set 102 represent planet carrier CA1 and the planet carrier CA2 of the second preposition planetary gear set 102 and the gear ring R1 that line Y4 represents the first preposition planetary gear set 100 of the first preposition planetary gear set 100 that links together.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 64 to Y8.In the drawings from left to right, line Y5 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 58 of the first rotating element RE1 and the sun gear S4 of the second rearmounted planetary gear set 60, line Y6 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 58 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 60, line Y7 represents to be equivalent to the gear ring R4 of the second rearmounted planetary gear set 60 of the 3rd rotating element RE3, and line Y8 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 58 of the 4th rotating element RE4.Nomogram shown in Figure 48 is similar to the nomogram shown in Figure 16, therefore omits the description to it.
By this way, revise example according to second of the 5th exemplary embodiment, clutch by each grade and the combination of the joint of break and suitably set the gear ratio of each planetary gear set can obtain to realize ten forward gearss and two reverse gears and its middle-grade level speed changer 98 for the speed ratio of comparatively dense.
Here, revise example as the 3rd of the 5th exemplary embodiment, as shown in Figure 49, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 98 can obtain ten forward gearss and two reverse gears.Figure 50 is and the corresponding nomogram of Figure 49 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 3rd correction example of Figure 49 different with aforementioned exemplary embodiment and the 5th exemplary embodiment shown in Figure 50 be described.
As shown in clutch among Figure 49 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, first grade " 1st " is to the tenth grade of 10th " in any one; perhaps two reverse gears; promptly; first reverse gear " R1 " or second reverse gear " R2 ", and can obtain the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that for each grade, changes with basic identical ratio.
In clutch shown in Figure 49 and brake engages figure, it is described identical with use Figure 17 to the operation of the friction engagement device of the tenth grade " 10th " to be used to set up first grade " 1st ", therefore with the descriptions thereof are omitted.In addition, also identical by the speed ratio that joint obtained of those friction engagement devices in each grade with the speed ratio shown in Figure 17, therefore with the descriptions thereof are omitted.
In the nomogram shown in Figure 50, four vertical curve Y1 represent the assembly of first speed changing portion 104 to Y4.In the drawings from left to right, line Y1 represents that sun gear S2, the line Y2 of the sun gear S1 of the first preposition planetary gear set 100 that links together and the second preposition planetary gear set 102 represent that gear ring R2, the line Y3 of the second preposition planetary gear set 102 represent planet carrier CA1 and the planet carrier CA2 of the second preposition planetary gear set 102 and the gear ring R1 that line Y4 represents the first preposition planetary gear set 100 of the first preposition planetary gear set 100 that links together.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 64 to Y8.In the drawings from left to right, line Y5 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 58 of the first rotating element RE1 and the sun gear S4 of the second rearmounted planetary gear set 60, line Y6 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 58 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 60, line Y7 represents to be equivalent to the gear ring R4 of the second rearmounted planetary gear set 60 of the 3rd rotating element RE3, and line Y8 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 58 of the 4th rotating element RE4.Nomogram shown in Figure 50 is similar to the nomogram shown in Figure 18, therefore omits the description to it.
By this way, revise example according to the 3rd of the 5th exemplary embodiment, clutch by each grade and the combination of the joint of break (such as above-described those) and suitably set the gear ratio of each planetary gear set, can obtain to realize ten forward gearss and two reverse gears and its middle-grade level speed changer 98 for the speed ratio of comparatively dense.
Here, revise example as the 4th of the 5th exemplary embodiment, as shown in Figure 51, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 98 can obtain nine forward gearss and two reverse gears.Figure 52 is and the corresponding nomogram of Figure 51 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 4th correction example of Figure 51 different with aforementioned exemplary embodiment and the 5th exemplary embodiment shown in Figure 52 be described.
As shown in clutch among Figure 51 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
As shown in Figure 51, first clutch C1 is engaged with the 4th rotating element RE4, the i.e. sun gear S3 of the first rearmounted planetary gear set 58, be connected with output element 32 in the middle of first, and the second break B2 is engaged with the second rotating element RE2, the gear ring R3 of the first rearmounted planetary gear set 58 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, be approximately 4.776.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and the first break B1 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up second grade, described second grade of speed ratio γ 2 that has less than first grade of speed ratio γ 1, for example, be approximately 2.925.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and three-clutch C3 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 32 in the middle of first, thereby the third gear of foundation, described third gear has the speed ratio γ 3 less than second grade of speed ratio γ 2, for example, be approximately 2.000.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and four clutches C4 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up fourth speed, described fourth speed has the speed ratio γ 4 less than third gear speed ratio γ 3, for example, be approximately 1.519.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up the 5th grade, described the 5th grade of speed ratio γ 5 that has less than fourth speed speed ratio γ 4, for example, be approximately 1.265.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and four clutches C4 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up the 6th grade, described the 6th grade of speed ratio γ 6 that has less than the 5th grade of speed ratio γ 5, for example, be approximately 1.000.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and three-clutch C3 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 32 in the middle of first, thereby set up the 7th grade, described the 7th grade of speed ratio γ 7 that has less than the 6th grade of speed ratio γ 6, for example, be approximately 0.800.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and the first break B1 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up the 8th grade, described the 8th grade of speed ratio γ 8 that has less than the 7th grade of speed ratio γ 7, for example, be approximately 0.667.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and the 5th clutch C5 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 34 in the middle of second, thereby set up the 9th grade, described the 9th grade has minimum speed ratio γ 9, for example, be approximately 0.588.
In addition, three-clutch C3 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 32 in the middle of first, and the second break B2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up first reverse gear " R1 ", described reverse gear " R1 " has and is approximately 4.000 speed ratio γ R1.
In addition, four clutches C4 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and the second break B2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up second reverse gear " R2 ", described reverse gear " R2 " has the speed ratio γ R2 less than the speed ratio γ R1 of first reverse gear, for example, 2.000.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 58 of gear ratio ρ 1, the second preposition planetary gear set 102 of the first preposition planetary gear set 100 and the gear ratio ρ 4 of the second rearmounted planetary gear set 60 are designed to be and can realize aforementioned speed ratio.
Obtaining in the speed changer 98 of shelves according to clutch shown in Figure 51 and brake engages figure, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.633, second grade speed ratio γ 2 is 1.463 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.316 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.201, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.265, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.250, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is 1.200, and the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of the 8th grade speed ratio γ 8 and the 9th grade is 1.133.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 9) of the speed ratio γ 9 of first grade speed ratio γ 1 and the 9th grade is 8.119, this is bigger numerical value.
In the nomogram shown in Figure 52, four vertical curve Y1 represent the assembly of first speed changing portion 104 to Y4.In the drawings from left to right, line Y1 represents that sun gear S2, the line Y2 of the sun gear S1 of the first preposition planetary gear set 100 that links together and the second preposition planetary gear set 102 represent that gear ring R2, the line Y3 of the second preposition planetary gear set 102 represent planet carrier CA1 and the planet carrier CA2 of the second preposition planetary gear set 102 and the gear ring R1 that line Y4 represents the first preposition planetary gear set 100 of the first preposition planetary gear set 100 that links together.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 64 to Y8.In the drawings from left to right, line Y5 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 58 of the first rotating element RE1 and the sun gear S4 of the second rearmounted planetary gear set 60, line Y6 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 58 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 60, line Y7 represents to be equivalent to the gear ring R4 of the second rearmounted planetary gear set 60 of the 3rd rotating element RE3, and line Y8 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 58 of the 4th rotating element RE4.Therefore, based on these rotating elements, therefore similar to shown in Fig. 9 of the nomogram shown in Figure 52 will omit the description to it.
By this way, revise example, set up first grade by engaging the first clutch C1 and the second break B2 according to the 4th of the 5th exemplary embodiment.Set up second grade by engaging the first clutch C1 and the first break B1.Set up third gear by engaging first clutch C1 and three-clutch C3.Set up fourth speed by engaging first clutch C1 and four clutches C4.Set up the 5th grade by engaging first clutch C1 and second clutch C2.Set up the 6th grade by engaging second clutch C2 and four clutches C4.Set up the 7th grade by engaging second clutch C2 and three-clutch C3, and set up the 8th grade by engaging the second clutch C2 and the first break B1.Therefore, the 4th of the 5th exemplary embodiment the speed changer 98 of revising example can be realized eight forward gearss.
The 4th of the 5th exemplary embodiment is revised the speed changer 98 of example can also realize the 9th grade by engaging second clutch C2 and the 5th clutch C5.Therefore, except that can realizing nine forward gearss, can be with intensive speed ratio preferably set the level between the 8th grade and the 9th grade less.
Here, revise example as the 5th of the 5th exemplary embodiment, as shown in Figure 53, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 98 can obtain nine forward gearss and two reverse gears.In addition, Figure 54 is and the corresponding nomogram of Figure 53 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 5th correction example of Figure 53 different with aforementioned exemplary embodiment and the 5th exemplary embodiment shown in Figure 54 be described.
As shown in clutch among Figure 53 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
As shown in Figure 53, the 5th clutch C5 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 34 in the middle of second, and the second break B2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, be approximately 4.971.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up second grade, described second grade of speed ratio γ 2 that has less than first grade of speed ratio γ 1, for example, be approximately 3.290.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and the first break B1 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby the third gear of foundation, described third gear has the speed ratio γ 3 less than second grade of speed ratio γ 2, for example, be approximately 2.222.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and three-clutch C3 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 32 in the middle of first, thereby set up fourth speed, described fourth speed has the speed ratio γ 4 less than third gear speed ratio γ 3, for example, be approximately 1.645.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and four clutches C4 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up the 5th grade, described the 5th grade of speed ratio γ 5 that has less than fourth speed speed ratio γ 4, for example, be approximately 1.409.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up the 6th grade, described the 6th grade of speed ratio γ 6 that has less than the 5th grade of speed ratio γ 5, for example, be approximately 1.244.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and four clutches C4 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up the 7th grade, described the 7th grade of speed ratio γ 7 that has less than the 6th grade of speed ratio γ 6, for example, be approximately 1.000.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and three-clutch C3 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, output element 32 in the middle of being connected in first, thus set up the 8th grade, described the 8th grade of speed ratio γ 8 that has less than the 7th grade of speed ratio γ 7, for example, be approximately 0.825.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and the first break B1 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up the 9th grade, described the 9th grade has minimum speed ratio γ 9, for example, be approximately 0.649.
In addition, three-clutch C3 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 32 in the middle of first, and the second break B2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up first reverse gear " R1 ", described reverse gear " R1 " has and is approximately 3.047 speed ratio γ R1.
In addition, four clutches C4 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and the second break B2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up second reverse gear " R2 ", described reverse gear " R2 " has the speed ratio γ R2 less than the speed ratio γ R1 of first reverse gear, for example, 1.852.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 58 of gear ratio ρ 1, the second preposition planetary gear set 102 of the first preposition planetary gear set 100 and the gear ratio ρ 4 of the second rearmounted planetary gear set 60 are designed to be and can realize aforementioned speed ratio.
Obtaining in the speed changer 98 of shelves according to clutch shown in Figure 53 and brake engages figure, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.511, second grade speed ratio γ 2 is 1.481 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.351 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.167, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.133, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.244, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is 1.212, and the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of the 8th grade speed ratio γ 8 and the 9th grade is 1.271.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 9) of the speed ratio γ 9 of first grade speed ratio γ 1 and the 9th grade is 7.655, this is bigger numerical value.
In the nomogram of Figure 54, four vertical curve Y1 represent the assembly of first speed changing portion 104 to Y4.In the drawings from left to right, line Y1 represents that sun gear S2, the line Y2 of the sun gear S1 of the first preposition planetary gear set 100 that links together and the second preposition planetary gear set 102 represent that gear ring R2, the line Y3 of the second preposition planetary gear set 102 represent planet carrier CA1 and the planet carrier CA2 of the second preposition planetary gear set 102 and the gear ring R1 that line Y4 represents the first preposition planetary gear set 100 of the first preposition planetary gear set 100 that links together.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 64 to Y8.In the drawings from left to right, line Y5 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 58 of the first rotating element RE1 and the sun gear S4 of the second rearmounted planetary gear set 60, line Y6 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 58 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 60, line Y7 represents to be equivalent to the gear ring R4 of the second rearmounted planetary gear set 60 of the 3rd rotating element RE3, and line Y8 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 58 of the 4th rotating element RE4.Therefore, based on these rotating elements, therefore similar to shown in Figure 11 of the nomogram shown in Figure 54 will omit the description to it.
By this way, revise example, by engaging the 5th clutch C5 and the second break B2 sets up first grade according to the 5th of the 5th exemplary embodiment.Set up second grade by engaging the first clutch C1 and the second break B2.Set up third gear by engaging the first clutch C1 and the first break B1.Set up fourth speed by engaging first clutch C1 and three-clutch C3.Set up the 5th grade by engaging first clutch C1 and four clutches C4.Set up the 6th grade by engaging first clutch C1 and second clutch C2.Set up the 7th grade by engaging second clutch C2 and four clutches C4, and set up the 8th grade by engaging second clutch C2 and three-clutch C3.Therefore, the 5th of the 5th exemplary embodiment the speed changer 98 of revising example can be realized eight forward gearss.
The 5th of the 5th exemplary embodiment is revised the speed changer 98 of example can also realize the 9th grade by engaging the second clutch C2 and the first break B1.Therefore, except that can realizing nine forward gearss, can be with intensive speed ratio preferably set the level between the 8th grade and the 9th grade less.
Here, revise example as the 6th of the 5th exemplary embodiment, as shown in Figure 55, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 98 can obtain nine forward gearss and two reverse gears, and can obtain the effect that is equal to aforementioned exemplary embodiment.In addition, Figure 56 is and the corresponding nomogram of Figure 55 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 6th correction example of Figure 55 different with aforementioned exemplary embodiment and the 5th exemplary embodiment shown in Figure 56 be described.
As shown in clutch among Figure 55 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.The speed ratio that is used to set up the operation of friction engagement device of described shelves and described shelves with use Figure 23 described identical, so will omit giving unnecessary details to it.
In the nomogram shown in Figure 56, because the structure shown in the perspective view is identical, represent that therefore four vertical curve Y1 of the assembly of first speed changing portion 104 represent and the identical rotating element shown in above-mentioned Figure 48 to Y8 with four vertical curve Y5 of the assembly of expression second speed changing portion 64 to Y4.In addition, in clutch shown in Figure 56 and brake engages figure, it is described identical with above-mentioned use Figure 23 to the operation of the friction engagement device of the 9th grade " 9th " to be used to set up first grade " 1st ".Therefore, nomogram is also corresponding with it.Therefore, the nomogram shown in Figure 56 is identical with the nomogram shown in Figure 24.
Therefore, revise example according to the 6th of the 5th exemplary embodiment, by with different compound mode engaging clutches and break and suitably set the gear ratio of each planetary gear set, also can obtain nine forward gearss and two reverse gears, and more particularly, the level between the 8th grade and the 9th grade can preferably be set lessly with intensive speed ratio.
Here, revise example as the 7th of the 5th exemplary embodiment, as shown in Figure 57, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 98 can obtain nine forward gearss and two reverse gears.In addition, Figure 58 is and the corresponding nomogram of Figure 57 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 7th correction example of Figure 57 different with aforementioned exemplary embodiment and the 5th exemplary embodiment shown in Figure 58 be described.
As shown in clutch among Figure 57 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
In clutch shown in Figure 57 and brake engages figure, it is described identical with the above-mentioned Figure 25 of use to the operation of the friction engagement device of the 9th grade " 9th " to be used to set up first grade " 1st ", therefore with the descriptions thereof are omitted.Similarly, the speed ratio that joint obtained by those friction engagement devices in each grade is identical with shown in Figure 25 also, therefore will the descriptions thereof are omitted.
In the nomogram shown in Figure 58, four vertical curve Y1 represent the assembly of first speed changing portion 104 to Y4.In the drawings from left to right, line Y1 represents that sun gear S2, the line Y2 of the sun gear S1 of the first preposition planetary gear set 100 that links together and the second preposition planetary gear set 102 represent that gear ring R2, the line Y3 of the second preposition planetary gear set 12 represent planet carrier CA1 and the planet carrier CA2 of the second preposition planetary gear set 102 and the gear ring R1 that line Y4 represents the first preposition planetary gear set 100 of the first preposition planetary gear set 100 that links together.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 64 to Y8.In the drawings from left to right, line Y5 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 58 of the first rotating element RE1 and the sun gear S4 of the second rearmounted planetary gear set 60, line Y6 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 58 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 60, line Y7 represents to be equivalent to the gear ring R4 of the second rearmounted planetary gear set 60 of the 3rd rotating element RE3, and line Y8 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 58 of the 4th rotating element RE4.Nomogram shown in Figure 58 is similar to the nomogram shown in Figure 26, therefore omits the description to it.
By this way, revise example according to the 7th of the 5th exemplary embodiment, clutch by each grade and the combination of the joint of break (such as above-described those) and suitably set the gear ratio of each planetary gear set, can obtain to realize nine forward gearss and two reverse gears and its middle-grade level speed changer 98 for the speed ratio of comparatively dense.
Figure 59 is the perspective view of the structure of the related speed changer 122 of the present invention's the 6th exemplary embodiment.It is middle-grade and be used to set up relation between the operation of the required friction engagement device of those grades that Figure 60 shows speed changer 122.Figure 61 shows the nomogram of the rotational velocity of rotating element in each grade.Except that the structure of first speed changing portion 128, the speed changer 122 of this exemplary embodiment is similar to the speed changer 66 shown in Figure 12 in configuration aspects, the effect of the equivalence that therefore can obtain by this exemplary embodiment and be obtained from previous embodiment.Hereinafter, will the part of the speed changer 122 of this exemplary embodiment different with the part of speed changer 66 be described.
As shown in Figure 59, the first preposition planetary gear set 124 that constitutes the part of first speed changing portion 128 be comprise sun gear S1, small gear P1, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA1 of support small gear P1 and the gear ring R1 that is meshed with sun gear S1 by small gear P1.The same second preposition planetary gear set 126 that constitutes the part of first speed changing portion 128 be comprise sun gear S2, intermeshing many group small gear P2, can rotation and can revolve round the sun the planetary gear set of double pinion type of the planet carrier CA2 of support small gear P2 and the gear ring R2 that is meshed with sun gear S2 by small gear P2.
In first speed changing portion 128, the gear ring R2 of the planet carrier CA1 of the first preposition planetary gear set 124 and the second preposition planetary gear set 126 links together and is connected in the nonrotationally gearbox 16 of element of conduct integratedly, thereby prevents to rotate with respect to gearbox 16.In addition, the sun gear S1 of the first preposition planetary gear set 124 is connected in the input shaft 22 as the input rotating element integratedly.In addition, output element 32 in the middle of the sun gear S2 of the second preposition planetary gear set 126 is connected in first integratedly.In addition, the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 124 and the second preposition planetary gear set 126 links together and is connected in the second middle output element 34 integratedly.This structure causes first speed changing portion 128 by the slow down rotation that comes from the input shaft 22 and rotation of being slowed down is delivered to second speed changing portion 64 of output element 32 in the middle of first, and makes the rotations that come from input shaft 22 oppositely and with described backward rotation be delivered to second speed changing portion 64 by output element 34 in the middle of second.
In the speed changer 122 that constitutes as mentioned above, as shown in Figure 60, for example can be by engaging simultaneously from first clutch C1 in response to the instruction that comes from ECU42, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
In the nomogram shown in Figure 61, four vertical curve Y1 represent the assembly of first speed changing portion 128 to Y4.In the drawings from left to right, line Y1 represents the sun gear S1 as the first preposition planetary gear set 124 of a rotating element, line Y2 represents the sun gear S2 as the second preposition planetary gear set 126 of another rotating element, line Y3 represents to link together with the planet carrier CA1 of the first preposition planetary gear set 124 that constitutes another rotating element and the gear ring R2 of the second preposition planetary gear set 126, and line Y4 represents to link together with the gear ring R1 of the first preposition planetary gear set 124 that constitutes another rotating element and the planet carrier CA2 of the second preposition planetary gear set 126.Therefore, based on these rotating elements, the nomogram shown in Figure 61 is similar to the nomogram shown in above-mentioned Figure 14, therefore omits the description to it.
By this way, according to the 6th exemplary embodiment, first speed changing portion 128 comprises first preposition planetary gear set 124 of single small gear type and the second preposition planetary gear set 126 of double pinion type.The gear ring R2 of the planet carrier CA1 of the first preposition planetary gear set 124 and the second preposition planetary gear set 126 always is connected in the gearbox 16 as nonrotational element, and the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 124 and the second preposition planetary gear set 126 links together.In addition, the sun gear S1 of the first preposition planetary gear set 124 and as the input rotating element input shaft 22 link together.Therefore, the sun gear S2 of the second preposition planetary gear set 126 is as the first middle output element 32, and the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 124 or the second preposition planetary gear set 126 is as the second middle output element 34 simultaneously.Therefore, can provide practical speed changer 122.
Here, revise example as first of the 6th exemplary embodiment, as shown in Figure 62, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 122 can obtain ten forward gearss and two reverse gears.In addition, Figure 63 is and the corresponding nomogram of Figure 62 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the first correction example of the 6th exemplary embodiment shown in Figure 62 and 63 different with aforementioned exemplary embodiment be described.
As shown in clutch among Figure 62 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
In clutch shown in Figure 62 and brake engages figure, it is described identical with use Figure 13 to the operation of the friction engagement device of the tenth grade " 10th " to be used to set up first grade " 1st ", therefore with the descriptions thereof are omitted.
Obtaining in the speed changer 122 of shelves according to clutch shown in Figure 62 and brake engages figure, first grade speed ratio γ 1 is approximately 6.667, second grade speed ratio γ 2 is approximately 4.400, the speed ratio γ 3 of third gear is approximately 2.800, the speed ratio γ 4 of fourth speed is approximately 2.000, the 5th grade speed ratio γ 5 is approximately 1.556, the 6th grade speed ratio γ 6 is approximately 1.294, the 7th grade speed ratio γ 7 is approximately 1.000, the 8th grade speed ratio γ 8 is approximately 0.800, the 9th grade speed ratio γ 9 is approximately 0.667, the tenth grade speed ratio γ 10 is approximately 0.606, the speed ratio γ R2 that the speed ratio γ R1 of first reverse gear is approximately 4.000 and second reverse gear is approximately 2.000.In addition, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.515, second grade speed ratio γ 2 is 1.571 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.400 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.286, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.202, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.294, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is that the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of 1.250, the eight grades speed ratio γ 8 and the 9th grade is 1.200, and the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.100.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 10) of the speed ratio γ 10 of first grade speed ratio γ 1 and the tenth grade is 11.000, this is bigger numerical value.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 58 of gear ratio ρ 1, the second preposition planetary gear set 126 of the first preposition planetary gear set 124 and the gear ratio ρ 4 of the second rearmounted planetary gear set 60 are designed to be and can realize aforementioned speed ratio.
In the nomogram shown in Figure 63, four vertical curve Y1 represent the assembly of first speed changing portion 128 to Y4.In the drawings from left to right, line Y1 represents that sun gear S1, the line Y2 of the first preposition planetary gear set 124 represent that sun gear S2, the line Y3 of the second preposition planetary gear set 126 represent that the gear ring R2 of the planet carrier CA1 of the first preposition planetary gear set 124 that links together and the second preposition planetary gear set 126 and line Y4 represent the gear ring R1 of the first preposition planetary gear set 124 that links together and the planet carrier CA2 of the second preposition planetary gear set 126.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 64 to Y8.In the drawings from left to right, line Y5 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 58 of the first rotating element RE1 and the sun gear S4 of the second rearmounted planetary gear set 60, line Y6 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 58 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 60, line Y7 represents to be equivalent to the gear ring R4 of the second rearmounted planetary gear set 60 of the 3rd rotating element RE3, and line Y8 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 58 of the 4th rotating element RE4.Nomogram shown in Figure 63 is similar to the nomogram shown in Figure 14, therefore omits the description to it.
By this way, revise example according to first of the 6th exemplary embodiment, clutch by each grade and the combination of the joint of break and the gear ratio of suitably setting each planetary gear set can obtain to set up the speed changer 122 of ten forward gearss and two reverse gears, and its middle-grade level is the speed ratio of comparatively dense.
Here, revise example as second of the 6th exemplary embodiment, as shown in Figure 64, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 122 can obtain ten forward gearss and two reverse gears.In addition, Figure 65 is and the corresponding nomogram of Figure 64 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the second correction example of Figure 64 different with aforementioned exemplary embodiment and the 6th exemplary embodiment shown in Figure 65 be described.
As shown in clutch among Figure 64 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, first grade " 1st " is to the tenth grade of 10th " in any one; perhaps two reverse gears; promptly; first reverse gear " R1 " or second reverse gear " R2 ", and can obtain the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that for each grade, changes with basic identical ratio.
In clutch shown in Figure 64 and brake engages figure, it is described identical with use Figure 17 to the operation of the friction engagement device of the tenth grade " 10th " to be used to set up first grade " 1st ", therefore with the descriptions thereof are omitted.In addition, the speed ratio that joint obtained by those friction engagement devices in each grade is identical with shown in Figure 17 also, therefore will the descriptions thereof are omitted.
In the nomogram shown in Figure 65, four vertical curve Y1 represent the assembly of first speed changing portion 128 to Y4.In the drawings from left to right, line Y1 represents that planet carrier CA2, the line Y2 of the gear ring R1 of the first preposition planetary gear set 124 that links together and the second preposition planetary gear set 126 represent that the planet carrier CA1 of the first preposition planetary gear set 124 that links together and gear ring R2, the line Y3 of the second preposition planetary gear set 126 represent the sun gear S2 of the second preposition planetary gear set 126 and the sun gear S1 that line Y4 represents the first preposition planetary gear set 124.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 64 to Y8.In the drawings from left to right, line Y5 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 58 of the first rotating element RE1 and the sun gear S4 of the second rearmounted planetary gear set 60, line Y6 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 58 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 60, line Y7 represents to be equivalent to the gear ring R4 of the second rearmounted planetary gear set 60 of the 3rd rotating element RE3, and line Y8 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 58 of the 4th rotating element RE4.Nomogram shown in Figure 65 is similar to the nomogram shown in Figure 18, therefore omits the description to it.
By this way, revise example according to second of the 6th exemplary embodiment, clutch by each grade and the combination of the joint of break and suitably set the gear ratio of each planetary gear set can obtain to realize ten forward gearss and two reverse gears and its middle-grade level speed changer 122 for the speed ratio of comparatively dense.
Here, revise example as the 3rd of the 6th exemplary embodiment, as shown in Figure 66, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 122 can obtain nine forward gearss and two reverse gears.In addition, Figure 67 is and the corresponding nomogram of Figure 66 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 3rd correction example of Figure 66 different with aforementioned exemplary embodiment and the 6th exemplary embodiment shown in Figure 67 be described.
As shown in clutch among Figure 66 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
As shown in Figure 66, first clutch C1 is engaged with the 4th rotating element RE4, the i.e. sun gear S3 of the first rearmounted planetary gear set 58, be connected with output element 32 in the middle of first, and the second break B2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, is approximately 4.776.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and the first break B1 is engaged with the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 58 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up second grade, described second grade of speed ratio γ 2 that has less than first grade of speed ratio γ 1, for example, be approximately 2.925.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and three-clutch C3 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 32 in the middle of first, thereby the third gear of foundation, described third gear has the speed ratio γ 3 less than second grade of speed ratio γ 2, for example, be approximately 2.000.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and four clutches C4 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up fourth speed, described fourth speed has the speed ratio γ 4 less than third gear speed ratio γ 3, for example, be approximately 1.519.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up the 5th grade, described the 5th grade of speed ratio γ 5 that has less than fourth speed speed ratio γ 4, for example, be approximately 1.265.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and four clutches C4 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up the 6th grade, described the 6th grade of speed ratio γ 6 that has less than the 5th grade of speed ratio γ 5, for example, be approximately 1.000.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and three-clutch C3 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 32 in the middle of first, thereby set up the 7th grade, described the 7th grade of speed ratio γ 7 that has less than the 6th grade of speed ratio γ 6, for example, be approximately 0.800.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and the first break B1 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up the 8th grade, described the 8th grade of speed ratio γ 8 that has less than the 7th grade of speed ratio γ 7, for example, be approximately 0.667.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and the 5th clutch C5 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 34 in the middle of second, thereby set up the 9th grade, described the 9th grade has minimum speed ratio γ 9, for example, be approximately 0.588.
In addition, three-clutch C3 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 32 in the middle of first, and the second break B2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up first reverse gear " R1 ", described reverse gear " R1 " has and is approximately 4.000 speed ratio γ R1.
In addition, four clutches C4 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and the second break B2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up second reverse gear " R2 ", described reverse gear " R2 " has the speed ratio γ R2 less than the speed ratio γ R1 of first reverse gear, for example, 2.000.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 58 of gear ratio ρ 1, the second preposition planetary gear set 126 of the first preposition planetary gear set 124 and the gear ratio ρ 4 of the second rearmounted planetary gear set 60 are designed to be and can realize aforementioned speed ratio.
Obtaining in the speed changer 122 of shelves according to clutch shown in Figure 66 and brake engages figure, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.633, second grade speed ratio γ 2 is 1.463 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.316 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.201, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.265, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.250, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is 1.200, and the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of the 8th grade speed ratio γ 8 and the 9th grade is 1.133.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 9) of the speed ratio γ 9 of first grade speed ratio γ 1 and the 9th grade is 8.119, this is bigger numerical value.
In the nomogram shown in Figure 67, four vertical curve Y1 represent the assembly of first speed changing portion 128 to Y4.In the drawings from left to right, line Y1 represents that planet carrier CA2, the line Y2 of the gear ring R1 of the first preposition planetary gear set 124 that links together and the second preposition planetary gear set 126 represent that the planet carrier CA1 of the first preposition planetary gear set 124 that links together and gear ring R2, the line Y3 of the second preposition planetary gear set 126 represent the sun gear S2 of the second preposition planetary gear set 126 and the sun gear S1 that line Y4 represents the first preposition planetary gear set 124.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 64 to Y8.In the drawings from left to right, line Y5 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 58 of the first rotating element RE1 and the sun gear S4 of the second rearmounted planetary gear set 60, line Y6 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 58 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 60, line Y7 represents to be equivalent to the gear ring R4 of the second rearmounted planetary gear set 60 of the 3rd rotating element RE3, and line Y8 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 58 of the 4th rotating element RE4.Therefore, based on these rotating elements, therefore similar to shown in Fig. 9 of the nomogram shown in Figure 67 will omit the description to it.
By this way, revise example, set up first grade by engaging the first clutch C1 and the second break B2 according to the 3rd of the 6th exemplary embodiment.Set up second grade by engaging the first clutch C1 and the first break B1.Set up third gear by engaging first clutch C1 and three-clutch C3.Set up fourth speed by engaging first clutch C1 and four clutches C4.Set up the 5th grade by engaging first clutch C1 and second clutch C2.Set up the 6th grade by engaging second clutch C2 and four clutches C4.Set up the 7th grade by engaging second clutch C2 and three-clutch C3, and set up the 8th grade by engaging the second clutch C2 and the first break B1.Therefore, the 3rd of the 6th exemplary embodiment the speed changer 122 of revising example can be realized eight forward gearss.
The 3rd of the 6th exemplary embodiment is revised the speed changer 122 of example can also realize the 9th grade by engaging second clutch C2 and the 5th clutch C5.Therefore, except that can realizing nine forward gearss, can be with intensive speed ratio preferably set the level between the 8th grade and the 9th grade less.
Here, revise example as the 4th of the 6th exemplary embodiment, as shown in Figure 68, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 122 can obtain nine forward gearss and two reverse gears.In addition, Figure 69 is and the corresponding nomogram of Figure 68 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 4th correction example of Figure 68 different with aforementioned exemplary embodiment and the 6th exemplary embodiment shown in Figure 69 be described.
As shown in clutch among Figure 68 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
As shown in Figure 68, the 5th clutch C5 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 34 in the middle of second, and the second break B2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, be approximately 4.971.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up second grade, described second grade of speed ratio γ 2 that has less than first grade of speed ratio γ 1, for example, be approximately 3.290.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and the first break B1 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby the third gear of foundation, described third gear has the speed ratio γ 3 less than second grade of speed ratio γ 2, for example, be approximately 2.222.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and three-clutch C3 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 32 in the middle of first, thereby set up fourth speed, described fourth speed has the speed ratio γ 4 less than third gear speed ratio γ 3, for example, be approximately 1.645.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and four clutches C4 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up the 5th grade, described the 5th grade of speed ratio γ 5 that has less than fourth speed speed ratio γ 4, for example, be approximately 1.409.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S3 of the first rearmounted planetary gear set 58 be connected with the first centre output element 32, and second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up the 6th grade, described the 6th grade of speed ratio γ 6 that has less than the 5th grade of speed ratio γ 5, for example, be approximately 1.244.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and four clutches C4 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, thereby set up the 7th grade, described the 7th grade of speed ratio γ 7 that has less than the 6th grade of speed ratio γ 6, for example, be approximately 1.000.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and three-clutch C3 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, output element 32 in the middle of being connected in first, thus set up the 8th grade, described the 8th grade of speed ratio γ 8 that has less than the 7th grade of speed ratio γ 7, for example, be approximately 0.825.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and the first break B1 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up the 9th grade, described the 9th grade has minimum speed ratio γ 9, for example, be approximately 0.649.
In addition, three-clutch C3 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with output element 32 in the middle of first, and the second break B2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up first reverse gear " R1 ", described reverse gear " R1 " has and is approximately 3.047 speed ratio γ R1.
In addition, four clutches C4 is engaged with the first rotating element RE1, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 58 that links together and the sun gear S4 of the second rearmounted planetary gear set 60, be connected with input shaft 22, and the second break B2 is engaged with the second rotating element RE2, promptly, the gear ring R3 of the first rearmounted planetary gear set 58 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 60, remain in gearbox 16, thereby set up second reverse gear " R2 ", described reverse gear " R2 " has the speed ratio γ R2 less than the speed ratio γ R1 of first reverse gear, for example, 1.852.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 58 of gear ratio ρ 1, the second preposition planetary gear set 126 of the first preposition planetary gear set 124 and the gear ratio ρ 4 of the second rearmounted planetary gear set 60 are designed to be and can realize aforementioned speed ratio.
Obtaining in the speed changer 122 of shelves according to clutch shown in Figure 68 and brake engages figure, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.511, second grade speed ratio γ 2 is 1.481 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.351 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.167, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.133, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.244, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is 1.212, and the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of the 8th grade speed ratio γ 8 and the 9th grade is 1.271.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 9) of the speed ratio γ 9 of first grade speed ratio γ 1 and the 9th grade is 7.655, this is bigger numerical value.
