CN109764095A - Nine speed transmission - Google Patents
Nine speed transmission Download PDFInfo
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- CN109764095A CN109764095A CN201910138581.8A CN201910138581A CN109764095A CN 109764095 A CN109764095 A CN 109764095A CN 201910138581 A CN201910138581 A CN 201910138581A CN 109764095 A CN109764095 A CN 109764095A
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Abstract
The invention discloses a kind of nine speed transmissions, gearbox case and the input shaft being installed on inside gearbox case, output shaft, epicyclic gear train group, coupling member group and torque transmitter, each planet row include the planetary gear of gear ring, sun gear, planet carrier and its support.The torque transmitter includes two clutches and four brakes, two clutches and four brakes are selectively engaged, make some rotation in sun gear, planet carrier, gear ring or four coupling members or fixes, and wherein torque transmitter can be selectively engaged in combination of at least two, nine forward speed ratios and a reverse speed ratio are set up between the input shaft and the output shaft, and nine forward speed ratios include five deceleration gears, a direct gear and three overgears；Speed changer structure of the present invention is compact, light-weight, small in size, easily arranges on automobile, and the speed ratio step between the transmission ratio of the various gears of speed changer meets the requirement of speed changer.
Description
Technical field
The present invention relates to system of vehicle transmission technical field more particularly to a kind of nine speed transmissions.
Background technique
Typical multi-speed transmission is realized more using the combination of friction clutch, epicyclic gearing and fixed interconnection
A transmission ratio.Quantity and the physics setting of planetary gear set are usually provided by encapsulation, cost and expected speed ratio.Although current
Speed changer realizes its expected purpose, but universal with automobile, and people need reality to what new-type and improved speed changer configured
It is continual in matter.
The improvement of the speed changer configuration is mainly set about in terms of following two, first is that performance, specifically includes the model of transmission ratio
It encloses, the angle of responsiveness and flatness；Second is that packaging, the mainly size and weight of reduction are realized and are fixed when gear determines
The quantity of component needed for gear accordingly determines, therefore the performance of speed changer is mainly improved to the improvement of speed changer, in speed change
In the case that device composition component remains unchanged substantially, how to pass through the connection relationship for improving each inter-module, it can to increase speed changer
The gear number and transmission ratio parameter of realization, become the difficult point and core of transmissions improved.Chinese invention application " nine gear automatic speed changings
Device " (application number: CN201510519055.8) and Chinese invention application " nine speed automatic transmissions " (application number:
CN201210002826.2 one kind) is disclosed by four planetary gear trains, six torque transmitters and five coupling member structures
At nine speed transmission, above-mentioned two speed changer realizes nine forward speed ratios and a reverse speed ratio, but there are speed ratio compared with
Problem small, volume is larger.
Summary of the invention
In view of the above technical problems, the purpose of the present invention is to provide a kind of nine speed transmissions, can reduce speed changer
Volume reduces the difficulty of control and expands the ratio coverage of speed changer.
To achieve the above object, the present invention is realized according to following technical scheme:
A kind of nine speed transmission, comprising: gearbox case and the input shaft being installed on inside gearbox case, output
Axis, epicyclic gear train group, coupling member group and torque transmitter, the epicyclic gear train group include installed from front to back
One epicyclic gear train, the second epicyclic gear train, third planet gear row and fourth planet gears, each epicyclic gear train by
Sun gear, planet carrier, planetary gear and gear ring are constituted, and the torque transmitter includes first clutch, second clutch, first
Brake, second brake, third brake and the 4th brake, the first brake, second brake, third brake and
Four brakes are in turn secured to from front to back on the shell of gearbox case, it is characterised in that:
The first planetary gear row, the second epicyclic gear train and third planet gear row are single planetary bevel gear gear rows, the
Four epicyclic gear trains are dual planetary gear gear rows, and third planet gear row and fourth planet gears constitute Ravigneaux planet
Gear mechanism, third planet gear row and fourth planet gears share gear ring；
The coupling member group includes first coupling member, second coupling member, third coupling member and the 4th connection structure
Part, the sun gear of planet carrier and the second epicyclic gear train that wherein first coupling member connection first planetary gear is arranged, second
Connection member connects the gear ring of first planetary gear row and the gear ring of the second epicyclic gear train, and third coupling member connects the second planet
The shared gear ring of the planet carrier and third planet gear row and fourth planet gears of gear row, the 4th coupling member connect third
The planet carrier of epicyclic gear train and the planet carrier of fourth planet gears；
First brake selectively interconnects first coupling member with case of transmission, and second brake is by second
Coupling member is selectively interconnected with case of transmission, third brake by third coupling member and case of transmission selectively
Interconnection, the 4th brake selectively interconnect the sun gear of fourth planet gears with case of transmission；
The input shaft and the sun gear of first planetary gear row are connected, and the output shaft is connect with the 4th coupling member,
The input shaft is selectively connectable with by first clutch and the sun gear of third planet gear row, and passes through the second clutch
Device and the sun gear of fourth planet gears are selectively connectable with.
