WO2013129440A1 - Automatic transmission device - Google Patents

Automatic transmission device Download PDF

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Publication number
WO2013129440A1
WO2013129440A1 PCT/JP2013/055049 JP2013055049W WO2013129440A1 WO 2013129440 A1 WO2013129440 A1 WO 2013129440A1 JP 2013055049 W JP2013055049 W JP 2013055049W WO 2013129440 A1 WO2013129440 A1 WO 2013129440A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch
brake
rotating element
planetary gear
automatic transmission
Prior art date
Application number
PCT/JP2013/055049
Other languages
French (fr)
Japanese (ja)
Inventor
政弘 大竹
融 左右田
糟谷　悟
宣和 池
加藤　博
慎司 大板
森瀬　勝
Original Assignee
アイシン・エィ・ダブリュ株式会社
トヨタ自動車株式会社
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 アイシン・エィ・ダブリュ株式会社, トヨタ自動車株式会社 filed Critical アイシン・エィ・ダブリュ株式会社
Publication of WO2013129440A1 publication Critical patent/WO2013129440A1/en

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    • 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
    • F16H2200/20—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
    • F16H2200/203—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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2064—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using at least one positive clutch, e.g. dog clutch

Definitions

  • the present invention relates to an automatic transmission apparatus that shifts the power input to an input member and outputs it to an output member.
  • an automatic transmission device when an automatic transmission is configured by three planetary gear mechanisms and a plurality of clutches and brakes, there are many ways to connect the rotating elements of the three planetary gear mechanisms and to attach a plurality of clutches and brakes. There are some that can function as an automatic transmission device and some that cannot function depending on the connection and installation. Further, when clutches and brakes are formed as friction engagement elements, drag at the time of release is unavoidable, so it is desirable that the number of clutches and brakes to be released at each shift stage is as small as possible. Furthermore, when the clutch or brake is formed as a friction engagement element, it is necessary to maintain the hydraulic pressure in order to maintain the engagement of the clutch or the brake. This reduces energy efficiency.
  • the automatic transmission apparatus is mainly intended to propose a new automatic transmission apparatus including three planetary gear mechanisms, five clutches, and two brakes, and reduces drag loss in the automatic transmission apparatus. Another object is to improve the transmission efficiency of the apparatus.
  • the automatic transmission apparatus employs the following means in order to achieve the main object described above.
  • the automatic transmission device of the present invention is An automatic transmission device that shifts the power input to the input member and outputs it to the output member, A first planetary gear mechanism having a first rotating element, a second rotating element, and a third rotating element in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram; A second planetary gear mechanism having a fourth rotating element, a fifth rotating element, and a sixth rotating element in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram; A third planetary gear mechanism having a seventh rotating element, an eighth rotating element, and a ninth rotating element in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram; A first connecting element that connects the second rotating element and the fifth rotating element; A first clutch for engaging and releasing the input member and the first rotating element; A second clutch that engages the first rotating element and the fourth rotating element and releases the engagement; A third clutch for engaging and releasing the sixth rotating element and the seventh rotating element; A fourth clutch for engaging and releasing the seventh rotating element and the first connecting element; A fifth clutch
  • the first planetary element having the first rotating element, the second rotating element, and the third rotating element in the arrangement order at intervals corresponding to the gear ratio in the velocity diagram as the three rotating elements.
  • the fifth rotating element is connected by the first connecting element.
  • the input member and the first rotating element are connected via the first clutch, the first rotating element and the fourth rotating element are connected via the second clutch, and the sixth rotating element is connected via the third clutch.
  • the seventh rotating element, the seventh rotating element and the first connecting element are connected via the fourth clutch, the fourth rotating element and the ninth rotating element are connected via the fifth clutch,
  • the first brake is connected to the sixth rotating element, the second brake is connected to the ninth rotating element, the input member is connected to the eighth rotating element, and the output member is connected to the third rotating element.
  • the first forward speed to the ninth forward speed and the reverse speed can be configured as follows.
  • the first forward speed is formed by engaging the first clutch, the second clutch, the fourth clutch, and the first brake and releasing the third clutch, the fifth clutch, and the second brake.
  • the second forward speed is formed by engaging the first clutch, the fourth clutch, the fifth clutch, and the first brake and releasing the second clutch, the third clutch, and the second brake.
  • the third forward speed is formed by engaging the first clutch, the third clutch, the fifth clutch, and the first brake and releasing the second clutch, the fourth clutch, and the second brake.
  • the fourth forward speed is formed by engaging the first clutch, the second clutch, the third clutch, and the fifth clutch and releasing the fourth clutch, the first brake, and the second brake.
  • the fifth forward speed is formed by engaging the first clutch, the third clutch, the fifth clutch, and the second brake and releasing the second clutch, the fourth clutch, and the first brake.
  • the sixth forward speed is formed by engaging the second clutch, the third clutch, the fifth clutch, and the second brake and releasing the first clutch, the fourth clutch, and the first brake.
  • the seventh forward speed is formed by engaging the first clutch, the second clutch, the third clutch, and the second brake and releasing the fourth clutch, the fifth clutch, and the first brake.
  • the eighth forward speed is formed by engaging the second clutch, the third clutch, the fourth clutch, and the second brake and releasing the first clutch, the fifth clutch, and the first brake.
  • the ninth forward speed is formed by engaging the first clutch, the second clutch, the fourth clutch, and the second brake and releasing the third clutch, the fifth clutch, and the first brake.
  • the reverse gear is formed by engaging the first clutch, the fifth clutch, the first brake, and the second brake and releasing the second clutch, the third clutch, and the fourth clutch.
  • the first brake may be configured as a dog brake.
  • the dog brake is susceptible to shock when engaged and requires synchronous control to synchronize its rotation, but the first brake is engaged continuously from the first forward speed to the third forward speed and moves forward from the fourth forward speed. Since the release continues up to the ninth gear, engagement and release are not repeated frequently, and the frequency of occurrence of synchronous control is low. For this reason, even if the dog brake is employed, the deterioration of the shift feeling is suppressed. On the other hand, since the dog brake does not need to hold the hydraulic pressure when engaged, energy loss can be suppressed as compared with a hydraulically driven brake that requires holding the hydraulic pressure. As a result, the energy efficiency of the apparatus can be improved.
  • the first planetary gear mechanism and the second planetary gear mechanism are configured as a single pinion type planetary gear mechanism having a sun gear, a ring gear, and a carrier as the three rotating elements.
  • the third planetary gear mechanism is configured as a double-pinion planetary gear mechanism having a sun gear, a ring gear, and a carrier as the three rotating elements, and the first rotating element and the second rotating element.
  • the third rotating element is a sun gear, a carrier, and a ring gear
  • the fourth rotating element, the fifth rotating element, and the sixth rotating element are a sun gear, a carrier, and a ring gear
  • the seventh rotating element The eighth rotating element and the ninth rotating element may be a sun gear, a ring gear, and a carrier.
  • the first planetary gear mechanism, the second planetary gear mechanism, and the third planetary gear mechanism are arranged in this order from the input member. It can also be.
  • FIG. 1 is a configuration diagram showing an outline of a configuration of an automatic transmission device 1 as an embodiment of the present invention. It is an operation
  • FIG. 1 is a block diagram showing an outline of the configuration of an automatic transmission device 1 as an embodiment of the present invention.
  • the automatic transmission device 1 includes two single-pinion planetary gear mechanisms 10 and 20, one double-pinion planetary gear mechanism 30, five clutches C1 to C5, and two brakes B1 and B2.
  • a vehicle for example, front engine front drive type
  • an engine as an internal combustion engine not shown
  • It is configured as a stepped transmission mechanism that is input from an input shaft (input shaft) 3 via a starting device such as a converter and that shifts the input power and outputs it to the output gear 4.
  • the power output to the output gear 4 is output to the left and right drive wheels 7a and 7b via the gear mechanism 5 and the differential gear 6.
  • the gear mechanism 5 includes a counter shaft 5a having a rotation shaft arranged parallel to the rotation shaft of the output gear 4, a counter driven gear 5b that is attached to the counter shaft 5a and meshes with the output gear 4, and a differential that is also attached to the counter shaft 5a.
  • the differential drive gear 5c meshes with the ring gear of the gear 6.
  • the lower side of the input shaft 3 in the drawing mainly shows the connection relationship between the output gear 4 and the gear mechanism 5 in the configuration of the automatic transmission device 1, and the others are omitted.
  • the automatic transmission device 1 of the embodiment includes three planetary gear mechanisms 10, 20, and 30 in order from the input shaft 3 side (right side in FIG. 1) connected to the engine side in order from the first planetary gear.
  • the mechanism 10, the second planetary gear mechanism 20, and the third planetary gear mechanism 30 are arranged.
  • the first planetary gear mechanism 10 includes a sun gear 11 as an external gear, a ring gear 13 as an internal gear disposed concentrically with the sun gear 11, and a plurality of gears meshed with the sun gear 11 and meshed with the ring gear 13.
  • a pinion gear 14 and a carrier 12 that couples and holds the plurality of pinion gears 14 so as to rotate and revolve freely. Since the first planetary gear mechanism 10 is configured as a single pinion type planetary gear mechanism, the three rotating elements, the sun gear 11, the ring gear 13, and the carrier 12, are spaced at intervals corresponding to the gear ratio in the velocity diagram. ,
  • the gear ratio ⁇ 1 of the first planetary gear mechanism 10 (the number of teeth of the sun gear 11 / the number of teeth of the ring gear 13) is set to 0.25, for example.
  • the second planetary gear mechanism 20 includes a sun gear 21 as an external gear, a ring gear 23 as an internal gear arranged concentrically with the sun gear 21, and a plurality of gears meshed with the sun gear 21 and meshed with the ring gear 23.
  • a pinion gear 24 and a carrier 22 that couples and holds the plurality of pinion gears 24 so as to rotate and revolve freely are provided. Since the second planetary gear mechanism 20 is configured as a single pinion type planetary gear mechanism, the three rotating elements, the sun gear 21, the ring gear 23, and the carrier 22, are spaced at intervals corresponding to the gear ratio in the velocity diagram. , The sun gear 21, the carrier 22, and the ring gear 23.
  • the gear ratio ⁇ 2 (number of teeth of the sun gear 21 / number of teeth of the ring gear 23) of the second planetary gear mechanism 20 is set to 0.65, for example.
  • the third planetary gear mechanism 30 includes a sun gear 31 as an external gear, a ring gear 32 as an internal gear disposed concentrically with the sun gear 31, and a plurality of first pinion gears 34 that mesh with the sun gear 31.
  • a plurality of second pinion gears 35 meshing with the first pinion gear 34 and meshing with the ring gear 32; and a plurality of first pinion gears 34 and a carrier 33 holding the plurality of second pinion gears 35 so as to rotate and revolve.
  • the third planetary gear mechanism 30 is configured as a double pinion planetary gear mechanism, the three rotating elements, the sun gear 31, the ring gear 32, and the carrier 33, are spaced at intervals corresponding to the gear ratio in the velocity diagram.