In the nomogram shown in Figure 69, four vertical curve Y1 represent the assembly of first speed changing portion 128 to Y4.In the drawings from left to right, line Y1 represents that planet carrier CA2, the line Y2 of the gear ring R1 of the first preposition planetary gear set 124 that links together and the second preposition planetary gear set 126 represent that the planet carrier CA1 of the first preposition planetary gear set 124 that links together and gear ring R2, the line Y3 of the second preposition planetary gear set 126 represent the sun gear S2 of the second preposition planetary gear set 126 and the sun gear S1 that line Y4 represents the first preposition planetary gear set 124.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 64 to Y8.In the drawings from left to right, line Y5 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 58 of the first rotating element RE1 and the sun gear S4 of the second rearmounted planetary gear set 60, line Y6 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 58 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 60, line Y7 represents to be equivalent to the gear ring R4 of the second rearmounted planetary gear set 60 of the 3rd rotating element RE3, and line Y8 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 58 of the 4th rotating element RE4.Therefore, based on these rotating elements, therefore similar to shown in Figure 11 of the nomogram shown in Figure 69 will omit the description to it.
By this way, revise example, by engaging the 5th clutch C5 and the second break B2 sets up first grade according to the 4th of the 6th exemplary embodiment.Set up second grade by engaging the first clutch C1 and the second break B2.Set up third gear by engaging the first clutch C1 and the first break B1.Set up fourth speed by engaging first clutch C1 and three-clutch C3.Set up the 5th grade by engaging first clutch C1 and four clutches C4.Set up the 6th grade by engaging first clutch C1 and second clutch C2.Set up the 7th grade by engaging second clutch C2 and four clutches C4, and set up the 8th grade by engaging second clutch C2 and three-clutch C3.Therefore, the 4th of the 6th exemplary embodiment the speed changer 122 of revising example can be realized eight forward gearss.
The 4th of the 6th exemplary embodiment is revised the speed changer 122 of example can also realize the 9th grade by engaging the second clutch C2 and the first break B1.Therefore, except that can realizing nine forward gearss, can be with intensive speed ratio preferably set the level between the 8th grade and the 9th grade less.
Here, revise example as the 5th of the 6th exemplary embodiment, as shown in Figure 70, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 122 can obtain nine forward gearss and two reverse gears, and can obtain the effect that is equal to aforementioned exemplary embodiment.In addition, Figure 71 is and the corresponding nomogram of Figure 70 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 5th correction example of Figure 70 different with aforementioned exemplary embodiment and the 6th exemplary embodiment shown in Figure 71 be described.
As shown in clutch among Figure 70 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.The speed ratio that is used to set up the operation of friction engagement device of described shelves and described shelves with use Figure 23 described identical, so will omit giving unnecessary details to it.
In the nomogram shown in Figure 71, because the structure shown in the perspective view is identical, represent that therefore four vertical curve Y1 of the assembly of first speed changing portion 128 represent and the identical rotating element shown in above-mentioned Figure 65 to Y8 with four vertical curve Y5 of the assembly of expression second speed changing portion 64 to Y4.In addition, in clutch shown in Figure 70 and brake engages figure, it is described identical with above-mentioned use Figure 23 to the operation of the friction engagement device of the 9th grade " 9th " to be used to set up first grade " 1st ".Therefore, nomogram is also corresponding with it.Therefore, the nomogram among Figure 71 is identical with the nomogram shown in Figure 24.
Therefore, revise example according to the 5th of the 6th exemplary embodiment, by with different compound mode engaging clutches and break and suitably set the gear ratio of each planetary gear set, also can obtain nine forward gearss and two reverse gears, and more particularly, the level between the 8th grade and the 9th grade can be set lessly with intensive speed ratio.
Here, revise example as the 6th of the 6th exemplary embodiment, as shown in Figure 72, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 122 can obtain nine forward gearss and two reverse gears, and can obtain the effect that is equal to aforementioned exemplary embodiment.In addition, Figure 73 is and the corresponding nomogram of Figure 72 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 6th correction example of Figure 72 different with aforementioned exemplary embodiment and the 6th exemplary embodiment shown in Figure 73 be described.
As shown in clutch among Figure 72 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.The speed ratio that is used to set up the operation of friction engagement device of described shelves and described shelves with use Figure 25 described identical, so will omit giving unnecessary details to it.
In the nomogram shown in Figure 73, because the structure shown in the perspective view is identical, represent that therefore four vertical curve Y1 of the assembly of first speed changing portion 128 represent and the identical rotating element shown in above-mentioned Figure 65 to Y8 with four vertical curve Y5 of the assembly of expression second speed changing portion 64 to Y4.In addition, in clutch shown in Figure 72 and brake engages figure, it is described identical with above-mentioned use Figure 25 to the operation of the friction engagement device of the 9th grade " 9th " to be used to set up first grade " 1st ".Therefore, nomogram is also corresponding with it.Therefore, the nomogram among Figure 73 is identical with the nomogram shown in Figure 26.
Therefore, revise example according to the 6th of the 6th exemplary embodiment, by with different compound mode engaging clutches and break and suitably set the gear ratio of each planetary gear set, also can obtain nine forward gearss and two reverse gears, and more particularly, the level between the 8th grade and the 9th grade can be set lessly with intensive speed ratio.
Figure 74 is the perspective view of the structure of the related speed changer 138 of the present invention's the 7th exemplary embodiment.It is middle-grade and be used to set up the figure of the relation between the operation of the required friction engagement device of those grades that Figure 75 shows speed changer 138.Figure 78 shows the nomogram of the rotational velocity of rotating element in each grade.Except that the structure of first speed changing portion 144, the speed changer 138 of this exemplary embodiment is similar to the speed changer 44 shown in Fig. 5 in configuration aspects, the effect of the equivalence that therefore can obtain by this exemplary embodiment and be obtained from previous embodiment.Hereinafter, will the part of the speed changer 138 of this exemplary embodiment different with the part of speed changer 44 be described.
As shown in Figure 74, the first preposition planetary gear set 140 that constitutes the part of first speed changing portion 144 be comprise sun gear S1, small gear P1, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA1 of support small gear P1 and the gear ring R1 that is meshed with sun gear S1 by small gear P1.The same second preposition planetary gear set 142 that constitutes the part of first speed changing portion 144 be comprise sun gear S2, intermeshing many group small gear P2, can rotation and can revolve round the sun the planetary gear set of double pinion type of the planet carrier CA2 of support small gear P2 and the gear ring R2 that is meshed with sun gear S2 by small gear P2.
In first speed changing portion 144, the sun gear S2 of the planet carrier CA1 of the first preposition planetary gear set 140 and the second preposition planetary gear set 142 links together and is connected in the nonrotationally gearbox 16 of element of conduct integratedly, thereby prevents to rotate with respect to gearbox 16.In addition, the second clutch C2 of the sun gear S1 of the first preposition planetary gear set 140 and the second preposition planetary gear set 142 links together and is connected in integratedly as the input shaft 22 of importing rotating element.In addition, output element 32 in the middle of the gear ring R2 of the second preposition planetary gear set 142 is connected in first integratedly.In addition, output element 34 in the middle of the gear ring R1 of the first preposition planetary gear set 140 is connected in second integratedly.This structure causes first speed changing portion 144 by the slow down rotation that comes from the input shaft 22 and rotation of being slowed down is delivered to second speed changing portion 50 of output element 32 in the middle of first, and makes the rotations that come from input shaft 22 oppositely and with described backward rotation be delivered to second speed changing portion 50 by output element 34 in the middle of second.
In the speed changer 138 that constitutes as mentioned above, as shown in Figure 75, for example can be by engaging simultaneously from first clutch C1 in response to the instruction that comes from ECU42, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
Obtaining in the speed changer 138 of shelves according to clutch shown in Figure 75 and brake engages figure, first grade speed ratio γ 1 is approximately 4.762, second grade speed ratio γ 2 is approximately 4.110, the speed ratio γ 3 of third gear is approximately 2.603, the speed ratio γ 4 of fourth speed is approximately 2.000, the 5th grade speed ratio γ 5 is approximately 1.624, the 6th grade speed ratio γ 6 is approximately 1.322, the 7th grade speed ratio γ 7 is approximately 1.000, the 8th grade speed ratio γ 8 is approximately 0.833, the 9th grade speed ratio γ 9 is approximately 0.714, the tenth grade speed ratio γ 10 is approximately 0.621, the speed ratio γ R2 that the speed ratio γ R1 of first reverse gear is approximately 5.000 and second reverse gear is approximately 2.500.In addition, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.159, second grade speed ratio γ 2 is 1.579 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.301 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.232, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.229, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.322, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is that the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of 1.200, the eight grades speed ratio γ 8 and the 9th grade is 1.167, and the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.150.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 10) of the speed ratio γ 10 of first grade speed ratio γ 1 and the tenth grade is 7.667, this is bigger numerical value.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 46 of gear ratio ρ 1, the second preposition planetary gear set 142 of the first preposition planetary gear set 140 and the gear ratio ρ 4 of the second rearmounted planetary gear set 48 are designed to be and can realize aforementioned speed ratio.
Revise example as first of the 7th exemplary embodiment, do not change, can obtain those grades shown in Figure 76 by the gear ratio ρ 1 to ρ 4 that suitably sets planetary gear set although be used for the bonding operation of each grade.Obtaining in the speed changer 138 of shelves according to clutch shown in Figure 76 and brake engages figure, first grade speed ratio γ 1 is approximately 4.971, second grade speed ratio γ 2 is approximately 3.290, the speed ratio γ 3 of third gear is approximately 2.222, the speed ratio γ 4 of fourth speed is approximately 1.645, the 5th grade speed ratio γ 5 is approximately 1.409, the 6th grade speed ratio γ 6 is approximately 1.244, the 7th grade speed ratio γ 7 is approximately 1.000, the 8th grade speed ratio γ 8 is approximately 0.825, the 9th grade speed ratio γ 9 is approximately 0.649, the tenth grade speed ratio γ 10 is approximately 0.574, the speed ratio γ R2 that the speed ratio γ R1 of first reverse gear is approximately 3.047 and second reverse gear is approximately 1.852.In addition, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.511, second grade speed ratio γ 2 is 1.481 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.351 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.167, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.133, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.244, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is that the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of 1.212, the eight grades speed ratio γ 8 and the 9th grade is 1.271, and the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.131.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 10) of the speed ratio γ 10 of first grade speed ratio γ 1 and the tenth grade is 8.655, this is bigger numerical value.By suitably setting the gear ratio of each planetary gear set by this way, the overall ratio scope can be set than the overall ratio wide ranges shown in Figure 75.
And, revise example as second of the 7th exemplary embodiment, speed changer 138 also can obtain to have the shelves of the speed ratio shown in Figure 77.Obtaining in the speed changer 138 of shelves according to clutch shown in Figure 77 and brake engages figure, first grade speed ratio γ 1 is approximately 6.667, second grade speed ratio γ 2 is approximately 4.400, the speed ratio γ 3 of third gear is approximately 2.800, the speed ratio γ 4 of fourth speed is approximately 2.000, the 5th grade speed ratio γ 5 is approximately 1.556, the 6th grade speed ratio γ 6 is approximately 1.294, the 7th grade speed ratio γ 7 is approximately 1.000, the 8th grade speed ratio γ 8 is approximately 0.800, the 9th grade speed ratio γ 9 is approximately 0.667, the tenth grade speed ratio γ 10 is approximately 0.606, the speed ratio γ R2 that the speed ratio γ R1 of first reverse gear is approximately 4.000 and second reverse gear is approximately 2.000.In addition, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.515, second grade speed ratio γ 2 is 1.571 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.400 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.286, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.202, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.294, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is that the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of 1.250, the eight grades speed ratio γ 8 and the 9th grade is 1.200, and the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.100.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 10) of the speed ratio γ 10 of first grade speed ratio γ 1 and the tenth grade is 11.000, this is bigger numerical value.
In the nomogram shown in Figure 78, four vertical curve Y1 represent the assembly of first speed changing portion 144 to Y4.In the drawings from left to right, line Y1 represents to link together with the sun gear S1 of the first preposition planetary gear set 140 that constitutes a rotating element and the planet carrier CA2 of the second preposition planetary gear set 142, line Y2 represents the gear ring R2 as the second preposition planetary gear set 142 of another rotating element, line Y3 represents to link together with the planet carrier CA1 of the first preposition planetary gear set 140 that constitutes another rotating element and the sun gear S2 of the second preposition planetary gear set 142, and line Y4 represents the gear ring R1 as the first preposition planetary gear set 140 of another rotating element.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 50 to Y8.In the drawings from left to right, line Y5 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 46 of the first rotating element RE1, line Y6 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 46 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 48, and line Y7 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 46 of the 3rd rotating element RE3 and the gear ring R4 of the second rearmounted planetary gear set 48, and line Y8 represents to be equivalent to the sun gear S4 of the second rearmounted planetary gear set 48 of the 4th rotating element RE4.Therefore, according to these rotating elements, the nomogram shown in Figure 78 is similar to the nomogram shown in above-mentioned Figure 14, therefore will omit the description to it.
By this way, revise example according to first and second of the 7th exemplary embodiment, first speed changing portion 144 comprises first preposition planetary gear set 140 of single small gear type and the second preposition planetary gear set 142 of double pinion type.The sun gear S2 of the planet carrier CA1 of the first preposition planetary gear set 140 and the second preposition planetary gear set 142 always is connected in the gearbox 16 as nonrotational element, and the planet carrier CA2 of the sun gear S1 of the first preposition planetary gear set 140 and the second preposition planetary gear set 142 is connected in the input shaft 22 as the input rotating element.Therefore, the gear ring R2 of the second preposition planetary gear set 142 is as the first middle output element 32, and the gear ring R1 of the first preposition planetary gear set 140 is as the second middle output element 34 simultaneously.Therefore, can provide practical speed changer 138.
Here, revise example as the 3rd of the 7th exemplary embodiment, as shown in Figure 79, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 138 can obtain ten forward gearss and two reverse gears, and can obtain the effect that is equal to aforementioned exemplary embodiment.In addition, Figure 80 is and the corresponding nomogram of Figure 79 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 3rd correction example of Figure 79 different with aforementioned exemplary embodiment and the 7th exemplary embodiment shown in Figure 80 be described.
As shown in clutch among Figure 79 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, first grade " 1st " is to the tenth grade of 10th " in any one; perhaps two reverse gears; promptly; first reverse gear " R1 " or second reverse gear " R2 ", and can obtain the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that for each grade, changes with basic identical ratio.The speed ratio that is used to set up the operation of friction engagement device of described shelves and described shelves with use Figure 17 described identical, so will omit giving unnecessary details to it.
In the nomogram shown in Figure 80, four vertical curve Y1 represent the assembly of first speed changing portion 144 to Y4.In the drawings from left to right, line Y1 represents that gear ring R1, the line Y2 of the first preposition planetary gear set 140 represent that sun gear S2, the line Y3 of the planet carrier CA1 of the first preposition planetary gear set 140 that links together and the second preposition planetary gear set 142 represent that the gear ring R2 of the second preposition planetary gear set 142 and line Y4 represent the sun gear S1 of the first preposition planetary gear set 140 that links together and the planet carrier CA2 of the second preposition planetary gear set 142.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 50 to Y8.In the drawings from left to right, line Y5 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 46 of the first rotating element RE1, line Y6 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 46 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 48, and line Y7 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 46 of the 3rd rotating element RE3 and the gear ring R4 of the second rearmounted planetary gear set 48, and line Y8 represents to be equivalent to the sun gear S4 of the second rearmounted planetary gear set 48 of the 4th rotating element RE4.Therefore, according to these rotating elements, the nomogram shown in Figure 80 is similar to the nomogram shown in above-mentioned Figure 18, therefore will omit the description to it.
By this way, revise example according to the 3rd of the 7th exemplary embodiment, by each grade with different compound mode engaging clutches and break and suitably set the gear ratio of each planetary gear set, can obtain ten forward gearss and two reverse gears, and more particularly, can set with intensive speed ratio between the 9th grade and the tenth grade the level.
Here, revise example as the 4th of the 7th exemplary embodiment, as shown in Figure 81, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 138 can obtain ten forward gearss and two reverse gears, and can obtain the effect that is equal to aforementioned exemplary embodiment.In addition, Figure 82 is and the corresponding nomogram of Figure 81 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 4th correction example of Figure 81 different with aforementioned exemplary embodiment and the 7th exemplary embodiment shown in Figure 82 be described.
As shown in clutch among Figure 81 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, first grade " 1st " is to the tenth grade of 10th " in any one; perhaps two reverse gears; promptly; first reverse gear " R1 " or second reverse gear " R2 ", and can obtain the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that for each grade, changes with basic identical ratio.
In addition, as shown in Figure 81, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 46 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gearbox 16, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, be approximately 4.596.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and the 5th clutch C5 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the second centre output element 34, thereby set up second grade, described second grade has speed ratio γ 2, for example, be approximately 4.088.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and the first break B1 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 remain in gearbox 16, thereby the third gear of foundation, described third gear has speed ratio γ 3, for example, be approximately 2.724.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the first centre output element 32, thereby set up fourth speed, described fourth speed has speed ratio γ 4, for example, be approximately 1.863.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and four clutches C4 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with input shaft 22, thereby set up the 5th grade, described the 5th grade has speed ratio γ 5, for example, be approximately 1.464.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the sun gear S4 of the second rearmounted planetary gear set 48 is connected with output element 32 in the middle of first, and second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, be connected with input shaft 22, thereby set up the 6th grade, described the 6th grade has speed ratio γ 6, for example, be approximately 1.231.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48 are connected with input shaft 22, and four clutches C4 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with input shaft 22, thereby set up the 7th grade, described the 7th grade has speed ratio γ 7, for example, is approximately 1.000.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48 are connected with input shaft 22, and three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the first centre output element 32, thereby set up the 8th grade, described the 8th grade has speed ratio γ 8, for example, is approximately 0.824.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48 are connected with input shaft 22, and the first break B1 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 remain in gearbox 16, thereby set up the 9th grade, described the 9th grade has speed ratio γ 9, for example, is approximately 0.685.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48 are connected with input shaft 22, and the 5th clutch C5 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the second centre output element 34, thereby set up the tenth grade, the described ten grade has speed ratio γ 10, for example, is approximately 0.611.
In addition, three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gearbox 16, thereby set up first reverse gear " R1 ", described reverse gear " R1 " has and is approximately 4.056 speed ratio γ R1.
In addition, four clutches C4 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with input shaft 22, and the second break B2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gearbox 16, thereby set up second reverse gear " R2 ", described reverse gear " R2 " has the speed ratio γ R2 less than the speed ratio γ R1 of first reverse gear, for example, be approximately 2.176.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 46 of gear ratio ρ 1, the second preposition planetary gear set 142 of the first preposition planetary gear set 140 and the gear ratio ρ 4 of the second rearmounted planetary gear set 48 are designed to be and can realize aforementioned speed ratio.
Obtaining in the speed changer 138 of shelves according to clutch shown in Figure 81 and brake engages figure, first grade speed ratio γ 1 is 1.688 with the ratio (=γ 1/ γ 3) of the speed ratio γ 3 of third gear, second grade speed ratio γ 2 is 1.501 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.462 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.273, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.189, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.231, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is 1.213, the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of the 8th grade speed ratio γ 8 and the 9th grade is 1.203, and the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.122.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 10) of the speed ratio γ 10 of first grade speed ratio γ 1 and the tenth grade is 7.522, this is bigger numerical value.
Because the structure shown in the perspective view is identical, represent that therefore four vertical curve Y1 of the assembly of first speed changing portion 144 represent and the identical rotating element shown in above-mentioned Figure 80 to Y8 with four vertical curve Y5 of the assembly of expression second speed changing portion 50 to Y4.
In the nomogram in Figure 82, in first grade, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (1st) expression, and (1st) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y6 and horizontal line XZ and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In second grade, the 5th clutch C5 is engaged the first rotating element RE1 being connected in output element 34 in the middle of second, and this causes rotating under the identical speed of first rotating element RE1 output element 34 in the middle of with second.Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (2nd) expression, and (2nd) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X1 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In third gear, the first break B1 is engaged so that the first rotating element RE1 is remained in gearbox 16, and this causes the rotational velocity of the first rotating element RE1 to be " 0 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (3rd) expression, and (3rd) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line XZ and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In fourth speed, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (4th) expression, and (4th) locates at point, and horizontal line X2 and vertical curve Y7 intersect.
In the 5th grade, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (5th) expression, and (5th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X3 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In the 6th grade, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (6th) expression, and (6th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y6 and horizontal line X3 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In the 7th grade, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (7th) expression, and (7th) locates at point, and horizontal line X3 and vertical curve Y7 intersect.
In the 8th grade, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (8th) expression, and (8th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X2 and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In the 9th grade, the first break B1 is engaged so that the first rotating element RE1 is remained in gearbox 16, and this causes the rotational velocity of the first rotating element RE1 to be " 0 ".Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (9th) expression, and (9th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line XZ and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In the tenth grade, the 5th clutch C5 is engaged the first rotating element RE1 being connected in output element 34 in the middle of second, and this causes rotating under the identical speed of first rotating element RE1 output element 34 in the middle of with second.Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (10th) expression, and (10th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X1 and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In first reverse gear, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (Rev1) expression, and (Rev1) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X2 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
In second reverse gear, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (Rev2) expression, and (Rev2) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X3 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
By this way, revise example according to the 4th of the 7th exemplary embodiment, clutch by engaging each grade with different compound modes and break (such as above-described) and suitably set the gear ratio of each planetary gear set, can obtain to set up the speed changer 138 of ten forward gearss and two reverse gears, the level of wherein said shelves has intensive speed ratio.
In addition, when the idling speed of motor increases, such as when motor is colder or when travelling on low friction road (driving force when preferably reduce to start to walk this moment), in first grade of meeting as bottom gear adverse effect (increase of the power of creeping during such as starting or the sensation of travelling obliquely suddenly) appears.Therefore, as in this exemplary embodiment, can make the optimized speed ratio of the power of creeping by second grade is set to, and optionally make vehicle, can be suppressed at during the starting vehicle suddenly banking (swing) and slide from second grade of starting.
Here, revise example as the 5th of the 7th exemplary embodiment, as shown in Figure 83, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 138 can obtain ten forward gearss and two reverse gears, and can obtain and the effect that is equal to that is obtained from aforementioned exemplary embodiment.In addition, Figure 84 is and the corresponding nomogram of Figure 83 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 5th correction example of Figure 83 different with aforementioned exemplary embodiment and the 7th exemplary embodiment shown in Figure 84 be described.
As shown in clutch among Figure 83 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.The speed ratio that is used to set up the operation of friction engagement device of described shelves and described shelves with use Figure 23 described identical, so will omit giving unnecessary details to it.
In the nomogram shown in Figure 84, because the structure shown in the perspective view is identical, represent that therefore four vertical curve Y1 of the assembly of first speed changing portion 144 represent and the identical rotating element shown in above-mentioned Figure 80 to Y8 with four vertical curve Y5 of the assembly of expression second speed changing portion 50 to Y4.In addition, in clutch shown in Figure 83 and brake engages figure, it is described identical with above-mentioned use Figure 23 to the operation of the friction engagement device of the 9th grade " 9th " to be used to set up first grade " 1st ".Therefore, based on described rotating element, nomogram is also corresponding with it.Therefore, the nomogram among Figure 84 is identical with the nomogram shown in Figure 24.
Therefore, revise example according to the 5th of the 7th exemplary embodiment, by with different compound mode engaging clutches and break and suitably set the gear ratio of each planetary gear set, also can obtain nine forward gearss and two reverse gears, and more particularly, the level between the 8th grade and the 9th grade can be set lessly with intensive speed ratio.
Here, revise example as the 6th of the 7th exemplary embodiment, as shown in Figure 85, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 138 can obtain ten forward gearss and two reverse gears.In addition, Figure 86 is and the corresponding nomogram of Figure 85 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 6th correction example of Figure 85 different with aforementioned exemplary embodiment and the 7th exemplary embodiment shown in Figure 86 be described.
As shown in clutch among Figure 85 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.The speed ratio that is used to set up the operation of friction engagement device of described shelves and described shelves with use Figure 25 described identical, so will omit giving unnecessary details to it.
In the nomogram shown in Figure 86, because the structure shown in the perspective view is identical, represent that therefore four vertical curve Y1 of the assembly of first speed changing portion 144 represent and the identical rotating element shown in above-mentioned Figure 80 to Y8 with four vertical curve Y5 of the assembly of expression second speed changing portion 50 to Y4.In addition, in clutch shown in Figure 85 and brake engages figure, it is described identical with above-mentioned use Figure 25 to the operation of the friction engagement device of the 9th grade " 9th " to be used to set up first grade " 1st ".Therefore, based on described rotating element, nomogram is also corresponding with it.Therefore, the nomogram shown in Figure 86 is identical with the nomogram shown in Figure 26.
Therefore, revise example according to the 6th of the 7th exemplary embodiment, by with different compound mode engaging clutches and break and suitably set the gear ratio of each planetary gear set, also can obtain nine forward gearss and two reverse gears, and more particularly, the level between the 8th grade and the 9th grade can be set lessly with intensive speed ratio.
Here, revise example as the 7th of the 7th exemplary embodiment, as shown in Figure 87, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 138 can obtain nine forward gearss and two reverse gears.In addition, Figure 88 is and the corresponding nomogram of Figure 87 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 7th correction example of Figure 87 different with aforementioned exemplary embodiment and the 7th exemplary embodiment shown in Figure 88 be described.
As shown in clutch among Figure 87 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
As shown in Figure 87, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gearbox 16, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, be approximately 4.596.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and the first break B1 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 remain in gearbox 16, thereby set up second grade, described second grade has speed ratio γ 2, for example, be approximately 2.724.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the first centre output element 32, thereby the third gear of foundation, described third gear has speed ratio γ 3, for example, be approximately 1.863.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and four clutches C4 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with input shaft 22, thereby set up fourth speed, described fourth speed has speed ratio γ 4, for example, be approximately 1.464.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and second clutch C2 is engaged with the second rotating element RE2 promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, be connected with input shaft 22, thereby set up the 5th grade, described the 5th grade has speed ratio γ 5, for example, be approximately 1.231.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48 are connected with input shaft 22, and four clutches C4 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with input shaft 22, thereby set up the 6th grade, described the 6th grade has speed ratio γ 6, for example, is approximately 1.000.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48 are connected with input shaft 22, and three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the first centre output element 32, thereby set up the 7th grade, described the 7th grade has speed ratio γ 7, for example, is approximately 0.824.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48 are connected with input shaft 22, and the first break B1 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 remain in gearbox 16, thereby set up the 8th grade, described the 8th grade has speed ratio γ 8, for example, is approximately 0.685.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48 are connected with input shaft 22, and the 5th clutch C5 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the second centre output element 34, thereby set up the 9th grade, described the 9th grade has speed ratio γ 9, for example, is approximately 0.598.
In addition, three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gearbox 16, thereby set up first reverse gear " R1 ", described reverse gear " R1 " has and is approximately 4.056 speed ratio γ R1.
In addition, four clutches C4 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with input shaft 22, and the second break B2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gearbox 16, thereby set up second reverse gear " R2 ", described reverse gear " R2 " has the speed ratio γ R2 less than the speed ratio γ R1 of first reverse gear, for example, be approximately 2.176.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 46 of gear ratio ρ 1, the second preposition planetary gear set 142 of the first preposition planetary gear set 140 and the gear ratio ρ 4 of the second rearmounted planetary gear set 48 are designed to be and can realize aforementioned speed ratio.
Obtaining in the speed changer 138 of shelves according to clutch shown in Figure 87 and brake engages figure, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.688, second grade speed ratio γ 2 is 1.462 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.273 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.189, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.231, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.213, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is 1.203, and the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of the 8th grade speed ratio γ 8 and the 9th grade is 1.146.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 9) of the speed ratio γ 9 of first grade speed ratio γ 1 and the 9th grade is 7.686, this is bigger numerical value.
In the nomogram shown in Figure 88, because the structure shown in the perspective view is identical, represent that therefore four vertical curve Y1 of the assembly of first speed changing portion 144 represent and the identical rotating element shown in above-mentioned Figure 80 to Y8 with four vertical curve Y5 of the assembly of expression second speed changing portion 50 to Y4.
In the nomogram in Figure 88, in first grade, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (1st) expression, and (1st) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y6 and horizontal line XZ and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In second grade, the first break B1 is engaged so that the first rotating element RE1 is remained in gearbox 16, and this causes the rotational velocity of the first rotating element RE1 to be " 0 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (2nd) expression, and (2nd) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line XZ and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In third gear, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (3rd) expression, and (3rd) locates at point, and horizontal line X2 and vertical curve Y7 intersect.
In fourth speed, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (4th) expression, and (4th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X3 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In the 5th grade, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (5th) expression, and (5th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y6 and horizontal line X3 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In the 6th grade, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (6th) expression, and (6th) locates at point, and horizontal line X3 and vertical curve Y7 intersect.
In the 7th grade, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (7th) expression, and (7th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X2 and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In the 8th grade, the first break B1 is engaged so that the first rotating element RE1 is remained in gearbox 16, and this causes the rotational velocity of the first rotating element RE1 to be " 0 ".Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (8th) expression, and (8th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line XZ and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In the 9th grade, the 5th clutch C5 is engaged the first rotating element RE1 being connected in output element 34 in the middle of second, and this causes rotating under the identical speed of first rotating element RE1 output element 34 in the middle of with second.Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (9th) expression, and (9th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X1 and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In first reverse gear, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (Rev1) expression, and (Rev1) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X2 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
In second reverse gear, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (Rev2) expression, and (Rev2) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X3 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
By this way, revise example according to the 7th of the 7th exemplary embodiment, clutch by engaging each grade with different compound modes and break (such as above-described) and suitably set the gear ratio of each planetary gear set, can obtain to set up the speed changer 138 of nine forward gearss and two reverse gears, the level of wherein said shelves has intensive speed ratio.
Here, revise example as the 8th of the 7th exemplary embodiment, as shown in Figure 89, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 138 can obtain 11 forward gearss and two reverse gears.In addition, Figure 90 is and the corresponding nomogram of Figure 89 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 8th correction example of Figure 89 different with aforementioned exemplary embodiment and the 7th exemplary embodiment shown in Figure 90 be described.
As shown in clutch among Figure 89 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up 11 forward gearss, promptly, in first grade " 1st " to the 11 grade " 11th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
In addition, as shown in Figure 89, the 5th clutch C5 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the second centre output element 34, and the second break B2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gearbox 16, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, be approximately 5.298.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gearbox 16, thereby set up second grade, described second grade has and for example is approximately 3.841 speed ratio γ 2.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and the 5th clutch C5 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the second centre output element 34, thereby the third gear of foundation, described third gear has speed ratio γ 3, for example, be approximately 3.233.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and the first break B1 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 remain in gearbox 16, thereby set up fourth speed, described fourth speed has speed ratio γ 4, for example, be approximately 2.280.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the first centre output element 32, thereby set up the 5th grade, described the 5th grade has speed ratio γ 5, for example, be approximately 1.714.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and four clutches C4 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with input shaft 22, thereby set up the 6th grade, described the 6th grade has speed ratio γ 6, for example, be approximately 1.456.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and second clutch C2 is engaged with the second rotating element RE2, that is, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48 are connected with input shaft 22, thereby set up the 7th grade, described the 7th grade has speed ratio γ 7, for example, is approximately 1.228.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48 are connected with input shaft 22, and four clutches C4 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with input shaft 22, thereby set up the 8th grade, described the 8th grade has speed ratio γ 8, for example, is approximately 1.000.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48 are connected with input shaft 22, and three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the first centre output element 32, thereby set up the 9th grade, described the 9th grade has speed ratio γ 9, for example, is approximately 0.869.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48 are connected with input shaft 22, and the first break B1 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 remain in gearbox 16, thereby set up the tenth grade, the described ten grade has speed ratio γ 10, for example, is approximately 0.734.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, be connected with input shaft 22, and the 5th clutch C5 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the second centre output element 34, thereby set up the 11 grade, described the 11 grade has speed ratio γ 11, for example, be approximately 0.645.
In addition, three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gearbox 16, thereby set up first reverse gear " R1 ", described reverse gear " R1 " has and is approximately 10.194 speed ratio γ R1.
In addition, four clutches C4 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with input shaft 22, and the second break B2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gearbox 16, thereby set up second reverse gear " R2 ", described reverse gear " R2 " has the speed ratio γ R2 less than the speed ratio γ R1 of first reverse gear, for example, be approximately 5.375.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 46 of gear ratio ρ 1, the second preposition planetary gear set 142 of the first preposition planetary gear set 140 and the gear ratio ρ 4 of the second rearmounted planetary gear set 48 are designed to be and can realize aforementioned speed ratio.
Obtaining in the speed changer 138 of shelves according to clutch shown in Figure 89 and brake engages figure, first grade speed ratio γ 1 is 1.639 with the ratio (=γ 1/ γ 3) of the speed ratio γ 3 of third gear, second grade speed ratio γ 2 is 1.685 with the ratio (=γ 2/ γ 4) of the speed ratio γ 4 of fourth speed, the speed ratio γ 3 of third gear is 1.418 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.330, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.177, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.185, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is 1.228, the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of the 8th grade speed ratio γ 8 and the 9th grade is 1.151, the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.184, and the ratio (=γ 10/ γ 11) of the speed ratio γ 11 of the tenth grade speed ratio γ 10 and the 11 grade is 1.139.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio of first grade speed ratio γ 1 and the 11 grade speed ratio γ 11 (=γ 1/ γ 11) is 8.124.