Compared with the prior art, the invention has the following advantages:
1, nine speed transmission of the invention uses Gear Planet Transmission, and third planet gear row and fourth planet gears are constituted
Ravigneaux planetary gear mechanism, gear concentrates on centre, and its power can be driven by several planetary gears, gear
Modulus it is small, compact-sized, lighter in weight is easily arranged on automobile；
2, The present invention reduces the number of torque-transfer members, nine speed transmission transmits structure only with six torques
Part largely reduces the volume of speed changer；
3, the control of each gear of the present invention only needs two combined members (clutch or brake), and control is simple；
4, speed changer of the invention is linked together the component of different gear rows using coupling member, can form new change
Su Qi mechanism, the quantity of coupling member and the difference of position will lead to the difference of the transmission mechanism to be formed substantially.The speed change
Device utilizes four coupling members, and connecting mode is verified feasible, and the characterisitic parameter by preferably obtaining makes the speed changer
Gear range is wider, and the total slewing range of various gears is up to 10.12, than the slewing range 7.37 of classical ZF8 speed transmission
It is wider with the slewing range 6.71 of Lexus LS460 speed changer；
5, the speed ratio step of three overgears of the invention is smaller, and respectively 1.18 and 1.22, it can steadily be driven, improve
The power performance of automobile.
Detailed description of the invention
In order to more clearly explain the embodiment of the invention or the technical proposal in the existing technology, to embodiment or will show below
There is attached drawing needed in technical description to be briefly described, it should be apparent that, the accompanying drawings in the following description is only this
Some embodiments of invention for those of ordinary skill in the art without creative efforts, can be with
Other attached drawings are obtained according to these attached drawings.
Fig. 1 is the structural schematic diagram of nine speed transmission provided by the invention；
Wherein, 1- input shaft, 2- first planetary gear rank star-wheel, 3- the second epicyclic gear train planetary gear, 4-
Ravigneaux planetary gear mechanism major planet wheel, 5-Ravigneaux planetary gear mechanism asteroid wheel, 6- first couple structure
Part, 7- second coupling member, 8- third coupling member, the 4th coupling member of 9-, 10- gearbox case, 11- output shaft, R1-
One epicyclic gear train gear ring, PC1- first planetary gear rank carrier, and S1- first planetary gear arranges sun gear, the second planet of R2-
Gear row gear ring, PC2- the second epicyclic gear train planet carrier, S2- the second epicyclic gear train sun gear, R3R4- third planet gear
The gear ring that row and fourth planet gears share, PC3- third planet gear row planet carrier, the S3- third planet gear row sun
Wheel, PC4- fourth planet gears row planets carrier, S4- fourth planet gears sun gear, C1- first clutch, the second clutch of C2-
Device, the first brake of B1-, B2- second brake, B3- third brake, the 4th brake of B4-.
Specific embodiment
In order to make the object, technical scheme and advantages of the embodiment of the invention clearer, below in conjunction with the embodiment of the present invention
In attached drawing, technical scheme in the embodiment of the invention is clearly and completely described, it is clear that described embodiment is
A part of the embodiment of the present invention, instead of all the embodiments.