  • the sun gear 31, the ring gear 32, and the carrier 33 are set to 0.50, for example.
  • the carrier 12 of the first planetary gear mechanism 10 is connected to the carrier 22 of the second planetary gear mechanism 20 by a first connecting element 51.
  • the input shaft 3 is connected to the sun gear 11 of the first planetary gear mechanism 10 via the clutch C1.
  • the sun gear 11 of the first planetary gear mechanism 10 is connected to the sun gear 21 of the second planetary gear mechanism 20 via the clutch C2.
  • the ring gear 23 of the second planetary gear mechanism 20 is connected to the sun gear 31 of the third planetary gear mechanism 30 via the clutch C3.
  • the sun gear 31 of the third planetary gear mechanism 30 is connected to the first coupling element 51 via the clutch C4.
  • the sun gear 21 of the second planetary gear mechanism 20 is connected to the carrier 33 of the third planetary gear mechanism 30 via the clutch C5.
  • the ring gear 23 of the second planetary gear mechanism 20 is connected to the case (automatic transmission device case) 2 via the brake B1, and the carrier 33 of the third planetary gear mechanism 30 is connected to the case via the brake B2. 2 is connected.
  • the input shaft 3 is connected to the ring gear 32 of the third planetary gear mechanism 30, and the output gear 4 is connected to the ring gear 13 of the first planetary gear mechanism 10.
  • the five clutches C1 to C5 and the two brakes B1 and B2 are each configured as a hydraulically driven friction clutch or friction brake that is engaged by pressing the friction plate with a piston.
  • the automatic transmission apparatus 1 has a first forward speed to a ninth forward speed by a combination of engagement and release of the five clutches C1 to C5 and engagement and release of the two brakes B1 and B2.
  • the reverse gear can be switched.
  • FIG. 2 shows an operation table of the automatic transmission device 1
  • FIG. 3 shows a speed diagram of the first to third planetary gear mechanisms 10, 20, 30 of the automatic transmission device 1.
  • FIG. 3 shows a velocity diagram of the first planetary gear mechanism 10, a velocity diagram of the second planetary gear mechanism 20, and a velocity diagram of the third planetary gear mechanism 30 in order from the left.
  • the sun gear, the carrier, and the ring gear are arranged in this order from the left.
  • the sun gear, the ring gear, and the carrier are arranged from the left. They are in order.
  • “1st” represents the first forward speed
  • “2nd” represents the second forward speed
  • “3rd” represents the third forward speed
  • “4th” to “9th” represents the fourth forward speed.
  • “Rev” indicates the reverse gear.
  • “ ⁇ 1” to “ ⁇ 3” indicate the gear ratio of each planetary gear mechanism
  • “B1” and “B2” indicate the brakes B1 and B2.
  • “Input” indicates the connection position of the input shaft 3
  • “Output” indicates the connection position of the output gear 4.
  • the first forward speed to the ninth forward speed and the reverse speed are formed as follows.
  • the gear ratio (the number of revolutions of the input shaft 3 / the number of revolutions of the output gear 4) is 0.25, 0,...
  • the case where 65,0.50 was used was shown.
  • the first forward speed can be formed by engaging the clutch C1, the clutch C2, the clutch C4, and the brake B1, and releasing the clutch C3, the clutch C5, and the brake B2, and the gear ratio is 4 .125.
  • the second forward speed can be formed by engaging the clutch C1, the clutch C4, the clutch C5, and the brake B1, and releasing the clutch C2, the clutch C3, and the brake B2, and the gear ratio is 2 .190.
  • the third forward speed can be formed by engaging the clutch C1, the clutch C3, the clutch C5, and the brake B1, and releasing the clutch C2, the clutch C4, and the brake B2, and the gear ratio is 1 .361.
  • the fourth forward speed can be formed by engaging the clutch C1, the clutch C2, the clutch C3, and the clutch C5 and releasing the clutch C4, the brake B1, and the brake B2, and the gear ratio is 1. .000.
  • the fifth forward speed can be established by engaging the clutch C1, the clutch C3, the clutch C5, and the brake B2, and releasing the clutch C2, the clutch C4, and the brake B1, and the gear ratio is 0. 790.
  • the sixth forward speed can be formed by engaging the clutch C2, the clutch C3, the clutch C5, and the brake B2, and releasing the clutch C1, the clutch C4, and the brake B1, and the gear ratio is 0. .660.
  • the seventh forward speed can be established by engaging the clutch C1, the clutch C2, the clutch C3, and the brake B2, and releasing the clutch C4, the clutch C5, and the brake B1, and the gear ratio is 0. .569.
  • the eighth forward speed can be formed by engaging the clutch C2, the clutch C3, the clutch C4, and the brake B2, and releasing the clutch C1, the clutch C5, and the brake B1, and the gear ratio is 0. .500.
  • the ninth forward speed can be established by engaging the clutch C1, the clutch C2, the clutch C4, and the brake B2, and releasing the clutch C3, the clutch C5, and the brake B1, and the gear ratio is 0. .444.
  • the reverse gear can be formed by engaging the clutch C1, the clutch C5, the brake B1, and the brake B2 and releasing the clutch C2, the clutch C3, and the clutch C4, and the gear ratio is ⁇ 4. 000.
  • the gear ratios ⁇ 1, ⁇ 2, ⁇ 3 of the first to third planetary gear mechanisms 10, 20, 30 0.25, 0.65, 0.50 are used as the gear ratios ⁇ 1, ⁇ 2, ⁇ 3 of the first to third planetary gear mechanisms 10, 20, 30.
  • the gear ratio of the first forward speed, which is the lowest speed stage is 4.125
  • the gear ratio of the ninth forward speed, which is the highest speed stage is 0.444. 9.291.
  • the automatic transmission device 1 according to the embodiment is configured as a transmission having nine speeds from the first forward speed to the ninth forward speed, it is compared with a transmission having eight or fewer forward speeds.
  • the driving performance can be improved by improving the acceleration performance and the fuel efficiency and reducing the shock at the time of shifting.
  • the five clutches C1 to C5 are configured as friction clutches and the two brakes B1 and B2 are configured as friction brakes.
  • the number of clutches and brakes to be released is three at any shift speed, drag loss due to the release of clutches and brakes is greater than that of four or more clutches or brakes to be released. Can be suppressed.
  • the single-pinion type first planetary gear mechanism 10 the single-pinion type second planetary gear mechanism 20, and the double-pinion-type third planetary gear.
  • a mechanism 30, five clutches C 1 to C 5, and two brakes B 1 and B 2 are provided, and the carrier 12 of the first planetary gear mechanism 10 is transferred to the carrier 22 of the second planetary gear mechanism 20 by the first connecting element 51.
  • the input shaft 3 is connected to the sun gear 11 of the first planetary gear mechanism 10 via the clutch C1, and the sun gear 11 of the first planetary gear mechanism 10 is connected to the sun gear 11 of the second planetary gear mechanism 20 via the clutch C2.
  • the ring gear 23 of the second planetary gear mechanism 20 is connected to the sun gear 31 of the third planetary gear mechanism 30 via the clutch C3, and the sun gear 31 of the third planetary gear mechanism 30 is connected. Is connected to the first coupling element 51 via the clutch C4, and the sun gear 21 of the second planetary gear mechanism 20 is connected to the carrier 33 of the third planetary gear mechanism 30 via the clutch C5.
  • the ring gear 23 of the planetary gear mechanism 20 is connected to the case 2 via the brake B1, the carrier 33 of the third planetary gear mechanism 30 is connected to the case 2 via the brake B2, and the ring gear of the third planetary gear mechanism 30 is connected.
  • the first forward speed is achieved by engaging the clutch C1, the clutch C2, the clutch C4, and the brake B1, and releasing the clutch C3, the clutch C5, and the brake B2.
  • the second forward speed is formed by engaging the clutch C1, the clutch C4, the clutch C5, and the brake B1 and releasing the clutch C2, the clutch C3, and the brake B2, and the third forward speed is defined as the clutch C1. It is formed by engaging the clutch C3, the clutch C5, and the brake B1, and releasing the clutch C2, the clutch C4, and the brake B2.
  • the fourth forward speed is established by engaging the clutch C1, the clutch C2, the clutch C3, and the clutch C5.
  • the 9th forward speed is shifted between clutch C1, clutch C2, and clutch C4.
  • the clutch B3 is engaged and the clutch C3, the clutch C5, and the brake B1 are released, and the reverse gear is engaged with the clutch C1, the clutch C5, the brake B1, and the brake B2, and the clutch C2 and the clutch C3.
  • the number of clutches and brakes to be released can be reduced to three at any shift stage, and the number of clutches and brakes to be released should be four or more. In comparison, loss due to dragging of the clutch or brake to be released can be reduced, and transmission efficiency of the entire apparatus can be improved. Further, since nine shift stages from the first forward speed to the ninth forward speed are formed, the driving performance can be improved as compared with the one that forms eight or less speed stages.
  • FIG. 4 shows a modified automatic transmission device 101 in which the brake B1 is configured as a dog brake.
  • the operation table and speed diagram of the automatic transmission device 101 of the modification are the same as those in FIGS.
  • the dog brake is easily shocked when engaged, and synchronous control is required to synchronize the rotation.
  • the brake B1 is continuously engaged from the first forward speed to the third forward speed, and from the fourth forward speed to the forward 9 speed.
  • the engine is mounted on a vehicle (for example, a front engine front drive type) in which the engine is disposed horizontally (in the left-right direction of the vehicle). It may be mounted on a vehicle of a type (for example, front engine rear drive type) arranged in the vehicle front-rear direction.
  • the first planetary gear mechanism 10 the second planetary gear mechanism 20, and the third planetary gear of the automatic transmission device 1 of FIG.
  • the input shaft 3 extends to the opposite side (left side in FIGS. 1 and 5) and the ring gear of the first planetary gear mechanism 10
  • a hollow rotating shaft 4a for transmitting the rotation to the output shaft 4b on the opposite side (right side in FIGS. 1 and 5) from the input shaft 3 may be connected to 13.
  • 0.25, 0.65, 0.50 are used as the gear ratios ⁇ 1, ⁇ 2, ⁇ 3 of the first to third planetary gear mechanisms 10, 20, 30.
  • the ratios ⁇ 1, ⁇ 2, and ⁇ 3 are not limited to these values.
  • the first planetary gear mechanism 10 and the second planetary gear mechanism 20 are configured as a single pinion type planetary gear mechanism
  • the third planetary gear mechanism 30 is configured as a double pinion type.
  • the first to third planetary gear mechanisms 10, 20, 30 may be configured as all single type planetary gear mechanisms, or the first to third planetary gear mechanisms 10, 20. 30, 30 as a double pinion planetary gear mechanism, or a part of the first to third planetary gear mechanisms 10, 20, 30 is configured as a single pinion planetary gear and the remaining portion It may be configured as a double pinion type planetary gear mechanism.
  • the automatic transmission device 1 In the automatic transmission device 1 according to the embodiment, four of the five clutches C1 to C5 and the two brakes B1 and B2 are engaged and the other three are released, thereby moving forward from the first forward speed 9
  • the automatic transmission apparatus may be capable of selecting a shift of a reverse speed and a reverse speed that is less than the 7th speed.
  • the input shaft (input shaft) 3 corresponds to an “input member”
  • the output gear 4 corresponds to an “output member”
  • the first planetary gear mechanism 10 corresponds to a “first planetary gear mechanism”.
  • the sun gear 11 corresponds to the “first rotating element”
  • the carrier 12 corresponds to the “second rotating element”
  • the ring gear 13 corresponds to the “third rotating element”
  • the second planetary gear mechanism 20 corresponds to “ It corresponds to the “second planetary gear mechanism”
  • the sun gear 21 corresponds to the “fourth rotating element”
  • the carrier 22 corresponds to the “fifth rotating element”
  • the ring gear 23 corresponds to the “sixth rotating element”
  • the third planetary gear mechanism 30 corresponds to a “third planetary gear mechanism”
  • the sun gear 31 corresponds to a “seventh rotating element”
  • the ring gear 32 corresponds to an “eighth rotating element”
  • the carrier 33 corresponds to “
  • the first connecting element 51 corresponds to the “ninth rotating element” and the “first connecting element”
  • the clutch C1 corresponds to the “first clutch”
  • the clutch C2 corresponds to the “second clutch”
  • the clutch C3 corresponds to the “third clutch”
  • the clutch C5 corresponds to the “fifth clutch”
  • the brake B1 corresponds to the “first brake”
  • the brake B2 corresponds to the “second brake”.
  • the present invention can be used in the manufacturing industry of automatic transmission devices.