In the nomogram in Figure 90, because the structure shown in the perspective view is identical, represent that therefore four vertical curve Y1 of the assembly of first speed changing portion 144 represent and the identical rotating element shown in Figure 80 to Y8 with four vertical curve Y5 of the assembly of expression second speed changing portion 50 to Y4.
In the nomogram in Figure 90, in first grade, the 5th clutch C5 is engaged the first rotating element RE1 being connected in output element 34 in the middle of second, and this causes rotating under the identical speed of first rotating element RE1 output element 34 in the middle of with second.Simultaneously, the second break B2 is engaged the second rotating element RE2 is remained in the gearbox 16 as nonrotational element, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (1st) expression, and (1st) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X1 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
In second grade, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (2nd) expression, and (2nd) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y6 and horizontal line XZ and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In third gear, the 5th clutch C5 is engaged the first rotating element RE1 being connected in output element 34 in the middle of second, and this causes rotating under the identical speed of first rotating element RE1 output element 34 in the middle of with second.Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (3rd) expression, and (3rd) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X1 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In fourth speed, the first break B1 is engaged so that the first rotating element RE1 is remained in gearbox 16, and this causes the rotational velocity of the first rotating element RE1 to be " 0 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (4th) expression, and (4th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line XZ and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In the 5th grade, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (5th) expression, and (5th) locates at point, and horizontal line X2 and vertical curve Y7 intersect.
In the 6th grade, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (6th) expression, and (6th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X3 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In the 7th grade, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (7th) expression, and (7th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y6 and horizontal line X3 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In the 8th grade, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (8th) expression, and (8th) locates at point, and horizontal line X3 and vertical curve Y7 intersect.
In the 9th grade, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (9th) expression, and (9th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X2 and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In the tenth grade, the first break B1 is engaged so that the first rotating element RE1 is remained in gearbox 16, and this causes the rotational velocity of the first rotating element RE1 to be " 0 ".Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (10th) expression, and (10th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line XZ and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In the 11 grade, the 5th clutch C5 is engaged the first rotating element RE1 being connected in output element 34 in the middle of second, and this causes rotating under the identical speed of first rotating element RE1 output element 34 in the middle of with second.Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (11th) expression, and (11th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X1 and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In first reverse gear, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (Rev1) expression, and (Rev1) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X2 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
In second reverse gear, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (Rev2) expression, and (Rev2) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X3 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
By this way, revise example according to the 8th of the 7th exemplary embodiment, clutch by engaging each grade with different compound modes and break (such as above-described) and suitably set the gear ratio of each planetary gear set, can obtain to set up the speed changer 138 of 11 forward gearss and two reverse gears, the level of wherein said shelves is the speed ratio of comparatively dense.
And, revise example according to the 8th of the 7th exemplary embodiment, can set level between level and second grade and the fourth speed between first grade and the third gear with good balance, described grade can according to circumstances suitably be used these jump gear shift.For example, requiring under the motor pattern of power performance, can use jump gear shift from first grade to third gear.On the other hand, when expectation suppresses to creep feature, can use jump gear shift from second grade to fourth speed.
Figure 91 is the perspective view of the structure of the related speed changer 146 of the present invention's the 8th exemplary embodiment.Figure 92 shows the shelves in the speed changer 146 and is used to set up the figure of the relation between the operation of the required friction engagement device of those grades.Figure 94 shows the nomogram of the rotational velocity of rotating element in each grade.Except that the structure of first speed changing portion 152, the speed changer 146 of this exemplary embodiment is similar to the speed changer 44 shown in Fig. 5 in configuration aspects, the effect of the equivalence that therefore can obtain by this exemplary embodiment and be obtained from previous embodiment.Hereinafter, will the part of the speed changer 146 of this exemplary embodiment different with the part of speed changer 44 be described.
As shown in Figure 91, the first preposition planetary gear set 148 that constitutes the part of first speed changing portion 152 be comprise sun gear S1, intermeshing many group small gear P1, can rotation and can revolve round the sun the planetary gear set of double pinion type of the planet carrier CA1 of support small gear P1 and the gear ring R1 that is meshed with sun gear S1 by small gear P1.The same second preposition planetary gear set 150 that constitutes the part of first speed changing portion 152 be comprise sun gear S2, small gear P2, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA2 of support small gear P2 and the gear ring R2 that is meshed with sun gear S2 by small gear P2.
In first speed changing portion 152, the sun gear S1 of the first preposition planetary gear set 148 is connected in the gearbox 16 as nonrotational element integratedly, thereby prevents to rotate with respect to gearbox 16.In addition, the gear ring R2 of the planet carrier CA1 of the first preposition planetary gear set 148 and the second preposition planetary gear set 150 links together and is connected in integratedly as the input shaft 22 of importing rotating element.In addition, the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 148 and the second preposition planetary gear set 150 links together and is connected in the first middle output element 32 integratedly.In addition, output element 34 in the middle of the sun gear S2 of the second preposition planetary gear set 150 is connected in second integratedly.This structure causes first speed changing portion 152 by the slow down rotation that comes from the input shaft 22 and rotation of being slowed down is delivered to second speed changing portion 50 of output element 32 in the middle of first, and makes the rotations that come from input shaft 22 oppositely and with described backward rotation be delivered to second speed changing portion 50 by output element 34 in the middle of second.
In the speed changer 146 that constitutes as mentioned above, as shown in Figure 92, for example can be by engaging simultaneously from first clutch C1 in response to the instruction that comes from ECU42, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
Obtaining in the speed changer 146 of shelves according to clutch shown in Figure 92 and brake engages figure, first grade speed ratio γ 1 is approximately 4.762, second grade speed ratio γ 2 is approximately 4.110, the speed ratio γ 3 of third gear is approximately 2.603, the speed ratio γ 4 of fourth speed is approximately 2.000, the 5th grade speed ratio γ 5 is approximately 1.624, the 6th grade speed ratio γ 6 is approximately 1.322, the 7th grade speed ratio γ 7 is approximately 1.000, the 8th grade speed ratio γ 8 is approximately 0.833, the 9th grade speed ratio γ 9 is approximately 0.714, the tenth grade speed ratio γ 10 is approximately 0.621, the speed ratio γ R2 that the speed ratio γ R1 of first reverse gear is approximately 5.000 and second reverse gear is approximately 2.500.In addition, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.159, second grade speed ratio γ 2 is 1.579 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.301 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.232, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.229, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.322, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is that the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of 1.200, the eight grades speed ratio γ 8 and the 9th grade is 1.167, and the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.150.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 10) of the speed ratio γ 10 of first grade speed ratio γ 1 and the tenth grade is 7.667, this is bigger numerical value.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 46 of gear ratio ρ 1, the second preposition planetary gear set 150 of the first preposition planetary gear set 148 and the gear ratio ρ 4 of the second rearmounted planetary gear set 48 are designed to be and can realize aforementioned speed ratio.
Revise example as first of the 8th exemplary embodiment, do not change, can obtain those grades shown in Figure 93 by the gear ratio ρ 1 to ρ 4 that suitably sets planetary gear set although be used for the bonding operation of each grade.Obtaining in the speed changer 1146 of shelves according to clutch shown in Figure 93 and brake engages figure, first grade speed ratio γ 1 is approximately 4.971, second grade speed ratio γ 2 is approximately 3.290, the speed ratio γ 3 of third gear is approximately 2.222, the speed ratio γ 4 of fourth speed is approximately 1.645, the 5th grade speed ratio γ 5 is approximately 1.409, the 6th grade speed ratio γ 6 is approximately 1.244, the 7th grade speed ratio γ 7 is approximately 1.000, the 8th grade speed ratio γ 8 is approximately 0.825, the 9th grade speed ratio γ 9 is approximately 0.649, the tenth grade speed ratio γ 10 is approximately 0.574, the speed ratio γ R2 that the speed ratio γ R1 of first reverse gear is approximately 3.047 and second reverse gear is approximately 1.852.In addition, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.511, second grade speed ratio γ 2 is 1.481 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.351 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.167, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.133, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.244, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is that the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of 1.212, the eight grades speed ratio γ 8 and the 9th grade is 1.271, and the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.131.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 10) of the speed ratio γ 10 of first grade speed ratio γ 1 and the tenth grade is 8.655, this is bigger numerical value.By suitably setting the gear ratio of each planetary gear set by this way, the overall ratio scope can be set widelyer than the overall ratio scope shown in Figure 92.
In the nomogram shown in Figure 94, four vertical curve Y1 represent the assembly of first speed changing portion 152 to Y4.In the drawings from left to right, line Y1 represents to link together with the planet carrier CA1 of the first preposition planetary gear set 148 that constitutes a rotating element and the gear ring R2 of the second preposition planetary gear set 150, line Y2 represents to link together with the gear ring R1 of the first preposition planetary gear set 148 that constitutes another rotating element and the planet carrier CA2 of the second preposition planetary gear set 150, line Y3 represents the sun gear S1 as the first preposition planetary gear set 148 of another rotating element, and line Y4 represents the sun gear S2 as the second preposition planetary gear set 150 of another rotating element.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 50 to Y8.In the drawings from left to right, line Y5 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 46 of the first rotating element RE1, line Y6 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 46 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 48, and line Y7 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 46 of the 3rd rotating element RE3 and the gear ring R4 of the second rearmounted planetary gear set 48, and line Y8 represents to be equivalent to the sun gear S4 of the second rearmounted planetary gear set 48 of the 4th rotating element RE4.Therefore, according to these rotating elements, the nomogram shown in Figure 94 is similar to the nomogram shown in above-mentioned Figure 14, therefore will omit the description to it.
By this way, revise example according to first of the 8th exemplary embodiment, first speed changing portion 152 comprises first preposition planetary gear set 148 of double pinion type and the second preposition planetary gear set 150 of single small gear type.The sun gear S1 of the first preposition planetary gear set 148 always is connected in the gearbox 16 as nonrotational element, and the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 148 and the second preposition planetary gear set 150 links together.Simultaneously, the gear ring R2 of the planet carrier CA1 of the first preposition planetary gear set 148 and the second preposition planetary gear set 150 is connected in the input shaft 22 as the input rotating element.Therefore, the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 148 or the second preposition planetary gear set 150 is as the first middle output element 32, and the sun gear S2 of the second preposition planetary gear set 150 is as the second middle output element 34 simultaneously.Therefore, can provide practical speed changer 146.
Here, revise example as second of the 8th exemplary embodiment, as shown in Figure 95, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 146 can obtain ten forward gearss and two reverse gears, and can obtain the effect that is equal to aforementioned exemplary embodiment.In addition, Figure 96 is and the corresponding nomogram of Figure 95 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the second correction example of Figure 95 different with aforementioned exemplary embodiment and the 8th exemplary embodiment shown in Figure 96 be described.
As shown in clutch among Figure 95 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, first grade " 1st " is to the tenth grade of 10th " in any one; perhaps two reverse gears; promptly; first reverse gear " R1 " or second reverse gear " R2 ", and can obtain the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that for each grade, changes with basic identical ratio.The speed ratio that is used to set up the operation of friction engagement device of described shelves and described shelves with use Figure 17 described identical, so will omit giving unnecessary details to it.
In the nomogram shown in Figure 96, four vertical curve Y1 represent the assembly of first speed changing portion 152 to Y4.In the drawings from left to right, line Y1 represents that sun gear S2, the line Y2 of the second preposition planetary gear set 150 represent that sun gear S1, the line Y3 of the first preposition planetary gear set 148 represent that the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 148 that links together and the second preposition planetary gear set 150 and line Y4 represent the planet carrier CA1 of the first preposition planetary gear set 148 that links together and the gear ring R2 of the second preposition planetary gear set 150.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 50 to Y8.In the drawings from left to right, line Y5 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 46 of the first rotating element RE1, line Y6 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 46 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 48, and line Y7 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 46 of the 3rd rotating element RE3 and the gear ring R4 of the second rearmounted planetary gear set 48, and line Y8 represents to be equivalent to the sun gear S4 of the second rearmounted planetary gear set 48 of the 4th rotating element RE4.Therefore, according to these rotating elements, the nomogram shown in Figure 96 is similar to the nomogram shown in above-mentioned Figure 18, therefore will omit the description to it.
By this way, revise example according to second of the 8th exemplary embodiment, by with different compound modes (such as above-described those) gear ratio that engages the clutch of each grade and break and suitably set each planetary gear set, can obtain ten forward gearss and two reverse gears, and more particularly, the level between the 9th grade and the tenth grade can be set lessly with intensive speed ratio.
Here, revise example as the 3rd of the 8th exemplary embodiment, as shown in Figure 97, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 146 can obtain nine forward gearss and two reverse gears.In addition, Figure 98 is and the corresponding nomogram of Figure 97 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 3rd correction example of Figure 97 different with aforementioned exemplary embodiment and the 8th exemplary embodiment shown in Figure 98 be described.
As shown in clutch among Figure 97 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
As shown in Figure 97, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gearbox 16, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, be approximately 4.776.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and the first break B1 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 remain in gearbox 16, thereby set up second grade, described second grade of speed ratio γ 2 that has less than first grade speed ratio γ 1, for example, be approximately 2.925.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the first centre output element 32, thereby the third gear of foundation, described third gear has the speed ratio γ 3 less than second grade of speed ratio γ 2, for example, be approximately 2.000.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and four clutches C4 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with input shaft 22, thereby set up fourth speed, described fourth speed has the speed ratio γ 4 less than third gear speed ratio γ 3, for example, be approximately 1.519.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, be connected with input shaft 22, thereby set up the 5th grade, described the 5th grade of speed ratio γ 4 that has less than fourth speed speed ratio γ 4, for example, be approximately 1.265.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, be connected with input shaft 22, and four clutches C4 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with input shaft 22, thereby set up the 6th grade, described the 6th grade of speed ratio γ 6 that has less than the 5th grade of speed ratio γ 5, for example, be approximately 1.000.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, be connected with input shaft 22, and three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the first centre output element 32, thereby set up the 7th grade, described the 7th grade of speed ratio γ 7 that has less than the 6th grade of speed ratio γ 6, for example, be approximately 0.800.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, be connected with input shaft 22, and the first break B1 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 remain in gearbox 16, thereby set up the 8th grade, described the 8th grade of speed ratio γ 8 that has less than the 7th grade of speed ratio γ 7, for example, be approximately 0.667.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48 are connected with input shaft 22, and the 5th clutch C5 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the second centre output element 34, thereby set up the 9th grade, described the 9th grade has minimum speed ratio γ 9, for example, is approximately 0.588.
In addition, three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gearbox 16, thereby set up first reverse gear " R1 ", described reverse gear " R1 " has and is approximately 4.000 speed ratio γ R1.
In addition, four clutches C4 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with input shaft 22, and the second break B2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gearbox 16, thereby set up second reverse gear " R2 ", described reverse gear " R2 " has the speed ratio γ R2 less than the speed ratio γ R1 of first reverse gear, for example is 2.000.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 46 of gear ratio ρ 1, the second preposition planetary gear set 150 of the first preposition planetary gear set 148 and the gear ratio ρ 4 of the second rearmounted planetary gear set 48 are designed to be and can realize aforementioned speed ratio.
Obtaining in the speed changer 146 of shelves according to clutch shown in Figure 97 and brake engages figure, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.633, second grade speed ratio γ 2 is 1.463 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.316 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.201, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.265, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.250, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is 1.200, and the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of the 8th grade speed ratio γ 8 and the 9th grade is 1.133.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 9) of the speed ratio γ 9 of first grade speed ratio γ 1 and the 9th grade is 8.119, this is bigger numerical value.
In the nomogram shown in Figure 98, four vertical curve Y1 represent the assembly of first speed changing portion 152 to Y4.In the drawings from left to right, line Y1 represents that sun gear S2, the line Y2 of the second preposition planetary gear set 150 represent that sun gear S1, the line Y3 of the first preposition planetary gear set 148 represent that the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 148 that links together and the second preposition planetary gear set 150 and line Y4 represent the planet carrier CA1 of the first preposition planetary gear set 148 that links together and the gear ring R2 of the second preposition planetary gear set 150.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 50 to Y8.In the drawings from left to right, line Y5 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 46 of the first rotating element RE1, line Y6 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 46 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 48, and line Y7 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 46 of the 3rd rotating element RE3 and the gear ring R4 of the second rearmounted planetary gear set 48, and line Y8 represents to be equivalent to the sun gear S4 of the second rearmounted planetary gear set 48 of the 4th rotating element RE4.Therefore, according to these rotating elements, the nomogram shown in Figure 98 is similar to the nomogram shown in above-mentioned Fig. 9, therefore will omit the description to it.
By this way, revise example, set up first grade by engaging the first clutch C1 and the second break B2 according to the 3rd of the 8th exemplary embodiment.Set up second grade by engaging the first clutch C1 and the first break B1.Set up third gear by engaging first clutch C1 and three-clutch C3.Set up fourth speed by engaging first clutch C1 and four clutches C4.Set up the 5th grade by engaging first clutch C1 and second clutch C2.Set up the 6th grade by engaging second clutch C2 and four clutches C4.Set up the 7th grade by engaging second clutch C2 and three-clutch C3, and set up the 8th grade by engaging the second clutch C2 and the first break B1.Therefore, the 3rd of the 8th exemplary embodiment the speed changer 146 of revising example can be realized eight forward gearss.
The 3rd of the 8th exemplary embodiment is revised the speed changer 146 of example can also realize the 9th grade by engaging second clutch C2 and the 5th clutch C5.Therefore, except that can realizing nine forward gearss, can be with intensive speed ratio preferably set the level between the 8th grade and the 9th grade less.
Here, revise example as the 4th of the 8th exemplary embodiment, as shown in Figure 99, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 146 can obtain nine forward gearss and two reverse gears.In addition, Figure 100 is and the corresponding nomogram of Figure 99 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 4th correction example of Figure 99 different with aforementioned exemplary embodiment and the 8th exemplary embodiment shown in Figure 100 be described.
As shown in clutch among Figure 99 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
As shown in Figure 99, the 5th clutch C5 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the second centre output element 34, and the second break B2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gearbox 16, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, be approximately 4.971.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gearbox 16, thereby set up second grade, described second grade of speed ratio γ 2 that has less than first grade of speed ratio γ 1, for example, be approximately 3.290.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and the first break B1 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 remain in gearbox 16, thereby the third gear of foundation, described third gear has the speed ratio γ 3 less than second grade of speed ratio γ 2, for example, be approximately 2.222.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the first centre output element 32, thereby set up fourth speed, described fourth speed has the speed ratio γ 4 less than third gear speed ratio γ 3, for example, be approximately 1.645.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and four clutches C4 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with input shaft 22, thereby set up the 5th grade, described the 5th grade of speed ratio γ 5 that has less than fourth speed speed ratio γ 4, for example, be approximately 1.409.
In addition, first clutch C1 be engaged with the 4th rotating element RE4 promptly the sun gear S4 of the second rearmounted planetary gear set 48 be connected with the first centre output element 32, and second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, be connected with input shaft 22, thereby set up the 6th grade, described the 6th grade of speed ratio γ 6 that has less than the 5th grade of speed ratio γ 5, for example, be approximately 1.244.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, be connected with input shaft 22, and four clutches C4 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with input shaft 22, thereby set up the 7th grade, described the 7th grade of speed ratio γ 7 that has less than the 6th grade of speed ratio γ 6, for example, be approximately 1.000.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, be connected with input shaft 22, and three-clutch C3 is engaged with output element 32 in the middle of promptly the sun gear S3 of the first rearmounted planetary gear set 46 is connected in first with the first rotating element RE1, thereby set up the 8th grade, described the 8th grade of speed ratio γ 8 that has less than the 7th grade of speed ratio γ 7, for example, be approximately 0.825.
In addition, second clutch C2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48 are connected with input shaft 22, and the first break B1 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 remain in gearbox 16, thereby set up the 9th grade, described the 9th grade has minimum speed ratio γ 9, for example, is approximately 0.649.
In addition, three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gearbox 16, thereby set up first reverse gear " R1 ", described reverse gear " R1 " has and is approximately 3.047 speed ratio γ R1.
In addition, four clutches C4 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 46 be connected with input shaft 22, and the second break B2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 46 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 48, remain in gearbox 16, thereby set up second reverse gear " R2 ", described reverse gear " R2 " has the speed ratio γ R2 less than the speed ratio γ R1 of first reverse gear, for example, 1.852.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 46 of gear ratio ρ 1, the second preposition planetary gear set 150 of the first preposition planetary gear set 148 and the gear ratio ρ 4 of the second rearmounted planetary gear set 48 are designed to be and can realize aforementioned speed ratio.
Obtaining in the speed changer 146 of shelves according to clutch shown in Figure 99 and brake engages figure, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.511, second grade speed ratio γ 2 is 1.481 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.351 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.167, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.133, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.244, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is 1.212, and the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of the 8th grade speed ratio γ 8 and the 9th grade is 1.271.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 9) of the speed ratio γ 9 of first grade speed ratio γ 1 and the 9th grade is 7.655, this is bigger numerical value.
In the nomogram shown in Figure 100, four vertical curve Y1 represent the assembly of first speed changing portion 152 to Y4.In the drawings from left to right, line Y1 represents that sun gear S2, the line Y2 of the second preposition planetary gear set 150 represent that sun gear S1, the line Y3 of the first preposition planetary gear set 148 represent that the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 148 that links together and the second preposition planetary gear set 150 and line Y4 represent the planet carrier CA1 of the first preposition planetary gear set 148 that links together and the gear ring R2 of the second preposition planetary gear set 150.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 50 to Y8.In the drawings from left to right, line Y5 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 46 of the first rotating element RE1, line Y6 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 46 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 48, line Y7 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 46 of the 3rd rotating element RE3 and the gear ring R4 of the second rearmounted planetary gear set 48, and line Y8 represents to be equivalent to the sun gear S4 of the second rearmounted planetary gear set 48 of the 4th rotating element RE4.Therefore, based on these rotating elements, therefore similar to shown in Figure 11 of the nomogram shown in Figure 100 will omit the description to it.
By this way, revise example, by engaging the 5th clutch C5 and the second break B2 sets up first grade according to the 4th of the 8th exemplary embodiment.Set up second grade by engaging the first clutch C1 and the second break B2.Set up third gear by engaging the first clutch C1 and the first break B1.Set up fourth speed by engaging first clutch C1 and three-clutch C3.Set up the 5th grade by engaging first clutch C1 and four clutches C4.Set up the 6th grade by engaging first clutch C1 and second clutch C2.Set up the 7th grade by engaging second clutch C2 and four clutches C4, and set up the 8th grade by engaging second clutch C2 and three-clutch C3.Therefore, the 4th of the 8th exemplary embodiment the speed changer 146 of revising example can be realized eight forward gearss.
The 4th of the 8th exemplary embodiment is revised the speed changer 146 of example can also realize the 9th grade by engaging the second clutch C2 and the first break B1.Therefore, except that can realizing nine forward gearss, can be with intensive speed ratio preferably set the level between the 8th grade and the 9th grade less.
Here, revise example as the 5th of the 8th exemplary embodiment, as shown in Figure 101, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 146 can obtain nine forward gearss and two reverse gears.In addition, Figure 102 is and the corresponding nomogram of Figure 101 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 5th correction example of Figure 101 different with aforementioned exemplary embodiment and the 8th exemplary embodiment shown in Figure 102 be described.
As shown in clutch among Figure 101 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.The speed ratio that is used to set up the operation of friction engagement device of described shelves and described shelves with use Figure 23 described identical, so will omit giving unnecessary details to it.
In the nomogram shown in Figure 102, because the structure shown in the perspective view is identical, represent that therefore four vertical curve Y1 of the assembly of first speed changing portion 152 represent and the identical rotating element shown in above-mentioned Figure 96 to Y8 with four vertical curve Y5 of the assembly of expression second speed changing portion 50 to Y4.In addition, in clutch shown in Figure 101 and brake engages figure, it is described identical with above-mentioned use Figure 23 to the operation of the friction engagement device of the 9th grade " 9th " to be used to set up first grade " 1st ".Therefore, based on rotating element, nomogram is also corresponding with it.Therefore, the nomogram among Figure 102 is identical with the nomogram shown in Figure 24.
Therefore, revise example according to the 5th of the 8th exemplary embodiment, by with different compound mode engaging clutches and break and suitably set the gear ratio of each planetary gear set, also can obtain nine forward gearss and two reverse gears, and more particularly, the level between the 8th grade and the 9th grade can be set lessly with intensive speed ratio.
Here, revise example as the 6th of the 8th exemplary embodiment, as shown in Figure 103, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 146 can obtain nine forward gearss and two reverse gears, and can obtain the effect that is equal to aforementioned exemplary embodiment.In addition, Figure 104 is and the corresponding nomogram of Figure 103 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 6th correction example of Figure 103 different with aforementioned exemplary embodiment and the 8th exemplary embodiment shown in Figure 104 be described.
As shown in clutch among Figure 103 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.The speed ratio that is used to set up the operation of friction engagement device of described shelves and described shelves with use Figure 25 described identical, so will omit giving unnecessary details to it.
In the nomogram shown in Figure 104, because the structure shown in the perspective view is identical, represent that therefore four vertical curve Y1 of the assembly of first speed changing portion 152 represent and the identical rotating element shown in above-mentioned Figure 96 to Y8 with four vertical curve Y5 of the assembly of expression second speed changing portion 50 to Y4.In addition, in clutch shown in Figure 103 and brake engages figure, it is described identical with above-mentioned use Figure 25 to the operation of the friction engagement device of the 9th grade " 9th " to be used to set up first grade " 1st ".Therefore, based on rotating element, nomogram is also corresponding with it.Therefore, the nomogram among Figure 104 is identical with the nomogram shown in Figure 26.
Therefore, revise example according to the 6th of the 8th exemplary embodiment, by with different compound mode engaging clutches and break and suitably set the gear ratio of each planetary gear set, can obtain nine forward gearss and two reverse gears, and more particularly, the level between the 8th grade and the 9th grade can be set lessly with intensive speed ratio.
Figure 105 is the perspective view of the structure of the related speed changer 154 of the present invention's the 9th exemplary embodiment.It is middle-grade and be used to set up the figure of the relation between the operation of the required friction engagement device of those grades that Figure 106 shows speed changer 154.Figure 108 shows the nomogram of the rotational velocity of rotating element in each grade.Hereinafter, will the part of the speed changer 154 of the 9th exemplary embodiment be described.
As shown in Figure 105, the first preposition planetary gear set 156 that constitutes the part of first speed changing portion 164 be comprise sun gear S1, intermeshing many group small gear P1, can rotation and can revolve round the sun the planetary gear set of double pinion type of the planet carrier CA1 of support small gear P1 and the gear ring R1 that is meshed with sun gear S1 by small gear P1.The same second preposition planetary gear set 158 that constitutes the part of first speed changing portion 164 be comprise sun gear S2, small gear P2, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA2 of support small gear P2 and the gear ring R2 that is meshed with sun gear S2 by small gear P2.
In first speed changing portion 164, the sun gear S1 of the first preposition planetary gear set 156 is connected in the gearbox 16 as nonrotational element integratedly, thereby prevents to rotate with respect to gearbox 16.In addition, the gear ring R2 of the planet carrier CA1 of the first preposition planetary gear set 156 and the second preposition planetary gear set 158 links together and is connected in integratedly as the input shaft 22 of importing rotating element.In addition, the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 156 and the second preposition planetary gear set 158 links together and is connected in the first middle output element 32 integratedly.In addition, output element 34 in the middle of the sun gear S2 of the second preposition planetary gear set 158 is connected in second integratedly.This structure causes first speed changing portion 164 by the slow down rotation that comes from the input shaft 22 and rotation of being slowed down is delivered to second speed changing portion 166 of output element 32 in the middle of first, and makes the rotations that come from input shaft 22 oppositely and with described backward rotation be delivered to second speed changing portion 166 by output element 34 in the middle of second.
The first rearmounted planetary gear set 160 that constitutes the part of second speed changing portion 166 be comprise sun gear S3, small gear P3, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA3 of support small gear P3 and the gear ring R3 that is meshed with sun gear S3 by small gear P3.The same second rearmounted planetary gear set 162 that constitutes the part of second speed changing portion 166 be many groups small gear P4 of comprising sun gear S4, being engaged with each other, can rotation and can revolve round the sun the planetary gear set of double pinion type of the planet carrier CA4 of support small gear P4 and the gear ring R4 that is meshed with sun gear S4 by small gear P4.
In second speed changing portion 166, the sun gear S3 of the first rearmounted planetary gear set 160 constitutes the first rotating element RE1.The planet carrier CA4 of the planet carrier CA3 of the first rearmounted planetary gear set 160 and the second rearmounted planetary gear set 162 links together to constitute the second rotating element RE2.The gear ring R4 of the second rearmounted planetary gear set 162 constitutes the 3rd rotating element RE3, and the sun gear S4 of the gear ring R3 of the first rearmounted planetary gear set 160 and the second rearmounted planetary gear set 162 links together to constitute the 4th rotating element RE4.Speed changer 154 also comprises first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, the first break B1 and the second break B2.First clutch C1 is the first clutch element that optionally the first middle output element 32 is connected with the 4th rotating element RE4.Second clutch C2 is the second clutch element that optionally input shaft 22 is connected with the second rotating element RE2.Three-clutch C3 is the three-clutch element that optionally the first middle output element 32 is connected with the first rotating element RE1.Four clutches C4 is the four clutches element that optionally input shaft 22 and the first rotating element RE1 is linked together.The 5th clutch C5 is the 5th clutch element that optionally output element 34 in the middle of second and the first rotating element RE1 is linked together.The first break B1 is first brake component that optionally the first rotating element RE1 is remained in as the gearbox 16 of nonrotational element, and the second break B2 is second brake component that optionally the second rotating element RE2 is remained in gearbox 16.
In the speed changer 154 that constitutes as mentioned above, for example, as shown in Figure 106, can be by engaging simultaneously from first clutch C1 in response to instruction from ECU42, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
That is to say, as shown in Figure 106, first clutch C1 is engaged with the 4th rotating element RE4, promptly, the gear ring R3 of the first rearmounted planetary gear set 160 that links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and the second break B2 is engaged with the second rotating element RE2, that is, the planet carrier CA3 of the first rearmounted planetary gear set 160 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 162 remain in the gearbox 16 as nonrotational element, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, is approximately 5.283.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, promptly, the gear ring R3 of the first rearmounted planetary gear set 160 that links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and the 5th clutch C5 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 be connected with the second centre output element 34, thereby set up second grade, described second grade of speed ratio γ 2 that has less than first grade of speed ratio γ 1, for example, be approximately 3.605.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the gear ring R3 of the first rearmounted planetary gear set 160 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and the first break B1 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 remain in gearbox 16, thereby the third gear of foundation, described third gear has the speed ratio γ 3 less than second grade of speed ratio γ 2, for example, be approximately 2.472.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the gear ring R3 of the first rearmounted planetary gear set 160 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 be connected with the first centre output element 32, thereby set up fourth speed, described fourth speed has the speed ratio γ 4 less than third gear speed ratio γ 3, for example, be approximately 1.897.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the gear ring R3 of the first rearmounted planetary gear set 160 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and four clutches C4 be engaged with the first rotating element RE1 promptly the first rearmounted planetary gear set 160 sun gear S3 be connected as the input shaft 22 of importing rotating element, thereby set up the 5th grade, described the 5th grade of speed ratio γ 5 that has less than fourth speed speed ratio γ 4, for example, be approximately 1.569.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the gear ring R3 of the first rearmounted planetary gear set 160 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, be connected with input shaft 22, thereby set up the 6th grade, described the 6th grade of speed ratio γ 6 that has less than the 5th grade of speed ratio γ 5, for example, be approximately 1.204.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, be connected with input shaft 22, and four clutches C4 be engaged with the first rotating element RE1 promptly the first rearmounted planetary gear set 160 sun gear S3 be connected as the input shaft 22 of importing rotating element, thereby set up the 7th grade, described the 7th grade of speed ratio γ 7 that has less than the 6th grade of speed ratio γ 6, for example, be approximately 1.000.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, be connected with input shaft 22, and three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 be connected with the first centre output element 32, thereby set up the 8th grade, described the 8th grade of speed ratio γ 8 that has less than the 7th grade of speed ratio γ 7, for example, being approximately 0. is 0.912.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, be connected with input shaft 22, and the first break B1 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 remain in gearbox 16, thereby set up the 9th grade, described the 9th grade of speed ratio γ 9 that has less than the 8th grade of speed ratio γ 8, for example, be approximately 0.830.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together is connected with input shaft 22 with the planet carrier CA4 of the second rearmounted planetary gear set 162, and the 5th clutch C5 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 be connected with the second centre output element 34, thereby set up the tenth grade, the described ten grade has minimum speed ratio γ 10, for example, being approximately 0. is 0.760.
In addition, three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, remain in gearbox 16, thereby set up first reverse gear " R1 ", described reverse gear " R1 " has and is approximately 9.257 speed ratio γ R1.
In addition, four clutches C4 be engaged with the first rotating element RE1 promptly the first rearmounted planetary gear set 160 sun gear S3 be connected as the input shaft 22 of importing rotating element, and the second break B2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, remain in gearbox 16, thereby set up second reverse gear " R2 ", described reverse gear " R2 " has the speed ratio γ R2 less than the speed ratio γ R1 of first reverse gear, for example, be approximately 4.881.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 160 of gear ratio ρ 1, the second preposition planetary gear set 158 of the first preposition planetary gear set 156 and the gear ratio ρ 4 of the second rearmounted planetary gear set 162 are designed to be and can realize aforementioned speed ratio.
Obtaining in the speed changer 154 of shelves according to clutch shown in Figure 106 and brake engages figure, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.466, second grade speed ratio γ 2 is 1.458 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.304 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.209, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.303, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.204, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is 1.097, the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of the 8th grade speed ratio γ 8 and the 9th grade is 1.098, and the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.093.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 10) of the speed ratio γ 10 of first grade speed ratio γ 1 and the tenth grade is 6.956, this is bigger numerical value.