Nine speed transmission provided by the invention, structure is as shown in Figure 1, including gearbox case 10 and being installed on speed change
Input shaft 1, output shaft 11, epicyclic gear train group, coupling member group and the torque transmitter of device interior of shell, the planet tooth
Schedule group includes the first planetary gear row successively installed from front to back, the second epicyclic gear train, third planet gear row and
Four epicyclic gear trains, each epicyclic gear train are made of sun gear, planet carrier, planetary gear and gear ring, wherein in epicyclic gear train
Planetary gear intermeshed by gear pair with sun gear and gear ring, the torque transmitter include first clutch C1,
Second clutch C2, the first brake B1, second brake B2, third brake B3 and the 4th brake B4, the first brake,
Second brake, third brake and the 4th brake are in turn secured to from front to back on the shell 10 of gearbox case,
The first planetary gear row, the second epicyclic gear train and third planet gear row are single planetary bevel gear gear rows, the
Four epicyclic gear trains are dual planetary gear gear rows, and third planet gear row and fourth planet gears constitute Ravigneaux planet
Gear mechanism, third planet gear row and fourth planet gears share gear ring R3R4；
The coupling member group includes first coupling member 6, second coupling member 7, third coupling member 8 and tetrad
Connection member 9, wherein first planetary gear is ranked carrier PC1 and the second epicyclic gear train sun gear S2 and connected by first coupling member 6
It connects；Second coupling member 7 is by first planetary gear toothrow circle R1 and the second epicyclic gear train gear ring R2 connection；Third coupling member
8 connect the second epicyclic gear train planet carrier PC2 gear ring R3R4 shared with third planet gear row and fourth planet gears；
4th coupling member 9 connects third planet gear row planet carrier PC3 with fourth planet gears row planets carrier PC4；
The torque transmitter includes first clutch C1, second clutch C2, the first brake B1, second brake
B2, third brake B3 and the 4th brake B4, wherein first clutch C1 is by input shaft 1 and third planet gear row sun gear
S3 connection；Input shaft 1 is connect by second clutch C2 with the sun gear S4 of fourth planet gears；First brake B1 is by first
Coupling member 6 and case of transmission 10 connect；Second coupling member 7 is connect by second brake B2 with case of transmission 10；The
Three brake B3 connect third coupling member 8 and case of transmission 10；4th brake B4 by fourth planet gears too
Sun wheel S4 is connect with case of transmission 10；
The output end of the input shaft 1 is connect with first planetary gear row sun gear S1 always, and the input terminal of input shaft 1 begins
It is connected to the turbine of engine or torque-converters eventually, the input terminal of output shaft 11 is connect with the 4th coupling member 9 always, output
The output end of axis 11 is connected to next stage retarder.
Nine speed transmission of the invention realizes speed changer nine by four epicyclic gear trains and six torque transmitters
Forward speed ratio and a reverse speed ratio, the formation of the speed ratio of each gear are obtained by engaging two torque transmitters
?；Wherein first clutch C1 is selectively engagable to connection input shaft 1 together with the sun gear S3 of third planet gear row
Rotation；Second clutch C2 is selectively engagable to connection input shaft 1 and revolves together with the sun gear S4 of fourth planet gears
Turn；First brake B1 is selectively engagable to connection first coupling member 6 and gearbox case 10, in order to prevent
Rotation of the first coupling member 6 relative to gearbox case 10；Second brake B2 is selectively engagable to connection second
Connection member 7 and gearbox case 10, in order to prevent second coupling member 7 relative to the rotation of gearbox case 10；The
Three brake B3 are selectively engagable to connection third coupling member 8 and gearbox case 10, in order to prevent third
Rotation of the coupling member 8 relative to gearbox case 10；4th brake B4 is selectively engagable to connection fourth planet tooth
The sun gear S4 and gearbox case 10 of schedule, in order to prevent the sun gear S4 of fourth planet gears relative to speed change
The rotation of device shell 10；
In the present invention, expression is selectively connectable under specific gear, and specified clutch or brake is selected to connect
It closes (working condition), wants the transmission ratio for realizing which gear, selection engagement specified that two clutches or brake.
