CN104373534A - Multiple-gear transmission with planetary gear structure - Google Patents
Multiple-gear transmission with planetary gear structure Download PDFInfo
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- CN104373534A CN104373534A CN201410418597.1A CN201410418597A CN104373534A CN 104373534 A CN104373534 A CN 104373534A CN 201410418597 A CN201410418597 A CN 201410418597A CN 104373534 A CN104373534 A CN 104373534A
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- planetary gear
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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
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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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
-
- 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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02086—Measures for reducing size of gearbox, e.g. for creating a more compact transmission casing
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
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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
- 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
- F16H2200/0082—Transmissions for multiple ratios characterised by the number of 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
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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
- 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
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
A multiple-gear transmission with a planetary gear structure comprises a housing, an input member, an output member, a first planetary gear set, a second planetary gear set, a third planetary gear set, a first interconnection member, a second interconnection member, a third interconnection member, a fourth interconnection member, a fifth interconnection member, a sixth interconnection member, a seventh interconnection member, a first torque transfer device, a second torque transfer device, a third torque transfer device, a fourth torque transfer device, a fifth torque transfer device and a sixth torque transfer device, wherein the first planetary gear set, the second planetary gear set and the third planetary gear set are sequentially arranged from the input end to the output end, the first torque transfer device, the second torque transfer device, the third torque transfer device, the fourth torque transfer device, the fifth torque transfer device and the sixth torque transfer device include three brakes and three clutches, and the first torque transfer device, the second torque transfer device and the third torque transfer device are located between the second planetary gear set and the third planetary gear set and are parallelly close to the housing. The fourth torque transfer device, the fifth torque transfer device and the sixth torque transfer device are located between the first planetary gear set and the second planetary gear set, the fourth torque transfer device is close to a rotation center, the fifth torque transfer device and the sixth torque transfer device are parallelly located above the fourth torque transfer device, and all the members are located in the housing. The multiple-gear transmission is compact in structure.
Description
Technical field
The present invention relates to a kind of multispeed manual transmission of planetary gear construction, particularly relate to a kind of automatic speed changing being applied to motor vehicle, belong to motor vehicle transmission technical field.
Background technique
Planetary gear construction is because possessing compact structure, carrying large advantage and being widely used in automatic gearbox field.The automatic transmission of planetary gear construction is adopted to need by realizing different forward gears in conjunction with different shifting elements such as break and clutch and reverse gear.
In addition, on May 30th, 2004, in US 6,712,731 B1, disclose a kind of multivariant automatic transmission power-transmission system, there is seven forward gears and a reverse gear shift.Three planetary gear set that the speed changer of this series comprises have six power gear shifting elements, and the anatomical connectivity that two fixing.Contain the motor and fluid torque converter that at least connect a planetary gear set in power system, output block is connected with the parts of another planetary gear set.Wherein six power transfer path provide multiple gear assembly, are fixedly connected with, input shaft, being interconnected between output shaft and case of transmission, the speed ratio of seven forward gears and a reverse gear shift by the connection establishment of three clutches.
On October 15th, 2013, in US 8,556,768 B2, disclose a kind of many gears planetary transmission system formed by four planetary gear set, achieved the change of nine gears by three breaks and three clutches.First group of planetary pinion exports one with the contrary rotating speed of steering input shaft, second group of planetary Main Function exports the reverse speed that passes over from first group of planetary pinion or changeed back forward rotational speed, finally by by the 3rd group and the 4th group of combined planetary gear group formed, achieve nine forward gears one and retreat gear.
Although adopt the automatic transmission of planetary gear construction to there is a large amount of introduction in the prior art at present, consider the factors such as gear number, gear range, efficiency, transmission dimensions and weight, prior art still possesses very large room for improvement.Especially in order to increase the gear number of automatic transmission, the quantity of planetary gear set, clutch and break also increases thereupon, causes the oversize of speed changer, is unfavorable for the layout of speed changer in vehicle transmission system.
Summary of the invention
(1) object
The object of the invention is the multispeed manual transmission being to provide a kind of planetary gear construction, it can overcome the difficult point of prior art, makes up the deficiency of existing market, proposes a kind of compact structure, is convenient to the multi-speed transmission of motor vehicle.