In addition, revise example, do not change, can obtain those grades shown in Figure 107 by the gear ratio ρ 1 to ρ 4 that suitably sets planetary gear set although be used for the bonding operation of each grade as first of the 9th exemplary embodiment.Obtaining in the speed changer 154 of shelves according to clutch shown in Figure 107 and brake engages figure, first grade speed ratio γ 1 is approximately 5.690, second grade speed ratio γ 2 is approximately 3.689, the speed ratio γ 3 of third gear is approximately 2.492, the speed ratio γ 4 of fourth speed is approximately 1.897, the 5th grade speed ratio γ 5 is approximately 1.562, the 6th grade speed ratio γ 6 is approximately 1.187, the 7th grade speed ratio γ 7 is approximately 1.000, it is 0.919 that the 8th grade speed ratio γ 8 is approximately 0., it is 0.843 that the 9th grade speed ratio γ 9 is approximately 0., it is 0.777 that the tenth grade speed ratio γ 10 is approximately 0., the speed ratio γ R2 that the speed ratio γ R1 of first reverse gear is approximately 10.194 and second reverse gear is approximately 5.375.In addition, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.542, second grade speed ratio γ 2 is 1.480 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.314 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.214, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.316, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.187, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is that the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of 1.088, the eight grades speed ratio γ 8 and the 9th grade is 1.090, and the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.086.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 10) of the speed ratio γ 10 of first grade speed ratio γ 1 and the tenth grade is 7.326, this is bigger numerical value.By suitably setting the gear ratio of each planetary gear set by this way, the overall ratio scope can be set widelyer than the overall ratio scope shown in Figure 106.
In the nomogram shown in Figure 108, four vertical curve Y1 represent the assembly of first speed changing portion 164 to Y4.In the drawings from left to right, line Y1 represents that gear ring R2, the line Y2 of the planet carrier CA1 of the first preposition planetary gear set 156 that links together and the second preposition planetary gear set 158 represent that the gear ring R1 of the first preposition planetary gear set 156 that links together and planet carrier CA2, the line Y3 of the second preposition planetary gear set 158 represent the sun gear S1 of the first preposition planetary gear set 156 and the sun gear S2 that line Y4 represents the second preposition planetary gear set 158.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 166 to Y8.In the drawings from left to right, line Y5 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 160 of the first rotating element RE1, line Y6 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 160 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 162, and line Y7 represents to be equivalent to the gear ring R4 of the second rearmounted planetary gear set 162 of the 3rd rotating element RE3, and line Y8 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 160 of the 4th rotating element RE4 and the sun gear S4 of the second rearmounted planetary gear set 162.
When using nomographing, in first speed changing portion 164 of the related speed changer 154 of this exemplary embodiment, link together and be connected with input shaft 22 as the input rotating element as the gear ring R2 of the planet carrier CA1 of the first preposition planetary gear set 156 one of in four rotating elements and the second preposition planetary gear set 158.Link together and is provided with integratedly, therefore play and the similar effect of the first centre output element as output element 32 in the middle of the planet carrier CA2 and first of the gear ring R1 of another the first preposition planetary gear set 156 in four rotating elements and the second preposition planetary gear set 158.Sun gear S1 as another the first preposition planetary gear set 156 in four rotating elements is held in the nonrotationally gearbox 16 of element of conduct, so that can not rotate with respect to it.Therefore is provided with integratedly as output element 34 in the middle of another the sun gear S2 and second of the second preposition planetary gear set 158 of four rotating elements, plays with the second centre output element similarly acting on.In addition, in second speed changing portion 166 of speed changer 154, output element 32 in the middle of the first rotating element RE1 (S3) optionally is connected in first by three-clutch C3 optionally is connected in as the input shaft 22 of importing rotating element, optionally is connected in the second middle output element 34 and is optionally remained in the nonrotationally gearbox 16 of element of conduct by the first break B1 by the 5th clutch C5 by four clutches C4.In addition, the second rotating element RE2 (CA3, CA4) optionally is connected in as the input shaft 22 of input rotating element and by the second break B2 by second clutch C2 and is optionally remained in the nonrotationally gearbox 16 of element of conduct.In addition, the 3rd rotating element RE3 (R4) is provided with integratedly with the output shaft 36 of conduct output rotating element, therefore plays the effect similar to exporting rotating element.In addition, output element 32 in the middle of the 4th rotating element RE4 (R3, S4) optionally is connected in first by first clutch C1.
In the nomogram in Figure 108, in first grade, first clutch C1 is engaged the 4th rotating element RE4 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of the 4th rotating element RE4 output element 32 in the middle of with first.Simultaneously, the second break B2 is engaged the second rotating element RE2 is remained in the gearbox 16 as nonrotational element, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (1st) expression, and (1st) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y6 and horizontal line XZ and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In second grade, the 5th clutch C5 is engaged so that the first rotating element RE1 is connected with output element 34 in the middle of second, and this causes the first rotating element RE1 to rotate under the speed identical with output element 34 in the middle of second.Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (2nd) expression, and (2nd) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X1 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In third gear, the first break B1 is engaged so that the first rotating element RE1 is remained in gearbox 16, and this causes the rotational velocity of the first rotating element RE1 to be " 0 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (3rd) expression, and (3rd) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line XZ and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In fourth speed, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (4th) expression, and (4th) locates at point, and horizontal line X2 and vertical curve Y7 intersect.
In the 5th grade, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (5th) expression, and (5th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X3 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In the 6th grade, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (6th) expression, and (6th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y6 and horizontal line X3 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In the 7th grade, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (7th) expression, and (7th) locates at point, and horizontal line X3 and vertical curve Y7 intersect.
In the 8th grade, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (8th) expression, and (8th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X2 and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In the 9th grade, the first break B1 is engaged so that the first rotating element RE1 is remained in gearbox 16, and this causes the rotational velocity of the first rotating element RE1 to be " 0 ".Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (9th) expression, and (9th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line XZ and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In the tenth grade, the 5th clutch C5 is engaged the first rotating element RE1 being connected in output element 34 in the middle of second, and this causes rotating under the identical speed of first rotating element RE1 output element 34 in the middle of with second.Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (10th) expression, and (10th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X1 and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In first reverse gear, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (Rev1) expression, and (Rev1) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X2 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
In second reverse gear, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (Rev2) expression, and (Rev2) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X3 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
By this way, according to this first correction example of the 9th exemplary embodiment, set up first grade by engaging the first clutch C1 and the second break B2.Set up second grade by engaging first clutch C1 and the 5th clutch C5.Set up third gear by engaging the first clutch C1 and the first break B1.Set up fourth speed by engaging first clutch C1 and three-clutch C3.Set up the 5th grade by engaging first clutch C1 and four clutches C4.Set up the 6th grade by engaging first clutch C1 and second clutch C2.Set up the 7th grade by engaging second clutch C2 and four clutches C4.Set up the 8th grade by engaging second clutch C2 and three-clutch C3, and set up the 9th grade by engaging the second clutch C2 and the first break B1.Therefore, this first speed changer 154 of revising example of the 9th exemplary embodiment can be realized nine forward gearss.
This first speed changer 154 of revising example of the 9th exemplary embodiment can also be realized the tenth grade by engaging second clutch C2 and the 5th clutch C5.Therefore, except that can realizing ten forward gearss, can be preferably set the level between the 9th grade and the tenth grade less with intensive speed ratio.
And second speed changing portion 166 comprises first rearmounted planetary gear set 160 of single small gear type and the second rearmounted planetary gear set 162 of double pinion type.The sun gear S3 of the first rearmounted planetary gear set 160 constitutes the first rotating element RE1, the planet carrier CA3 of the first rearmounted planetary gear set 160 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 162 constitute the second rotating element RE2, the gear ring R4 of the second rearmounted planetary gear set 162 constitutes the 3rd rotating element RE3, and the gear ring R3 of the first rearmounted planetary gear set 160 that links together and the sun gear S4 of the second rearmounted planetary gear set 162 constitute the 4th rotating element RE4.Therefore, can provide practical speed changer 154.
Here, revise example as second of the 9th exemplary embodiment, as shown in Figure 109, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 154 can obtain nine forward gearss and two reverse gears.In addition, Figure 110 is and the corresponding nomogram of Figure 109 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the second correction example of Figure 109 different with aforementioned exemplary embodiment and the 9th exemplary embodiment shown in Figure 110 be described.
As shown in clutch among Figure 109 and brake engages figure, by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
As shown in Figure 109, first clutch C1 is engaged with the 4th rotating element RE4, promptly, the gear ring R3 of the first rearmounted planetary gear set 160 that links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and the second break B2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 160 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, remain in the gearbox 16 as nonrotational element, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, be approximately 5.690.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the gear ring R3 of the first rearmounted planetary gear set 160 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and the 5th clutch C5 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 be connected with the second centre output element 34, thereby set up second grade, described second grade of speed ratio γ 2 that has less than first grade of speed ratio γ 1, for example, be approximately 3.689.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the gear ring R3 of the first rearmounted planetary gear set 160 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and the first break B1 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 remain in gearbox 16, thereby the third gear of foundation, described third gear has the speed ratio γ 3 less than second grade of speed ratio γ 2, for example, be approximately 2.492.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the gear ring R3 of the first rearmounted planetary gear set 160 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 be connected with the first centre output element 32, thereby set up fourth speed, described fourth speed has the speed ratio γ 4 less than third gear speed ratio γ 3, for example, be approximately 1.897.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the gear ring R3 of the first rearmounted planetary gear set 160 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and four clutches C4 be engaged with the first rotating element RE1 promptly the first rearmounted planetary gear set 160 sun gear S3 be connected as the input shaft 22 of importing rotating element, thereby set up the 5th grade, described the 5th grade of speed ratio γ 5 that has less than fourth speed speed ratio γ 4, for example, be approximately 1.562.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the gear ring R3 of the first rearmounted planetary gear set 160 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, be connected with input shaft 22, thereby set up the 6th grade, described the 6th grade of speed ratio γ 6 that has less than the 5th grade of speed ratio γ 5, for example, be approximately 1.187.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, be connected with input shaft 22, and four clutches C4 be engaged with the first rotating element RE1 promptly the first rearmounted planetary gear set 160 sun gear S3 be connected as the input shaft 22 of importing rotating element, thereby set up the 7th grade, described the 7th grade of speed ratio γ 7 that has less than the 6th grade of speed ratio γ 6, for example, be approximately 1.000.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, be connected with input shaft 22, and three-clutch C3 is engaged with output element 32 in the middle of promptly the sun gear S3 of the first rearmounted planetary gear set 160 is connected in first with the first rotating element RE1, thereby set up the 8th grade, described the 8th grade of speed ratio γ 8 that has less than the 7th grade of speed ratio γ 7, for example, be approximately 0.919.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, be connected with input shaft 22, and the first break B1 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 remain in gearbox 16, thereby set up the 9th grade, described the 9th grade of speed ratio γ 9 that has less than the 8th grade of speed ratio γ 8, for example, be approximately 0.843.
In addition, three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 160 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, remain in gearbox 16, thereby set up first reverse gear " R1 ", described reverse gear " R1 " has and is approximately 10.194 speed ratio γ R1.
In addition, four clutches C4 be engaged with the first rotating element RE1 promptly the first rearmounted planetary gear set 160 sun gear S3 be connected as the input shaft 22 of importing rotating element, and the second break B2 is engaged with the second rotating element RE2, promptly, the planet carrier CA3 of the first rearmounted planetary gear set 160 that links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, remain in gearbox 16, thereby set up second reverse gear " R2 ", described reverse gear " R2 " has the speed ratio γ R2 less than the speed ratio γ R1 of first reverse gear, for example, be approximately 5.375.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 160 of gear ratio ρ 1, the second preposition planetary gear set 158 of the first preposition planetary gear set 156 and the gear ratio ρ 4 of the second rearmounted planetary gear set 162 are designed to be and can realize aforementioned speed ratio.
In addition, obtaining in the speed changer 154 of shelves according to clutch shown in Figure 109 and brake engages figure, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.542, second grade speed ratio γ 2 is 1.480 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.314 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.214, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.316, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.187, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is that the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of 1.088, the eight grades speed ratio γ 8 and the 9th grade is 1.090.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 9) of the speed ratio γ 9 of first grade speed ratio γ 1 and the 9th grade is 6.748, this is bigger value.
In the nomogram shown in Figure 110, four vertical curve Y1 represent the assembly of first speed changing portion 164 to Y4.In the drawings from left to right, line Y1 represents that sun gear S2, the line Y2 of the second preposition planetary gear set 158 represent that sun gear S1, the line Y3 of the first preposition planetary gear set 156 represent that the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 156 that links together and the second preposition planetary gear set 158 and line Y4 represent the planet carrier CA1 of the first preposition planetary gear set 156 that links together and the gear ring R2 of the second preposition planetary gear set 158.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 166 to Y8.In the drawings from left to right, line Y5 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 160 of the first rotating element RE1, line Y6 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 160 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 162, and line Y7 represents to be equivalent to the gear ring R4 of the second rearmounted planetary gear set 162 of the 3rd rotating element RE3, and line Y8 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 160 of the 4th rotating element RE4 and the sun gear S4 of the second rearmounted planetary gear set 162.
In the nomogram in Figure 110, in first grade, first clutch C1 is engaged the 4th rotating element RE4 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of the 4th rotating element RE4 output element 32 in the middle of with first.Simultaneously, the second break B2 is engaged the second rotating element RE2 is remained in the gearbox 16 as nonrotational element, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (1st) expression, and (1st) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y6 and horizontal line XZ and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In second grade, the 5th clutch C5 is engaged so that the first rotating element RE1 is connected with output element 34 in the middle of second, and this causes the first rotating element RE1 to rotate under the speed identical with output element 34 in the middle of second.Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (2nd) expression, and (2nd) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X1 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In third gear, the first break B1 is engaged so that the first rotating element RE1 is remained in gearbox 16, and this causes the rotational velocity of the first rotating element RE1 to be " 0 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (3rd) expression, and (3rd) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line XZ and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In fourth speed, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (4th) expression, and (4th) locates at point, and horizontal line X2 and vertical curve Y7 intersect.
In the 5th grade, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (5th) expression, and (5th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X3 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In the 6th grade, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (6th) expression, and (6th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y6 and horizontal line X3 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In the 7th grade, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (7th) expression, and (7th) locates at point, and horizontal line X3 and vertical curve Y7 intersect.
In the 8th grade, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (8th) expression, and (8th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X2 and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In the 9th grade, the first break B1 is engaged so that the first rotating element RE1 is remained in gearbox 16, and this causes the rotational velocity of the first rotating element RE1 to be " 0 ".Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (9th) expression, and (9th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line XZ and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In first reverse gear, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (Rev1) expression, and (Rev1) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X2 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
In second reverse gear, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (Rev2) expression, and (Rev2) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X3 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
By this way, according to this second correction example of the 9th exemplary embodiment, set up first grade by engaging the first clutch C1 and the second break B2.Set up second grade by engaging first clutch C1 and the 5th clutch C5.Set up third gear by engaging the first clutch C1 and the first break B1.Set up fourth speed by engaging first clutch C1 and three-clutch C3.Set up the 5th grade by engaging first clutch C1 and four clutches C4.Set up the 6th grade by engaging first clutch C1 and second clutch C2.Set up the 7th grade by engaging second clutch C2 and four clutches C4, and set up the 8th grade by engaging second clutch C2 and three-clutch C3.Therefore, this second speed changer 154 of revising example of the 9th exemplary embodiment can be realized eight forward gearss.
This second speed changer 154 of revising example of the 9th exemplary embodiment can also be realized the 9th grade by engaging the second clutch C2 and the first break B1.Therefore, except that can realizing nine forward gearss, can be preferably set the level between the 8th grade and the 9th grade less with intensive speed ratio.
In addition, revise example as the 3rd of the 9th exemplary embodiment, as shown in Figure 111, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 154 can obtain 11 forward gearss and two reverse gears.In addition, Figure 112 is and the corresponding nomogram of Figure 111 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the 3rd correction example of Figure 111 different with aforementioned exemplary embodiment and the 9th exemplary embodiment shown in Figure 112 be described.
As shown in clutch among Figure 111 and brake engages figure, by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up 11 forward gearss, promptly, in first grade " 1st " to the 11 grade " 11th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
As shown in Figure 111, the 5th clutch C5 is engaged with the first rotating element RE1, the i.e. sun gear S3 of the first rearmounted planetary gear set 160, be connected with output element 34 in the middle of second, and the second break B2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, remain in gearbox 16 as nonrotational element, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, be approximately 9.854.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the gear ring R3 of the first rearmounted planetary gear set 160 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and the second break B2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, remain in gearbox 16 as nonrotational element, thereby set up second grade, described second grade has and for example is approximately 5.690 speed ratio γ 2 less than first grade of speed ratio γ 1.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the gear ring R3 of the first rearmounted planetary gear set 160 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and the 5th clutch C5 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 be connected with the second centre output element 34, thereby the third gear of foundation, described third gear has the speed ratio γ 3 less than second grade of speed ratio γ 2, for example, be approximately 3.689.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the gear ring R3 of the first rearmounted planetary gear set 160 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and the first break B1 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 remain in gearbox 16, thereby set up fourth speed, described fourth speed has the speed ratio γ 4 less than third gear speed ratio γ 3, for example, be approximately 2.492.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the gear ring R3 of the first rearmounted planetary gear set 160 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 be connected with the first centre output element 32, thereby set up the 5th grade, described the 5th grade of speed ratio γ 5 that has less than fourth speed speed ratio γ 4, for example, be approximately 1.897.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the gear ring R3 of the first rearmounted planetary gear set 160 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and four clutches C4 be engaged with the first rotating element RE1 promptly the first rearmounted planetary gear set 160 sun gear S3 be connected as the input shaft 22 of importing rotating element, thereby set up the 6th grade, described the 6th grade of speed ratio γ 6 that has less than the 5th grade of speed ratio γ 5, for example, be approximately 1.562.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the gear ring R3 of the first rearmounted planetary gear set 160 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, be connected with input shaft 22, thereby set up the 7th grade, described the 7th grade of speed ratio γ 7 that has less than the 6th grade of speed ratio γ 6, for example, be approximately 1.187.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, be connected with input shaft 22, and four clutches C4 be engaged with the first rotating element RE1 promptly the first rearmounted planetary gear set 160 sun gear S3 be connected as the input shaft 22 of importing rotating element, thereby set up the 8th grade, described the 8th grade of speed ratio γ 8 that has less than the 7th grade of speed ratio γ 7, for example, be approximately 1.000.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, be connected with input shaft 22, and three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 be connected with the first centre output element 32, thereby set up the 9th grade, described the 9th grade of speed ratio γ 9 that has less than the 8th grade of speed ratio γ 8, for example, be approximately 0.919.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, be connected with input shaft 22, and the first break B1 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 remain in gearbox 16, thereby set up the tenth grade, the described ten grade of speed ratio γ 10 that has less than the 9th grade of speed ratio γ 9, for example, be approximately 0.843.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, be connected with input shaft 22, and the 5th clutch C5 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 be connected with the second centre output element 34, thereby set up the 11 grade, described the 11 grade has minimum speed ratio γ 11, for example, be approximately 0.777.
In addition, three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, remain in gearbox 16, thereby set up first reverse gear " R1 ", described reverse gear " R1 " has and is approximately 10.194 speed ratio γ R1.
In addition, four clutches C4 be engaged with the first rotating element RE1 promptly the first rearmounted planetary gear set 160 sun gear S3 be connected as the input shaft 22 of importing rotating element, and the second break B2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, remain in gearbox 16, thereby set up second reverse gear " R2 ", described reverse gear " R2 " has the speed ratio γ R2 less than the speed ratio γ R1 of first reverse gear, for example, be approximately 5.375.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 160 of gear ratio ρ 1, the second preposition planetary gear set 158 of the first preposition planetary gear set 156 and the gear ratio ρ 4 of the second rearmounted planetary gear set 162 are designed to be and can realize aforementioned speed ratio.
In addition, obtaining in the speed changer 154 of shelves according to clutch shown in Figure 111 and brake engages figure, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.732, second grade speed ratio γ 2 is 1.542 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.480 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.314, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.214, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.316, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is 1.187, the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of the 8th grade speed ratio γ 8 and the 9th grade is 1.088, the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.090, and the ratio (=γ 10/ γ 11) of the speed ratio γ 11 of the tenth grade speed ratio γ 10 and the 11 grade is 1.086.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio of first grade speed ratio γ 1 and the 11 grade speed ratio γ 11 (=γ 1/ γ 11) is 12.688, this is bigger numerical value.
In the nomogram in Figure 112, because the structure shown in the perspective view is identical, represent that therefore four vertical curve Y1 of the assembly of first speed changing portion 164 represent and the identical rotating element shown in Figure 106 to Y8 with four vertical curve Y5 of the assembly of expression second speed changing portion 166 to Y4.
In the nomogram in Figure 112, in first grade, the 5th clutch C5 is engaged the first rotating element RE1 being connected in output element 34 in the middle of second, and this causes rotating under the identical speed of first rotating element RE1 output element 34 in the middle of with second.Simultaneously, the second break B2 is engaged the second rotating element RE2 is remained in the gearbox 16 as nonrotational element, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (1st) expression, and (1st) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X1 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
In second grade, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Simultaneously, the second break B2 is engaged the second rotating element RE2 is remained in the gearbox 16 as nonrotational element, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (2nd) expression, and (2nd) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y6 and horizontal line XZ and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In third gear, the 5th clutch C5 is engaged the first rotating element RE1 being connected in output element 34 in the middle of second, and this causes rotating under the identical speed of first rotating element RE1 output element 34 in the middle of with second.Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (3rd) expression, and (3rd) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X1 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In fourth speed, the first break B1 is engaged so that the first rotating element RE1 is remained in gearbox 16, and this causes the rotational velocity of the first rotating element RE1 to be " 0 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (4th) expression, and (4th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line XZ and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In the 5th grade, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (5th) expression, and (5th) locates at point, and horizontal line X2 and vertical curve Y7 intersect.
In the 6th grade, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (6th) expression, and (6th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X3 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In the 7th grade, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Simultaneously, first clutch C1 is engaged so that the 4th rotating element RE4 is connected with output element 32 in the middle of first, and this causes the 4th rotating element RE4 to rotate under the speed identical with output element 32 in the middle of first.Therefore, the rotational velocity of output shaft 36 is by point (7th) expression, and (7th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y6 and horizontal line X3 and the point of intersection of vertical curve Y8 and horizontal line X2 intersect.
In the 8th grade, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (8th) expression, and (8th) locates at point, and horizontal line X3 and vertical curve Y7 intersect.
In the 9th grade, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (9th) expression, and (9th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X2 and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In the tenth grade, the first break B1 is engaged so that the first rotating element RE1 is remained in gearbox 16, and this causes the rotational velocity of the first rotating element RE1 to be " 0 ".Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (10th) expression, and (10th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line XZ and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In the 11 grade, the 5th clutch C5 is engaged the first rotating element RE1 being connected in output element 34 in the middle of second, and this causes rotating under the identical speed of first rotating element RE1 output element 34 in the middle of with second.Simultaneously, second clutch C2 is engaged the second rotating element RE2 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the second rotating element RE2 to be " 1 ".Therefore, the rotational velocity of output shaft 36 is by point (11th) expression, and (11th) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X1 and the point of intersection of vertical curve Y6 and horizontal line X3 intersect.
In first reverse gear, three-clutch C3 is engaged the first rotating element RE1 being connected in output element 32 in the middle of first, and this causes rotating under the identical speed of first rotating element RE1 output element 32 in the middle of with first.Simultaneously, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (Rev1) expression, and (Rev1) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X2 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
In second reverse gear, four clutches C4 is engaged the first rotating element RE1 is connected in the input shaft 22 as the input rotating element, and this causes the rotational velocity of the first rotating element RE1 to be " 1 ".Simultaneously, the second break B2 is engaged so that the second rotating element RE2 is remained in gearbox 16, and this causes the rotational velocity of the second rotating element RE2 to be " 0 ".Therefore, the rotational velocity of output shaft 36 is by point (Rev2) expression, and (Rev2) locates at point, and the straight line and the vertical curve Y7 of the point of intersection of connection vertical curve Y5 and horizontal line X3 and the point of intersection of vertical curve Y6 and horizontal line XZ intersect.
By this way, revise example, by engaging the 5th clutch C5 and the second break B2 sets up first grade according to the 3rd of the 9th exemplary embodiment.Set up second grade by engaging the first clutch C1 and the second break B2.Set up third gear by engaging first clutch C1 and the 5th clutch C5.Set up fourth speed by engaging the first clutch C1 and the first break B1.Set up the 5th grade by engaging first clutch C1 and three-clutch C3.Set up the 6th grade by engaging first clutch C1 and four clutches C4.Set up the 7th grade by engaging first clutch C1 and second clutch C2.Set up the 8th grade by engaging second clutch C2 and four clutches C4.Set up the 9th grade by engaging second clutch C2 and three-clutch C3.Set up the tenth grade by engaging the second clutch C2 and the first break B1, and set up the 11 grade by engaging second clutch and C2 the 5th clutch C5.Therefore, except that can realizing 11 forward gearss, the level between the 8th grade and the 11 grade can preferably be set lessly with intensive speed ratio.
In addition, in traditional 4WD vehicle etc., transfer case (transfer) accommodates low grade or high-grade switching mechanism, so that use is lower than the low grade of " 1st " when travelling on abominable road surface or when vehicle is walked out from mud.This switching mechanism has increased the size of transfer case, and this has not only increased the weight of vehicle but also has hindered installation.In the related speed changer of this exemplary embodiment, can set extremely lowly with first grade, this has got rid of the needs to this transfer case switching mechanism, thereby can make that transfer case is simpler and weight is lighter.
Figure 113 is the perspective view of the structure of the related speed changer 168 of the present invention's the tenth exemplary embodiment.It is middle-grade and be used to set up the figure of the relation between the operation of the required friction engagement device of those grades that Figure 114 and 115 shows speed changer 168.Figure 116 shows the nomogram of the rotational velocity of rotating element in each grade.Except that the structure of first speed changing portion 174, the speed changer 168 of this exemplary embodiment is similar to the speed changer 154 shown in Figure 105 in configuration aspects, the effect of the equivalence that therefore can obtain by this exemplary embodiment and be obtained from previous embodiment.Hereinafter, will the part of the speed changer 168 of this exemplary embodiment different with the part of speed changer 154 be described.
As shown in Figure 113, the first preposition planetary gear set 170 that constitutes the part of first speed changing portion 174 be comprise sun gear S1, small gear P1, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA1 of support small gear P1 and the gear ring R1 that is meshed with sun gear S1 by small gear P1.The same second preposition planetary gear set 172 that constitutes the part of first speed changing portion 174 be comprise sun gear S2, intermeshing many group small gear P2, can rotation and can revolve round the sun the planetary gear set of double pinion type of the planet carrier CA2 of support small gear P2 and the gear ring R2 that is meshed with sun gear S2 by small gear P2.
In first speed changing portion 174, the sun gear S2 of the planet carrier CA1 of the first preposition planetary gear set 170 and the second preposition planetary gear set 172 links together and is connected in the nonrotationally gearbox 16 of element of conduct integratedly, thereby prevents to rotate with respect to gearbox 16.The planet carrier CA2 of the sun gear S1 of the first preposition planetary gear set 170 and the second preposition planetary gear set 172 links together and is connected in integratedly as the input shaft 22 of importing rotating element.In addition, output element 32 in the middle of the gear ring R2 of the second preposition planetary gear set 172 is connected in first integratedly, and the gear ring R1 of the first preposition planetary gear set 170 is connected in the second middle output element 34 integratedly.This structure causes first speed changing portion 174 by the slow down rotation that comes from the input shaft 22 and rotation of being slowed down is delivered to second speed changing portion 166 of output element 32 in the middle of first, and makes the rotations that come from input shaft 22 oppositely and with described backward rotation be delivered to second speed changing portion 166 by output element 34 in the middle of second.
In the speed changer 168 that constitutes as mentioned above, as shown in Figure 114, can be by for example engaging simultaneously from first clutch C1 in response to instruction from ECU42, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
Obtaining in the speed changer 168 of shelves according to clutch shown in Figure 114 and brake engages figure, first grade speed ratio γ 1 is approximately 5.283, second grade speed ratio γ 2 is approximately 3.605, the speed ratio γ 3 of third gear is approximately 2.472, the speed ratio γ 4 of fourth speed is approximately 1.897, the 5th grade speed ratio γ 5 is approximately 1.569, the 6th grade speed ratio γ 6 is approximately 1.024, the 7th grade speed ratio γ 7 is approximately 1.000, the 8th grade speed ratio γ 8 is approximately 0.912, the 9th grade speed ratio γ 9 is approximately 0.830, the tenth grade speed ratio γ 10 is approximately 0.760, the speed ratio γ R2 that the speed ratio γ R1 of first reverse gear is approximately 9.257 and second reverse gear is approximately 4.881.In addition, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.466, second grade speed ratio γ 2 is 1.458 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.304 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.209, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.303, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.204, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is that the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of 1.097, the eight grades speed ratio γ 8 and the 9th grade is 1.098, and the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.093.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 10) of the speed ratio γ 10 of first grade speed ratio γ 1 and the tenth grade is 6.956, this is bigger numerical value.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 160 of gear ratio ρ 1, the second preposition planetary gear set 172 of the first preposition planetary gear set 170 and the gear ratio ρ 4 of the second rearmounted planetary gear set 162 are designed to be and can realize aforementioned speed ratio.
In addition, revise example as first of the tenth exemplary embodiment, although the bonding operation of each grade does not change, by the gear ratio ρ 1 to ρ 4 that suitably sets planetary gear set, speed changer 168 can obtain those shelves shown in Figure 115.Obtaining in the speed changer 168 of shelves according to clutch shown in Figure 115 and brake engages figure, first grade speed ratio γ 1 is approximately 5.690, second grade speed ratio γ 2 is approximately 3.689, the speed ratio γ 3 of third gear is approximately 2.492, the speed ratio γ 4 of fourth speed is approximately 1.897, the 5th grade speed ratio γ 5 is approximately 1.562, the 6th grade speed ratio γ 6 is approximately 1.187, the 7th grade speed ratio γ 7 is approximately 1.000, the 8th grade speed ratio γ 8 is approximately 0.919, the 9th grade speed ratio one is approximately 0.843, the tenth grade speed ratio γ 10 is approximately 0.777, the speed ratio γ R2 that the speed ratio γ R1 of first reverse gear is approximately 10.194 and second reverse gear is approximately 5.375.In addition, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.542, second grade speed ratio γ 2 is 1.480 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.314 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.214, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.316, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.187, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is that the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of 1.088, the eight grades speed ratio γ 8 and the 9th grade is 1.090, and the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.086.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 10) of the speed ratio γ 10 of first grade speed ratio γ 1 and the tenth grade is 7.326, this is bigger numerical value.By suitably setting the gear ratio of each planetary gear set by this way, the overall ratio scope can be set widelyer than the overall ratio scope shown in Figure 114.
In the nomogram shown in Figure 116, four vertical curve Y1 represent the assembly of first speed changing portion 174 to Y4.In the drawings from left to right, line Y1 represents to link together with the sun gear S1 of the first preposition planetary gear set 170 that constitutes a rotating element and the planet carrier CA2 of the second preposition planetary gear set 172, line Y2 represents the gear ring R2 as the second preposition planetary gear set 172 of another rotating element, line Y3 represents to link together with the planet carrier CA1 of the first preposition planetary gear set 170 that constitutes another rotating element and the sun gear S2 of the second preposition planetary gear set 172, and line Y4 represents the gear ring R1 as the first preposition planetary gear set 170 of another rotating element.Therefore, based on these rotating elements, the nomogram shown in Figure 116 is similar to for example nomogram shown in above-mentioned Figure 108, therefore omits the description to it.
Here, revise example as second of the tenth exemplary embodiment, as shown in Figure 117, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 168 can obtain nine forward gearss and two reverse gears.In addition, Figure 118 is and the corresponding nomogram of Figure 117 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the second correction example of Figure 117 different with aforementioned exemplary embodiment and the tenth exemplary embodiment shown in Figure 118 be described.
As shown in clutch among Figure 117 and brake engages figure, by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
As shown in Figure 117, first clutch C1 is engaged with the 4th rotating element RE4, the gear ring R3 of the first rearmounted planetary gear set 160 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and the second break B2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, remain in gearbox 16 as nonrotational element, thereby set up first grade, described first grade has maximum speed ratio γ 1, for example, be approximately 5.690.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the gear ring R3 of the first rearmounted planetary gear set 160 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and the 5th clutch C5 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 be connected with the second centre output element 34, thereby set up second grade, described second grade of speed ratio γ 2 that has less than first grade of speed ratio γ 1, for example, be approximately 3.689.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the gear ring R3 of the first rearmounted planetary gear set 160 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and the first break B1 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 remain in gearbox 16, thereby the third gear of foundation, described third gear has the speed ratio γ 3 less than second grade of speed ratio γ 2, for example, be approximately 2.492.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the gear ring R3 of the first rearmounted planetary gear set 160 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 be connected with the first centre output element 32, thereby set up fourth speed, described fourth speed has the speed ratio γ 4 less than third gear speed ratio γ 3, for example, be approximately 1.897.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the gear ring R3 of the first rearmounted planetary gear set 160 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and four clutches C4 be engaged with the first rotating element RE1 promptly the first rearmounted planetary gear set 160 sun gear S3 be connected as the input shaft 22 of importing rotating element, thereby set up the 5th grade, described the 5th grade of speed ratio γ 5 that has less than fourth speed speed ratio γ 4, for example, be approximately 1.562.