Two clutches and four brakes are selectively engaged (rotation) or fixed moving link (sun gear, planet
Some in frame, gear ring or four coupling members), and wherein torque transmitter can be in combination of at least two
It is selectively engagable to that nine forward speed ratios and a speed of reversing gear can be set up between the input shaft and the output shaft
Than, nine forward gears include five decelerations gears, a direct gear and three overgears, specifically:
1) second clutch C2 and third brake B3 engagement, realizes the foundation reversed gear, and the transmission ratio to reverse gear is -3；
2) foundation of a gear (slow down gear), the transmission ratio of a gear are realized in second clutch C2 and second brake B2 engagement
It is 5.57；
3) foundation of second gear (slow down gear), the transmission ratio of second gear are realized in first clutch C1 and third brake B3 engagement
It is 3.3, speed ratio step is 1.69；
4) foundation of three gears (slow down gear), the transmission ratio of three gears are realized in second brake B2 and the 4th brake B4 engagement
It is 1.95, speed ratio step is 1.69.
5) foundation of four gears (slow down gear), the transmission ratio of four gears are realized in first clutch C1 and second brake B2 engagement
It is 1.75, speed ratio step is 1.11；
6) foundation of five gears (slow down gear), the transmission ratio of five gears are realized in first clutch C1 and the 4th brake B4 engagement
It is 1.58, speed ratio step is 1.11；
7) foundation of six gears (direct gear), the transmission ratio of six gears are realized in first clutch C1 and second clutch C2 engagement
It is 1, speed ratio step is 1.58；
8) foundation of seven gears (overgear), the transmission ratio of seven gears are realized in first clutch C1 and the first brake B1 engagement
It is 0.80, speed ratio step is 1.25；
9) foundation of eight gears (overgear), the transmission ratio of eight gears are realized in second clutch C2 and the first brake B1 engagement
It is 0.67, speed ratio step is 1.18；
10) foundation of nine gears (overgear), the transmission ratio of nine gears are realized in the first brake B1 and the 4th brake B4 engagement
It is 0.55, speed ratio step is 1.22.
The variable block principle of nine speed transmission provided by the invention is introduced below, which is able to achieve nine advances
Speed ratio and a reverse speed ratio are kept off, the formation of the speed ratio of each gear is obtained by engaging two torque transmitters, under
The course of work of each gear is discussed in detail in face:
The foundation reversed gear, second clutch C2 and third brake B3 engagement.Specifically, second clutch C2 is engaged
It is rotated together with connecting sun gear S1 and sun gear S4.Third brake B3 is engaged so that third coupling member 8 and speed change
Device shell 10 is connected, and prevents third coupling member 8 relative to the rotation of case of transmission 10.Result in formation of single planetary gears
Row's transmission, thus sets up the transmission ratio to reverse gear between input link 1 and output link 11.
The foundation of one gear (slow down gear), second clutch C2 and second brake B2 are engaged.Specifically, the second clutch
Device C2 is engaged to connection sun gear S1 and sun gear S4 and rotates together.Second brake B2 is engaged so that the second connection structure
Part 7 is connected with case of transmission 10, prevents second coupling member 7 relative to the rotation of case of transmission 10.It is inputting as a result,
The transmission ratio of a gear is established between component 1 and output link 11.
The foundation of second gear (slow down gear), first clutch C1 and third brake B3 are engaged.Specifically, the first clutch
Device C1 is engaged to connection sun gear S1 and sun gear S3 and rotates together.Third brake B3 is engaged so that third couples structure
Part 8 is connected with case of transmission 10, prevents third coupling member 8 relative to the rotation of case of transmission 10.Result in formation of
Single planetary gear row's transmission, thus establishes the transmission ratio of second gear between input shaft 1 and output shaft 11.
The foundation of three gears (slow down gear), second brake B2 and the 4th brake B4 are engaged.Specifically, the second braking
Device B2 is engaged so that second coupling member 7 is connected with case of transmission 10, prevents second coupling member 7 relative to speed change
The rotation of device shell 10.4th brake B4 is engaged so that the sun gear S4 and case of transmission 10 of fourth planet gears
It is connected, prevents rotation of the sun gear S4 of fourth planet gears relative to case of transmission 10.As a result, in 1 He of input shaft
The transmission ratio of three gears is established between output shaft 11.