(2) technological scheme
The present invention is a kind of multispeed manual transmission of planetary gear construction, it contains housing, input link, output link, first, second, third planetary gear set, first, second, third and fourth, five, six, seven interconnecting components and first, second, third and fourth, five, six torque transmitters.First, second, third planetary gear set is arranged in order from input end to output terminal; First, second, third and fourth, five, six torque transmitters include three breaks and three clutches, the position annexation between it is: first, second, and third torque transmitter between second and third planet gear train side by side near housing; Four, the 5th and the 6th torque transmitter is between the first and second planetary gear set, and wherein the 4th torque transmitter closes on rotating center, and the 5th, the 6th torque transmitter is positioned at above the 4th torque transmitter side by side.And above-mentioned each parts are all positioned within housing.
Described housing is the shell of planetary transmission, is fixed, and for holding and support other components of speed changer, its shape and structure is determined because of layout, there is not general fixed form.
Described input link is the input shaft of planetary transmission, by this input link, the output speed of motor and torque is input to planetary transmission transmission, only has an input link in this scenario, is positioned at first planet gear train front.
Described output link is the output shaft of planetary transmission, by this output link, the rotating speed of planetary transmission and moment of torsion is exported to follow-up transmission shaft, only has an output link in this scenario, is in third planet gear train rear.
Described first planet gear train is positive sign planetary gear set, be made up of sun gear, gear ring, planet carrier three basic building blocks, sun gear, planet carrier, gear ring is from inside to outside followed successively by, this planet wheel and sun gear outer gearing, another one planet wheel and gear ring internal messing between three.
Described second planetary gear set is negative sign planetary gear set, is made up of, is from inside to outside followed successively by sun gear, planet carrier, gear ring, this planet wheel and sun gear outer gearing, with gear ring internal messing between three sun gear, gear ring, planet carrier three basic building blocks; In like manner, third planet gear train structure composition is identical with this planetary gear set.
Described third planet gear train is negative sign planetary gear set, is made up of, is from inside to outside followed successively by sun gear, planet carrier, gear ring, this planet wheel and sun gear outer gearing, with gear ring internal messing between three sun gear, gear ring, planet carrier three basic building blocks; In like manner, the second planetary gear set structure composition is as identical in this planetary gear set.
Described first interconnecting component is coupling shaft, and the sun gear of first planet gear train is fixedly linked with input link by this interconnecting component.
Described second interconnecting component is coupling shaft, and the gear ring of third planet gear train is fixedly linked with output link by this interconnecting component.
Described 3rd interconnecting component is coupling shaft, and first planet gear set carrier is fixedly linked with the second planetary gear set carrier by this interconnecting component, and is connected with the first torque transmitter.
Described 4th interconnecting component is coupling shaft, and the second planetary gear set sun gear is connected with the second torque transmitter by this interconnecting component.
Described 5th interconnecting component is coupling shaft, and third planet gear set carrier and the 3rd, the 4th is connected with the 5th torque transmitter by this interconnecting component.
Described 6th interconnecting component is coupling shaft, and first planet gear train gear ring and the 5th, the 6th torque transmitter are connected by this interconnecting component.
Described 7th interconnecting component is coupling shaft, and the second planetary gear set gear ring is fixedly linked with third planet gear train tooth sun gear by this interconnecting component, and is connected with the 6th torque transmitter.
Described six torque transmitters, are all wet friction formula binding member, by the joint of different torque transmitter, two corresponding components are linked together, have identical motion state.Six torque transmitters can optionally locking, and by two of correspondence, component is temporary couples together.
This first torque transmitter can optionally locking, first planet gear set carrier and the second planetary gear set carrier and housing is coupled together.
This second torque transmitter can optionally locking, the second planetary gear set sun gear and housing is coupled together.
3rd torque transmitter can optionally locking, third planet gear set carrier and housing is coupled together.
4th torque transmitter can optionally locking, first planet gear train sun gear and third planet gear set carrier is coupled together.
5th torque transmitter can optionally locking, first planet gear train gear ring and third planet gear set carrier is coupled together.
6th torque transmitter can optionally locking, first planet gear train gear ring and third planet gear train sun gear is coupled together.
Wherein, transmission scheme involved in the present invention produce eight forward gears by the joint of control six torque transmitters and one reverse gear, realize speed changing function.
Wherein, above-mentioned three planetary gear set are followed successively by first planet gear train, the second planetary gear set, third planet gear train and output shaft from input end; Gear involved in above-mentioned three groups of planetary gear set is all helical teeth profile of tooth.