In addition, first clutch C1 is engaged with the 4th rotating element RE4, the gear ring R3 of the first rearmounted planetary gear set 160 that promptly links together and the sun gear S4 of the second rearmounted planetary gear set 162, be connected with output element 32 in the middle of first, and second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, be connected with input shaft 22, thereby set up the 6th grade, described the 6th grade of speed ratio γ 6 that has less than the 5th grade of speed ratio γ 5, for example, be approximately 1.187.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, be connected with input shaft 22, and four clutches C4 be engaged with the first rotating element RE1 promptly the first rearmounted planetary gear set 160 sun gear S3 be connected as the input shaft 22 of importing rotating element, thereby set up the 7th grade, described the 7th grade of speed ratio γ 7 that has less than the 6th grade of speed ratio γ 6, for example, be approximately 1.000.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, be connected with input shaft 22, and three-clutch C3 is engaged with output element 32 in the middle of promptly the sun gear S3 of the first rearmounted planetary gear set 160 is connected in first with the first rotating element RE1, thereby set up the 8th grade, described the 8th grade of speed ratio γ 8 that has less than the 7th grade of speed ratio γ 7, for example, be approximately 0.919.
In addition, second clutch C2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, be connected with input shaft 22, and the first break B1 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 remain in gearbox 16, thereby set up the 9th grade, described the 9th grade of speed ratio γ 9 that has less than the 8th grade of speed ratio γ 8, for example, be approximately 0.843.
In addition, three-clutch C3 be engaged with the first rotating element RE1 promptly the sun gear S3 of the first rearmounted planetary gear set 160 be connected with the first centre output element 32, and the second break B2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, remain in gearbox 16, thereby set up first reverse gear " R1 ", described reverse gear " R1 " has and is approximately 10.194 speed ratio γ R1.
In addition, four clutches C4 be engaged with the first rotating element RE1 promptly the first rearmounted planetary gear set 160 sun gear S3 be connected as the input shaft 22 of importing rotating element, and the second break B2 is engaged with the second rotating element RE2, the planet carrier CA3 of the first rearmounted planetary gear set 160 that promptly links together and the planet carrier CA4 of the second rearmounted planetary gear set 162, remain in gearbox 16, thereby set up second reverse gear " R2 ", described reverse gear " R2 " has the speed ratio γ R2 less than the speed ratio γ R1 of first reverse gear, for example, be approximately 5.375.The gear ratio ρ 3 of gear ratio ρ 2, the first rearmounted planetary gear set 160 of gear ratio ρ 1, the second preposition planetary gear set 172 of the first preposition planetary gear set 170 and the gear ratio ρ 4 of the second rearmounted planetary gear set 162 are designed to be and can realize aforementioned speed ratio.
Obtaining in the speed changer 168 of shelves according to clutch shown in Figure 117 and brake engages figure, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.542, second grade speed ratio γ 2 is 1.480 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.314 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.214, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.316, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.187, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is that the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of 1.088, the eight grades speed ratio γ 8 and the 9th grade is 1.090.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 9) of the speed ratio γ 9 of first grade speed ratio γ 1 and the 9th grade is 6.748, this is bigger numerical value.
In the nomogram shown in Figure 118, four vertical curve Y1 represent the assembly of first speed changing portion 174 to Y4.In the drawings from left to right, line Y1 represents that gear ring R1, the line Y2 of the first preposition planetary gear set 170 represent that sun gear S2, the line Y3 of the planet carrier CA1 of the first preposition planetary gear set 170 that links together and the second preposition planetary gear set 172 represent that the gear ring R2 of the second preposition planetary gear set 172 and line Y4 represent the sun gear S1 of the first preposition planetary gear set 170 that links together and the planet carrier CA2 of the second preposition planetary gear set 172.In addition, four vertical curve Y5 represent the assembly of second speed changing portion 166 to Y8.In the drawings from left to right, line Y5 represents to be equivalent to the sun gear S3 of the first rearmounted planetary gear set 160 of the first rotating element RE1, line Y6 represents to link together and is equivalent to the planet carrier CA3 of the first rearmounted planetary gear set 160 of the second rotating element RE2 and the planet carrier CA4 of the second rearmounted planetary gear set 162, and line Y7 represents to be equivalent to the gear ring R4 of the second rearmounted planetary gear set 162 of the 3rd rotating element RE3, and line Y8 represents to link together and is equivalent to the gear ring R3 of the first rearmounted planetary gear set 160 of the 4th rotating element RE4 and the sun gear S4 of the second rearmounted planetary gear set 162.Based on these rotating elements, therefore similar to shown in Figure 110 of the nomogram shown in Figure 118 will omit the description to it.
By this way, according to this second correction example of the tenth exemplary embodiment, set up first grade by engaging the first clutch C1 and the second break B2.Set up second grade by engaging first clutch C1 and the 5th clutch C5.Set up third gear by engaging the first clutch C1 and the first break B1.Set up fourth speed by engaging first clutch C1 and three-clutch C3.Set up the 5th grade by engaging first clutch C1 and four clutches C4.Set up the 6th grade by engaging first clutch C1 and second clutch C2.Set up the 7th grade by engaging second clutch C2 and four clutches C4, and set up the 8th grade by engaging second clutch C2 and three-clutch C3.Therefore, second of the tenth exemplary embodiment speed changer 168 of revising example can be realized eight forward gearss.
This second speed changer 168 of revising example of the tenth exemplary embodiment can also be realized the 9th grade by engaging the second clutch C2 and the first break B1.Therefore, except that can realizing nine forward gearss, can be preferably set the level between the 8th grade and the 9th grade less with intensive speed ratio.
Figure 119 is the perspective view of the structure of the related speed changer 169 of the present invention's the 11 exemplary embodiment.It is middle-grade and be used to set up the figure of the relation between the operation of the required friction engagement device of those grades that Figure 120 shows speed changer 169.Figure 121 shows the nomogram of the rotational velocity of rotating element in each grade.Except that the structure of first speed changing portion 175, the speed changer 169 of this exemplary embodiment is similar to the speed changer 168 shown in Figure 113 in configuration aspects, the effect of the equivalence that therefore can obtain by this exemplary embodiment and be obtained from previous embodiment.Hereinafter, will the part of the speed changer 169 of this exemplary embodiment different with the part of speed changer 168 be described.
In first speed changing portion 175, being equal in annexation between the first preposition planetary gear set 171 and the second preposition planetary gear set 173 and first speed changing portion 174 of above-mentioned speed changer 168,, therefore first speed changing portion 175 is first speed changing portion of equivalence substantially.Yet in above-mentioned speed changer 168, four clutches C4 and the 5th clutch C5 are arranged between first speed changing portion 174 and second speed changing portion 166.In contrast, in the related speed changer 169 of this exemplary embodiment, four clutches C4 and the 5th clutch C5 are set to and are close to first speed changing portion 175.That is to say that speed changer 169 is configured to clutch is suitably distributed.
In the speed changer 169 that constitutes as mentioned above, as shown in Figure 120, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up 11 forward gearss, promptly, in first grade " 1st " to the 11 grade " 11th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.Bonding operation of each grade of the speed changer 169 that this exemplary embodiment is related and speed ratio are described identical with above-mentioned Figure 111, therefore will omit giving unnecessary details it.
In the nomogram of Figure 121, because those in its annexation and the above-mentioned speed changer 168 are essentially identical, so four vertical curve Y1 of first speed changing portion 175 are identical with among Figure 118 those to Y4.In addition, because the structure of second speed changing portion 166 is identical, therefore, the vertical curve Y5 of second speed changing portion 166 is also identical with among Figure 118 those to Y9.Therefore, based on these rotating elements, the nomogram shown in Figure 121 is similar to the nomogram shown in above-mentioned Figure 112, therefore will omit the description to it.
Therefore, in the related speed changer 169 of the 11 exemplary embodiment, by with different compound mode engaging clutches and break and suitably set the gear ratio of each planetary gear set, can obtain 11 forward gearss and two reverse gears, and more particularly, the level between the 8th grade and the 11 grade can be set lessly with intensive speed ratio.And, by clutch being arranged in equably the structure that can simplify in the speed changer 169 in the speed changer 169.
In addition, in traditional 4WD vehicle etc., transfer case accommodates low grade or high-grade switching mechanism, so that be lower than the low grade of " 1st " when travelling or when use when vehicle is walked out from mud on abominable road surface.This switching mechanism has increased the size of transfer case, and this has not only increased the weight of vehicle but also has hindered installation.Yet, in the related speed changer of this exemplary embodiment, can set extremely lowly with first grade, this has got rid of the needs to this transfer case switching mechanism, thereby can make that transfer case is simpler and weight is lighter.
Figure 122 is the perspective view of the structure of the related speed changer 176 of the present invention's the 12 exemplary embodiment.It is middle-grade and be used to set up the figure of the relation between the operation of the required friction engagement device of those grades that Figure 123 shows speed changer 176.Figure 124 shows the nomogram of the rotational velocity of rotating element in each grade.Except that the structure of first speed changing portion 182, the speed changer 176 of this exemplary embodiment is similar to the speed changer 66 shown in Figure 12 in configuration aspects, the effect of the equivalence that therefore can obtain by this exemplary embodiment and be obtained from previous embodiment.Hereinafter, will the part of the speed changer 176 of this exemplary embodiment different with the part of speed changer 66 be described.
As shown in Figure 122, the first preposition planetary gear set 178 that constitutes the part of first speed changing portion 182 be comprise sun gear S1, small gear P1, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA1 of support small gear P1 and the gear ring R1 that is meshed with sun gear S1 by small gear P1.The same second preposition planetary gear set 180 that constitutes the part of first speed changing portion 182 be comprise sun gear S2, small gear P2, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA2 of support small gear P2 and the gear ring R2 that is meshed with sun gear S2 by small gear P2.In this first speed changing portion 182, the small gear P1 of the first preposition planetary gear set 178 has the diameter greater than the small gear P2 of the second preposition planetary gear set 180.And those small gears P1 and P2 form mutually, form stepped pinion SP.In addition, the planet carrier CA2 of the planet carrier CA1 of the first preposition planetary gear set 178 and the second preposition planetary gear set 180 is individual unit and the gear ring R2 that dispenses the second preposition planetary gear set 180.
In first speed changing portion 182, aforesaid, be that the first preposition planetary gear set 178 and the second preposition planetary gear set 180 common planet carrier CA1 (CA2) are connected in the gearbox 16 as nonrotational element integratedly, this prevents that planet carrier CA1 (CA2) from rotating with respect to gearbox 16.In addition, the sun gear S1 of the first preposition planetary gear set 178 is connected in the input shaft 22 as the input rotating element integratedly.In addition, the sun gear S2 of the second preposition planetary gear set 180 is connected in output element 32 in the middle of first integratedly, therefore as output element in the middle of similar to output element 32 in the middle of first first.In addition, the gear ring R1 of the first preposition planetary gear set 178 is connected in output element 34 in the middle of second integratedly, therefore as output element in the middle of similar to output element 34 in the middle of second second.This structure causes first speed changing portion 182 by the slow down rotation that comes from the input shaft 22 and rotation of being slowed down is delivered to second speed changing portion 64 of output element 32 in the middle of first, and makes the rotations that come from input shaft 22 oppositely and with described backward rotation be delivered to second speed changing portion 64 by output element 34 in the middle of second.
In the speed changer 176 that constitutes as mentioned above, as shown in Figure 123, can be by for example engaging simultaneously from first clutch C1 in response to instruction from ECU42, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
Obtaining in the speed changer 176 of shelves according to clutch shown in Figure 123 and brake engages figure, first grade speed ratio γ 1 is approximately 4.917, second grade speed ratio γ 2 is approximately 3.290, the speed ratio γ 3 of third gear is approximately 2.222, the speed ratio γ 4 of fourth speed is approximately 1.645, the 5th grade speed ratio γ 5 is approximately 1.409, the 6th grade speed ratio γ 6 is approximately 1.244, the 7th grade speed ratio γ 7 is approximately 1.000, the 8th grade speed ratio γ 8 is approximately 0.825, the 9th grade speed ratio γ 9 is approximately 0.649, the tenth grade speed ratio γ 10 is approximately 0.574, the speed ratio γ R2 that the speed ratio γ R1 of first reverse gear is approximately 3.047 and second reverse gear is approximately 1.852.In addition, the ratio of first grade speed ratio γ 1 and second grade speed ratio γ 2 (=γ 1/ γ 2) is 1.511, second grade speed ratio γ 2 is 1.481 with the ratio (=γ 2/ γ 3) of the speed ratio γ 3 of third gear, the speed ratio γ 3 of third gear is 1.351 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.167, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.133, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.244, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is that the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of 1.212, the eight grades speed ratio γ 8 and the 9th grade is 1.271, and
The ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.131.Therefore, each speed ratio γ changes with essentially identical ratio.In addition, the overall ratio scope, that is, the ratio (=γ 1/ γ 10) of the speed ratio γ 10 of first grade speed ratio γ 1 and the tenth grade is 8.655, this is bigger numerical value.
In the nomogram shown in Figure 124, four vertical curve Y1 represent the assembly of first speed changing portion 182 to Y4.In the drawings from left to right, line Y1 represents that sun gear S1, line Y2 as the first preposition planetary gear set 178 of a rotating element represents that sun gear S2, line Y3 as the second preposition planetary gear set 180 of another rotating element represents to link together and represent gear ring R1 as the first preposition planetary gear set 178 of another rotating element with the planet carrier CA2 of the planet carrier CA1 of the first preposition planetary gear set 178 that constitutes another rotating element and the second preposition planetary gear set 180 and line Y4.In addition, the rotational velocity of the gear ring R2 of the second preposition planetary gear set 180 is represented by the length dotted line that replaces.Therefore, based on these rotating elements, the nomogram shown in Figure 124 is similar to for example nomogram shown in above-mentioned Figure 14, therefore omits the description to it.
By this way, according to the 12 exemplary embodiment, first speed changing portion 182 comprises first preposition planetary gear set 178 of single small gear type and the second preposition planetary gear set 180 of single small gear type.The planet carrier CA2 of the planet carrier CA1 of the first preposition planetary gear set 178 and the second preposition planetary gear set 180 always is connected in the gearbox 16 as nonrotational element, and the sun gear S1 of the first preposition planetary gear set 178 is connected in the input shaft 22 as the input rotating element.Therefore, the sun gear S2 of the second preposition planetary gear set 180 is as the first middle output element 32, and the gear ring R1 of the first preposition planetary gear set 178 is as the second middle output element 34 simultaneously.Therefore, can provide practical speed changer 176.
Figure 125 is the perspective view of the structure of the related speed changer 184 of the present invention's the 13 exemplary embodiment.It is middle-grade and be used to set up the figure of the relation between the operation of the required friction engagement device of those grades that Figure 126 shows speed changer 184.Figure 127 shows the nomogram of the rotational velocity of rotating element in each grade.Except that the structure of first speed changing portion 190, the speed changer 184 of this exemplary embodiment is similar to the speed changer 66 shown in Figure 12 in configuration aspects, the effect of the equivalence that therefore can obtain by this exemplary embodiment and be obtained from previous embodiment.Hereinafter, will the part of the speed changer 186 of this exemplary embodiment different with the part of speed changer 66 be described.
As shown in Figure 125, the first preposition planetary gear set 186 that constitutes the part of first speed changing portion 190 be comprise sun gear S1, small gear P1, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA1 of support small gear P1 and the gear ring R1 that is meshed with sun gear S1 by small gear P1.The same second preposition planetary gear set 188 that constitutes the part of first speed changing portion 190 be comprise sun gear S2, small gear P2, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA2 of support small gear P2 and the gear ring R2 that is meshed with sun gear S2 by small gear P2.In this first speed changing portion 190, the small gear P1 of the first preposition planetary gear set 186 has the diameter greater than the small gear P2 of the second preposition planetary gear set 188.And those small gears P1 and P2 form mutually, form stepped pinion SP.In addition, the planet carrier CA2 of the planet carrier CA1 of the first preposition planetary gear set 186 and the second preposition planetary gear set 188 is individual unit and the gear ring R1 that dispenses the first preposition planetary gear set 186.
In first speed changing portion 190, aforesaid, be that the first preposition planetary gear set 186 and the second preposition planetary gear set 188 common planet carrier CA1 (CA2) are connected in the gearbox 16 as nonrotational element integratedly, this prevents that planet carrier CA1 (CA2) from rotating with respect to gearbox 16.In addition, the sun gear S1 of the first preposition planetary gear set 186 is connected in the input shaft 22 as the input rotating element integratedly.In addition, the sun gear S2 of the second preposition planetary gear set 188 is connected in output element 32 in the middle of first integratedly, therefore as output element in the middle of similar to output element 32 in the middle of first first.In addition, the gear ring R2 of the second preposition planetary gear set 188 is connected in output element 34 in the middle of second integratedly, therefore as output element in the middle of similar to output element 34 in the middle of second second.This structure causes first speed changing portion 190 by the slow down rotation that comes from the input shaft 22 and rotation of being slowed down is delivered to second speed changing portion 64 of output element 32 in the middle of first, and makes the rotations that come from input shaft 22 oppositely and with described backward rotation be delivered to second speed changing portion 64 by output element 34 in the middle of second.
In the speed changer 184 that constitutes as mentioned above, as shown in Figure 126, can be by for example engaging simultaneously from first clutch C1 in response to instruction from ECU42, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
In the nomogram shown in Figure 127, four vertical curve Y1 represent the assembly of first speed changing portion 190 to Y4.In the drawings from left to right, line Y1 represents that sun gear S1, line Y2 as the first preposition planetary gear set 186 of a rotating element represents that sun gear S2, line Y3 as the second preposition planetary gear set 188 of another rotating element represents to link together and represent gear ring R2 as the second preposition planetary gear set 188 of another rotating element with the planet carrier CA2 of the planet carrier CA1 of the first preposition planetary gear set 186 that constitutes another rotating element and the second preposition planetary gear set 188 and line Y4.In addition, the rotational velocity of the gear ring R1 of the first preposition planetary gear set 186 is represented by the length dotted line that replaces.Therefore, based on these rotating elements, the nomogram shown in Figure 127 is similar to for example nomogram shown in above-mentioned Figure 14, therefore omits the description to it.
By this way, according to the 13 exemplary embodiment, first speed changing portion 190 comprises first preposition planetary gear set 186 of single small gear type and the second preposition planetary gear set 188 of single small gear type.The planet carrier CA2 of the planet carrier CA1 of the first preposition planetary gear set 186 and the second preposition planetary gear set 188 always is connected in the gearbox 16 as nonrotational element, and the sun gear S1 of the first preposition planetary gear set 186 is connected in the input shaft 22 as the input rotating element.Therefore, the sun gear S2 of the second preposition planetary gear set 188 is as the first middle output element 32, and the gear ring R2 of the second preposition planetary gear set 188 is as the second middle output element 34 simultaneously.Therefore, can provide practical speed changer 184.
Figure 128 is the perspective view of the structure of the related speed changer 192 of the present invention's the 14 exemplary embodiment.It is middle-grade and be used to set up the figure of the relation between the operation of the required friction engagement device of those grades that Figure 129 shows speed changer 192.Figure 130 shows the nomogram of the rotational velocity of rotating element in each grade.Except that the structure of first speed changing portion 198, the speed changer 192 of this exemplary embodiment is similar to the speed changer 66 shown in Figure 12 in configuration aspects, the effect of the equivalence that therefore can obtain by this exemplary embodiment and be obtained from previous embodiment.Hereinafter, will the part of the speed changer 192 of this exemplary embodiment different with the part of speed changer 66 be described.
As shown in Figure 128, the first preposition planetary gear set 194 that constitutes the part of first speed changing portion 198 be comprise sun gear S1, small gear P1, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA1 of support small gear P1 and the gear ring R1 that is meshed with sun gear S1 by small gear P1.The same second preposition planetary gear set 196 that constitutes the part of first speed changing portion 198 be comprise sun gear S2, small gear P2, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA2 of support small gear P2 and the gear ring R2 that is meshed with sun gear S2 by small gear P2.In this first speed changing portion 198, the small gear P1 of the first preposition planetary gear set 194 has the diameter greater than the small gear P2 of the second preposition planetary gear set 196.And those small gears P1 and P2 form mutually, form stepped pinion SP.In addition, the planet carrier CA2 of the planet carrier CA1 of the first preposition planetary gear set 194 and the second preposition planetary gear set 196 is individual unit and the gear ring R1 that dispenses the first preposition planetary gear set 194.
In first speed changing portion 198, the sun gear S2 of the second preposition planetary gear set 196 is connected in the gearbox 16 as nonrotational element integratedly, and this prevents that sun gear S2 from rotating with respect to gearbox 16.In addition, the gear ring R2 of the second preposition planetary gear set 196 is connected in the input shaft 22 as the input rotating element integratedly.And, aforesaid, be that the first preposition planetary gear set 194 and the second preposition planetary gear set 196 common planet carrier CA1 (CA2) are connected in output element 32 in the middle of first integratedly, therefore as output element in the middle of similar to output element 32 in the middle of first first.In addition, the sun gear S1 of the first preposition planetary gear set 194 is connected in output element 34 in the middle of second integratedly, therefore as output element in the middle of similar to output element 34 in the middle of second second.This structure causes first speed changing portion 198 by the slow down rotation that comes from the input shaft 22 and rotation of being slowed down is delivered to second speed changing portion 64 of output element 32 in the middle of first, and makes the rotations that come from input shaft 22 oppositely and with described backward rotation be delivered to second speed changing portion 64 by output element 34 in the middle of second.
In the speed changer 192 that constitutes as mentioned above, as shown in Figure 129, can be by for example engaging simultaneously from first clutch C1 in response to instruction from ECU42, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
In the nomogram shown in Figure 130, four vertical curve Y1 represent the assembly of first speed changing portion 198 to Y4.In the drawings from left to right, line Y1 represents that gear ring R2, line Y2 as the second preposition planetary gear set 196 of a rotating element represent to link together planet carrier CA2, line Y3 with the planet carrier CA1 of the first preposition planetary gear set 194 that constitutes another rotating element and the second preposition planetary gear set 196 represents to represent sun gear S1 as the first preposition planetary gear set 194 of another rotating element as the sun gear S2 of the second preposition planetary gear set 196 of another rotating element and line Y4.In addition, the rotational velocity of the gear ring R1 of the first preposition planetary gear set 194 is represented by the length dotted line that replaces.Therefore, based on these rotating elements, the nomogram shown in Figure 130 is similar to for example nomogram shown in above-mentioned Figure 14, therefore omits the description to it.
By this way, according to the 14 exemplary embodiment, first speed changing portion 198 comprises first preposition planetary gear set 194 of single small gear type and the second preposition planetary gear set 196 of single small gear type.The sun gear S2 of the second preposition planetary gear set 196 always is connected in the gearbox 16 as nonrotational element.The planet carrier CA2 of the planet carrier CA1 of the first preposition planetary gear set 194 and the second preposition planetary gear set 196 links together constituting a rotating element, and the gear ring R2 of the second preposition planetary gear set 196 is connected in the input shaft 22 as the input rotating element.Therefore, a rotating element, promptly, the planet carrier CA1 of the first preposition planetary gear set 194 that links together and the planet carrier CA2 of the second preposition planetary gear set 196 are as the first middle output element 32, and the sun gear S1 of the first preposition planetary gear set 194 is as the second middle output element 34 simultaneously.Therefore, can provide practical speed changer 192.
Figure 131 is the perspective view of the structure of the related speed changer 200 of the present invention's the 15 exemplary embodiment.It is middle-grade and be used to set up the figure of the relation between the operation of the required friction engagement device of those grades that Figure 132 shows speed changer 200.Figure 133 shows the nomogram of the rotational velocity of rotating element in each grade.Except that the structure of first speed changing portion 206, the speed changer 200 of this exemplary embodiment is similar to the speed changer 66 shown in Figure 12 in configuration aspects, the effect of the equivalence that therefore can obtain by this exemplary embodiment and be obtained from previous embodiment.Hereinafter, will the part of the speed changer 200 of this exemplary embodiment different with the part of speed changer 66 be described.
As shown in Figure 131, the first preposition planetary gear set 202 that constitutes the part of first speed changing portion 206 be comprise sun gear S1, small gear P1, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA1 of support small gear P1 and the gear ring R1 that is meshed with sun gear S1 by small gear P1.The same second preposition planetary gear set 204 that constitutes the part of first speed changing portion 206 be comprise sun gear S2, small gear P2, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA2 of support small gear P2 and the gear ring R2 that is meshed with sun gear S2 by small gear P2.In this first speed changing portion 206, the small gear P1 of the first preposition planetary gear set 202 has the diameter greater than the small gear P2 of the second preposition planetary gear set 204.And those small gears P1 and P2 form mutually, form stepped pinion SP.In addition, the planet carrier CA2 of the planet carrier CA1 of the first preposition planetary gear set 202 and the second preposition planetary gear set 204 is individual unit and the gear ring R2 that dispenses the second preposition planetary gear set 204.
In first speed changing portion 206, the sun gear S2 of the second preposition planetary gear set 204 is connected in the gearbox 16 as nonrotational element integratedly, and this prevents that sun gear S2 from rotating with respect to gearbox 16.In addition, the gear ring R1 of the first preposition planetary gear set 202 is connected in the input shaft 22 as the input rotating element integratedly.And, aforesaid, be that the first preposition planetary gear set 202 and the second preposition planetary gear set 204 common planet carrier CA1 (CA2) are connected in output element 32 in the middle of first integratedly, therefore as output element in the middle of similar to output element 32 in the middle of first first.In addition, the sun gear S1 of the first preposition planetary gear set 202 is connected in output element 34 in the middle of second integratedly, therefore as output element in the middle of similar to output element 34 in the middle of second second.This structure causes first speed changing portion 206 by the slow down rotation that comes from the input shaft 22 and rotation of being slowed down is delivered to second speed changing portion 64 of output element 32 in the middle of first, and makes the rotations that come from input shaft 22 oppositely and with described backward rotation be delivered to second speed changing portion 64 by output element 34 in the middle of second.
In the speed changer 200 that constitutes as mentioned above, as shown in Figure 132, can be by for example engaging simultaneously from first clutch C1 in response to instruction from ECU42, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
In the nomogram shown in Figure 133, four vertical curve Y1 represent the assembly of first speed changing portion 206 to Y4.In the drawings from left to right, line Y1 represents that gear ring R1, line Y2 as the first preposition planetary gear set 202 of a rotating element represent to link together planet carrier CA2, line Y3 with the planet carrier CA1 of the first preposition planetary gear set 202 that constitutes another rotating element and the second preposition planetary gear set 204 represents to represent sun gear S1 as the first preposition planetary gear set 202 of another rotating element as the sun gear S2 of the second preposition planetary gear set 204 of another rotating element and line Y4.In addition, the rotational velocity of the gear ring R2 of the second preposition planetary gear set 204 is represented by the length dotted line that replaces.Therefore, based on these rotating elements, the nomogram shown in Figure 133 is similar to for example nomogram shown in above-mentioned Figure 14, therefore omits the description to it.
By this way, according to the 15 exemplary embodiment, first speed changing portion 206 comprises first preposition planetary gear set 202 of single small gear type and the second preposition planetary gear set 204 of single small gear type.The sun gear S2 of the second preposition planetary gear set 204 always is connected in the gearbox 16 as nonrotational element.The planet carrier CA2 of the planet carrier CA1 of the first preposition planetary gear set 202 and the second preposition planetary gear set 204 links together constituting a rotating element, and the gear ring R1 of the first preposition planetary gear set 202 is connected in the input shaft 22 as the input rotating element.Therefore, a rotating element, promptly, the planet carrier CA1 of the first preposition planetary gear set 202 that links together and the planet carrier CA2 of the second preposition planetary gear set 204 are as the first middle output element 32, and the sun gear S1 of the first preposition planetary gear set 202 is as the second middle output element 34 simultaneously.Therefore, can provide practical speed changer 192.
Figure 134 is the perspective view of the structure of the related speed changer 210 of the present invention's the 16 exemplary embodiment.It is middle-grade and be used to set up the figure of the relation between the operation of the required friction engagement device of those grades that Figure 135 shows speed changer 210.Figure 136 shows the nomogram of the rotational velocity of rotating element in each grade.Except that the structure of first speed changing portion 216, the speed changer 210 of this exemplary embodiment is similar to the speed changer 66 shown in Figure 12 in configuration aspects, the effect of the equivalence that therefore can obtain by this exemplary embodiment and be obtained from previous embodiment.Hereinafter, will the part of the speed changer 210 of this exemplary embodiment different with the part of speed changer 66 be described.
As shown in Figure 134, the first preposition planetary gear set 212 that constitutes the part of first speed changing portion 216 be comprise sun gear S1, small gear P1, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA1 of support small gear P1 and the gear ring R1 that is meshed with sun gear S1 by small gear P1.The same second preposition planetary gear set 214 that constitutes the part of first speed changing portion 216 be comprise sun gear S2, intermeshing many group small gear P2, can rotation and can revolve round the sun the planetary gear set of double pinion type of the planet carrier CA2 of support small gear P2 and the gear ring R2 that is meshed with sun gear S2 by small gear P2.
In first speed changing portion 216, the gear ring R2 of the second preposition planetary gear set 214 is connected in the gearbox 16 as nonrotational element integratedly, and this prevents that gear ring R2 from rotating with respect to gearbox 16.In addition, the gear ring R1 of the first preposition planetary gear set 212 is connected in the input shaft 22 as the input rotating element integratedly.In addition, the planet carrier CA1 of the first preposition planetary gear set 212 that links together and the sun gear S2 of the second preposition planetary gear set 214 are connected in output element 32 in the middle of first integratedly, therefore as output element in the middle of similar to output element 32 in the middle of first first.In addition, the sun gear S1 of the first preposition planetary gear set 212 that links together and the planet carrier CA2 of the second preposition planetary gear set 214 are connected in output element 34 in the middle of second integratedly, therefore as output element in the middle of similar to output element 34 in the middle of second second.This structure causes first speed changing portion 216 by the slow down rotation that comes from the input shaft 22 and rotation of being slowed down is delivered to second speed changing portion 64 of output element 32 in the middle of first, and makes the rotations that come from input shaft 22 oppositely and with described backward rotation be delivered to second speed changing portion 64 by output element 34 in the middle of second.
In the speed changer 200 that constitutes as mentioned above, as shown in Figure 135, can be by for example engaging simultaneously from first clutch C1 in response to instruction from ECU42, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
In the nomogram shown in Figure 136, four vertical curve Y1 represent the assembly of first speed changing portion 216 to Y4.In the drawings from left to right, line Y1 represents to link together with the sun gear S1 of the first preposition planetary gear set 212 that constitutes a rotating element and the planet carrier CA2 of the second preposition planetary gear set 214, line Y2 represents the gear ring R2 as the second preposition planetary gear set 214 of another rotating element, line Y3 represents to link together with the planet carrier CA1 of the first preposition planetary gear set 212 that constitutes another rotating element and the sun gear S2 of the second preposition planetary gear set 214, and line Y4 represents the gear ring R1 as the first preposition planetary gear set 212 of another rotating element.Therefore, based on these rotating elements, the nomogram shown in Figure 136 is similar to for example nomogram shown in above-mentioned Figure 16, therefore omits the description to it.
By this way, according to the 16 exemplary embodiment, first speed changing portion 216 comprises first preposition planetary gear set 212 of single small gear type and the second preposition planetary gear set 214 of double pinion type.The gear ring R2 of the second preposition planetary gear set 214 always is connected in the gearbox 16 as nonrotational element.The sun gear S2 of the planet carrier CA1 of the first preposition planetary gear set 212 and the second preposition planetary gear set 214 links together, the planet carrier CA2 of the sun gear S1 of the first preposition planetary gear set 212 and the second preposition planetary gear set 214 links together, and the gear ring R1 of the first preposition planetary gear set 212 is connected in input shaft 22.Therefore, the planet carrier CA1 of the first preposition planetary gear set 212 that links together and the sun gear S2 of the second preposition planetary gear set 214 are as the first middle output element 32, and the planet carrier CA2 of the sun gear S1 of the first preposition planetary gear set 212 that links together and the second preposition planetary gear set 214 is as the second middle output element 34.Therefore, can provide practical speed changer 210.
Figure 137 is the perspective view of the structure of the related speed changer 220 of the present invention's the 17 exemplary embodiment.It is middle-grade and be used to set up the figure of the relation between the operation of the required friction engagement device of those grades that Figure 138 shows speed changer 220.Figure 139 shows the nomogram of the rotational velocity of rotating element in each grade.Except that the structure of first speed changing portion 226, the speed changer 220 of this exemplary embodiment is similar to the speed changer 66 shown in Figure 12 in configuration aspects, the effect of the equivalence that therefore can obtain by this exemplary embodiment and be obtained from previous embodiment.Hereinafter, will the part of the speed changer 220 of this exemplary embodiment different with the part of speed changer 66 be described.
As shown in Figure 137, the first preposition planetary gear set 222 that constitutes the part of first speed changing portion 226 be comprise sun gear S1, small gear P1, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA1 of support small gear P1 and the gear ring R1 that is meshed with sun gear S1 by small gear P1.The same second preposition planetary gear set 224 that constitutes the part of first speed changing portion 226 be comprise sun gear S2, intermeshing many group small gear P2, can rotation and can revolve round the sun the planetary gear set of double pinion type of the planet carrier CA2 of support small gear P2 and the gear ring R2 that is meshed with sun gear S2 by small gear P2.
In first speed changing portion 226, the gear ring R2 of the second preposition planetary gear set 224 is connected in the gearbox 16 as nonrotational element integratedly, and this prevents that gear ring R2 from rotating with respect to gearbox 16.The gear ring R1 of the first preposition planetary gear set 222 that links together in addition, and the planet carrier CA2 of the second preposition planetary gear set 224 are connected in the input shaft 22 as the input rotating element integratedly.In addition, the planet carrier CA1 of the first preposition planetary gear set 222 is connected in output element 32 in the middle of first integratedly, therefore as output element in the middle of similar to output element 32 in the middle of first first.In addition, the sun gear S1 of the first preposition planetary gear set 222 that links together and the sun gear S2 of the second preposition planetary gear set 224 are connected in output element 34 in the middle of second integratedly, therefore as output element in the middle of similar to output element 34 in the middle of second second.This structure causes first speed changing portion 226 by the slow down rotation that comes from the input shaft 22 and rotation of being slowed down is delivered to second speed changing portion 64 of output element 32 in the middle of first, and makes the rotations that come from input shaft 22 oppositely and with described backward rotation be delivered to second speed changing portion 64 by output element 34 in the middle of second.
In the speed changer 220 that constitutes as mentioned above, as shown in Figure 138, can be by for example engaging simultaneously from first clutch C1 in response to instruction from ECU42, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
In the nomogram shown in Figure 139, four vertical curve Y1 represent the assembly of first speed changing portion 226 to Y4.In the drawings from left to right, line Y1 represents to link together with the sun gear S1 of the first preposition planetary gear set 222 that constitutes a rotating element and the planet carrier CA2 of the second preposition planetary gear set 224, line Y2 represents the gear ring R2 as the second preposition planetary gear set 224 of another rotating element, line Y3 represents to link together with the planet carrier CA1 of the first preposition planetary gear set 222 that constitutes another rotating element and the sun gear S2 of the second preposition planetary gear set 224, and line Y4 represents the gear ring R1 as the first preposition planetary gear set 222 of another rotating element.Therefore, based on these rotating elements, the nomogram shown in Figure 139 is similar to for example nomogram shown in above-mentioned Figure 16, therefore omits the description to it.
By this way, according to the 17 exemplary embodiment, first speed changing portion 226 comprises first preposition planetary gear set 222 of single small gear type and the second preposition planetary gear set 224 of double pinion type.The gear ring R2 of the second preposition planetary gear set 224 always is connected in the gearbox 16 as nonrotational element.The sun gear S2 of the sun gear S1 of the first preposition planetary gear set 222 and the second preposition planetary gear set 224 links together, and the planet carrier CA2 of the gear ring R1 of the first preposition planetary gear set 222 and the second preposition planetary gear set 224 links together and is connected in input shaft 22.Therefore, the planet carrier CA1 of the first preposition planetary gear set 222 is as the first middle output element 32, and the sun gear S2 of the sun gear S1 of the first preposition planetary gear set 222 that links together and the second preposition planetary gear set 224 is as the second middle output element 34.Therefore, can provide practical speed changer 220.
Figure 140 is the perspective view of the structure of the related speed changer 230 of the present invention's the 18 exemplary embodiment.It is middle-grade and be used to set up the figure of the relation between the operation of the required friction engagement device of those grades that Figure 141 shows speed changer 230.Figure 142 shows the nomogram of the rotational velocity of rotating element in each grade.Except that the structure of first speed changing portion 236, the speed changer 230 of this exemplary embodiment is similar to the speed changer 66 shown in Figure 12 in configuration aspects, the effect of the equivalence that therefore can obtain by this exemplary embodiment and be obtained from previous embodiment.Hereinafter, will the part of the speed changer 230 of this exemplary embodiment different with the part of speed changer 66 be described.
As shown in Figure 140, the first preposition planetary gear set 232 that constitutes the part of first speed changing portion 236 be comprise sun gear S1, small gear P1, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA1 of support small gear P1 and the gear ring R1 that is meshed with sun gear S1 by small gear P1.The same second preposition planetary gear set 234 that constitutes the part of first speed changing portion 236 be comprise sun gear S2, intermeshing many group small gear P2, can rotation and can revolve round the sun the planetary gear set of double pinion type of the planet carrier CA2 of support small gear P2 and the gear ring R2 that is meshed with sun gear S2 by small gear P2.
In first speed changing portion 236, the gear ring R2 of the planet carrier CA1 of the first preposition planetary gear set 232 and the second preposition planetary gear set 234 is connected in the gearbox 16 as nonrotational element integratedly, and this prevents that they are with respect to gearbox 16 rotations.In addition, the sun gear S2 of the gear ring R1 of the first preposition planetary gear set 232 and the second preposition planetary gear set 234 links together, and the sun gear S1 of the first preposition planetary gear set 232 is connected in the input shaft 22 as the input rotating element integratedly.According to this structure, output element 32 in the middle of the planet carrier CA2 of the second preposition planetary gear set 234 is connected in first integratedly, therefore as output element in the middle of similar to output element 32 in the middle of first first, and the sun gear S2 of the gear ring R1 of the first preposition planetary gear set 232 that links together and the second preposition planetary gear set 234 is connected in output element 34 in the middle of second integratedly, therefore as output element in the middle of similar to output element 34 in the middle of second second.