The foundation of four gears (slow down gear), first clutch C1 and second brake B2 are engaged.Specifically, the first clutch
Device C1 is engaged to connection sun gear S1 and sun gear S3 and rotates together.Second brake B2 is engaged so that the second connection structure
Part 7 is connected with case of transmission 10, prevents second coupling member 7 relative to the rotation of case of transmission 10.It is inputting as a result,
The transmission ratio of four gears is established between axis 1 and output shaft 11.
The foundation of five gears (slow down gear), first clutch C1 and the 4th brake B4 are engaged.Specifically, the first clutch
Device C1 is engaged to connection sun gear S1 and sun gear S3 and rotates together.4th brake B4 is engaged so that fourth planet tooth
The sun gear S4 of schedule is connected with case of transmission 10, prevents the sun gear S4 of fourth planet gears relative to transmission case
The rotation of body 10.The transmission ratio of five gears is established between input shaft 1 and output shaft 11 as a result,.
The foundation of six gears (direct gear), first clutch C1 and second clutch C2 are engaged.Specifically, the first clutch
Device C1 is engaged to connection first planetary gear row sun gear S1 and third planet gear row sun gear S3 and rotates together.Second from
Clutch C2 is engaged to connection sun gear S1 and sun gear S4 and rotates together.It is established between input shaft 1 and output shaft 11 as a result,
The transmission ratio of six gears is played.
The foundation of seven gears (overgear), first clutch C1 and the first brake B1 are engaged.Specifically, the first clutch
Device C1 is engaged to connection sun gear S1 and sun gear S3 and rotates together.First brake B1 is engaged so that the first connection structure
Part 6 is connected with case of transmission 10, prevents first coupling member 6 relative to the rotation of case of transmission 10.It is inputting as a result,
The transmission ratio of seven gears is set up between axis 1 and output shaft 11.
The foundation of eight gears (overgear), second clutch C2 and the first brake B1 are engaged.Specifically, the second clutch
Device C2 is engaged to connection sun gear S1 and sun gear S4 and rotates together.First brake B1 is engaged so that the first connection structure
Part 6 is connected with case of transmission 10, prevents first coupling member 6 relative to the rotation of case of transmission 10.It is inputting as a result,
The transmission ratio of eight gears is set up between axis 1 and output shaft 11.
The foundation of nine gears (overgear), the first brake B1 and the 4th brake B4 are engaged.Specifically, the first braking
Device B1 is engaged so that first coupling member 6 is connected with case of transmission 10, prevents first coupling member 6 relative to speed change
The rotation of device shell 10.4th brake B4 is engaged so that the sun gear S4 and case of transmission 10 of fourth planet gears
It is connected, prevents rotation of the sun gear S4 of fourth planet gears relative to case of transmission 10.As a result, in 1 He of input shaft
The transmission ratio of nine gears is set up between output shaft 11.
The transmission ratio of each gear, speed ratio step and each gear torque transfer device engagement are as shown in the table:
In table: X indicates engagement and transmits torque, and O indicates engagement but do not transmit torque.
Specific embodiments of the present invention are described above.It is to be appreciated that the invention is not limited to above-mentioned
Particular implementation, those skilled in the art can make a variety of changes or modify within the scope of the claims, this not shadow
Ring substantive content of the invention.In the absence of conflict, the feature in embodiments herein and embodiment can any phase
Mutually combination.