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

Abstract

The present invention is provided with three planetary gear mechanisms (10, 20, 30), five clutches (C1 to C5), and two brakes (B1, B2), wherein the carrier (12) of the first planetary gear mechanism (10) is connected to the carrier (22) of the second planetary gear mechanism (20) by means of a first connection element (51), an input shaft (3) is connected to the ring gear (32) of the third planetary gear mechanism (30), an output gear (4) is connected to the ring gear (13) of the first planetary gear mechanism (10), and gears 1 to 9 and a reverse gear are formed by engaging four and release three clutches (C1 to C5) and brakes (B1, B2).

Description

自動変速機装置Automatic transmission device
　本発明は、入力部材に入力された動力を変速して出力部材に出力する自動変速機装置に関する。 The present invention relates to an automatic transmission apparatus that shifts the power input to an input member and outputs it to an output member.
　従来、この種の自動変速機装置としては、３つの遊星歯車機構と、６つの摩擦係合要素とにより前進８速段と後進段とを形成可能なものが提案されている（例えば、特許文献１参照）。この装置では、６つの摩擦係合要素を４つのクラッチＣ１～Ｃ４と２つのブレーキＢ１，Ｂ２とにより構成し、前進１速段ではクラッチＣ１とブレーキＢ１とを係合し、前進２速段ではクラッチＣ３とブレーキＢ１とを係合し、前進３速段ではクラッチＣ２とブレーキＢ１とを係合し、前進４速段ではクラッチＣ２とクラッチＣ３とを係合し、前進５速段ではクラッチＣ１とクラッチＣ２とを係合し、前進６速段ではクラッチＣ２とクラッチＣ４とを係合し、前進７速段ではクラッチＣ１とクラッチＣ４とを係合し、前進８速段ではクラッチＣ３とクラッチＣ４とを係合している。 Conventionally, as this type of automatic transmission device, an apparatus capable of forming an eighth forward speed and a reverse speed by using three planetary gear mechanisms and six friction engagement elements has been proposed (for example, Patent Documents). 1). In this device, six friction engagement elements are constituted by four clutches C1 to C4 and two brakes B1 and B2, and the clutch C1 and the brake B1 are engaged at the first forward speed, and at the second forward speed. The clutch C3 and the brake B1 are engaged, the clutch C2 and the brake B1 are engaged at the third forward speed, the clutch C2 and the clutch C3 are engaged at the fourth forward speed, and the clutch C1 is engaged at the fifth forward speed. And the clutch C2, the clutch C2 and the clutch C4 are engaged at the sixth forward speed, the clutch C1 and the clutch C4 are engaged at the seventh forward speed, and the clutch C3 and the clutch are engaged at the eighth forward speed. C4 is engaged.
特開２０１１－１１７５６６号公報JP 2011-117466 A
　こうした自動変速機装置では、３つの遊星歯車機構と複数のクラッチやブレーキとによって自動変速機を構成する場合、３つの遊星歯車機構の各回転要素の接続や複数のクラッチやブレーキの取り付け方は多数存在し、接続や取り付け方によっては自動変速機装置として機能することができるものと機能することができないものとが存在する。また、クラッチやブレーキを摩擦係合要素として形成する場合、解放時の引き摺りが避けられないため、各変速段において解放するクラッチやブレーキの数ができる限り少ない方が望ましい。さらに、クラッチやブレーキを摩擦係合要素として形成している場合、クラッチやブレーキの係合を保持するためには油圧を保持する必要があり、係合の保持が長いクラッチやブレーキでは油圧の保持のためにエネルギ効率が低下してしまう。 In such an automatic transmission device, when an automatic transmission is configured by three planetary gear mechanisms and a plurality of clutches and brakes, there are many ways to connect the rotating elements of the three planetary gear mechanisms and to attach a plurality of clutches and brakes. There are some that can function as an automatic transmission device and some that cannot function depending on the connection and installation. Further, when clutches and brakes are formed as friction engagement elements, drag at the time of release is unavoidable, so it is desirable that the number of clutches and brakes to be released at each shift stage is as small as possible. Furthermore, when the clutch or brake is formed as a friction engagement element, it is necessary to maintain the hydraulic pressure in order to maintain the engagement of the clutch or the brake. This reduces energy efficiency.
　本発明の自動変速機装置は、３つの遊星歯車機構と５つのクラッチと２つのブレーキとによる新たな自動変速機装置を提案することを主目的とし、その自動変速機装置において引き摺り損失を低減させ、装置の伝達効率を向上させることを更なる目的とする。 The automatic transmission apparatus according to the present invention is mainly intended to propose a new automatic transmission apparatus including three planetary gear mechanisms, five clutches, and two brakes, and reduces drag loss in the automatic transmission apparatus. Another object is to improve the transmission efficiency of the apparatus.
　本発明の自動変速機装置は、上述の主目的を達成するために以下の手段を採った。 The automatic transmission apparatus according to the present invention employs the following means in order to achieve the main object described above.
　本発明の自動変速機装置は、
　入力部材に入力された動力を変速して出力部材に出力する自動変速機装置であって、
　速度線図におけるギヤ比に対応する間隔での並び順に第１回転要素と第２回転要素と第３回転要素とを有する第１の遊星歯車機構と、
　速度線図におけるギヤ比に対応する間隔での並び順に第４回転要素と第５回転要素と第６回転要素とを有する第２の遊星歯車機構と、
　速度線図におけるギヤ比に対応する間隔での並び順に第７回転要素と第８回転要素と第９回転要素とを有する第３の遊星歯車機構と、
　前記第２回転要素と前記第５回転要素とを連結する第１連結要素と、
　前記入力部材と前記第１回転要素とを係合すると共に該係合を解放する第１クラッチと、
　前記第１回転要素と前記第４回転要素とを係合すると共に該係合を解放する第２クラッチと、
　前記第６回転要素と前記第７回転要素とを係合すると共に該係合を解放する第３クラッチと、
　前記第７回転要素と前記第１連結要素とを係合すると共に該係合を解放する第４クラッチと、
　前記第４回転要素と前記第９回転要素とを係合すると共に該係合を解放する第５クラッチと、
　前記第６回転要素を自動変速機装置ケースに固定可能に係合すると共に該係合を解放する第１ブレーキと、
　前記第９回転要素を前記自動変速機装置ケースに固定可能に係合すると共に該係合を解放する第２ブレーキと、
　を備え、
　前記入力部材を前記第８回転要素に接続し、
　前記出力部材を前記第３回転要素に接続してなる、
　ことを特徴とする。 The automatic transmission device of the present invention is
An automatic transmission device that shifts the power input to the input member and outputs it to the output member,
A first planetary gear mechanism having a first rotating element, a second rotating element, and a third rotating element in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram;
A second planetary gear mechanism having a fourth rotating element, a fifth rotating element, and a sixth rotating element in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram;
A third planetary gear mechanism having a seventh rotating element, an eighth rotating element, and a ninth rotating element in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram;
A first connecting element that connects the second rotating element and the fifth rotating element;
A first clutch for engaging and releasing the input member and the first rotating element;
A second clutch that engages the first rotating element and the fourth rotating element and releases the engagement;
A third clutch for engaging and releasing the sixth rotating element and the seventh rotating element;
A fourth clutch for engaging and releasing the seventh rotating element and the first connecting element;
A fifth clutch for engaging and releasing the fourth rotating element and the ninth rotating element;
A first brake for fixedly engaging the sixth rotating element with the automatic transmission device case and releasing the engagement;
A second brake for fixedly engaging the ninth rotating element with the automatic transmission device case and releasing the engagement;
With
Connecting the input member to the eighth rotating element;
Connecting the output member to the third rotating element;
It is characterized by that.
　この本発明の自動変速機装置では、３つの回転要素として速度線図におけるギヤ比に対応する間隔での並び順に第１回転要素と第２回転要素と第３回転要素とを有する第１の遊星歯車機構と、３つの回転要素として速度線図におけるギヤ比に対応する間隔での並び順に第４回転要素と第５回転要素と第６回転要素とを有する第２の遊星歯車機構と、３つの回転要素として速度線図におけるギヤ比に対応する間隔での並び順に第７回転要素と第８回転要素と第９回転要素とを有する第３の遊星歯車機構と、を備え、第２回転要素と第５回転要素とを第１連結要素により連結する。そして、第１クラッチを介して入力部材と第１回転要素とを接続し、第２クラッチを介して第１回転要素と第４回転要素とを接続し、第３クラッチを介して第６回転要素と第７回転要素とを接続し、第４クラッチを介して第７回転要素と第１連結要素とを接続し、第５クラッチを介して第４回転要素と第９回転要素とを接続し、第１ブレーキを第６回転要素に接続し、第２ブレーキを第９回転要素に接続し、入力部材を第８回転要素に接続し、出力部材を第３回転要素に接続する。これにより、３つの遊星歯車機構と５つのクラッチと２つのブレーキとにより機能可能な自動変速機装置を構成することができる。 In the automatic transmission device according to the present invention, the first planetary element having the first rotating element, the second rotating element, and the third rotating element in the arrangement order at intervals corresponding to the gear ratio in the velocity diagram as the three rotating elements. A gear mechanism, a second planetary gear mechanism having three rotation elements, a fourth rotation element, a fifth rotation element, and a sixth rotation element in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram, A third planetary gear mechanism having a seventh rotating element, an eighth rotating element, and a ninth rotating element in order of arrangement at intervals corresponding to the gear ratio in the speed diagram as a rotating element, and the second rotating element The fifth rotating element is connected by the first connecting element. The input member and the first rotating element are connected via the first clutch, the first rotating element and the fourth rotating element are connected via the second clutch, and the sixth rotating element is connected via the third clutch. And the seventh rotating element, the seventh rotating element and the first connecting element are connected via the fourth clutch, the fourth rotating element and the ninth rotating element are connected via the fifth clutch, The first brake is connected to the sixth rotating element, the second brake is connected to the ninth rotating element, the input member is connected to the eighth rotating element, and the output member is connected to the third rotating element. Thus, an automatic transmission device that can function by three planetary gear mechanisms, five clutches, and two brakes can be configured.
　こうした本発明の自動変速機装置において、前進１速段から前進９速段および後進段を以下のように構成することができる。
（１）前進１速段は、第１クラッチと第２クラッチと第４クラッチと第１ブレーキとを係合すると共に第３クラッチと第５クラッチと第２ブレーキとを解放することにより形成する。
（２）前進２速段は、第１クラッチと第４クラッチと第５クラッチと第１ブレーキとを係合すると共に第２クラッチと第３クラッチと第２ブレーキとを解放することにより形成する。
（３）前進３速段は、第１クラッチと第３クラッチと第５クラッチと第１ブレーキとを係合すると共に第２クラッチと第４クラッチと第２ブレーキとを解放することにより形成する。
（４）前進４速段は、第１クラッチと第２クラッチと第３クラッチと第５クラッチとを係合すると共に第４クラッチと第１ブレーキと第２ブレーキとを解放することにより形成する。
（５）前進５速段は、第１クラッチと第３クラッチと第５クラッチと第２ブレーキとを係合すると共に第２クラッチと第４クラッチと第１ブレーキとを解放することにより形成する。
（６）前進６速段は、第２クラッチと第３クラッチと第５クラッチと第２ブレーキとを係合すると共に第１クラッチと第４クラッチと第１ブレーキとを解放することにより形成する。