In the speed changer 230 that constitutes as mentioned above, as shown in Figure 141, can be by for example engaging simultaneously from first clutch C1 in response to instruction from ECU42, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.The bonding operation of the shelves of the speed changer 230 that present embodiment is related and speed ratio and use Figure 23 are described, and those are identical, so will omit giving unnecessary details it.
In the nomogram shown in Figure 142, four vertical curve Y1 represent the assembly of first speed changing portion 236 to Y4.In the drawings from left to right, line Y1 represents to link together with the gear ring R1 of the first preposition planetary gear set 232 that constitutes a rotating element and the sun gear S2 of the second preposition planetary gear set 234, line Y2 represents to link together with the planet carrier CA1 of the first preposition planetary gear set 232 that constitutes another rotating element and the gear ring R2 of the second preposition planetary gear set 234, line Y3 represents the planet carrier CA2 as the second preposition planetary gear set 234 of another rotating element, and line Y4 represents the sun gear S1 as the first preposition planetary gear set 232 of another rotating element.Therefore, based on these rotating elements, the nomogram shown in Figure 142 is similar to the nomogram shown in above-mentioned Figure 24, therefore omits the description to it.
Therefore, according to the 18 exemplary embodiment, by with different compound mode engaging clutches and break and suitably set the gear ratio of each planetary gear set, also can obtain nine forward gearss and two reverse gears, and more particularly, the level between the 8th grade and the 9th grade can be set lessly with intensive speed ratio.
By this way, according to the 18 exemplary embodiment, first speed changing portion 236 comprises first preposition planetary gear set 232 of single small gear type and the second preposition planetary gear set 234 of double pinion type.The gear ring R2 of the planet carrier CA1 of the first preposition planetary gear set 232 and the second preposition planetary gear set 234 always is connected in the gearbox 16 as nonrotational element.The sun gear S2 of the gear ring R1 of the first preposition planetary gear set 232 and the second preposition planetary gear set 234 links together, and the sun gear S1 of the first preposition planetary gear set 232 is connected in input shaft 22.Therefore, the planet carrier CA2 of the second preposition planetary gear set 234 is as the first middle output element 32, and the sun gear S2 of the gear ring R1 of the first preposition planetary gear set 232 that links together and the second preposition planetary gear set 234 is as the second middle output element 34.Therefore, can provide practical speed changer 230.
Here, revise example as first of the 18 exemplary embodiment, as shown in Figure 143, by in response to the instruction that comes from ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 230 can obtain ten forward gearss and two reverse gears, and can obtain the effect that is equal to aforementioned exemplary embodiment.In addition, Figure 144 is and the corresponding nomogram of Figure 143 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the first correction example of Figure 143 different with aforementioned exemplary embodiment and the 18 exemplary embodiment shown in Figure 144 be described.
As shown in clutch among Figure 143 and brake engages figure, can be by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.The speed ratio that is used to set up the operation of friction engagement device of described shelves and described shelves with use Figure 17 described identical, so will omit giving unnecessary details to it.
In the nomogram shown in Figure 144, because the structure shown in the perspective view is identical, represent that therefore four vertical curve Y1 of the assembly of first speed changing portion 236 represent and the identical rotating element shown in above-mentioned Figure 142 to Y8 with four vertical curve Y5 of the assembly of expression second speed changing portion 64 to Y4.In addition, in clutch shown in Figure 143 and brake engages figure, it is described identical with above-mentioned use Figure 17 to the operation of the friction engagement device of the tenth grade " 10th " to be used to set up first grade " 1st ".Therefore, based on rotating element, nomogram is also corresponding with it.Therefore, the nomogram among Figure 144 is identical with the nomogram shown in Figure 18.
Therefore, revise example according to first of the 18 exemplary embodiment, by with different compound mode engaging clutches and break and suitably set the gear ratio of each planetary gear set, also can obtain ten forward gearss and two reverse gears, and more particularly, the level between the 9th grade and the tenth grade can be set lessly with intensive speed ratio.
Figure 145 is the perspective view of the structure of the related speed changer 240 of the present invention's the 19 exemplary embodiment.It is middle-grade and be used to set up the figure of the relation between the operation of the required friction engagement device of those grades that Figure 146 shows speed changer 240.Figure 147 shows the nomogram of the rotational velocity of rotating element in each grade.Except that the structure of first speed changing portion 246, the speed changer 240 of this exemplary embodiment is similar to the speed changer 66 shown in Figure 12 in configuration aspects, the effect of the equivalence that therefore can obtain by this exemplary embodiment and be obtained from previous embodiment.Hereinafter, will the part of the speed changer 240 of this exemplary embodiment different with the part of speed changer 66 be described.
As shown in Figure 145, the first preposition planetary gear set 242 that constitutes the part of first speed changing portion 246 be comprise sun gear S1, intermeshing many group small gear P1, can rotation and can revolve round the sun the planetary gear set of double pinion type of the planet carrier CA1 of support small gear P1 and the gear ring R1 that is meshed with sun gear S1 by small gear P1.The same second preposition planetary gear set 244 that constitutes the part of first speed changing portion 246 be comprise sun gear S2, small gear P2, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA2 of support small gear P2 and the gear ring R2 that is meshed with sun gear S2 by small gear P2.
In first speed changing portion 246, the gear ring R1 of the first preposition planetary gear set 242 is connected in the gearbox 16 as nonrotational element integratedly, thereby prevents that gear ring R1 from rotating with respect to gearbox 16.In addition, the sun gear S2 of the planet carrier CA1 of the first preposition planetary gear set 242 and the second preposition planetary gear set 244 links together, and the gear ring R2 of the sun gear S1 of the first preposition planetary gear set 242 and the second preposition planetary gear set 244 is connected in the input shaft 22 as the input rotating element integratedly.According to this structure, output element 32 in the middle of the planet carrier CA2 of the second preposition planetary gear set 244 is connected in first integratedly, therefore as output element in the middle of similar to output element 32 in the middle of first first, and the sun gear S2 of the planet carrier CA1 of the first preposition planetary gear set 242 that links together and the second preposition planetary gear set 244 is connected in output element 34 in the middle of second integratedly, therefore as output element in the middle of similar to output element 34 in the middle of second second.
In the speed changer 240 that constitutes as mentioned above, as shown in Figure 146, can be by for example engaging simultaneously from first clutch C1 in response to instruction from ECU42, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up nine forward gearss, promptly, in first grade " 1st " to the 9th grade " 9th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.The bonding operation of the shelves of the speed changer 240 that present embodiment is related and speed ratio and use Figure 25 are described, and those are identical, so will omit giving unnecessary details it.
In the nomogram shown in Figure 147, four vertical curve Y1 represent the assembly of first speed changing portion 246 to Y4.In the drawings from left to right, line Y1 represents to link together with the planet carrier CA1 of the first preposition planetary gear set 242 that constitutes a rotating element and the sun gear S2 of the second preposition planetary gear set 244, line Y2 represents the gear ring R1 as the first preposition planetary gear set 242 of another rotating element, line Y3 represents the planet carrier CA2 as the second preposition planetary gear set 244 of another rotating element, and line Y4 represents to link together with the sun gear S1 of the first preposition planetary gear set 242 that constitutes another rotating element and the gear ring R2 of the second preposition planetary gear set 244.Therefore, based on these rotating elements, the nomogram shown in Figure 147 is similar to the nomogram shown in above-mentioned Figure 26, therefore omits the description to it.
Therefore, according to the 19 exemplary embodiment, by with different compound mode engaging clutches and break and suitably set the gear ratio of each planetary gear set, also can obtain nine forward gearss and two reverse gears, and more particularly, the level between the 8th grade and the 9th grade can be set lessly with intensive speed ratio.
By this way, according to the 19 exemplary embodiment, first speed changing portion 246 comprises first preposition planetary gear set 242 of double pinion type and the second preposition planetary gear set 244 of single small gear type.The gear ring R1 of the first preposition planetary gear set 242 always is connected in the gearbox 16 as nonrotational element.The sun gear S2 of the planet carrier CA1 of the first preposition planetary gear set 242 and the second preposition planetary gear set 244 links together, and the gear ring R1 of the sun gear S1 of the first preposition planetary gear set 242 and the second preposition planetary gear set 244 is connected in input shaft 22.Therefore, the planet carrier CA2 of the second preposition planetary gear set 244 is as the first middle output element 32, and the sun gear S2 of the planet carrier CA1 of the first preposition planetary gear set 242 that links together and the second preposition planetary gear set 244 is as the second middle output element 34.Therefore, can provide practical speed changer 240.
Figure 148 is the perspective view of the structure of the related speed changer 250 of the present invention's the 20 exemplary embodiment.It is middle-grade and be used to set up the figure of the relation between the operation of the required friction engagement device of those grades that Figure 149 shows speed changer 250.Figure 150 shows the nomogram of the rotational velocity of rotating element in each grade.Except that the structure of first speed changing portion 256, the speed changer 250 of this exemplary embodiment is similar to the speed changer 66 shown in Figure 12 in configuration aspects, the effect of the equivalence that therefore can obtain by this exemplary embodiment and be obtained from previous embodiment.Hereinafter, will the part of the speed changer 250 of this exemplary embodiment different with the part of speed changer 66 be described.
As shown in Figure 148, the first preposition planetary gear set 252 that constitutes the part of first speed changing portion 256 be comprise sun gear S1, small gear P1, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA1 of support small gear P1 and the gear ring R1 that is meshed with sun gear S1 by small gear P1.The same second preposition planetary gear set 254 that constitutes the part of first speed changing portion 256 be comprise sun gear S2, small gear P2, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA2 of support small gear P2 and the gear ring R2 that is meshed with sun gear S2 by small gear P2.
In first speed changing portion 256, the planet carrier CA1 of the first preposition planetary gear set 252 is connected in the gearbox 16 as nonrotational element integratedly, thereby prevents that planet carrier CA1 from rotating with respect to gearbox 16.In addition, the sun gear S2 of the gear ring R1 of the first preposition planetary gear set 252 and the second preposition planetary gear set 254 links together, and the gear ring R2 of the sun gear S1 of the first preposition planetary gear set 252 and the second preposition planetary gear set 254 is connected in the input shaft 22 as the input rotating element integratedly.According to this structure, the planet carrier CA2 of the second preposition planetary gear set 254 is connected in output element 32 in the middle of first integratedly, therefore as output element in the middle of similar to output element 32 in the middle of first first.In addition, the gear ring R11 of the first preposition planetary gear set 252 that links together and the sun gear S2 of the second preposition planetary gear set 254 are connected in output element 34 in the middle of second integratedly, therefore as output element in the middle of similar to output element 34 in the middle of second second.
In the speed changer 250 that constitutes as mentioned above, as shown in Figure 149, can be by for example engaging simultaneously from first clutch C1 in response to instruction from ECU42, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up 11 forward gearss, promptly, in first grade " 1st " to the 11 grade " 11th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
Setting up in the speed changer 250 of shelves according to clutch shown in Figure 149 and brake engages figure, first grade speed ratio γ 1 is approximately 5.128, second grade speed ratio γ 2 is approximately 3.601, the speed ratio γ 3 of third gear is approximately 3.060, the speed ratio γ 4 of fourth speed is approximately 2.259, the 5th grade speed ratio γ 5 is approximately 1.694, the 6th grade speed ratio γ 6 is approximately 1.444, the 7th grade speed ratio γ 7 is approximately 1.239, the 8th grade speed ratio γ 8 is approximately 1.000, the 9th grade speed ratio γ 9 is approximately 0.853, the tenth grade speed ratio γ 10 is approximately 0.704, the 11 grade speed ratio γ 11 is approximately 0.619, the speed ratio γ R2 that the speed ratio γ R1 of first reverse gear is approximately 4.024 and second reverse gear is approximately 2.375.In addition, first grade speed ratio γ 1 is 1.676 with the ratio (=γ 1/ γ 3) of the speed ratio γ 3 of third gear, second grade speed ratio γ 2 is 1.594 with the ratio (=γ 2/ γ 4) of the speed ratio γ 4 of fourth speed, the speed ratio γ 3 of third gear is 1.354 with the ratio (=γ 3/ γ 4) of the speed ratio γ 4 of fourth speed, the ratio (=γ 4/ γ 5) of the speed ratio γ 5 of the speed ratio γ 4 of fourth speed and the 5th grade is 1.333, the ratio (=γ 5/ γ 6) of the speed ratio γ 6 of the 5th grade speed ratio γ 5 and the 6th grade is 1.174, the ratio (=γ 6/ γ 7) of the speed ratio γ 7 of the 6th grade speed ratio γ 6 and the 7th grade is 1.165, the ratio (=γ 7/ γ 8) of the speed ratio γ 8 of the 7th grade speed ratio γ 7 and the 8th grade is that the ratio (=γ 8/ γ 9) of the speed ratio γ 9 of 1.239, the eight grades speed ratio γ 8 and the 9th grade is 1.173, the ratio (=γ 9/ γ 10) of the speed ratio γ 10 of the 9th grade speed ratio γ 9 and the tenth grade is 1.212, and the ratio (=γ 10/ γ 11) of the speed ratio γ 11 of the tenth grade speed ratio γ 10 and the 11 grade is 1.137.Therefore, speed ratio γ changes in well balanced mode.In addition, the overall ratio scope, that is, the ratio of first grade speed ratio γ 1 and the 11 grade speed ratio γ 11 (=γ 1/ γ 11) is 8.288, this is bigger numerical value.Here, in order to make planetary gear set obtain aforementioned speed ratio, the gear ratio ρ 4 that the gear ratio ρ 3 that the gear ratio ρ 2 that the gear ratio ρ 1 of the first preposition planetary gear set 252 is set to for example about 0.463, second preposition planetary gear set 254 is set to for example about 0.389, first rearmounted planetary gear set 58 is set to for example about 0.528 and second rearmounted planetary gear set 60 is set to for example about 0.421.
In the nomogram shown in Figure 150, four vertical curve Y1 represent the assembly of first speed changing portion 256 to Y4.In the drawings from left to right, line Y1 represents to link together with the gear ring R1 of the first preposition planetary gear set 252 that constitutes a rotating element and the sun gear S2 of the second preposition planetary gear set 254, line Y2 represents the planet carrier CA1 as the first preposition planetary gear set 252 of another rotating element, line Y3 represents the planet carrier CA2 as the second preposition planetary gear set 254 of another rotating element, and line Y4 represents to link together with the sun gear S1 of the first preposition planetary gear set 252 that constitutes another rotating element and the gear ring R2 of the second preposition planetary gear set 254.In addition, represent that four vertical curve Y5 of parts of second speed changing portion 64 are to Y8 identical with shown in Figure 14.Therefore, based on these rotating elements, the nomogram shown in Figure 150 is similar to the nomogram shown in above-mentioned Figure 90, therefore omits the description to it.
Therefore, according to this exemplary embodiment, by with different compound mode engaging clutches and break and suitably set the gear ratio of each planetary gear set, can obtain 11 forward gearss and two reverse gears, and can well balanced mode set the speed ratio level between the shelves.
In addition, according to this exemplary embodiment, first speed changing portion 256 comprises first preposition planetary gear set 252 of single small gear type and the second preposition planetary gear set 254 of single small gear type.The planet carrier CA1 of the first preposition planetary gear set 252 always is connected in the gearbox 16 as nonrotational element, the sun gear S2 of the gear ring R1 of the first preposition planetary gear set 252 and the second preposition planetary gear set 254 links together, and the gear ring R2 of the sun gear S1 of the first preposition planetary gear set 252 and the second preposition planetary gear set 254 is connected in input shaft 22.Therefore, the planet carrier CA2 of the second preposition planetary gear set 254 is as the first middle output element 32, and the sun gear S2 of the gear ring R1 of the first preposition planetary gear set 252 that links together and the second preposition planetary gear set 254 is as the second middle output element 34.Therefore, can be provided for the practical multi-speed transmission of vehicle.
Figure 151 is the perspective view of the structure of the related speed changer 260 of the present invention's the 21 exemplary embodiment.It is middle-grade and be used to set up the figure of the relation between the operation of the required friction engagement device of those grades that Figure 152 shows speed changer 260.Figure 153 shows the nomogram of the rotational velocity of rotating element in each grade.Except that the structure of second speed changing portion 266, the speed changer 260 of this exemplary embodiment is similar to the speed changer 138 shown in Figure 74 in configuration aspects, the effect of the equivalence that therefore can obtain by this exemplary embodiment and be obtained from previous embodiment.Hereinafter, will the part of the speed changer 260 of this exemplary embodiment different with the part of speed changer 138 be described.
As shown in Figure 151, the first rearmounted planetary gear set 262 that constitutes the part of second speed changing portion 266 be comprise sun gear S3, intermeshing many group small gear P3, can rotation and can revolve round the sun the planetary gear set of double pinion type of the planet carrier CA3 of support small gear P3 and the gear ring R3 that is meshed with sun gear S3 by small gear P3.The same second rearmounted planetary gear set 264 that constitutes the part of second speed changing portion 266 be comprise sun gear S4, intermeshing many group small gear P4, can rotation and can revolve round the sun the planetary gear set of double pinion type of the planet carrier CA4 of support small gear P4 and the gear ring R4 that is meshed with sun gear S4 by small gear P4.
In second speed changing portion 266, the sun gear S3 of the first rearmounted planetary gear set 262 forms the first rotating element RE1.The planet carrier CA4 of the gear ring R3 of the first rearmounted planetary gear set 262 and the second rearmounted planetary gear set 264 is joined together to form the second rotating element RE2.The gear ring R4 of the second rearmounted planetary gear set 264 forms the 3rd rotating element RE3, and the sun gear S4 of the planet carrier CA3 of the first rearmounted planetary gear set 262 and the second rearmounted planetary gear set 264 is joined together to form the 4th rotating element RE4.Speed changer 260 also comprises first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, the first break B1 and the second break B2.First clutch C1 is the first clutch element that optionally the first middle output element 32 is connected with the 4th rotating element RE4.Second clutch C2 is the second clutch element that optionally input shaft 22 is connected with the second rotating element RE2.Three-clutch C3 is the three-clutch element that optionally the first middle output element 32 is connected with the first rotating element RE1.Four clutches C4 is the four clutches element that optionally input shaft 22 and the first rotating element RE1 is linked together.The 5th clutch C5 is the 5th clutch element that optionally output element 34 in the middle of second and the first rotating element RE1 is linked together.The first break B1 is first brake component that optionally the first rotating element RE1 is remained in as the gearbox 16 of nonrotational element, and the second break B2 is second brake component that optionally the second rotating element RE2 is remained in gearbox 16.
In the speed changer 260 that constitutes as mentioned above, as shown in Figure 152, can be by for example engaging simultaneously from first clutch C1 in response to instruction from ECU42, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up 11 forward gearss, promptly, in first grade " 1st " to the 11 grade " 11th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.The bonding operation and the speed ratio of the described shelves of the speed changer 260 that this exemplary embodiment is related are described identical with above-mentioned use Figure 149, therefore will omit giving unnecessary details it.And, in order to make planetary gear set obtain aforementioned speed ratio, the gear ratio ρ 4 that the gear ratio ρ 3 that the gear ratio ρ 2 that the gear ratio ρ 1 of the first preposition planetary gear set 140 is set to for example about 0.463, second preposition planetary gear set 142 is set to for example about 0.410, first rearmounted planetary gear set 262 is set to for example about 0.472 and second rearmounted planetary gear set 264 is set to for example about 0.471.
In the nomogram shown in Figure 153, four vertical curve Y5 represent the assembly of first speed changing portion 266 to Y8.In the drawings from left to right, line Y5 represents the sun gear S3 as the first rearmounted planetary gear set 262 of a rotating element, line Y6 represents to link together with the gear ring R3 of the first rearmounted planetary gear set 262 that constitutes another rotating element and the planet carrier CA4 of the second rearmounted planetary gear set 264, line Y7 represents the gear ring R4 as the second rearmounted planetary gear set 264 of another rotating element, and line Y8 represents to link together with the planet carrier CA3 of the first rearmounted planetary gear set 262 that constitutes another rotating element and the sun gear S4 of the second rearmounted planetary gear set 264.In addition, represent that four vertical curve Y1 of parts of first speed changing portion 144 are to Y4 identical with shown in Figure 80.Therefore, based on these rotating elements, the nomogram shown in Figure 153 is similar to the nomogram shown in above-mentioned Figure 150, therefore omits the description to it.
Therefore, according to this exemplary embodiment, by with different compound mode engaging clutches and break and suitably set the gear ratio of each planetary gear set, can obtain 11 forward gearss and two reverse gears, and can well balanced mode set the speed ratio level between the shelves.Therefore, can be provided for the practical multi-speed transmission of vehicle.In addition, in this exemplary embodiment, the second break B2 radially is arranged in the outside of gear ring R3 of the first rearmounted planetary gear set 262 of double pinion type, and is therefore far away from axial centre.Therefore, for example, when speed changer is in first grade " 1st " and the second break B2 and is engaged, even the suitable hour second break B2 of braking reaction force when engaging also can be engaged.
In addition, according to this exemplary embodiment, second speed changing portion 266 comprises first rearmounted planetary gear set 262 of double pinion type and the second rearmounted planetary gear set 264 of double pinion type.The first rotating element RE1 is that the sun gear S3 by the first rearmounted planetary gear set 262 forms, and the second rotating element RE2 is that the planet carrier CA4 by the gear ring R3 of the first rearmounted planetary gear set 262 that links together and the second rearmounted planetary gear set 264 forms.The 3rd rotating element RE3 is that the gear ring R4 by the second rearmounted planetary gear set 264 forms, and the 4th rotating element RE4 is formed by the planet carrier CA3 of the first rearmounted planetary gear set 262 that links together and the sun gear S4 of the second rearmounted planetary gear set 264.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, revise example as first of the 21 exemplary embodiment, as shown in Figure 154, can by in response to from the instruction of ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 260 can obtain ten forward gearss and two reverse gears.In addition, Figure 155 is and the corresponding nomogram of Figure 154 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the first correction example of Figure 154 different with aforementioned exemplary embodiment and the 21 exemplary embodiment shown in Figure 155 be described.
As shown in clutch among Figure 154 and brake engages figure, by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.In addition, in order to make planetary gear set obtain the speed ratio shown in Figure 154, the gear ratio ρ 4 that the gear ratio ρ 3 that the gear ratio ρ 2 that the gear ratio ρ 1 of the first preposition planetary gear set 140 is set to for example about 0.580, second preposition planetary gear set 142 is set to for example about 0.463, first rearmounted planetary gear set 262 is set to for example about 0.515 and second rearmounted planetary gear set 264 is set to for example about 0.471.
In the nomogram shown in Figure 155, because perspective view wherein is identical, represent that therefore four vertical curve Y1 of the assembly of first speed changing portion 144 represent and the identical rotating element shown in above-mentioned Figure 153 to Y8 with four vertical curve Y5 of the assembly of expression second speed changing portion 266 to Y4.Therefore, based on described rotating element, the nomogram shown in Figure 155 is also similar to the nomogram shown in above-mentioned Fig. 4, therefore omits the description to it.
Therefore, according to this exemplary embodiment, by with different compound mode engaging clutches and break and suitably set the gear ratio of each planetary gear set, can obtain ten forward gearss and two reverse gears, and can well balanced mode set the speed ratio level between the shelves.Therefore, can be provided for the practical multi-speed transmission of vehicle.
Figure 156 is the perspective view of the structure of the related speed changer 270 of the present invention's the 22 exemplary embodiment.It is middle-grade and be used to set up the figure of the relation between the operation of the required friction engagement device of those grades that Figure 157 shows speed changer 270.Figure 158 shows the nomogram of the rotational velocity of rotating element in each grade.Except that the structure of second speed changing portion 276, the speed changer 270 of this exemplary embodiment is similar to the speed changer 138 shown in Figure 74 in configuration aspects, the effect of the equivalence that therefore can obtain by this exemplary embodiment and be obtained from previous embodiment.Hereinafter, will the part of the speed changer 270 of this exemplary embodiment different with the part of speed changer 138 be described.
As shown in Figure 156, the first rearmounted planetary gear set 272 that constitutes the part of second speed changing portion 276 be comprise sun gear S3, intermeshing many group small gear P3, can rotation and can revolve round the sun the planetary gear set of double pinion type of the planet carrier CA3 of support small gear P3 and the gear ring R3 that is meshed with sun gear S3 by small gear P3.The same second rearmounted planetary gear set 274 that constitutes the part of second speed changing portion 276 be comprise sun gear S4, intermeshing many group small gear P4, can rotation and can revolve round the sun the planetary gear set of double pinion type of the planet carrier CA4 of support small gear P4 and the gear ring R4 that is meshed with sun gear S4 by small gear P4.
In second speed changing portion 276, the planet carrier CA3 of the first rearmounted planetary gear set 272 forms the first rotating element RE1.The planet carrier CA4 of the gear ring R3 of the first rearmounted planetary gear set 272 and the second rearmounted planetary gear set 274 is joined together to form the second rotating element RE2.The gear ring R4 of the second rearmounted planetary gear set 274 forms the 3rd rotating element RE3, and the sun gear S4 of the sun gear S3 of the first rearmounted planetary gear set 272 and the second rearmounted planetary gear set 274 is joined together to form the 4th rotating element RE4.Speed changer 270 also comprises first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, the first break B1 and the second break B2.First clutch C1 is the first clutch element that optionally the first middle output element 32 is connected with the 4th rotating element RE4.Second clutch C2 is the second clutch element that optionally input shaft 22 is connected with the second rotating element RE2.Three-clutch C3 is the three-clutch element that optionally the first middle output element 32 is connected with the first rotating element RE1.Four clutches C4 is the four clutches element that optionally input shaft 22 and the first rotating element RE1 is linked together.The 5th clutch C5 is the 5th clutch element that optionally output element 34 in the middle of second and the first rotating element RE1 is linked together.The first break B1 is first brake component that optionally the first rotating element RE1 is remained in as the gearbox 16 of nonrotational element, and the second break B2 is second brake component that optionally the second rotating element RE2 is remained in gearbox 16.
In the speed changer 270 that constitutes as mentioned above, as shown in Figure 157, can be by for example engaging simultaneously from first clutch C1 in response to instruction from ECU42, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up 11 forward gearss, promptly, in first grade " 1st " to the 11 grade " 11th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.The bonding operation and the speed ratio of the described shelves of the speed changer 270 that this exemplary embodiment is related are described identical with above-mentioned use Figure 149, therefore will omit giving unnecessary details it.In addition, in order to make planetary gear set obtain aforementioned speed ratio, the gear ratio ρ 4 that the gear ratio ρ 3 that the gear ratio ρ 2 that the gear ratio ρ 1 of the first preposition planetary gear set 140 is set to for example about 0.463, second preposition planetary gear set 142 is set to for example about 0.410, first rearmounted planetary gear set 272 is set to for example about 0.528 and second rearmounted planetary gear set 274 is set to for example about 0.471.
In the nomogram shown in Figure 158, four vertical curve Y5 represent the assembly of first speed changing portion 276 to Y8.In the drawings from left to right, line Y5 represents the planet carrier CA3 as the first rearmounted planetary gear set 272 of a rotating element, line Y6 represents to link together with the gear ring R3 of the first rearmounted planetary gear set 272 that constitutes another rotating element and the planet carrier CA4 of the second rearmounted planetary gear set 274, line Y7 represents the gear ring R4 as the second rearmounted planetary gear set 274 of another rotating element, and line Y8 represents to link together with the sun gear S3 of the first rearmounted planetary gear set 272 that constitutes another rotating element and the sun gear S4 of the second rearmounted planetary gear set 274.In addition, represent that four vertical curve Y1 of parts of first speed changing portion 144 are to Y4 identical with shown in Figure 80.Therefore, based on these rotating elements, the nomogram shown in Figure 158 is similar to the nomogram shown in above-mentioned Figure 150, therefore omits the description to it.
Therefore, according to this exemplary embodiment, by with different compound mode engaging clutches and break and suitably set the gear ratio of each planetary gear set, can obtain 11 forward gearss and two reverse gears, and can well balanced mode set the speed ratio level between the shelves.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, in this exemplary embodiment, second speed changing portion 276 comprises first rearmounted planetary gear set 272 of double pinion type and the second rearmounted planetary gear set 274 of double pinion type.The first rotating element RE1 is that the planet carrier CA3 by the first rearmounted planetary gear set 272 forms, the second rotating element RE2 is that the planet carrier CA4 by the gear ring R3 of the first rearmounted planetary gear set 272 that links together and the second rearmounted planetary gear set 274 forms, the 3rd rotating element RE3 is that the gear ring R4 by the second rearmounted planetary gear set 274 forms, and the 4th rotating element RE4 is formed by the sun gear S3 of the first rearmounted planetary gear set 272 that links together and the sun gear S4 of the second rearmounted planetary gear set 274.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, revise example as first of the 22 exemplary embodiment, as shown in Figure 159, can by in response to from the instruction of ECU42 with different compound mode engaging clutch and break, and suitably set the gear ratio of each planetary gear set, speed changer 270 can obtain ten forward gearss and two reverse gears.In addition, Figure 160 is and the corresponding nomogram of Figure 159 wherein to show the rotational velocity of rotating element in each grade.Hereinafter, will clutch and the brake engages figure and the nomogram of the first correction example of Figure 159 different with aforementioned exemplary embodiment and the 22 exemplary embodiment shown in Figure 160 be described.
As shown in clutch among Figure 159 and brake engages figure, by engaging simultaneously from first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up ten forward gearss, promptly, in first grade " 1st " to the tenth grade " 10th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.In addition, in order to make planetary gear set obtain aforementioned speed ratio, the gear ratio ρ 4 that the gear ratio ρ 3 that the gear ratio ρ 2 that the gear ratio ρ 1 of the first preposition planetary gear set 140 is set to for example about 0.580, second preposition planetary gear set 142 is set to for example about 0.463, first rearmounted planetary gear set 272 is set to for example about 0.485 and second rearmounted planetary gear set 274 is set to for example about 0.471.
In the nomogram shown in Figure 160, because perspective view wherein is identical, represent that therefore four vertical curve Y1 of the assembly of first speed changing portion 144 represent and the identical rotating element shown in above-mentioned Figure 158 to Y8 with four vertical curve Y5 of the assembly of expression second speed changing portion 276 to Y4.Therefore, based on these rotating elements, the nomogram shown in Figure 160 is also similar to the nomogram shown in above-mentioned Fig. 4, therefore omits the description to it.
Therefore, according to this exemplary embodiment, by with different compound mode engaging clutches and break and suitably set the gear ratio of each planetary gear set, can obtain ten forward gearss and two reverse gears, and can well balanced mode set the speed ratio level between the shelves.Therefore, can be provided for the practical multi-speed transmission of vehicle.
Figure 161 is the perspective view of the structure of the related speed changer 280 of the present invention's the 23 exemplary embodiment.It is middle-grade and be used to set up the figure of the relation between the operation of the required friction engagement device of those grades that Figure 162 shows speed changer 280.Figure 163 shows the nomogram of the rotational velocity of rotating element in each grade.Except that the structure of second speed changing portion 286, the speed changer 280 of this exemplary embodiment is similar to the speed changer 138 shown in Figure 74 in configuration aspects, the effect of the equivalence that therefore can obtain by this exemplary embodiment and be obtained from previous embodiment.Hereinafter, will the part of the speed changer 280 of this exemplary embodiment different with the part of speed changer 138 be described.
As shown in Figure 161, the first rearmounted planetary gear set 282 that constitutes the part of second speed changing portion 286 be comprise sun gear S3, small gear P3, can rotation and can revolve round the sun the planetary gear set of single small gear type of the planet carrier CA3 of support small gear P3 and the gear ring R3 that is meshed with sun gear S3 by small gear P3.The same second rearmounted planetary gear set 284 that constitutes the part of second speed changing portion 286 be comprise sun gear S4, intermeshing many group small gear P4, can rotation and can revolve round the sun the planetary gear set of double pinion type of the planet carrier CA4 of support small gear P4 and the gear ring R4 that is meshed with sun gear S4 by small gear P4.
In second speed changing portion 286, the sun gear S3 of the first rearmounted planetary gear set 282 forms the first rotating element RE1.The planet carrier CA4 of the planet carrier CA3 of the first rearmounted planetary gear set 282 and the second rearmounted planetary gear set 284 is joined together to form the second rotating element RE2.The gear ring R4 of the gear ring R3 of the first rearmounted planetary gear set 282 and the second rearmounted planetary gear set 284 is joined together to form the 3rd rotating element RE3, and the sun gear S4 of the second rearmounted planetary gear set 284 forms the 4th rotating element RE4.Speed changer 280 also comprises first clutch C1, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, the first break B1 and the second break B2.First clutch C1 is the first clutch element that optionally the first middle output element 32 is connected with the 4th rotating element RE4.Second clutch C2 is the second clutch element that optionally input shaft 22 is connected with the second rotating element RE2.Three-clutch C3 is the three-clutch element that optionally the first middle output element 32 is connected with the first rotating element RE1.Four clutches C4 is the four clutches element that optionally input shaft 22 and the first rotating element RE1 is linked together.The 5th clutch C5 is the 5th clutch element that optionally output element 34 in the middle of second and the first rotating element RE1 is linked together.The first break B1 is first brake component that optionally the first rotating element RE1 is remained in as the gearbox 16 of nonrotational element, and the second break B2 is second brake component that optionally the second rotating element RE2 is remained in gearbox 16.
In the speed changer 280 that constitutes as mentioned above, as shown in Figure 162, can be by for example engaging simultaneously from first clutch C1 in response to instruction from ECU42, second clutch C2, three-clutch C3, four clutches C4, the 5th clutch C5, two hydraulic frictional bonding apparatuss that choose among the first break B1 and the second break B2 and optionally set up 11 forward gearss, promptly, in first grade " 1st " to the 11 grade " 11th " any one, perhaps two reverse gears, promptly, first reverse gear " R1 " or second reverse gear " R2 ", and can obtain for each grade the speed ratio γ (=input shaft rotates speed NIN/ output shaft rotational velocity NOUT) that changes with basic identical ratio.
The bonding operation and the speed ratio of the described shelves of the speed changer 280 that this exemplary embodiment is related are described identical with above-mentioned use Figure 149, therefore will omit giving unnecessary details it.Therefore, in order to make planetary gear set obtain aforementioned speed ratio, the gear ratio ρ 4 that the gear ratio ρ 3 that the gear ratio ρ 2 that the gear ratio ρ 1 of the first preposition planetary gear set 140 is set to for example about 0.463, second preposition planetary gear set 142 is set to for example about 0.410, first rearmounted planetary gear set 282 is set to for example about 0.421 and second rearmounted planetary gear set 284 is set to for example about 0.529.
In the nomogram shown in Figure 163, four vertical curve Y5 represent the assembly of first speed changing portion 286 to Y8.In the drawings from left to right, line Y5 represents the sun gear S3 as the first rearmounted planetary gear set 282 of a rotating element, line Y6 represents to link together with the planet carrier CA3 of the first rearmounted planetary gear set 282 that constitutes another rotating element and the planet carrier CA4 of the second rearmounted planetary gear set 284, line Y7 represents to link together with the gear ring R3 of the first rearmounted planetary gear set 282 that constitutes another rotating element and the gear ring R4 of the second rearmounted planetary gear set 284, and line Y8 represents the sun gear S4 as the second rearmounted planetary gear set 284 of another rotating element.In addition, represent that four vertical curve Y1 of parts of first speed changing portion 144 are to Y4 identical with shown in Figure 80.Therefore, based on these rotating elements, the nomogram shown in Figure 163 is similar to for example nomogram shown in above-mentioned Figure 150, therefore omits the description to it.
Therefore, according to this exemplary embodiment, by with different compound mode engaging clutches and break and suitably set the gear ratio of each planetary gear set, can obtain 11 forward gearss and two reverse gears, and can well balanced mode set the speed ratio level between the shelves.Therefore, can be provided for the practical multi-speed transmission of vehicle.
In addition, in this exemplary embodiment, second speed changing portion 286 comprises first rearmounted planetary gear set 282 of single small gear type and the second rearmounted planetary gear set 284 of double pinion type.The first rotating element RE1 is that the sun gear S3 by the first rearmounted planetary gear set 282 forms, the second rotating element RE2 is that the planet carrier CA4 by the planet carrier CA3 of the first rearmounted planetary gear set 282 that links together and the second rearmounted planetary gear set 284 forms, the 3rd rotating element RE3 is that the gear ring R4 by the gear ring R3 of the first rearmounted planetary gear set 282 that links together and the second rearmounted planetary gear set 284 forms, and the 4th rotating element RE4 is that sun gear S4 by the second rearmounted planetary gear set 284 forms.Therefore, can be provided for the practical multi-speed transmission of vehicle.
Although describe various exemplary embodiments in detail with reference to accompanying drawing in the text, the present invention is not limited to these embodiments and can other changes and revise and implement the present invention.
For example, in aforementioned exemplary embodiment's speed changer 14 grades, obtained a plurality of shelves, for example, first grade to the tenth grade, first reverse gear and second reverse gear.Yet, perhaps, can use the suitable shelves that come from those grades to carry out gear shift (speed change).
In addition, in aforementioned exemplary embodiment's speed changer 14 grades, can use any eight shelves in default first grade to the tenth grade to carry out gear shift, therefore obtain eight forward gearss.Certainly also can use in first reverse gear and second reverse gear one as reverse gear.
In addition, in aforementioned exemplary embodiment's speed changer 14 grades, motor 10 directly is connected by bent axle 12 with fluid torque converter 20.Yet, perhaps, can connect them by for example operability ground such as pre-fixed gear or band.In addition, they need not and must be arranged on the common shaft.In addition, also can be used as prime mover motor is provided.
And, in aforementioned exemplary embodiment's speed changer 14 grades, can overrunning clutch be set with the mode of any one serial or parallel connection among first clutch C1 to the five clutch C5, the first break B1 and the second break B2, and gear shift control becomes more simple, this is favourable.In addition, can replace any one use overrunning clutch among first clutch C1 to the five clutch C5, the first break B1 and the second break B2.Even in doing so, still can realize gear shift.
In addition, in aforementioned exemplary embodiment, the fluid torque converter 20 with lock-up clutch 18 is arranged between motor 10 and the input shaft 22 as dydraudynamic drive unit.Yet, not necessarily must provide lock-up clutch 18.In addition.Can provide hydraulic couplers, magnetic formula magnetic clutch or list or polydisc hydraulic coupling to replace fluid torque converter 20.
In addition, in the nomogram in aforementioned exemplary embodiment, vertical curve Y1 is by being disposed in order from left to right to Y8 or Y1 to Y10.Yet, perhaps, can by from right to left be disposed in order them.In addition, the horizontal line X2 that is equivalent to rotational velocity " 1 " is disposed in the top of the horizontal line XZ that is equivalent to rotational velocity " 0 ".Yet perhaps, horizontal line X2 can be disposed in the below of horizontal line XZ.
In addition, in aforementioned exemplary embodiment, provide such as hydraulic frictional bonding apparatuss such as first clutch C1 to the five clutch C5, the first break B1 and the second break B2 as joint element.Yet, perhaps, can use electromagnet-type bonding apparatus such as magnetic clutch or magnetic particle coupling.
Though described the present invention with reference to its exemplary embodiment, it should be understood that the present invention is not limited to exemplary embodiment or structure.In contrast, the invention is intended to cover various corrections and equivalence setting.In addition, though show the various elements of exemplary embodiment with exemplary various combinations and structure, comprise more, still less or only other combinations and the structure of an element also drop in spirit of the present invention and the protection domain.