Wherein, first, second, third torque transmitter is friction disk type wet brake.
Wherein, the 4th, the 5th, the 6th torque transmitter is friction disk type wet clutch.
Wherein, the size gear ring of break and clutch, needs the torque arithmetic that exports according to mated power input device and obtains, and the present invention does not limit and specifically uses model and specification.
Structure working principle overview of the present invention is as follows: when all torque transmitters are in separated state, and this planetary gear set mechanism freedom is 4, does not have transmission of power between input link and output link; When second, third, the 5th torque transmitter be in blocking time, second planetary gear set sun gear is fixed, third planet gear set carrier is fixed, first planet gear set carrier is identical with third planet gear set carrier rotating speed, the degrees of freedom of planetary gears reduces to 1, pure in transmission of power between input output component, the ratio of input link rotating speed and output link rotating speed is a gear velocity ratio.
When first, second, the 5th torque transmitter be in blocking time, first planet gear train gear ring and the second planetary gear set carrier are fixed, second planetary gear set sun gear is fixed, first planet gear set carrier is identical with third planet gear set carrier rotating speed, the degrees of freedom of planetary gears reduces to 1, pure in transmission of power between input output component, the ratio of input link rotating speed and output link rotating speed is two gear velocity ratios.
When the second, the 5th, the 6th torque transmitter is in blocking, second planetary gear set sun gear is fixed, first planet gear set carrier is identical with third planet gear set carrier rotating speed, first planet gear set carrier is identical with third planet gear train gear ring rotating speed with the second planetary gear set gear ring, the degrees of freedom of planetary gears reduces to 1, pure in transmission of power between input output component, the ratio of input link rotating speed and output link rotating speed is three gear velocity ratios.
When the second, the 4th, the 5th torque transmitter is in blocking, second planetary gear set sun gear is fixed, first planet gear train sun gear is identical with third planet gear set carrier rotating speed, first planet gear set carrier is identical with third planet gear set carrier rotating speed, the degrees of freedom of planetary gears reduces to 1, pure in transmission of power between input output component, the ratio of input link rotating speed and output link rotating speed is four gear velocity ratios.
When the 4th, the 5th, the 6th torque transmitter is in blocking, first planet gear train sun gear is identical with third planet gear set carrier rotating speed, first planet gear set carrier is identical with third planet gear set carrier rotating speed, first planet gear set carrier is identical with third planet gear train gear ring rotating speed with the second planetary gear set gear ring, the degrees of freedom of planetary gears reduces to 1, pure in transmission of power between input output component, the ratio of input link rotating speed and output link rotating speed is five gear velocity ratios.
When the second, the 4th, the 6th torque transmitter is in blocking, second planetary gear set sun gear is fixed, first planet gear set carrier is identical with third planet gear set carrier rotating speed, first planet gear set carrier is identical with third planet gear train gear ring rotating speed with the second planetary gear set gear ring, the degrees of freedom of planetary gears reduces to 1, pure in transmission of power between input output component, the ratio of input link rotating speed and output link rotating speed is six gear velocity ratios.
When the first, the 4th, the 6th torque transmitter is in blocking, first planet gear train gear ring and the second planetary gear set carrier are fixed, first planet gear set carrier is identical with third planet gear set carrier rotating speed, first planet gear set carrier is identical with third planet gear train gear ring rotating speed with the second planetary gear set gear ring, the degrees of freedom of planetary gears reduces to 1, pure in transmission of power between input output component, the ratio of input link rotating speed and output link rotating speed is seven gear velocity ratios.
When first, second, the 4th torque transmitter be in blocking time, first planet gear train gear ring and the second planetary gear set carrier are fixed, second planetary gear set sun gear is fixed, first planet gear set carrier is identical with third planet gear set carrier rotating speed, the degrees of freedom of planetary gears reduces to 1, pure in transmission of power between input output component, the ratio of input link rotating speed and output link rotating speed is eight gear velocity ratios.
When second, third, the 6th torque transmitter be in blocking time, second planetary gear set sun gear is fixed, third planet gear set carrier is fixed, first planet gear set carrier is identical with third planet gear train gear ring rotating speed with the second planetary gear set gear ring, the degrees of freedom of planetary gears reduces to 1, pure in transmission of power between input output component, the ratio of input link rotating speed and output link rotating speed is back gear ratio.