（７）前進７速段は、第１クラッチと第２クラッチと第３クラッチと第２ブレーキとを係合すると共に第４クラッチと第５クラッチと第１ブレーキとを解放することにより形成する。
（８）前進８速段は、第２クラッチと第３クラッチと第４クラッチと第２ブレーキとを係合すると共に第１クラッチと第５クラッチと第１ブレーキとを解放することにより形成する。
（９）前進９速段は、第１クラッチと第２クラッチと第４クラッチと第２ブレーキとを係合すると共に第３クラッチと第５クラッチと第１ブレーキとを解放することにより形成する。
（１０）後進段は、第１クラッチと第５クラッチと第１ブレーキと第２ブレーキとを係合すると共に第２クラッチと第３クラッチと第４クラッチとを解放することにより形成する。
　こうすれば、各変速段を形成する際に、解放するクラッチやブレーキを３つとすることにより、各変速段を形成する際に解放するクラッチやブレーキが４つ以上となるものに比して、引き摺り損失をより低減させることができる。この結果、装置の伝達効率を向上させることができる。また、前進１速段から前進９速段までの９段の変速段を形成するから、８段以下の変速段を形成するものに比して、運転性能を向上させることができる。 In such an automatic transmission device of the present invention, the first forward speed to the ninth forward speed and the reverse speed can be configured as follows.
(1) The first forward speed is formed by engaging the first clutch, the second clutch, the fourth clutch, and the first brake and releasing the third clutch, the fifth clutch, and the second brake.
(2) The second forward speed is formed by engaging the first clutch, the fourth clutch, the fifth clutch, and the first brake and releasing the second clutch, the third clutch, and the second brake.
(3) The third forward speed is formed by engaging the first clutch, the third clutch, the fifth clutch, and the first brake and releasing the second clutch, the fourth clutch, and the second brake.
(4) The fourth forward speed is formed by engaging the first clutch, the second clutch, the third clutch, and the fifth clutch and releasing the fourth clutch, the first brake, and the second brake.
(5) The fifth forward speed is formed by engaging the first clutch, the third clutch, the fifth clutch, and the second brake and releasing the second clutch, the fourth clutch, and the first brake.
(6) The sixth forward speed is formed by engaging the second clutch, the third clutch, the fifth clutch, and the second brake and releasing the first clutch, the fourth clutch, and the first brake.
(7) The seventh forward speed is formed by engaging the first clutch, the second clutch, the third clutch, and the second brake and releasing the fourth clutch, the fifth clutch, and the first brake.
(8) The eighth forward speed is formed by engaging the second clutch, the third clutch, the fourth clutch, and the second brake and releasing the first clutch, the fifth clutch, and the first brake.
(9) The ninth forward speed is formed by engaging the first clutch, the second clutch, the fourth clutch, and the second brake and releasing the third clutch, the fifth clutch, and the first brake.
(10) The reverse gear is formed by engaging the first clutch, the fifth clutch, the first brake, and the second brake and releasing the second clutch, the third clutch, and the fourth clutch.
In this way, by forming three clutches and brakes to be released when forming each shift stage, compared to those having four or more clutches and brakes to be released when forming each shift stage, Drag loss can be further reduced. As a result, the transmission efficiency of the apparatus can be improved. Further, since nine shift stages from the first forward speed to the ninth forward speed are formed, the driving performance can be improved as compared with the one that forms eight or less speed stages.
　こうした前進１速段から前進９速段および後進段を構成する本発明の自動変速機装置において、前記第１ブレーキはドグブレーキとして構成されてなることを特徴とするものとすることもできる。ドグブレーキは係合時にショックが生じやすく、回転を同期させる同期制御が必要となるが、第１ブレーキは前進１速段から前進３速段まで係合が連続していると共に前進４速段から前進９速段まで解放が連続しているから、係合と解放が頻繁に繰り返されることがなく、同期制御が発生する頻度が少ない。このため、ドグブレーキを採用しても変速フィーリングの悪化は抑制される。一方、ドグブレーキは、係合時に油圧を保持する必要がないため、油圧の保持が必要となる油圧駆動のブレーキに比して、エネルギ損失を抑制することができる。この結果、装置のエネルギ効率を向上させることができる。 In the automatic transmission apparatus according to the present invention that constitutes the first forward speed to the ninth forward speed and the reverse speed, the first brake may be configured as a dog brake. The dog brake is susceptible to shock when engaged and requires synchronous control to synchronize its rotation, but the first brake is engaged continuously from the first forward speed to the third forward speed and moves forward from the fourth forward speed. Since the release continues up to the ninth gear, engagement and release are not repeated frequently, and the frequency of occurrence of synchronous control is low. For this reason, even if the dog brake is employed, the deterioration of the shift feeling is suppressed. On the other hand, since the dog brake does not need to hold the hydraulic pressure when engaged, energy loss can be suppressed as compared with a hydraulically driven brake that requires holding the hydraulic pressure. As a result, the energy efficiency of the apparatus can be improved.
　また、本発明の自動変速機装置において、前記第１の遊星歯車機構と前記第２の遊星歯車機構はサンギヤとリングギヤとキャリアとを前記３つの回転要素とするシングルピニオン式の遊星歯車機構として構成されてなり、前記第３の遊星歯車機構はサンギヤとリングギヤとキャリアとを前記３つの回転要素とするダブルピニオン式の遊星歯車機構として構成されてなり、前記第１回転要素，前記第２回転要素，前記第３回転要素は、サンギヤ，キャリア，リングギヤであり、前記第４回転要素，前記第５回転要素，前記第６回転要素は、サンギヤ，キャリア，リングギヤであり、前記第７回転要素，前記第８回転要素，前記第９回転要素は、サンギヤ，リングギヤ，キャリアである、ことを特徴とするものとすることもできる。 In the automatic transmission device according to the present invention, the first planetary gear mechanism and the second planetary gear mechanism are configured as a single pinion type planetary gear mechanism having a sun gear, a ring gear, and a carrier as the three rotating elements. The third planetary gear mechanism is configured as a double-pinion planetary gear mechanism having a sun gear, a ring gear, and a carrier as the three rotating elements, and the first rotating element and the second rotating element. The third rotating element is a sun gear, a carrier, and a ring gear, and the fourth rotating element, the fifth rotating element, and the sixth rotating element are a sun gear, a carrier, and a ring gear, and the seventh rotating element, The eighth rotating element and the ninth rotating element may be a sun gear, a ring gear, and a carrier.
　さらに、本発明の自動変速機装置において、前記入力部材から前記第１の遊星歯車機構，前記第２の遊星歯車機構，前記第３の遊星歯車機構の順に配置されてなる、ことを特徴とするものとすることもできる。 Furthermore, in the automatic transmission apparatus according to the present invention, the first planetary gear mechanism, the second planetary gear mechanism, and the third planetary gear mechanism are arranged in this order from the input member. It can also be.
本発明の一実施例としての自動変速機装置１の構成の概略を示す構成図である。1 is a configuration diagram showing an outline of a configuration of an automatic transmission device 1 as an embodiment of the present invention. 実施例の自動変速機装置１の作動表である。It is an operation | movement table | surface of the automatic transmission apparatus 1 of an Example. 実施例の自動変速機装置１の速度線図である。It is a speed diagram of automatic transmission device 1 of an example. 変形例の自動変速機装置１０１の構成の概略を示す構成図である。It is a block diagram which shows the outline of a structure of the automatic transmission apparatus 101 of a modification. 変形例の自動変速機装置２０１の構成の概略を示す構成図である。It is a block diagram which shows the outline of a structure of the automatic transmission apparatus 201 of a modification.
　次に、本発明の実施の形態を実施例を用いて説明する。 Next, embodiments of the present invention will be described using examples.
　図１は本発明の一実施例としての自動変速機装置１の構成の概略を示す構成図である。実施例の自動変速機装置１は、２つのシングルピニオン式の遊星歯車機構１０，２０と、１つのダブルピニオン式の遊星歯車機構３０と、５つのクラッチＣ１～Ｃ５と、２つのブレーキＢ１，Ｂ２とを備え、図示しない内燃機関としてのエンジンが横置き（車両の左右方向に）配置されたタイプ（例えば、フロントエンジンフロントドライブ式）の車両に搭載されており、エンジンからの動力を図示しないトルクコンバータなどの発進装置を介して入力軸（インプットシャフト）３から入力すると共に入力した動力を変速して出力ギヤ４に出力する有段変速機構として構成されている。出力ギヤ４に出力された動力は、ギヤ機構５とデファレンシャルギヤ６とを介して左右の駆動輪７ａ，７ｂに出力される。ギヤ機構５は、回転軸が出力ギヤ４の回転軸と平行に配置されたカウンタシャフト５ａと、カウンタシャフト５ａに取り付けられ出力ギヤ４と噛合するカウンタドリブンギヤ５ｂと、同じくカウンタシャフト５ａに取り付けられデファレンシャルギヤ６のリングギヤと噛合するデファレンシャルドライブギヤ５ｃとにより構成されている。なお、図１では、図中の入力軸３の下側については自動変速機装置１の構成のうち出力ギヤ４とギヤ機構５との接続関係を中心に示し、他は省略した。 FIG. 1 is a block diagram showing an outline of the configuration of an automatic transmission device 1 as an embodiment of the present invention. The automatic transmission device 1 according to the embodiment includes two single-pinion planetary gear mechanisms 10 and 20, one double-pinion planetary gear mechanism 30, five clutches C1 to C5, and two brakes B1 and B2. Is mounted on a vehicle (for example, front engine front drive type) in which an engine as an internal combustion engine (not shown) is disposed horizontally (in the left-right direction of the vehicle), and torque from the engine is not shown. It is configured as a stepped transmission mechanism that is input from an input shaft (input shaft) 3 via a starting device such as a converter and that shifts the input power and outputs it to the output gear 4. The power output to the output gear 4 is output to the left and right drive wheels 7a and 7b via the gear mechanism 5 and the differential gear 6. The gear mechanism 5 includes a counter shaft 5a having a rotation shaft arranged parallel to the rotation shaft of the output gear 4, a counter driven gear 5b that is attached to the counter shaft 5a and meshes with the output gear 4, and a differential that is also attached to the counter shaft 5a. The differential drive gear 5c meshes with the ring gear of the gear 6. In FIG. 1, the lower side of the input shaft 3 in the drawing mainly shows the connection relationship between the output gear 4 and the gear mechanism 5 in the configuration of the automatic transmission device 1, and the others are omitted.
　実施例の自動変速機装置１は、図示するように、３つの遊星歯車機構１０，２０，３０が、エンジン側に接続された入力軸３側（図１中右側）から順に第１の遊星歯車機構１０，第２の遊星歯車機構２０，第３の遊星歯車機構３０となるよう配置されている。 As shown in the figure, the automatic transmission device 1 of the embodiment includes three planetary gear mechanisms 10, 20, and 30 in order from the input shaft 3 side (right side in FIG. 1) connected to the engine side in order from the first planetary gear. The mechanism 10, the second planetary gear mechanism 20, and the third planetary gear mechanism 30 are arranged.