Claims (31)

1. multi-speed transmission that is used for vehicle, described multi-speed transmission is characterised in that, comprising:
First speed changing portion, described first speed changing portion have slow down and transmission come from input rotating element (22) rotation first in the middle of output element (32) and make come from described input rotating element (22) rotation oppositely and transmit this rotation second in the middle of output element (34);
Second speed changing portion, described second speed changing portion comprise four rotating elements that some sun gears, planet carrier and the gear ring by two planetary gear set that link together constitutes;
First clutch element (C1), described first clutch element (C1) optionally link together the described first middle output element (32) with the 4th rotating element (RE4);
Second clutch element (C2), described second clutch element (C2) optionally link together described input rotating element (22) and second rotating element (RE2);
Three-clutch element (C3), described three-clutch element (C3) optionally link together the described first middle output element (32) with first rotating element (RE1);
Four clutches element (C4), described four clutches element (C4) optionally link together described input rotating element (22) and described first rotating element (RE1);
The 5th clutch element (C5), described the 5th clutch element (C5) optionally link together the described second middle output element (34) with described first rotating element (RE1);
First brake component (B1), described first brake component (B1) optionally remains in nonrotational element (16) with described first rotating element (RE1);
Second brake component (B2), described second brake component (B2) optionally remains in described nonrotational element (16) with described second rotating element (RE2);
Wherein, on the nomogram of the rotating speed that can represent four rotating elements by straight line, by the order that passes through, with described four rotating elements as first rotating element (RE1), second rotating element (RE2), the 3rd rotating element (RE3) and the 4th rotating element (RE4).
2. according to the described multi-speed transmission that is used for vehicle of claim 1, it is characterized in that: by engaging described first clutch element (C1) and second brake component (B2) is set up first grade; By engaging described first clutch element (C1) and first brake component (B1) is set up second grade; Set up third gear by engaging described first clutch element (C1) and three-clutch element (C3); Set up fourth speed by engaging described first clutch element (C1) and four clutches element (C4); Set up the 5th grade by engaging described first clutch element (C1) and second clutch element (C2); Set up the 6th grade by engaging described second clutch element (C2) and four clutches element (C4); Set up the 7th grade by engaging described second clutch element (C2) and three-clutch element (C3); Set up the 8th grade by engaging described second clutch element (C2) and first brake component (B1); And set up the 9th grade by engaging described second clutch element (C2) and the 5th clutch element (C5).
3. according to the described multi-speed transmission that is used for vehicle of claim 1, it is characterized in that: set up first grade by engaging first clutch element (C1) and the 5th clutch element (C5); By engaging described first clutch element (C1) and first brake component (B1) is set up second grade; Set up third gear by engaging described first clutch element (C1) and three-clutch element (C3); Set up fourth speed by engaging described first clutch element (C1) and four clutches element (C4); Set up the 5th grade by engaging described first clutch element (C1) and second clutch element (C2); Set up the 6th grade by engaging described second clutch element (C2) and four clutches element (C4); Set up the 7th grade by engaging described second clutch element (C2) and three-clutch element (C3); Set up the 8th grade by engaging described second clutch element (C2) and first brake component (B1); And set up the 9th grade by engaging described second clutch element (C2) and the 5th clutch element (C5).
4. according to the described multi-speed transmission that is used for vehicle of claim 1, it is characterized in that: by engaging described the 5th clutch element (C5) and second brake component (B2) is set up first grade; By engaging described first clutch element (C1) and first brake component (B1) is set up second grade; Set up third gear by engaging described first clutch element (C1) and three-clutch element (C3); Set up fourth speed by engaging described first clutch element (C1) and four clutches element (C4); Set up the 5th grade by engaging described first clutch element (C1) and second clutch element (C2); Set up the 6th grade by engaging described second clutch element (C2) and four clutches element (C4); Set up the 7th grade by engaging described second clutch element (C2) and three-clutch element (C3); Set up the 8th grade by engaging described second clutch element (C2) and first brake component (B1); And set up the 9th grade by engaging described second clutch element (C2) and the 5th clutch element (C5).
5. according to the described multi-speed transmission that is used for vehicle of claim 1, it is characterized in that: by engaging described the 5th clutch element (C5) and second brake component (B2) is set up first grade; By engaging described first clutch element (C1) and second brake component (B2) is set up second grade; By engaging described first clutch element (C1) and first brake component (B1) is set up third gear; Set up fourth speed by engaging described first clutch element (C1) and three-clutch element (C3); Set up the 5th grade by engaging described first clutch element (C1) and four clutches element (C4); Set up the 6th grade by engaging described first clutch element (C1) and second clutch element (C2); Set up the 7th grade by engaging described second clutch element (C2) and four clutches element (C4); Set up the 8th grade by engaging described second clutch element (C2) and three-clutch element (C3); And set up the 9th grade by engaging described second clutch element (C2) and first brake component (B1).
6. according to the described multi-speed transmission that is used for vehicle of claim 1, it is characterized in that: by engaging described first clutch element (C1) and second brake component (B2) is set up first grade; By engaging described first clutch element (C1) and the 5th clutch element (C5) is set up second grade; By engaging described first clutch element (C1) and first brake component (B1) is set up third gear; Set up fourth speed by engaging described first clutch element (C1) and three-clutch element (C3); Set up the 5th grade by engaging described first clutch element (C1) and four clutches element (C4); Set up the 6th grade by engaging described first clutch element (C1) and second clutch element (C2); Set up the 7th grade by engaging described second clutch element (C2) and four clutches element (C4); Set up the 8th grade by engaging described second clutch element (C2) and three-clutch element (C3); And set up the 9th grade by engaging described second clutch element (C2) and first brake component (B1).
7. according to the described multi-speed transmission that is used for vehicle of claim 1, it is characterized in that: by engaging described the 5th clutch element (C5) and second brake component (B2) is set up first grade; By engaging described first clutch element (C1) and the 5th clutch element (C5) is set up second grade; By engaging described first clutch element (C1) and first brake component (B1) is set up third gear; Set up fourth speed by engaging described first clutch element (C1) and three-clutch element (C3); Set up the 5th grade by engaging described first clutch element (C1) and four clutches element (C4); Set up the 6th grade by engaging described first clutch element (C1) and second clutch element (C2); Set up the 7th grade by engaging described second clutch element (C2) and four clutches element (C4); Set up the 8th grade by engaging described second clutch element (C2) and three-clutch element (C3); And set up the 9th grade by engaging described second clutch element (C2) and first brake component (B1).
8. according to the described multi-speed transmission that is used for vehicle of claim 1, it is characterized in that: by engaging described first clutch element (C1) and the 5th clutch element (C5) is set up first grade; By engaging described first clutch element (C1) and second brake component (B2) is set up second grade; By engaging described first clutch element (C1) and first brake component (B1) is set up third gear; Set up fourth speed by engaging described first clutch element (C1) and three-clutch element (C3); Set up the 5th grade by engaging described first clutch element (C1) and four clutches element (C4); Set up the 6th grade by engaging described first clutch element (C1) and second clutch element (C2); Set up the 7th grade by engaging described second clutch element (C2) and four clutches element (C4); Set up the 8th grade by engaging described second clutch element (C2) and three-clutch element (C3); Set up the 9th grade by engaging described second clutch element (C2) and first brake component (B1); And set up the tenth grade by engaging described second clutch element (C2) and the 5th clutch element (C5).
9. according to the described multi-speed transmission that is used for vehicle of claim 1, it is characterized in that: by engaging described the 5th clutch element (C5) and second brake component (B2) is set up first grade; By engaging described first clutch element (C1) and second brake component (B2) is set up second grade; By engaging described first clutch element (C1) and first brake component (B1) is set up third gear; Set up fourth speed by engaging described first clutch element (C1) and three-clutch element (C3); Set up the 5th grade by engaging described first clutch element (C1) and four clutches element (C4); Set up the 6th grade by engaging described first clutch element (C1) and second clutch element (C2); Set up the 7th grade by engaging described second clutch element (C2) and four clutches element (C4); Set up the 8th grade by engaging described second clutch element (C2) and three-clutch element (C3); Set up the 9th grade by engaging described second clutch element (C2) and first brake component (B1); And set up the tenth grade by engaging described second clutch element (C2) and the 5th clutch element (C5).
10. according to the described multi-speed transmission that is used for vehicle of claim 1, it is characterized in that: by engaging described first clutch element (C1) and second brake component (B2) is set up first grade; By engaging described first clutch element (C1) and the 5th clutch element (C5) is set up second grade; By engaging described first clutch element (C1) and first brake component (B1) is set up third gear; Set up fourth speed by engaging described first clutch element (C1) and three-clutch element (C3); Set up the 5th grade by engaging described first clutch element (C1) and four clutches element (C4); Set up the 6th grade by engaging described first clutch element (C1) and second clutch element (C2); Set up the 7th grade by engaging described second clutch element (C2) and four clutches element (C4); Set up the 8th grade by engaging described second clutch element (C2) and three-clutch element (C3); Set up the 9th grade by engaging described second clutch element (C2) and first brake component (B1); And set up the tenth grade by engaging described second clutch element (C2) and the 5th clutch element (C5).
11., it is characterized in that: by engaging described the 5th clutch element (C5) and second brake component (B2) is set up first grade according to the described multi-speed transmission that is used for vehicle of claim 1; By engaging described first clutch element (C1) and the 5th clutch element (C5) is set up second grade; By engaging described first clutch element (C1) and first brake component (B1) is set up third gear; Set up fourth speed by engaging described first clutch element (C1) and three-clutch element (C3); Set up the 5th grade by engaging described first clutch element (C1) and four clutches element (C4); Set up the 6th grade by engaging described first clutch element (C1) and second clutch element (C2); Set up the 7th grade by engaging described second clutch element (C2) and four clutches element (C4); Set up the 8th grade by engaging described second clutch element (C2) and three-clutch element (C3); Set up the 9th grade by engaging described second clutch element (C2) and first brake component (B1); And set up the tenth grade by engaging described second clutch element (C2) and the 5th clutch element (C5).
12., it is characterized in that: by engaging described the 5th clutch element (C5) and second brake component (B2) is set up first grade according to the described multi-speed transmission that is used for vehicle of claim 1; By engaging described first clutch element (C1) and second brake component (B2) is set up second grade; By engaging described first clutch element (C1) and the 5th clutch element (C5) is set up third gear; By engaging described first clutch element (C1) and first brake component (B1) is set up fourth speed; Set up the 5th grade by engaging described first clutch element (C1) and three-clutch element (C3); Set up the 6th grade by engaging described first clutch element (C1) and four clutches element (C4); Set up the 7th grade by engaging described first clutch element (C1) and second clutch element (C2); Set up the 8th grade by engaging described second clutch element (C2) and four clutches element (C4); Set up the 9th grade by engaging described second clutch element (C2) and three-clutch element (C3); Set up the tenth grade by engaging described second clutch element (C2) and first brake component (B1); And set up the 11 grade by engaging described second clutch element (C2) and the 5th clutch element (C5).
13. according to each described multi-speed transmission that is used for vehicle in the claim 1 to 12, it is characterized in that: described first speed changing portion (38,144,174,175) comprise the first preposition planetary gear set (24 of single small gear type, 140,170,171) and the second preposition planetary gear set (26 of double pinion type, 142,172,173), the sun gear (S2) of planet carrier of the wherein said first preposition planetary gear set (CA1) and the described second preposition planetary gear set always is connected in described nonrotational element (16), and the planet carrier (CA2) of sun gear of the described first preposition planetary gear set (S1) and the described second preposition planetary gear set is connected in described input rotating element (22), so that the gear ring of the described second preposition planetary gear set (R2) is used as the described first middle output element (32), and the gear ring of the described first preposition planetary gear set (R1) is as the described second middle output element (34).
14. according to each described multi-speed transmission that is used for vehicle in the claim 1 to 12, it is characterized in that: described first speed changing portion (72) comprises first preposition planetary gear set (68) of double pinion type and the second preposition planetary gear set (70) of single small gear type, the planet carrier of the wherein said first preposition planetary gear set (CA1) always is connected in described nonrotational element (16), the planet carrier (CA2) of gear ring of the described first preposition planetary gear set (R1) and the described second preposition planetary gear set links together, and the gear ring (R2) of sun gear of the described first preposition planetary gear set (S1) and the described second preposition planetary gear set is connected in described input rotating element (22), so that the planet carrier (CA2) of gear ring of the described first preposition planetary gear set (R1) or the described second preposition planetary gear set is used as the described first middle output element (32), and the sun gear of the described second preposition planetary gear set (S2) is as the described second middle output element (34).
15. according to each described multi-speed transmission that is used for vehicle in the claim 1 to 12, it is characterized in that: described first speed changing portion (80,152,164) comprise the first preposition planetary gear set (76 of double pinion type, 148,156) and the second preposition planetary gear set (78 of single small gear type, 150,158), the sun gear of the wherein said first preposition planetary gear set (S1) always is connected in described nonrotational element (16), the planet carrier (CA2) of gear ring of the described first preposition planetary gear set (R1) and the described second preposition planetary gear set links together, and the gear ring (R2) of planet carrier of the described first preposition planetary gear set (CA1) and the described second preposition planetary gear set is connected in described input rotating element (22), so that the planet carrier (CA2) of gear ring of the described first preposition planetary gear set (R1) or the described second preposition planetary gear set is used as the described first middle output element (32), and the sun gear of the described second preposition planetary gear set (S2) is as the described second middle output element (34).
16. according to each described multi-speed transmission that is used for vehicle in the claim 1 to 12, it is characterized in that: described first speed changing portion (104) comprises first preposition planetary gear set (100) of single small gear type and the second preposition planetary gear set (102) of double pinion type, the gear ring of the wherein said second preposition planetary gear set (R2) always is connected in described nonrotational element (16), the sun gear (S2) of sun gear of the described first preposition planetary gear set (S1) and the described second preposition planetary gear set links together, the planet carrier (CA2) of planet carrier of the described first preposition planetary gear set (CA1) and the described second preposition planetary gear set links together, and the gear ring of the described first preposition planetary gear set (R1) is connected in described input rotating element (22), so that the planet carrier (CA2) of planet carrier of the described first preposition planetary gear set (CA1) or the described second preposition planetary gear set is used as the described first middle output element (32), and the sun gear (S2) of sun gear of the described first preposition planetary gear set (S1) or the described second preposition planetary gear set is as the described second middle output element (34).
17. according to each described multi-speed transmission that is used for vehicle in the claim 1 to 12, it is characterized in that: described first speed changing portion (128) comprises first preposition planetary gear set (124) of single small gear type and the second preposition planetary gear set (126) of double pinion type, the gear ring (R2) of planet carrier of the wherein said first preposition planetary gear set (CA1) and the described second preposition planetary gear set always is connected in described nonrotational element (16), the planet carrier (CA2) of gear ring of the described first preposition planetary gear set (R1) and the described second preposition planetary gear set links together, and the sun gear of the described first preposition planetary gear set (S1) is connected in described input rotating element (22), so that the sun gear of the described second preposition planetary gear set (S2) is used as the described first middle output element (32), and the planet carrier (CA2) of gear ring of the described first preposition planetary gear set (R1) or the described second preposition planetary gear set is as the described second middle output element (34).
18. according to each described multi-speed transmission that is used for vehicle in the claim 1 to 12, it is characterized in that: described first speed changing portion (182) comprises first preposition planetary gear set (178) of single small gear type and the second preposition planetary gear set (180) of single small gear type, the planet carrier (CA2) of planet carrier of the wherein said first preposition planetary gear set (CA1) and the described second preposition planetary gear set always is connected in described nonrotational element (16), and the sun gear of the described first preposition planetary gear set (S1) is connected in described input rotating element (22), so that the sun gear of the described second preposition planetary gear set (S2) is used as the described first middle output element (32), and the gear ring of the described first preposition planetary gear set (R1) is as the described second middle output element (34).
19. according to each described multi-speed transmission that is used for vehicle in the claim 1 to 12, it is characterized in that: described first speed changing portion (190) comprises first preposition planetary gear set (178) of single small gear type and the second preposition planetary gear set (180) of single small gear type, the planet carrier (CA2) of planet carrier of the wherein said first preposition planetary gear set (CA1) and the described second preposition planetary gear set always is connected in described nonrotational element (16), and the sun gear of the described first preposition planetary gear set (S1) is connected in described input rotating element (22), so that the sun gear of the described second preposition planetary gear set (S2) is used as the described first middle output element (32), and the gear ring of the described second preposition planetary gear set (R2) is as the described second middle output element (34).
20. according to each described multi-speed transmission that is used for vehicle in the claim 1 to 12, it is characterized in that: described first speed changing portion (198) comprises first preposition planetary gear set (194) of single small gear type and the second preposition planetary gear set (196) of single small gear type, the sun gear of the wherein said second preposition planetary gear set (S2) always is connected in described nonrotational element (16), the planet carrier (CA2) of planet carrier of the described first preposition planetary gear set (CA1) and the described second preposition planetary gear set is joined together to form single rotating element, and the gear ring of the described second preposition planetary gear set (R2) is connected in described input rotating element (22), so that described single rotating element is used as the described first middle output element (32), and the sun gear of the described first preposition planetary gear set (S1) is as the described second middle output element (34).
21. according to each described multi-speed transmission that is used for vehicle in the claim 1 to 12, it is characterized in that: described first speed changing portion (206) comprises first preposition planetary gear set (202) of single small gear type and the second preposition planetary gear set (204) of single small gear type, the sun gear of the wherein said second preposition planetary gear set (S2) always is connected in described nonrotational element (16), the planet carrier (CA2) of planet carrier of the described first preposition planetary gear set (CA1) and the described second preposition planetary gear set is joined together to form single rotating element, and the gear ring of the described first preposition planetary gear set (R1) is connected in described input rotating element (22), so that described single rotating element is used as the described first middle output element (32), and the sun gear of the described first preposition planetary gear set (S1) is as the described second middle output element (34).
22. according to each described multi-speed transmission that is used for vehicle in the claim 1 to 12, it is characterized in that: described first speed changing portion (216) comprises first preposition planetary gear set (212) of single small gear type and the second preposition planetary gear set (214) of double pinion type, the gear ring of the wherein said second preposition planetary gear set (R2) always is connected in described nonrotational element (16), the sun gear (S2) of planet carrier of the described first preposition planetary gear set (CA1) and the described second preposition planetary gear set links together, the planet carrier (CA2) of sun gear of the described first preposition planetary gear set (S1) and the described second preposition planetary gear set links together, and the gear ring of the described first preposition planetary gear set (R1) is connected in described input rotating element (22), so that the sun gear (S2) of the planet carrier (CA1) of the described first preposition planetary gear set that links together and the described second preposition planetary gear set is used as the described first middle output element (32), and the planet carrier (CA2) of the sun gear (S1) of the described first preposition planetary gear set that links together and the described second preposition planetary gear set is as the described second middle output element (34).
23. according to each described multi-speed transmission that is used for vehicle in the claim 1 to 12, it is characterized in that: described first speed changing portion (226) comprises first preposition planetary gear set (222) of single small gear type and the second preposition planetary gear set (224) of double pinion type, the gear ring of the wherein said second preposition planetary gear set (R2) always is connected in described nonrotational element (16), the sun gear (S2) of sun gear of the described first preposition planetary gear set (S1) and the described second preposition planetary gear set links together, and the planet carrier (CA2) of gear ring of the described first preposition planetary gear set (R1) and the described second preposition planetary gear set links together and is connected in described input rotating element (22), so that the planet carrier of the described first preposition planetary gear set (CA1) is used as the described first middle output element (32), and the sun gear (S2) of the sun gear (S1) of the described first preposition planetary gear set that links together and the described second preposition planetary gear set is as the described second middle output element (34).
24. according to each described multi-speed transmission that is used for vehicle in the claim 1 to 12, it is characterized in that: described first speed changing portion (236) comprises first preposition planetary gear set (232) of single small gear type and the second preposition planetary gear set (234) of double pinion type, the gear ring (R2) of planet carrier of the wherein said first preposition planetary gear set (CA1) and the described second preposition planetary gear set always is connected in described nonrotational element (16), the sun gear (S2) of gear ring of the described first preposition planetary gear set (R1) and the described second preposition planetary gear set links together, and the sun gear of the described first preposition planetary gear set (S1) is connected in described input rotating element (22), so that the planet carrier of the described second preposition planetary gear set (CA2) is used as the described first middle output element (32), and the sun gear (S2) of the gear ring (R1) of the described first preposition planetary gear set that links together and the described second preposition planetary gear set is as the described second middle output element (34).
25. according to each described multi-speed transmission that is used for vehicle in the claim 1 to 12, it is characterized in that: described first speed changing portion (246) comprises first preposition planetary gear set (242) of double pinion type and the second preposition planetary gear set (244) of single small gear type, the gear ring of the wherein said first preposition planetary gear set (R1) always is connected in described nonrotational element (16), the sun gear (S2) of planet carrier of the described first preposition planetary gear set (CA1) and the described second preposition planetary gear set links together, and the sun gear of the described first preposition planetary gear set (S1) is connected in described input rotating element (22) with the gear ring (R2) of the described second preposition planetary gear set, so that the planet carrier of the described second preposition planetary gear set (CA2) is used as the described first middle output element (32), and the sun gear (S2) of the planet carrier (CA1) of the described first preposition planetary gear set that links together and the described second preposition planetary gear set is as the described second middle output element (34).
26. according to each described multi-speed transmission that is used for vehicle in the claim 1 to 12, it is characterized in that: described first speed changing portion (256) comprises first preposition planetary gear set (252) of single small gear type and the second preposition planetary gear set (254) of single small gear type, the planet carrier (CA1) of the wherein said first preposition planetary gear set (252) always is connected in described nonrotational element (16), the sun gear (S2) of the gear ring (R1) of the described first preposition planetary gear set (252) and the described second preposition planetary gear set (254) links together, and the sun gear (S1) of the described first preposition planetary gear set (252) is connected in described input rotating element (22) with the gear ring (R2) of the described second preposition planetary gear set (254), so that the planet carrier (CA2) of the described second preposition planetary gear set (254) is used as the described first middle output element (32), and the sun gear (S2) of the gear ring (R1) of the described first preposition planetary gear set (252) that links together and the described second preposition planetary gear set (254) is as the described second middle output element (34).
27. according to each described multi-speed transmission that is used for vehicle in the claim 1 to 12, it is characterized in that: described second speed changing portion (50) comprises first rearmounted planetary gear set (46) of single small gear type and the second rearmounted planetary gear set (48) of double pinion type, wherein said first rotating element (RE1) is to be made of the sun gear (S3) of the described first rearmounted planetary gear set, described second rotating element (RE2) is to be made of the planet carrier (CA4) of the planet carrier (CA3) of the described first rearmounted planetary gear set that links together and the described second rearmounted planetary gear set, described the 3rd rotating element (RE3) is to be made of the gear ring (R4) of the gear ring (R3) of the described first rearmounted planetary gear set that links together and the described second rearmounted planetary gear set, and described the 4th rotating element (RE4) is that sun gear (S4) by the described second rearmounted planetary gear set constitutes.
28. according to each described multi-speed transmission that is used for vehicle in the claim 1 to 12, it is characterized in that: described second speed changing portion (40) comprises first rearmounted planetary gear set (28) of single small gear type and the second rearmounted planetary gear set (30) of double pinion type, wherein said first rotating element (RE1) is to be made of the planet carrier (CA4) of the sun gear (S3) of the described first rearmounted planetary gear set that links together and the described second rearmounted planetary gear set, described second rotating element (RE2) is to be made of the gear ring (R4) of the planet carrier (CA3) of the described first rearmounted planetary gear set that links together and the described second rearmounted planetary gear set, described the 3rd rotating element (RE3) is to be made of the gear ring (R3) of the described first rearmounted planetary gear set, and described the 4th rotating element (RE4) is that sun gear (S4) by the described second rearmounted planetary gear set constitutes.
29. according to each described multi-speed transmission that is used for vehicle in the claim 1 to 12, it is characterized in that: described second speed changing portion (166) comprises first rearmounted planetary gear set (160) of single small gear type and the second rearmounted planetary gear set (162) of double pinion type, wherein said first rotating element (RE1) is to be made of the sun gear (S3) of the described first rearmounted planetary gear set, described second rotating element (RE2) is to be made of the planet carrier (CA4) of the planet carrier (CA3) of the described first rearmounted planetary gear set that links together and the described second rearmounted planetary gear set, described the 3rd rotating element (RE3) is to be made of the gear ring (R4) of the described second rearmounted planetary gear set, and described the 4th rotating element (RE4) is by sun gear (S4) formation of the gear ring (R3) of the described first rearmounted planetary gear set that links together and the described second rearmounted planetary gear set.
30. according to each described multi-speed transmission that is used for vehicle in the claim 1 to 12, it is characterized in that: described second speed changing portion (266) comprises first rearmounted planetary gear set (262) of double pinion type and the second rearmounted planetary gear set (264) of double pinion type, wherein said first rotating element (RE1) is to be made of the sun gear (S3) of the described first rearmounted planetary gear set (262), described second rotating element (RE2) is to be made of the planet carrier (CA4) of the gear ring (R3) of the described first rearmounted planetary gear set (262) that links together and the described second rearmounted planetary gear set (264), described the 3rd rotating element (RE3) is to be made of the gear ring (R4) of the described second rearmounted planetary gear set (264), and described the 4th rotating element (RE4) is by sun gear (S4) formation of the planet carrier (CA3) of the described first rearmounted planetary gear set (262) that links together and the described second rearmounted planetary gear set (264).
31. according to each described multi-speed transmission that is used for vehicle in the claim 1 to 12, it is characterized in that: described second speed changing portion (276) comprises first rearmounted planetary gear set (272) of double pinion type and the second rearmounted planetary gear set (274) of double pinion type, wherein said first rotating element (RE1) is to be made of the planet carrier (CA3) of the described first rearmounted planetary gear set (272), described second rotating element (RE2) is to be made of the planet carrier (CA4) of the gear ring (R3) of the described first rearmounted planetary gear set (272) that links together and the described second rearmounted planetary gear set (274), described the 3rd rotating element (RE3) is to be made of the gear ring (R4) of the described second rearmounted planetary gear set (274), and described the 4th rotating element (RE4) is by sun gear (S4) formation of the sun gear (S3) of the described first rearmounted planetary gear set (272) that links together and the described second rearmounted planetary gear set (274).
CN 200510097408 2004-12-28 2005-12-28 The multi-speed transmission that is used for vehicle Expired - Fee Related CN100540943C (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP2004381497 2004-12-28
JP381497/2004 2004-12-28
JP127209/2005 2005-04-25
JP177052/2005 2005-06-16
JP244282/2005 2005-08-25