(3) advantage
Follow the velocity ratio that gearshift logical order locking simultaneously three torque transmitters can obtain corresponding gear, described power system can realize altogether eight forward gear velocity ratios and a reverse gear ratio, and the simple gearshift that the gearshift between adjacent gear all meets an only conversion torque transmitter requires to realize smooth shift.
This multispeed manual transmission can obtain nine forward gear velocity ratios, after the gear number increase of power train, increases the probability of engine operation under efficient routine, is conducive to improving fuel consumption rate; More gear also reduces the saltus step of the velocity ratio between adjacent gear, is conducive to reducing shift shock and improving riding comfort.
In addition, the basic building block of the planetary gear set of this multispeed manual transmission and torque transmitter possess lower rotating speed and torque, are conducive to reducing the wearing and tearing between mesh component, reduce the design size of component and device thus lower manufacture cost further.
Accompanying drawing explanation
Fig. 1 is the embodiment structural representation according to nine shift transmissions of the present invention;
Reference character
0 housing
1 first interconnecting component
2 second interconnecting components
3 the 3rd interconnecting components
4 the 4th interconnecting components
5 the 5th interconnecting components
6 the 6th interconnecting components
7 the 7th interconnecting components
03 first torque transmitter
04 second torque transmitter
05 the 3rd torque transmitter
15 the 4th torque transmitters
56 the 5th torque transmitters
67 the 6th torque transmitters
IN input shaft
OUT output shaft
P1 first planet gear train
P2 second planetary gear set
P3 third planet gear train
S1 first planet gear train sun gear
S2 second planetary gear set sun gear
S3 third planet gear train sun gear
A1 first planet gear set carrier
A2 second planetary gear set carrier
A3 third planet gear set carrier
G1 first planet gear train the first row star-wheel
G10 first planet gear train second planet wheel
The planet wheel that G2 second planetary gear set engages with sun gear
G3 third planet gear train planet wheel
R1 first planet gear train gear ring
R2 second planetary gear set gear ring
R3 third planet gear train gear ring
Embodiment
Following illustrative in nature be only exemplary and be not intended to limit absolutely of the present invention, application or use.
The multispeed manual transmission of a kind of planetary gear construction of the present invention, it comprises housing; Input link; Output link; First, second, third planetary gear set; First interconnecting component; Second interconnecting component; 3rd interconnecting component; 4th interconnecting component; 5th interconnecting component; 6th interconnecting component; 7th interconnecting component and first, second, third and fourth, five, six totally six torque transmitters compositions, the position annexation between them is: first, second, third planetary gear set is arranged in order from input end to output terminal; Six torque transmitters include three breaks, three clutches, and the first and second torque transmitters are arranged side by side near housing between second and third planet gear train; 3rd torque transmitter be positioned on the right side of third planet gear train with output link homonymy; Four, the 5th and the 6th torque transmitter is between the first and second planetary gear set, and wherein the 4th torque transmitter closes on rotating center, and the 5th, the 6th torque transmitter is positioned at above the 4th torque transmitter side by side.Above-mentioned all parts is all positioned at housing.
First, the mode of execution of multi-speed automatic transmission of the present invention has the setting of permanent mechanical connection between the element of three planetary gear set.Such as, between the gear ring of first planet gear train and the planet carrier of the second planetary gear set for being fixedly connected with; For being fixedly connected with between the gear ring of the second planetary gear set and the sun gear of third planet gear train.。。
With reference to figure 1, this speed changer scheme comprises input link IN, first planet gear train P1, the second planetary gear set P2, third planet gear train P3, housing 0, output link OUT, the first torque transmitter 03, second torque transmitter 04, the 3rd torque transmitter 05, the 4th torque transmitter 15, the 5th torque transmitter 56 and the 6th torque transmitter 67.In embodiments of the present invention, three planetary gear set P1, P2, P3 are simple planetary groups, as described below.
First planet gear train P1 includes first planet gear train sun gear S1, first planet gear set carrier A1, first planet gear train gear ring R1 and first planet gear train planet wheel G1 and G10 (only indicating a group in this group planet wheel).First planet gear train sun gear S1 is fixedly connected with input link IN by the first interconnecting component 1; First planet gear train gear ring R1 is fixedly connected with the 6th interconnecting component 6; First planet gear set carrier A1 is fixedly connected with the second planetary gear set P2 planet carrier A2 by the 3rd interconnecting component 3.