　第１の遊星歯車機構１０は、外歯歯車としてのサンギヤ１１と、このサンギヤ１１と同心円上に配置された内歯歯車としてのリングギヤ１３と、サンギヤ１１に噛合すると共にリングギヤ１３に噛合する複数のピニオンギヤ１４と、複数のピニオンギヤ１４を連結して自転かつ公転自在に保持するキャリア１２とを備える。第１の遊星歯車機構１０は、シングルピニオン式の遊星歯車機構として構成されているから、３つの回転要素であるサンギヤ１１，リングギヤ１３，キャリア１２は、速度線図におけるギヤ比に対応する間隔での並び順に示すと、サンギヤ１１，キャリア１２，リングギヤ１３となる。第１の遊星歯車機構１０のギヤ比λ１（サンギヤ１１の歯数／リングギヤ１３の歯数）は、例えば０．２５に設定されている。 The first planetary gear mechanism 10 includes a sun gear 11 as an external gear, a ring gear 13 as an internal gear disposed concentrically with the sun gear 11, and a plurality of gears meshed with the sun gear 11 and meshed with the ring gear 13. A pinion gear 14 and a carrier 12 that couples and holds the plurality of pinion gears 14 so as to rotate and revolve freely. Since the first planetary gear mechanism 10 is configured as a single pinion type planetary gear mechanism, the three rotating elements, the sun gear 11, the ring gear 13, and the carrier 12, are spaced at intervals corresponding to the gear ratio in the velocity diagram. , The sun gear 11, the carrier 12, and the ring gear 13. The gear ratio λ1 of the first planetary gear mechanism 10 (the number of teeth of the sun gear 11 / the number of teeth of the ring gear 13) is set to 0.25, for example.
　第２の遊星歯車機構２０は、外歯歯車としてのサンギヤ２１と、このサンギヤ２１と同心円上に配置された内歯歯車としてのリングギヤ２３と、サンギヤ２１に噛合すると共にリングギヤ２３に噛合する複数のピニオンギヤ２４と、複数のピニオンギヤ２４を連結して自転かつ公転自在に保持するキャリア２２とを備える。第２の遊星歯車機構２０は、シングルピニオン式の遊星歯車機構として構成されているから、３つの回転要素であるサンギヤ２１，リングギヤ２３，キャリア２２は、速度線図におけるギヤ比に対応する間隔での並び順に示すと、サンギヤ２１，キャリア２２，リングギヤ２３となる。第２の遊星歯車機構２０のギヤ比λ２（サンギヤ２１の歯数／リングギヤ２３の歯数）は、例えば０．６５に設定されている。 The second planetary gear mechanism 20 includes a sun gear 21 as an external gear, a ring gear 23 as an internal gear arranged concentrically with the sun gear 21, and a plurality of gears meshed with the sun gear 21 and meshed with the ring gear 23. A pinion gear 24 and a carrier 22 that couples and holds the plurality of pinion gears 24 so as to rotate and revolve freely are provided. Since the second planetary gear mechanism 20 is configured as a single pinion type planetary gear mechanism, the three rotating elements, the sun gear 21, the ring gear 23, and the carrier 22, are spaced at intervals corresponding to the gear ratio in the velocity diagram. , The sun gear 21, the carrier 22, and the ring gear 23. The gear ratio λ2 (number of teeth of the sun gear 21 / number of teeth of the ring gear 23) of the second planetary gear mechanism 20 is set to 0.65, for example.
　第３の遊星歯車機構３０は、外歯歯車としてのサンギヤ３１と、このサンギヤ３１と同心円上に配置された内歯歯車としてのリングギヤ３２と、サンギヤ３１に噛合する複数の第１のピニオンギヤ３４と、第１のピニオンギヤ３４に噛合すると共にリングギヤ３２に噛合する複数の第２のピニオンギヤ３５と、複数の第１のピニオンギヤ３４および複数の第２のピニオンギヤ３５を自転かつ公転自在に保持するキャリア３３とを備える。第３の遊星歯車機構３０は、ダブルピニオン式の遊星歯車機構として構成されているから、３つの回転要素であるサンギヤ３１，リングギヤ３２，キャリア３３は、速度線図におけるギヤ比に対応する間隔での並び順に示すと、サンギヤ３１，リングギヤ３２，キャリア３３となる。第３の遊星歯車機構３０のギヤ比λ３（サンギヤ３１の歯数／リングギヤ３２の歯数）は、例えば０．５０に設定されている。 The third planetary gear mechanism 30 includes a sun gear 31 as an external gear, a ring gear 32 as an internal gear disposed concentrically with the sun gear 31, and a plurality of first pinion gears 34 that mesh with the sun gear 31. A plurality of second pinion gears 35 meshing with the first pinion gear 34 and meshing with the ring gear 32; and a plurality of first pinion gears 34 and a carrier 33 holding the plurality of second pinion gears 35 so as to rotate and revolve. Is provided. Since the third planetary gear mechanism 30 is configured as a double pinion planetary gear mechanism, the three rotating elements, the sun gear 31, the ring gear 32, and the carrier 33, are spaced at intervals corresponding to the gear ratio in the velocity diagram. , The sun gear 31, the ring gear 32, and the carrier 33. The gear ratio λ3 (the number of teeth of the sun gear 31 / the number of teeth of the ring gear 32) of the third planetary gear mechanism 30 is set to 0.50, for example.
　第１の遊星歯車機構１０のキャリア１２は第１連結要素５１により第２の遊星歯車機構２０のキャリア２２に連結されている。 The carrier 12 of the first planetary gear mechanism 10 is connected to the carrier 22 of the second planetary gear mechanism 20 by a first connecting element 51.
　入力軸３は、クラッチＣ１を介して第１の遊星歯車機構１０のサンギヤ１１に接続されている。第１の遊星歯車機構１０のサンギヤ１１は、クラッチＣ２を介して第２の遊星歯車機構２０のサンギヤ２１に接続されている。第２の遊星歯車機構２０のリングギヤ２３は、クラッチＣ３を介して第３の遊星歯車機構３０のサンギヤ３１に接続されている。第３の遊星歯車機構３０のサンギヤ３１は、クラッチＣ４を介して第１連結要素５１に接続されている。第２の遊星歯車機構２０のサンギヤ２１は、クラッチＣ５を介して第３の遊星歯車機構３０のキャリア３３に接続されている。また、第２の遊星歯車機構２０のリングギヤ２３はブレーキＢ１を介してケース（自動変速機装置ケース）２に接続されており、第３の遊星歯車機構３０のキャリア３３はブレーキＢ２を介してケース２に接続されている。そして、第３の遊星歯車機構３０のリングギヤ３２に入力軸３が接続されており、第１の遊星歯車機構１０のリングギヤ１３に出力ギヤ４が接続されている。ここで、５つのクラッチＣ１～Ｃ５と２つのブレーキＢ１，Ｂ２は、実施例では、いずれも摩擦プレートをピストンで押圧することにより係合する油圧駆動の摩擦クラッチや摩擦ブレーキとして構成されている。 The input shaft 3 is connected to the sun gear 11 of the first planetary gear mechanism 10 via the clutch C1. The sun gear 11 of the first planetary gear mechanism 10 is connected to the sun gear 21 of the second planetary gear mechanism 20 via the clutch C2. The ring gear 23 of the second planetary gear mechanism 20 is connected to the sun gear 31 of the third planetary gear mechanism 30 via the clutch C3. The sun gear 31 of the third planetary gear mechanism 30 is connected to the first coupling element 51 via the clutch C4. The sun gear 21 of the second planetary gear mechanism 20 is connected to the carrier 33 of the third planetary gear mechanism 30 via the clutch C5. The ring gear 23 of the second planetary gear mechanism 20 is connected to the case (automatic transmission device case) 2 via the brake B1, and the carrier 33 of the third planetary gear mechanism 30 is connected to the case via the brake B2. 2 is connected. The input shaft 3 is connected to the ring gear 32 of the third planetary gear mechanism 30, and the output gear 4 is connected to the ring gear 13 of the first planetary gear mechanism 10. Here, the five clutches C1 to C5 and the two brakes B1 and B2 are each configured as a hydraulically driven friction clutch or friction brake that is engaged by pressing the friction plate with a piston.
　こうして構成された実施例の自動変速機装置１は、５つのクラッチＣ１～Ｃ５の係合と解放および２つのブレーキＢ１，Ｂ２の係合と解放の組み合わせにより前進１速段～前進９速段と後進段とを切り替えることができる。図２に自動変速機装置１の作動表を示し、図３に自動変速機装置１の第１ないし第３の遊星歯車機構１０，２０，３０の速度線図を示す。図３には、左から順に、第１の遊星歯車機構１０の速度線図，第２の遊星歯車機構２０の速度線図，第３の遊星歯車機構３０の速度線図を示し、第１の遊星歯車機構１０と第２の遊星歯車機構２０の速度線図では左からサンギヤ，キャリア，リングギヤの順に並んでおり、第３の遊星歯車機構３０の速度線図では左からサンギヤ，リングギヤ，キャリアの順に並んでいる。また、図３中、「１ｓｔ」は前進１速段を示し、「２ｎｄ」は前進２速段を示し、「３ｒｄ」は前進３速段を示し、「４ｔｈ」～「９ｔｈ」は前進４速段～前進９速段を示し、「Ｒｅｖ」は後進段を示している。「λ１」～「λ３」は各遊星歯車機構のギヤ比を示し、「Ｂ１」，「Ｂ２」はブレーキＢ１，Ｂ２を示している。「入力」は入力軸３の接続位置を示し、「出力」は出力ギヤ４の接続位置を示している。 The automatic transmission apparatus 1 according to the embodiment thus configured has a first forward speed to a ninth forward speed by a combination of engagement and release of the five clutches C1 to C5 and engagement and release of the two brakes B1 and B2. The reverse gear can be switched. FIG. 2 shows an operation table of the automatic transmission device 1, and FIG. 3 shows a speed diagram of the first to third planetary gear mechanisms 10, 20, 30 of the automatic transmission device 1. FIG. 3 shows a velocity diagram of the first planetary gear mechanism 10, a velocity diagram of the second planetary gear mechanism 20, and a velocity diagram of the third planetary gear mechanism 30 in order from the left. In the speed diagram of the planetary gear mechanism 10 and the second planetary gear mechanism 20, the sun gear, the carrier, and the ring gear are arranged in this order from the left. In the speed diagram of the third planetary gear mechanism 30, the sun gear, the ring gear, and the carrier are arranged from the left. They are in order. In FIG. 3, “1st” represents the first forward speed, “2nd” represents the second forward speed, “3rd” represents the third forward speed, and “4th” to “9th” represents the fourth forward speed. “Rev” indicates the reverse gear. “Λ1” to “λ3” indicate the gear ratio of each planetary gear mechanism, and “B1” and “B2” indicate the brakes B1 and B2. “Input” indicates the connection position of the input shaft 3, and “Output” indicates the connection position of the output gear 4.
　実施例の自動変速機装置１では、図２に示すように、以下のように前進１速段～前進９速段と後進段とを形成する。なお、ギヤ比（入力軸３の回転数／出力ギヤ４の回転数）は、第１ないし第３の遊星歯車機構１０，２０，３０のギヤ比λ１，λ２，λ３として０．２５，０．６５，０．５０を用いた場合を示した。
（１）前進１速段は、クラッチＣ１とクラッチＣ２とクラッチＣ４とブレーキＢ１とを係合すると共にクラッチＣ３とクラッチＣ５とブレーキＢ２とを解放することにより形成することができ、ギヤ比は４．１２５となる。
（２）前進２速段は、クラッチＣ１とクラッチＣ４とクラッチＣ５とブレーキＢ１とを係合すると共にクラッチＣ２とクラッチＣ３とブレーキＢ２とを解放することにより形成することができ、ギヤ比は２．１９０となる。
（３）前進３速段は、クラッチＣ１とクラッチＣ３とクラッチＣ５とブレーキＢ１とを係合すると共にクラッチＣ２とクラッチＣ４とブレーキＢ２とを解放することにより形成することができ、ギヤ比は１．３６１となる。
（４）前進４速段は、クラッチＣ１とクラッチＣ２とクラッチＣ３とクラッチＣ５とを係合すると共にクラッチＣ４とブレーキＢ１とブレーキＢ２とを解放することにより形成することができ、ギヤ比は１．０００となる。
（５）前進５速段は、クラッチＣ１とクラッチＣ３とクラッチＣ５とブレーキＢ２とを係合すると共にクラッチＣ２とクラッチＣ４とブレーキＢ１とを解放することにより形成することができ、ギヤ比は０．７９０となる。
（６）前進６速段は、クラッチＣ２とクラッチＣ３とクラッチＣ５とブレーキＢ２とを係合すると共にクラッチＣ１とクラッチＣ４とブレーキＢ１とを解放することにより形成することができ、ギヤ比は０．６６０となる。
（７）前進７速段は、クラッチＣ１とクラッチＣ２とクラッチＣ３とブレーキＢ２とを係合すると共にクラッチＣ４とクラッチＣ５とブレーキＢ１とを解放することにより形成することができ、ギヤ比は０．５６９となる。
（８）前進８速段は、クラッチＣ２とクラッチＣ３とクラッチＣ４とブレーキＢ２とを係合すると共にクラッチＣ１とクラッチＣ５とブレーキＢ１とを解放することにより形成することができ、ギヤ比は０．５００となる。
（９）前進９速段は、クラッチＣ１とクラッチＣ２とクラッチＣ４とブレーキＢ２とを係合すると共にクラッチＣ３とクラッチＣ５とブレーキＢ１とを解放することにより形成することができ、ギヤ比は０．４４４となる。
（１０）後進段は、クラッチＣ１とクラッチＣ５とブレーキＢ１とブレーキＢ２とを係合すると共にクラッチＣ２とクラッチＣ３とクラッチＣ４とを解放することにより形成することができ、ギヤ比は－４．０００となる。 In the automatic transmission device 1 of the embodiment, as shown in FIG. 2, the first forward speed to the ninth forward speed and the reverse speed are formed as follows. The gear ratio (the number of revolutions of the input shaft 3 / the number of revolutions of the output gear 4) is 0.25, 0,... As the gear ratios λ1, λ2, λ3 of the first to third planetary gear mechanisms 10, 20, 30. The case where 65,0.50 was used was shown.