Publications (2)

Publication Number Publication Date
CN1796825A true CN1796825A (en) 2006-07-05
CN100540943C CN100540943C (en) 2009-09-16

Family

ID=36818066

Family Applications (1)

Application Number Title Priority Date Filing Date
CN 200510097408 Expired - Fee Related CN100540943C (en) 2004-12-28 2005-12-28 The multi-speed transmission that is used for vehicle

Country Status (1)

Country Link
CN (1) CN100540943C (en)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100580283C (en) * 2006-10-31 2010-01-13 丰田自动车株式会社 Control equipment for vehicle drive system
CN101839337A (en) * 2009-03-16 2010-09-22 通用汽车环球科技运作公司 Multiple-speed gear-box with selectable one-way brake coupling
CN103270338A (en) * 2010-12-21 2013-08-28 腓特烈斯港齿轮工厂股份公司 Multi-stage gearbox
CN106195157A (en) * 2014-10-16 2016-12-07 现代自动车株式会社 Many gears automatic transmission for vehicle
CN106438877A (en) * 2015-08-05 2017-02-22 爱信精机株式会社 Automatic transmission device for vehicle
CN106812889A (en) * 2015-12-02 2017-06-09 现代自动车株式会社 For the epicyclic train of the automatic transmission of vehicle
CN107202101A (en) * 2016-03-16 2017-09-26 现代自动车株式会社 Epicyclic train for the automatic transmission of vehicle
CN109906323A (en) * 2016-11-22 2019-06-18 Zf 腓德烈斯哈芬股份公司 The speed changer of motor vehicle

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100580283C (en) * 2006-10-31 2010-01-13 丰田自动车株式会社 Control equipment for vehicle drive system
CN101839337A (en) * 2009-03-16 2010-09-22 通用汽车环球科技运作公司 Multiple-speed gear-box with selectable one-way brake coupling
CN101839337B (en) * 2009-03-16 2014-08-27 通用汽车环球科技运作公司 Multi-speed transmission with selectable one-way braking clutch
CN103270338A (en) * 2010-12-21 2013-08-28 腓特烈斯港齿轮工厂股份公司 Multi-stage gearbox
CN103270338B (en) * 2010-12-21 2015-10-14 腓特烈斯港齿轮工厂股份公司 Multiple-speed gear-box
CN106195157A (en) * 2014-10-16 2016-12-07 现代自动车株式会社 Many gears automatic transmission for vehicle
CN106195157B (en) * 2014-10-16 2019-04-30 现代自动车株式会社 More gear automatic transmission for vehicle
CN106438877A (en) * 2015-08-05 2017-02-22 爱信精机株式会社 Automatic transmission device for vehicle
CN106812889A (en) * 2015-12-02 2017-06-09 现代自动车株式会社 For the epicyclic train of the automatic transmission of vehicle
CN107202101A (en) * 2016-03-16 2017-09-26 现代自动车株式会社 Epicyclic train for the automatic transmission of vehicle
CN107202101B (en) * 2016-03-16 2021-02-09 现代自动车株式会社 Planetary gear train of automatic transmission for vehicle
CN109906323A (en) * 2016-11-22 2019-06-18 Zf 腓德烈斯哈芬股份公司 The speed changer of motor vehicle

Also Published As

Publication number Publication date
CN100540943C (en) 2009-09-16

Similar Documents

Publication Publication Date Title
CN1295452C (en) Gear shifter for automatic transmission
CN1796825A (en) Multi-speed transmission for vehicle
CN1926356A (en) Drive system for vehicle, method of controlling the system, and device for controlling the system
CN1547648A (en) Automatic transmission
CN1573167A (en) Multistage transmission
CN1598364A (en) Hydraulic control system of a six-speed automatic transmission
CN101031738A (en) Automatic transmission for vehicle
CN1793694A (en) Six-speed power train of an automatic transmission
CN100343389C (en) Method of detecting gene mutation
CN1580500A (en) Airfoil shape for a turbine nozzle
CN1576516A (en) Airfoil shape for a turbine bucket
CN1677286A (en) Control system for movable body
CN1942690A (en) Automatic transmission for vehicle
CN101030138A (en) Application framework
CN1757155A (en) Motor driving apparatus is equipped with the vehicle of this equipment and stores and makes the computer-readable recording medium of program of computer control voltage transitions
CN1596376A (en) Zoom lens and video camera using it
CN1576941A (en) Imaging lens and imaging device
CN1746538A (en) Coupler with two-way same or different characteristic
CN1573173A (en) Plant control system
CN1241046C (en) Vari-focus lens system
CN1749801A (en) Wide zoom lens system
CN1692239A (en) Automatic speed changer
CN1727726A (en) Six-speed powertrain of an automatic transmission
CN1603881A (en) Zoom lens system
CN1877328A (en) Method for detecting aquatic animal pathogenic bacteria by using 23S ribosome gene probe array

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
C14 Grant of patent or utility model
GR01 Patent grant
CF01 Termination of patent right due to non-payment of annual fee

Granted publication date: 20090916

Termination date: 20171228

CF01 Termination of patent right due to non-payment of annual fee