Second planetary gear set P2, include the second planetary gear set sun gear S2, second planetary gear set carrier A2, the second planetary gear set R2, the second planetary gear set gear ring R2 and the second planetary gear set planet wheel G2 (only indicating a group in each group of planet wheel).Second planetary gear set P2 sun gear S2 is fixedly connected with the 4th interconnecting component 4; Second planetary gear set P2 planet carrier A2 is fixedly linked with first planet gear train P1 planet carrier A1 by the 3rd interconnecting component 3; Second planetary gear set P2 gear ring R2 is fixedly linked with third planet gear train P3 sun gear S3 by the 7th interconnecting component 7.
Third planet gear train P3 includes third planet gear train sun gear S3, third planet gear set carrier A3 and third planet gear train planet wheel G3 (only indicating in this group planet wheel).Third planet gear train P3 gear ring R3 is fixedly linked with output link OUT by the second interconnecting component 2; Third planet gear train P3 planet carrier A3 is connected with the 5th interconnecting component 5; Third planet gear train P3 sun gear S3 is fixedly linked by the 7th interconnecting component 7 and the second planetary gear set P2 gear ring R2.
What input shaft IN was continued by fluid torque converter (not shown) is connected to motor (not shown).What output shaft OUT continued is connected to final gear unit or transfer case (not shown).
The contiguous fluid torque converter (not shown) of first planet gear train P1, the contiguous second planetary gear set P2 of the second planetary gear set P2 contiguous first planet gear train P1, third planet gear train P3.
Shift gears logic diagram and each gear velocity ratio so that the gear shift operation of this mode of execution to be described with reference to rear list one.Moment of torsion can be delivered to output shaft OUT from input shaft IN with reverse gear speed ratio or torque ratio of eight forward gear velocity ratios or torque ratio and by this speed changer.By three joints in torque-transmitting mechanisms (shifting element), each forward gear and the velocity ratio reversed gear or torque ratio can be obtained.Table one shows the various combination truth tables of the torque-transmitting mechanisms being activated or engaging to realize various shifting state.As shown in table one, it is engaged to realize expecting shifting state that "×" represents this concrete torque transmitter (shifting element).When the fixed drive ratio of first planet gear train P1, the second planetary gear set P2, third planet gear train P3 is respectively 4.0000 ,-2.0000, when-2.2663, try to achieve the gear ratio value of each gear of speed changer shown in table one.Such as, by engaging the second torque transmitter 04, the 3rd torque transmitter 05, the 6th torque transmitter 67 can realize transmission reverse gear function.Similar, the various combination engaged by shifting element, realizes nine forward gear ratios, as shown in table one.
To the operation of six shift transmissions and the aforementioned explanation hypothesis of shifting state: first, be that all shifting elements specifically mentioned all depart from given shifting state; Secondly, gearshift (namely the changing shifting state) period between adjacent shifting state, the shifting element all engaged under two shifting state will keep jointing state.
Of the present inventionly say that face is only exemplary in essence, and do not depart from the distortion that the present invention makes it and be intended to comprise within the scope of the invention.This modification is considered to without departing from the spirit and scope of the present invention.
Transmission scheme gear ratio calculation method is as follows:
The kinematical equation group of 1 planetary gears is as follows:
2 calculate each axle rotating speed, and kinology formula can regard M × N=A as, and computational methods are as follows:
N＝(M
T×M)
-1×M
T×A
In formula, symbol description is as follows:
N is for solving vector
M matrix of the coefficients
A constant term
N1 the 3rd interconnecting component rotating speed
N2 the 4th interconnecting component rotating speed
N3 the 5th interconnecting component rotating speed
N4 the 6th interconnecting component rotating speed
N5 the 7th interconnecting component rotating speed
N6 first interconnecting component rotating speed
N7 second interconnecting component rotating speed
I1 first planet gear train fixed drive ratio
I2 second planetary gear set fixed drive ratio
I3 third planet gear train fixed drive ratio
A first torque transmitter joint efficiency
B second torque transmitter joint efficiency
C the 3rd torque transmitter joint efficiency
D the 4th torque transmitter joint efficiency
E the 5th torque transmitter joint efficiency
F the 6th torque transmitter joint efficiency
3 gear ratio calculations:
Symbol description in formula:
I velocity ratio
N1 the 3rd interconnecting component rotating speed
N2 the 4th interconnecting component rotating speed
Wherein, be 1 for the ease of calculating another input shaft IN rotating speed, other axle rotating speeds change with input speed change.By above-mentioned three formula, by closing the assignment (joint is 1, is broken as 0) of coefficient (a, b, c, d, e, f) to torque transmitter, each axle rotating speed and the gear velocity ratio of different gear can be calculated.