(1) The first forward speed can be formed by engaging the clutch C1, the clutch C2, the clutch C4, and the brake B1, and releasing the clutch C3, the clutch C5, and the brake B2, and the gear ratio is 4 .125.
(2) The second forward speed can be formed by engaging the clutch C1, the clutch C4, the clutch C5, and the brake B1, and releasing the clutch C2, the clutch C3, and the brake B2, and the gear ratio is 2 .190.
(3) The third forward speed can be formed by engaging the clutch C1, the clutch C3, the clutch C5, and the brake B1, and releasing the clutch C2, the clutch C4, and the brake B2, and the gear ratio is 1 .361.
(4) The fourth forward speed can be formed by engaging the clutch C1, the clutch C2, the clutch C3, and the clutch C5 and releasing the clutch C4, the brake B1, and the brake B2, and the gear ratio is 1. .000.
(5) The fifth forward speed can be established by engaging the clutch C1, the clutch C3, the clutch C5, and the brake B2, and releasing the clutch C2, the clutch C4, and the brake B1, and the gear ratio is 0. 790.
(6) The sixth forward speed can be formed by engaging the clutch C2, the clutch C3, the clutch C5, and the brake B2, and releasing the clutch C1, the clutch C4, and the brake B1, and the gear ratio is 0. .660.
(7) The seventh forward speed can be established by engaging the clutch C1, the clutch C2, the clutch C3, and the brake B2, and releasing the clutch C4, the clutch C5, and the brake B1, and the gear ratio is 0. .569.
(8) The eighth forward speed can be formed by engaging the clutch C2, the clutch C3, the clutch C4, and the brake B2, and releasing the clutch C1, the clutch C5, and the brake B1, and the gear ratio is 0. .500.
(9) The ninth forward speed can be established by engaging the clutch C1, the clutch C2, the clutch C4, and the brake B2, and releasing the clutch C3, the clutch C5, and the brake B1, and the gear ratio is 0. .444.
(10) The reverse gear can be formed by engaging the clutch C1, the clutch C5, the brake B1, and the brake B2 and releasing the clutch C2, the clutch C3, and the clutch C4, and the gear ratio is −4. 000.
　こうして構成された実施例の自動変速機装置１では、第１ないし第３の遊星歯車機構１０，２０，３０のギヤ比λ１，λ２，λ３として０．２５，０．６５，０．５０を用いた場合には、最低速段である前進１速段のギヤ比が４．１２５であり、最高速段である前進９速段のギヤ比が０．４４４であるから、両者のギヤ比幅は９．２９１となる。このように、最低速段をよりローギヤ側に最高速段をよりハイギヤ側に設定することにより、加速性能と燃費性能とを両立させることができる。しかも、実施例の自動変速機装置１は前進１速段から前進９速段までの９段の変速段を有する変速機として構成したから、前進８段以下の変速段を有する変速機に比して、加速性能と燃費性能とを向上させると共に変速時のショックを低減させるなど、運転性能を向上させることができる。 In the automatic transmission device 1 of the embodiment thus configured, 0.25, 0.65, 0.50 are used as the gear ratios λ1, λ2, λ3 of the first to third planetary gear mechanisms 10, 20, 30. In this case, the gear ratio of the first forward speed, which is the lowest speed stage, is 4.125, and the gear ratio of the ninth forward speed, which is the highest speed stage, is 0.444. 9.291. Thus, by setting the lowest speed stage to the lower gear side and the highest speed stage to the higher gear side, both acceleration performance and fuel efficiency performance can be achieved. Moreover, since the automatic transmission device 1 according to the embodiment is configured as a transmission having nine speeds from the first forward speed to the ninth forward speed, it is compared with a transmission having eight or fewer forward speeds. Thus, the driving performance can be improved by improving the acceleration performance and the fuel efficiency and reducing the shock at the time of shifting.
　実施例の自動変速機装置１では、５つのクラッチＣ１～Ｃ５を摩擦クラッチとして構成すると共に２つのブレーキＢ１，Ｂ２を摩擦ブレーキとして構成しているから、解放時の摩擦プレートによる引き摺りは生じるが、上述したように、いずれの変速段においても、解放するクラッチやブレーキの数を３つとしているから、解放するクラッチやブレーキが４つ以上のものに比して、クラッチやブレーキの解放による引き摺り損失の発生を抑制することができる。 In the automatic transmission device 1 according to the embodiment, the five clutches C1 to C5 are configured as friction clutches and the two brakes B1 and B2 are configured as friction brakes. As described above, since the number of clutches and brakes to be released is three at any shift speed, drag loss due to the release of clutches and brakes is greater than that of four or more clutches or brakes to be released. Can be suppressed.
　以上説明した実施例の自動変速機装置１によれば、シングルピニオン式の第１の遊星歯車機構１０と、シングルピニオン式の第２の遊星歯車機構２０と、ダブルピニオン式の第３の遊星歯車機構３０と、５つのクラッチＣ１～Ｃ５と、２つのブレーキＢ１，Ｂ２とを備え、第１の遊星歯車機構１０のキャリア１２を第１連結要素５１により第２の遊星歯車機構２０のキャリア２２に連結し、入力軸３をクラッチＣ１を介して第１の遊星歯車機構１０のサンギヤ１１に接続し、第１の遊星歯車機構１０のサンギヤ１１をクラッチＣ２を介して第２の遊星歯車機構２０のサンギヤ２１に接続し、第２の遊星歯車機構２０のリングギヤ２３をクラッチＣ３を介して第３の遊星歯車機構３０のサンギヤ３１に接続し、第３の遊星歯車機構３０のサンギヤ３１をクラッチＣ４を介して第１連結要素５１に接続し、第２の遊星歯車機構２０のサンギヤ２１をクラッチＣ５を介して第３の遊星歯車機構３０のキャリア３３に接続し、第２の遊星歯車機構２０のリングギヤ２３をブレーキＢ１を介してケース２に接続し、第３の遊星歯車機構３０のキャリア３３をブレーキＢ２を介してケース２に接続し、第３の遊星歯車機構３０のリングギヤ３２に入力軸３を接続し、第１の遊星歯車機構１０のリングギヤ１３に出力ギヤ４を接続することにより、３つの遊星歯車機構１０，２０，３０と５つのクラッチＣ１～Ｃ５と２つのブレーキＢ１，Ｂ２とにより、前進９速段と後進段とに変速可能な自動変速機装置を構成することができる。 According to the automatic transmission device 1 of the embodiment described above, the single-pinion type first planetary gear mechanism 10, the single-pinion type second planetary gear mechanism 20, and the double-pinion-type third planetary gear. A mechanism 30, five clutches C 1 to C 5, and two brakes B 1 and B 2 are provided, and the carrier 12 of the first planetary gear mechanism 10 is transferred to the carrier 22 of the second planetary gear mechanism 20 by the first connecting element 51. The input shaft 3 is connected to the sun gear 11 of the first planetary gear mechanism 10 via the clutch C1, and the sun gear 11 of the first planetary gear mechanism 10 is connected to the sun gear 11 of the second planetary gear mechanism 20 via the clutch C2. Connected to the sun gear 21, the ring gear 23 of the second planetary gear mechanism 20 is connected to the sun gear 31 of the third planetary gear mechanism 30 via the clutch C3, and the sun gear 31 of the third planetary gear mechanism 30 is connected. Is connected to the first coupling element 51 via the clutch C4, and the sun gear 21 of the second planetary gear mechanism 20 is connected to the carrier 33 of the third planetary gear mechanism 30 via the clutch C5. The ring gear 23 of the planetary gear mechanism 20 is connected to the case 2 via the brake B1, the carrier 33 of the third planetary gear mechanism 30 is connected to the case 2 via the brake B2, and the ring gear of the third planetary gear mechanism 30 is connected. By connecting the input shaft 3 to 32 and connecting the output gear 4 to the ring gear 13 of the first planetary gear mechanism 10, three planetary gear mechanisms 10, 20, 30 and five clutches C1 to C5 and two brakes are connected. By B1 and B2, it is possible to configure an automatic transmission device capable of shifting between the ninth forward speed and the reverse speed.
　また、実施例の自動変速機装置１によれば、前進１速段をクラッチＣ１とクラッチＣ２とクラッチＣ４とブレーキＢ１とを係合すると共にクラッチＣ３とクラッチＣ５とブレーキＢ２とを解放することにより形成し、前進２速段をクラッチＣ１とクラッチＣ４とクラッチＣ５とブレーキＢ１とを係合すると共にクラッチＣ２とクラッチＣ３とブレーキＢ２とを解放することにより形成し、前進３速段をクラッチＣ１とクラッチＣ３とクラッチＣ５とブレーキＢ１とを係合すると共にクラッチＣ２とクラッチＣ４とブレーキＢ２とを解放することにより形成し、前進４速段をクラッチＣ１とクラッチＣ２とクラッチＣ３とクラッチＣ５とを係合すると共にクラッチＣ４とブレーキＢ１とブレーキＢ２とを解放することにより形成し、前進５速段をクラッチＣ１とクラッチＣ３とクラッチＣ５とブレーキＢ２とを係合すると共にクラッチＣ２とクラッチＣ４とブレーキＢ１とを解放することにより形成し、前進６速段をクラッチＣ２とクラッチＣ３とクラッチＣ５とブレーキＢ２とを係合すると共にクラッチＣ１とクラッチＣ４とブレーキＢ１とを解放することにより形成し、前進７速段をクラッチＣ１とクラッチＣ２とクラッチＣ３とブレーキＢ２とを係合すると共にクラッチＣ４とクラッチＣ５とブレーキＢ１とを解放することにより形成し、前進８速段をクラッチＣ２とクラッチＣ３とクラッチＣ４とブレーキＢ２とを係合すると共にクラッチＣ１とクラッチＣ５とブレーキＢ１とを解放することにより形成し、前進９速段をクラッチＣ１とクラッチＣ２とクラッチＣ４とブレーキＢ２とを係合すると共にクラッチＣ３とクラッチＣ５とブレーキＢ１とを解放することにより形成し、後進段をクラッチＣ１とクラッチＣ５とブレーキＢ１とブレーキＢ２とを係合すると共にクラッチＣ２とクラッチＣ３とクラッチＣ４とを解放することにより形成することにより、いずれの変速段においても、解放するクラッチやブレーキの数を３つとすることができ、解放するクラッチやブレーキの数が４つ以上のものに比して、解放するクラッチやブレーキの引き摺りに起因する損失を低減することができ、装置全体の伝達効率を向上させることができる。また、前進１速段から前進９速段までの９段の変速段を形成するから、８段以下の変速段を形成するものに比して、運転性能を向上させることができる。 Further, according to the automatic transmission device 1 of the embodiment, the first forward speed is achieved by engaging the clutch C1, the clutch C2, the clutch C4, and the brake B1, and releasing the clutch C3, the clutch C5, and the brake B2. The second forward speed is formed by engaging the clutch C1, the clutch C4, the clutch C5, and the brake B1 and releasing the clutch C2, the clutch C3, and the brake B2, and the third forward speed is defined as the clutch C1. It is formed by engaging the clutch C3, the clutch C5, and the brake B1, and releasing the clutch C2, the clutch C4, and the brake B2. The fourth forward speed is established by engaging the clutch C1, the clutch C2, the clutch C3, and the clutch C5. And is formed by releasing the clutch C4, the brake B1, and the brake B2, and the fifth forward speed Is formed by engaging the clutch C1, the clutch C3, the clutch C5, and the brake B2 and releasing the clutch C2, the clutch C4, and the brake B1, and the sixth forward speed is established by the clutch C2, the clutch C3, the clutch C5, and the brake. B2 is engaged and clutch C1, clutch C4 and brake B1 are disengaged, and the seventh forward speed is engaged with clutch C1, clutch C2, clutch C3 and brake B2, and clutch C4 and clutch B2. Formed by releasing C5 and brake B1, and the eighth forward speed is formed by engaging clutch C2, clutch C3, clutch C4 and brake B2 and releasing clutch C1, clutch C5 and brake B1. The 9th forward speed is shifted between clutch C1, clutch C2, and clutch C4. The clutch B3 is engaged and the clutch C3, the clutch C5, and the brake B1 are released, and the reverse gear is engaged with the clutch C1, the clutch C5, the brake B1, and the brake B2, and the clutch C2 and the clutch C3. And by releasing the clutch C4, the number of clutches and brakes to be released can be reduced to three at any shift stage, and the number of clutches and brakes to be released should be four or more. In comparison, loss due to dragging of the clutch or brake to be released can be reduced, and transmission efficiency of the entire apparatus can be improved. Further, since nine shift stages from the first forward speed to the ninth forward speed are formed, the driving performance can be improved as compared with the one that forms eight or less speed stages.
　実施例の自動変速機装置１では、５つのクラッチＣ１～Ｃ５のすべてを摩擦クラッチとして構成すると共に２つのブレーキＢ１，Ｂ２の双方を摩擦ブレーキとして構成するものとしたが、一部のクラッチやブレーキを摩擦クラッチや摩擦ブレーキに代えてドグクラッチやドグブレーキによって構成するものとしてもよい。例えば、ブレーキＢ１をドグブレーキとして構成した変形例の自動変速機装置１０１を図４に示す。変形例の自動変速機装置１０１の作動表および速度線図は図２および図３と同一である。ドグブレーキは係合時にショックが生じやすく、回転を同期させる同期制御が必要となるが、ブレーキＢ１は前進１速段から前進３速段まで係合が連続していると共に前進４速段から前進９速段まで解放が連続しているから、係合と解放が頻繁に繰り返されることがなく、同期制御が発生する頻度が少ない。このため、ドグブレーキを採用しても変速フィーリングの悪化は抑制される。一方、ドグブレーキは、係合時に油圧を保持する必要がないため、油圧の保持が必要となる油圧駆動のブレーキに比して、エネルギ損失を抑制することができる。この結果、装置のエネルギ効率を向上させることができる。 In the automatic transmission device 1 of the embodiment, all of the five clutches C1 to C5 are configured as friction clutches, and both the two brakes B1 and B2 are configured as friction brakes. May be constituted by a dog clutch or a dog brake instead of a friction clutch or a friction brake. For example, FIG. 4 shows a modified automatic transmission device 101 in which the brake B1 is configured as a dog brake. The operation table and speed diagram of the automatic transmission device 101 of the modification are the same as those in FIGS. The dog brake is easily shocked when engaged, and synchronous control is required to synchronize the rotation. However, the brake B1 is continuously engaged from the first forward speed to the third forward speed, and from the fourth forward speed to the forward 9 speed. Since the release is continued up to the speed stage, the engagement and release are not repeated frequently, and the frequency of occurrence of the synchronous control is low. For this reason, even if the dog brake is employed, the deterioration of the shift feeling is suppressed. On the other hand, since the dog brake does not need to hold the hydraulic pressure when engaged, energy loss can be suppressed as compared with a hydraulically driven brake that requires holding the hydraulic pressure. As a result, the energy efficiency of the apparatus can be improved.
　実施例の自動変速機装置１では、エンジンが横置き（車両の左右方向に）配置されたタイプ（例えば、フロントエンジンフロントドライブ式）の車両に搭載されるものとしたが、エンジンが縦置き（車両の前後方向に）配置されたタイプ（例えば、フロントエンジンリヤドライブ式）の車両に搭載されるものとしてもよい。この場合、図５に例示する変形例の自動変速機装置２０１のように、図１の自動変速機装置１の第１の遊星歯車機構１０，第２の遊星歯車機構２０，第３の遊星歯車機構３０，クラッチＣ１～Ｃ５，ブレーキＢ１，Ｂ２の配置や接続はそのままに、入力軸３を反対側（図１，５中の左側）に延出すると共に、第１の遊星歯車機構１０のリングギヤ１３にその回転を入力軸３とは反対側（図１，５中の右側）の出力軸４ｂに伝達する中空の回転シャフト４ａを接続するものとすればよい。 In the automatic transmission device 1 according to the embodiment, the engine is mounted on a vehicle (for example, a front engine front drive type) in which the engine is disposed horizontally (in the left-right direction of the vehicle). It may be mounted on a vehicle of a type (for example, front engine rear drive type) arranged in the vehicle front-rear direction. In this case, like the automatic transmission device 201 of the modified example illustrated in FIG. 5, the first planetary gear mechanism 10, the second planetary gear mechanism 20, and the third planetary gear of the automatic transmission device 1 of FIG. While the arrangement and connection of the mechanism 30, the clutches C1 to C5 and the brakes B1 and B2 are not changed, the input shaft 3 extends to the opposite side (left side in FIGS. 1 and 5) and the ring gear of the first planetary gear mechanism 10 A hollow rotating shaft 4a for transmitting the rotation to the output shaft 4b on the opposite side (right side in FIGS. 1 and 5) from the input shaft 3 may be connected to 13.
　実施例の自動変速機装置１では、第１ないし第３の遊星歯車機構１０，２０，３０のギヤ比λ１，λ２，λ３として０．２５，０．６５，０．５０を用いたが、ギヤ比λ１，λ２，λ３はこの値に限定されるものではない。 In the automatic transmission device 1 of the embodiment, 0.25, 0.65, 0.50 are used as the gear ratios λ1, λ2, λ3 of the first to third planetary gear mechanisms 10, 20, 30. The ratios λ1, λ2, and λ3 are not limited to these values.
　実施例の自動変速機装置１では、第１の遊星歯車機構１０と第２の遊星歯車機構２０とをシングルピニオン式の遊星歯車機構として構成し、第３の遊星歯車機構３０をダブルピニオン式の遊星歯車機構として構成したが、第１ないし第３の遊星歯車機構１０，２０，３０の全てのシングル式の遊星歯車機構として構成するものとしたり、第１ないし第３の遊星歯車機構１０，２０，３０の全てのダブルピニオン式の遊星歯車機構として構成するものとしたり、第１ないし第３の遊星歯車機構１０，２０，３０のうち一部をシングルピニオン式の遊星歯車として構成すると共に残部をダブルピニオン式の遊星歯車機構として構成するものとしてもよい。 In the automatic transmission device 1 according to the embodiment, the first planetary gear mechanism 10 and the second planetary gear mechanism 20 are configured as a single pinion type planetary gear mechanism, and the third planetary gear mechanism 30 is configured as a double pinion type. Although configured as a planetary gear mechanism, the first to third planetary gear mechanisms 10, 20, 30 may be configured as all single type planetary gear mechanisms, or the first to third planetary gear mechanisms 10, 20. 30, 30 as a double pinion planetary gear mechanism, or a part of the first to third planetary gear mechanisms 10, 20, 30 is configured as a single pinion planetary gear and the remaining portion It may be configured as a double pinion type planetary gear mechanism.
　実施例の自動変速機装置１では、５つのクラッチＣ１～Ｃ５と２つのブレーキＢ１，Ｂ２とのうち４つを係合すると共に他の３つを解放することにより、前進１速段から前進９速段と後進段が可能な自動変速機装置として構成したが、前進１速段から前進９速段の９段のうちのいずれか１つの変速段を除いた８段変速または複数の変速段を除いた７段変速以下の変速と後進段の選択とが可能な自動変速機装置としても構わない。 In the automatic transmission device 1 according to the embodiment, four of the five clutches C1 to C5 and the two brakes B1 and B2 are engaged and the other three are released, thereby moving forward from the first forward speed 9 Although configured as an automatic transmission device capable of high speed and reverse speed, an 8-speed shift or a plurality of shift speeds excluding any one of 9 speeds from the first forward speed to the ninth forward speed The automatic transmission apparatus may be capable of selecting a shift of a reverse speed and a reverse speed that is less than the 7th speed.
　ここで、実施例の主要な要素と発明の概要の欄に記載した発明の主要な要素との対応関係について説明する。実施例では、入力軸（インプットシャフト）３が「入力部材」に相当し、出力ギヤ４が「出力部材」に相当し、第１の遊星歯車機構１０が「第１の遊星歯車機構」に相当し、サンギヤ１１が「第１回転要素」に相当し、キャリア１２が「第２回転要素」に相当し、リングギヤ１３が「第３回転要素」に相当し、第２の遊星歯車機構２０が「第２の遊星歯車機構」に相当し、サンギヤ２１が「第４回転要素」に相当し、キャリア２２が「第５回転要素」に相当し、リングギヤ２３が「第６回転要素」に相当し、第３の遊星歯車機構３０が「第３の遊星歯車機構」に相当し、サンギヤ３１が「第７回転要素」に相当し、リングギヤ３２が「第８回転要素」に相当し、キャリア３３が「第９回転要素」に相当し、第１連結要素５１が「第１連結要素」に相当し、クラッチＣ１が「第１クラッチ」に相当し、クラッチＣ２が「第２クラッチ」に相当し、クラッチＣ３が「第３クラッチ」に相当し、クラッチＣ４が「第４クラッチ」に相当し、クラッチＣ５が「第５クラッチ」に相当し、ブレーキＢ１が「第１ブレーキ」に相当し、ブレーキＢ２が「第２ブレーキ」に相当する。なお、実施例の主要な要素と発明の概要の欄に記載した発明の主要な要素との対応関係は、実施例が発明の概要の欄に記載した発明を実施するための最良の形態を具体的に説明するための一例であることから、発明の概要の欄に記載した発明の要素を限定するものではない。即ち、発明の概要の欄に記載した発明についての解釈はその欄の記載に基づいて行なわれるべきものであり、実施例は発明の概要の欄に記載した発明の具体的な一例に過ぎないものである。 Here, the correspondence between the main elements of the embodiment and the main elements of the invention described in the summary section of the invention will be described. In the embodiment, the input shaft (input shaft) 3 corresponds to an “input member”, the output gear 4 corresponds to an “output member”, and the first planetary gear mechanism 10 corresponds to a “first planetary gear mechanism”. The sun gear 11 corresponds to the “first rotating element”, the carrier 12 corresponds to the “second rotating element”, the ring gear 13 corresponds to the “third rotating element”, and the second planetary gear mechanism 20 corresponds to “ It corresponds to the “second planetary gear mechanism”, the sun gear 21 corresponds to the “fourth rotating element”, the carrier 22 corresponds to the “fifth rotating element”, the ring gear 23 corresponds to the “sixth rotating element”, The third planetary gear mechanism 30 corresponds to a “third planetary gear mechanism”, the sun gear 31 corresponds to a “seventh rotating element”, the ring gear 32 corresponds to an “eighth rotating element”, and the carrier 33 corresponds to “ The first connecting element 51 corresponds to the “ninth rotating element” and the “first connecting element” The clutch C1 corresponds to the “first clutch”, the clutch C2 corresponds to the “second clutch”, the clutch C3 corresponds to the “third clutch”, and the clutch C4 corresponds to the “fourth clutch”. The clutch C5 corresponds to the “fifth clutch”, the brake B1 corresponds to the “first brake”, and the brake B2 corresponds to the “second brake”. It should be noted that the correspondence between the main elements of the embodiment and the main elements of the invention described in the summary of the invention is the best mode for carrying out the invention described in the overview of the embodiment. Therefore, the elements of the invention described in the summary section of the invention are not limited. That is, the interpretation of the invention described in the Summary of Invention column should be made based on the description in that column, and the Examples are only specific examples of the invention described in the Summary of Invention column. It is.
　以上、本発明を実施するための最良の形態について実施例を用いて説明したが、本発明はこうした実施例に何等限定されるものではなく、本発明の要旨を逸脱しない範囲内において、種々なる形態で実施し得ることは勿論である。 The best mode for carrying out the present invention has been described with reference to the embodiments. However, the present invention is not limited to these embodiments, and various modifications can be made without departing from the gist of the present invention. Of course, it can be implemented in the form.
　本発明は、自動変速機装置の製造産業などに利用可能である。 The present invention can be used in the manufacturing industry of automatic transmission devices.