The gearshift logic matrix of table 1 scheme 1
"×" represents this concrete torque transmitter (shifting element) and is engaged.
Claims (5)
1. the multispeed manual transmission of a planetary gear construction, it is characterized in that: it contains housing, input link, output link, first, second, third planetary gear set, first, second, third and fourth, five, six, seven interconnecting components and first, second, third and fourth, five, six torque transmitters; First, second, third planetary gear set is arranged in order from input end to output terminal; First, second, third and fourth, five, six torque transmitters include three breaks and three clutches, first, second, and third torque transmitter between second and third planet gear train side by side near housing; Four, the 5th and the 6th torque transmitter is between the first and second planetary gear set, wherein the 4th torque transmitter closes on rotating center, five, the 6th torque transmitter is positioned at above the 4th torque transmitter side by side, and above-mentioned each parts are all positioned within housing;
Described housing is the shell of planetary transmission, is fixed, and for holding and support other components of speed changer, its shape and structure is determined because of layout;
Described input link is the input shaft of planetary transmission, by this input link, the output speed of motor and torque is input to planetary transmission transmission, only has an input link in this scenario, is positioned at first planet gear train front;
Described output link is the output shaft of planetary transmission, by this output link, the rotating speed of planetary transmission and moment of torsion is exported to follow-up transmission shaft, only has an output link in this scenario, is in third planet gear train rear;
Described first planet gear train is positive sign planetary gear set, be made up of sun gear, gear ring, planet carrier three basic building blocks, sun gear, planet carrier, gear ring is from inside to outside followed successively by, this planet wheel and sun gear outer gearing, another one planet wheel and gear ring internal messing between three;
Described second planetary gear set is negative sign planetary gear set, is made up of, is from inside to outside followed successively by sun gear, planet carrier, gear ring, this planet wheel and sun gear outer gearing, with gear ring internal messing between three sun gear, gear ring, planet carrier three basic building blocks;
Described third planet gear train is negative sign planetary gear set, is made up of, is from inside to outside followed successively by sun gear, planet carrier, gear ring, this planet wheel and sun gear outer gearing, with gear ring internal messing between three sun gear, gear ring, planet carrier three basic building blocks;
Described first interconnecting component is coupling shaft, and the sun gear of first planet gear train is fixedly linked with input link by this interconnecting component;
Described second interconnecting component is coupling shaft, and the gear ring of third planet gear train is fixedly linked with output link by this interconnecting component;
Described 3rd interconnecting component is coupling shaft, and first planet gear set carrier is fixedly linked with the second planetary gear set carrier by this interconnecting component, and is connected with the first torque transmitter;
Described 4th interconnecting component is coupling shaft, and the second planetary gear set sun gear is connected with the second torque transmitter by this interconnecting component;
Described 5th interconnecting component is coupling shaft, and third planet gear set carrier and the 3rd, the 4th is connected with the 5th torque transmitter by this interconnecting component;
Described 6th interconnecting component is coupling shaft, and first planet gear train gear ring and the 5th, the 6th torque transmitter are connected by this interconnecting component;
Described 7th interconnecting component is coupling shaft, and the second planetary gear set gear ring is fixedly linked with third planet gear train tooth sun gear by this interconnecting component, and is connected with the 6th torque transmitter;
Described six torque transmitters, are all wet friction formula binding member, by the joint of different torque transmitter, two corresponding components are linked together, have identical motion state; Six torque transmitters can optionally locking, and by two of correspondence, component is temporary couples together;
This first torque transmitter can optionally locking, first planet gear set carrier and the second planetary gear set carrier and housing is coupled together;
This second torque transmitter can optionally locking, the second planetary gear set sun gear and housing is coupled together;
3rd torque transmitter can optionally locking, third planet gear set carrier and housing is coupled together;
4th torque transmitter can optionally locking, first planet gear train sun gear and third planet gear set carrier is coupled together;
5th torque transmitter can optionally locking, first planet gear train gear ring and third planet gear set carrier is coupled together;
6th torque transmitter can optionally locking, first planet gear train gear ring and third planet gear train sun gear is coupled together.