Claims (5)

  1. 　入力部材に入力された動力を変速して出力部材に出力する自動変速機装置であって、
    　速度線図におけるギヤ比に対応する間隔での並び順に第１回転要素と第２回転要素と第３回転要素とを有する第１の遊星歯車機構と、
    　速度線図におけるギヤ比に対応する間隔での並び順に第４回転要素と第５回転要素と第６回転要素とを有する第２の遊星歯車機構と、
    　速度線図におけるギヤ比に対応する間隔での並び順に第７回転要素と第８回転要素と第９回転要素とを有する第３の遊星歯車機構と、
    　前記第２回転要素と前記第５回転要素とを連結する第１連結要素と、
    　前記入力部材と前記第１回転要素とを係合すると共に該係合を解放する第１クラッチと、
    　前記第１回転要素と前記第４回転要素とを係合すると共に該係合を解放する第２クラッチと、
    　前記第６回転要素と前記第７回転要素とを係合すると共に該係合を解放する第３クラッチと、
    　前記第７回転要素と前記第１連結要素とを係合すると共に該係合を解放する第４クラッチと、
    　前記第４回転要素と前記第９回転要素とを係合すると共に該係合を解放する第５クラッチと、
    　前記第６回転要素を自動変速機装置ケースに固定可能に係合すると共に該係合を解放する第１ブレーキと、
    　前記第９回転要素を前記自動変速機装置ケースに固定可能に係合すると共に該係合を解放する第２ブレーキと、
    　を備え、
    　前記入力部材を前記第８回転要素に接続し、
    　前記出力部材を前記第３回転要素に接続してなる、
    　ことを特徴とする自動変速機装置。     An automatic transmission device that shifts the power input to the input member and outputs it to the output member,
    A first planetary gear mechanism having a first rotating element, a second rotating element, and a third rotating element in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram;
    A second planetary gear mechanism having a fourth rotating element, a fifth rotating element, and a sixth rotating element in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram;
    A third planetary gear mechanism having a seventh rotating element, an eighth rotating element, and a ninth rotating element in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram;
    A first connecting element that connects the second rotating element and the fifth rotating element;
    A first clutch for engaging and releasing the input member and the first rotating element;
    A second clutch that engages the first rotating element and the fourth rotating element and releases the engagement;
    A third clutch for engaging and releasing the sixth rotating element and the seventh rotating element;
    A fourth clutch for engaging and releasing the seventh rotating element and the first connecting element;
    A fifth clutch for engaging and releasing the fourth rotating element and the ninth rotating element;
    A first brake for fixedly engaging the sixth rotating element with the automatic transmission device case and releasing the engagement;
    A second brake for fixedly engaging the ninth rotating element with the automatic transmission device case and releasing the engagement;
    With
    Connecting the input member to the eighth rotating element;
    Connecting the output member to the third rotating element;
    An automatic transmission device characterized by that.
  2. 　請求項１記載の自動変速機装置であって、
    　前進１速段は、前記第１クラッチと前記第２クラッチと前記第４クラッチと前記第１ブレーキとを係合すると共に前記第３クラッチと前記第５クラッチと前記第２ブレーキとを解放することにより形成し、
    　前進２速段は、前記第１クラッチと前記第４クラッチと前記第５クラッチと前記第１ブレーキとを係合すると共に前記第２クラッチと前記第３クラッチと前記第２ブレーキとを解放することにより形成し、
    　前進３速段は、前記第１クラッチと前記第３クラッチと前記第５クラッチと前記第１ブレーキとを係合すると共に前記第２クラッチと前記第４クラッチと前記第２ブレーキとを解放することにより形成し、
    　前進４速段は、前記第１クラッチと前記第２クラッチと前記第３クラッチと前記第５クラッチとを係合すると共に前記第４クラッチと前記第１ブレーキと前記第２ブレーキとを解放することにより形成し、
    　前進５速段は、前記第１クラッチと前記第３クラッチと前記第５クラッチと前記第２ブレーキとを係合すると共に前記第２クラッチと前記第４クラッチと前記第１ブレーキとを解放することにより形成し、
    　前進６速段は、前記第２クラッチと前記第３クラッチと前記第５クラッチと前記第２ブレーキとを係合すると共に前記第１クラッチと前記第４クラッチと前記第１ブレーキとを解放することにより形成し、
    　前進７速段は、前記第１クラッチと前記第２クラッチと前記第３クラッチと前記第２ブレーキとを係合すると共に前記第４クラッチと前記第５クラッチと前記第１ブレーキとを解放することにより形成し、
    　前進８速段は、前記第２クラッチと前記第３クラッチと前記第４クラッチと前記第２ブレーキとを係合すると共に前記第１クラッチと前記第５クラッチと前記第１ブレーキとを解放することにより形成し、
    　前進９速段は、前記第１クラッチと前記第２クラッチと前記第４クラッチと前記第２ブレーキとを係合すると共に前記第３クラッチと前記第５クラッチと前記第１ブレーキとを解放することにより形成し、
    　後進段は、前記第１クラッチと前記第５クラッチと前記第１ブレーキと前記第２ブレーキとを係合すると共に前記第２クラッチと前記第３クラッチと前記第４クラッチとを解放することにより形成する、
    　ことを特徴とする自動変速機装置。     The automatic transmission device according to claim 1,
    The first forward speed engages the first clutch, the second clutch, the fourth clutch, and the first brake, and releases the third clutch, the fifth clutch, and the second brake. Formed by
    The second forward speed engages the first clutch, the fourth clutch, the fifth clutch, and the first brake, and releases the second clutch, the third clutch, and the second brake. Formed by
    In the third forward speed, the first clutch, the third clutch, the fifth clutch, and the first brake are engaged, and the second clutch, the fourth clutch, and the second brake are released. Formed by
    In the fourth forward speed, the first clutch, the second clutch, the third clutch, and the fifth clutch are engaged, and the fourth clutch, the first brake, and the second brake are released. Formed by
    In the fifth forward speed, the first clutch, the third clutch, the fifth clutch, and the second brake are engaged, and the second clutch, the fourth clutch, and the first brake are released. Formed by
    The sixth forward speed engages the second clutch, the third clutch, the fifth clutch, and the second brake and releases the first clutch, the fourth clutch, and the first brake. Formed by
    The seventh forward speed engages the first clutch, the second clutch, the third clutch, and the second brake and releases the fourth clutch, the fifth clutch, and the first brake. Formed by
    The eighth forward speed engages the second clutch, the third clutch, the fourth clutch, and the second brake and releases the first clutch, the fifth clutch, and the first brake. Formed by
    The ninth forward speed engages the first clutch, the second clutch, the fourth clutch, and the second brake and releases the third clutch, the fifth clutch, and the first brake. Formed by
    The reverse gear is formed by engaging the first clutch, the fifth clutch, the first brake, and the second brake and releasing the second clutch, the third clutch, and the fourth clutch. To
    An automatic transmission device characterized by that.
  3. 　請求項２記載の自動変速機装置であって、
    　前記第１ブレーキは、ドグブレーキとして構成されてなる、
    　ことを特徴とする自動変速機装置。     The automatic transmission device according to claim 2,
    The first brake is configured as a dog brake,
    An automatic transmission device characterized by that.
  4. 　請求項１ないし３のうちのいずれか１つ請求項に記載の自動変速機装置であって、
    　前記第１の遊星歯車機構と前記第２の遊星歯車機構はサンギヤとリングギヤとキャリアとを前記３つの回転要素とするシングルピニオン式の遊星歯車機構として構成されてなり、
    　前記第３の遊星歯車機構はサンギヤとリングギヤとキャリアとを前記３つの回転要素とするダブルピニオン式の遊星歯車機構として構成されてなり、
    　前記第１回転要素，前記第２回転要素，前記第３回転要素は、サンギヤ，キャリア，リングギヤであり、
    　前記第４回転要素，前記第５回転要素，前記第６回転要素は、サンギヤ，キャリア，リングギヤであり、
    　前記第７回転要素，前記第８回転要素，前記第９回転要素は、サンギヤ，リングギヤ，キャリアである、
    　ことを特徴とする自動変速機装置。     The automatic transmission device according to any one of claims 1 to 3,
    The first planetary gear mechanism and the second planetary gear mechanism are configured as a single pinion planetary gear mechanism having a sun gear, a ring gear, and a carrier as the three rotating elements,
    The third planetary gear mechanism is configured as a double pinion planetary gear mechanism having a sun gear, a ring gear, and a carrier as the three rotating elements,
    The first rotating element, the second rotating element, and the third rotating element are a sun gear, a carrier, and a ring gear,
    The fourth rotating element, the fifth rotating element, and the sixth rotating element are a sun gear, a carrier, and a ring gear,
    The seventh rotating element, the eighth rotating element, and the ninth rotating element are a sun gear, a ring gear, and a carrier.
    An automatic transmission device characterized by that.
  5. 　請求項１ないし４のうちのいずれか１つの請求項に記載の自動変速機装置であって、
    　前記入力部材から前記第１の遊星歯車機構，前記第２の遊星歯車機構，前記第３の遊星歯車機構の順に配置されてなる、
    　ことを特徴とする自動変速機装置。     An automatic transmission device according to any one of claims 1 to 4, wherein
    The first planetary gear mechanism, the second planetary gear mechanism, and the third planetary gear mechanism are arranged in this order from the input member.
    An automatic transmission device characterized by that.
PCT/JP2013/055049 2012-02-29 2013-02-27 Automatic transmission device WO2013129440A1 (en)

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JP2012-044706 2012-02-29
JP2012044706 2012-02-29

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3102050B2 (en) * 1991-03-28 2000-10-23 日産自動車株式会社 Planetary gear train of automatic transmission
JP2011231897A (en) * 2010-04-28 2011-11-17 Honda Motor Co Ltd Automatic transmission
JP2012013209A (en) * 2010-07-05 2012-01-19 Jatco Ltd Automatic transmission

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3102050B2 (en) * 1991-03-28 2000-10-23 日産自動車株式会社 Planetary gear train of automatic transmission
JP2011231897A (en) * 2010-04-28 2011-11-17 Honda Motor Co Ltd Automatic transmission
JP2012013209A (en) * 2010-07-05 2012-01-19 Jatco Ltd Automatic transmission

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