2. the multispeed manual transmission of a kind of planetary gear construction according to claim 1, is characterized in that: involved transmission scheme produce eight forward gears by the joint of control six torque transmitters and one reverse gear, realize speed changing function.
3. the multispeed manual transmission of a kind of planetary gear construction according to claim 1, is characterized in that: three planetary gear set are followed successively by first planet gear train from input end, the second planetary gear set, third planet gear train and output shaft; Gear involved in above-mentioned three groups of planetary gear set is all helical teeth profile of tooth.
4. the multispeed manual transmission of a kind of planetary gear construction according to claim 1, it is characterized in that: first, second, third torque transmitter is friction disk type wet brake, the 4th, the 5th, the 6th torque transmitter is friction disk type wet clutch.
5. the multispeed manual transmission of a kind of planetary gear construction according to claim 1, it is characterized in that: the size gear ring of break and clutch, need the torque arithmetic that exports according to mated power input device and obtain, not limiting concrete use model and specification.
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| CN201410418597.1A CN104373534B (en) | 2014-08-22 | 2014-08-22 | A kind of multi-shifting speed variator of planetary gear construction |
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| CN201410418597.1A CN104373534B (en) | 2014-08-22 | 2014-08-22 | A kind of multi-shifting speed variator of planetary gear construction |
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| CN104373534B CN104373534B (en) | 2018-06-05 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116379112A (en) * | 2023-06-05 | 2023-07-04 | 北京航空航天大学 | Multi-gear planetary gear speed change mechanism and automatic speed changer thereof |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5884248A (en) * | 1981-11-11 | 1983-05-20 | Toyota Motor Corp | Driving equipment for automobile |
| JPS63145848A (en) * | 1986-12-09 | 1988-06-17 | Aisin Warner Ltd | Automatic transmission mechanism |
| EP0757189A2 (en) * | 1995-07-31 | 1997-02-05 | Aisin Aw Co., Ltd. | Automatic transmission |
| CN1531634A (en) * | 2001-03-30 | 2004-09-22 | 腓特烈斯港齿轮工厂股份公司 | Multi-stage transmission |
| DE102006001760A1 (en) * | 2006-01-13 | 2007-08-09 | Zf Friedrichshafen Ag | Multistep gear for use in motor vehicle automatic transmission, has planetary sets arranged in axial direction, brake coupled at housing, and output shaft connected with internal gear of one planatery set |
| CN101021247A (en) * | 2006-02-14 | 2007-08-22 | Zf腓德烈斯哈芬股份公司 | Multi-gear transmission |
| CN101021257A (en) * | 2006-02-14 | 2007-08-22 | Zf腓德烈斯哈芬股份公司 | Multi-gear transmission |
-
2014
- 2014-08-22 CN CN201410418597.1A patent/CN104373534B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5884248A (en) * | 1981-11-11 | 1983-05-20 | Toyota Motor Corp | Driving equipment for automobile |
| JPS63145848A (en) * | 1986-12-09 | 1988-06-17 | Aisin Warner Ltd | Automatic transmission mechanism |
| EP0757189A2 (en) * | 1995-07-31 | 1997-02-05 | Aisin Aw Co., Ltd. | Automatic transmission |
| CN1531634A (en) * | 2001-03-30 | 2004-09-22 | 腓特烈斯港齿轮工厂股份公司 | Multi-stage transmission |
| DE102006001760A1 (en) * | 2006-01-13 | 2007-08-09 | Zf Friedrichshafen Ag | Multistep gear for use in motor vehicle automatic transmission, has planetary sets arranged in axial direction, brake coupled at housing, and output shaft connected with internal gear of one planatery set |
| CN101021247A (en) * | 2006-02-14 | 2007-08-22 | Zf腓德烈斯哈芬股份公司 | Multi-gear transmission |
| CN101021257A (en) * | 2006-02-14 | 2007-08-22 | Zf腓德烈斯哈芬股份公司 | Multi-gear transmission |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116379112A (en) * | 2023-06-05 | 2023-07-04 | 北京航空航天大学 | Multi-gear planetary gear speed change mechanism and automatic speed changer thereof |
| CN116379112B (en) * | 2023-06-05 | 2023-07-28 | 北京航空航天大学 | Multi-gear planetary gear speed change mechanism and automatic speed changer thereof |
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| Publication number | Publication date |
|---|---|
| CN104373534B (en) | 2018-06-05 |
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