Claims (1)
1. a kind of nine speed transmission, comprising: gearbox case and the input shaft being installed on inside gearbox case, output shaft,
Epicyclic gear train group, coupling member group and torque transmitter, the epicyclic gear train group include first installed from front to back
Epicyclic gear train, the second epicyclic gear train, third planet gear row and fourth planet gears, each epicyclic gear train is by too
Positive wheel, planet carrier, planetary gear and gear ring are constituted, and the torque transmitter includes first clutch, second clutch, the first system
Dynamic device, second brake, third brake and the 4th brake, the first brake, second brake, third brake and the 4th
Brake is in turn secured to from front to back on the shell of gearbox case, it is characterised in that:
The first planetary gear row, the second epicyclic gear train and third planet gear row are single planetary bevel gear gear row, fourth line
Star gear row is dual planetary gear gear row, and third planet gear row and fourth planet gears constitute Ravigneaux planetary gear
Mechanism, third planet gear row and fourth planet gears share gear ring；
The coupling member group includes first coupling member, second coupling member, third coupling member and the 4th coupling member,
The planet carrier of middle first coupling member connection first planetary gear row and the sun gear of the second epicyclic gear train, second coupling member
The gear ring of first planetary gear row and the gear ring of the second epicyclic gear train are connected, third coupling member connects the second epicyclic gear train
Planet carrier and the shared gear ring of third planet gear row and fourth planet gears, the 4th coupling member connect third planet tooth
The planet carrier of schedule and the planet carrier of fourth planet gears；
First brake selectively interconnects first coupling member with case of transmission, and second brake couples second
Component is selectively interconnected with case of transmission, and third brake is selectively mutual by third coupling member and case of transmission
Even, the 4th brake selectively interconnects the sun gear of fourth planet gears with case of transmission；
The input shaft and the sun gear of first planetary gear row are connected, and the output shaft is connect with the 4th coupling member, described
Input shaft is selectively connectable with by first clutch and the sun gear of third planet gear row, and by second clutch with
The sun gear of fourth planet gears is selectively connectable with.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910138581.8A CN109764095B (en) | 2019-02-25 | 2019-02-25 | Nine-gear transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910138581.8A CN109764095B (en) | 2019-02-25 | 2019-02-25 | Nine-gear transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109764095A true CN109764095A (en) | 2019-05-17 |
| CN109764095B CN109764095B (en) | 2022-02-18 |
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ID=66457241
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910138581.8A Active CN109764095B (en) | 2019-02-25 | 2019-02-25 | Nine-gear transmission |
Country Status (1)
| Country | Link |
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| CN (1) | CN109764095B (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112324877A (en) * | 2020-11-19 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission |
| CN112324874A (en) * | 2020-11-30 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission with stable step ratio |
| CN112324875A (en) * | 2020-11-19 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission with small step ratio |
| CN112324876A (en) * | 2020-11-19 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission with large speed ratio range |
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| CN103148182A (en) * | 2013-03-28 | 2013-06-12 | 长城汽车股份有限公司 | Automobile and speed changer thereof |
| CN105090394A (en) * | 2015-07-17 | 2015-11-25 | 中国地质大学（武汉） | Nine-gear speed changer |
| CN105082976A (en) * | 2014-05-12 | 2015-11-25 | 腓特烈斯港齿轮工厂股份公司 | Method of Operating a Transmission |
| DE112016004798T5 (en) * | 2015-10-20 | 2018-07-19 | Exedy Corporation | Drive device for a vehicle and vehicle |
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| CN103154569A (en) * | 2010-10-20 | 2013-06-12 | 腓特烈斯港齿轮工厂股份公司 | Power-shiftable transmission |
| CN103148182A (en) * | 2013-03-28 | 2013-06-12 | 长城汽车股份有限公司 | Automobile and speed changer thereof |
| CN105082976A (en) * | 2014-05-12 | 2015-11-25 | 腓特烈斯港齿轮工厂股份公司 | Method of Operating a Transmission |
| CN105090394A (en) * | 2015-07-17 | 2015-11-25 | 中国地质大学（武汉） | Nine-gear speed changer |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112324877A (en) * | 2020-11-19 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission |
| CN112324875A (en) * | 2020-11-19 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission with small step ratio |
| CN112324876A (en) * | 2020-11-19 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission with large speed ratio range |
| CN112324877B (en) * | 2020-11-19 | 2023-04-18 | 中国地质大学（武汉） | Nine-gear automatic transmission |
| CN112324875B (en) * | 2020-11-19 | 2023-04-18 | 中国地质大学（武汉） | Nine-gear automatic transmission with small step ratio |
| CN112324874A (en) * | 2020-11-30 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission with stable step ratio |
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| Publication number | Publication date |
|---|---|
| CN109764095B (en) | 2022-02-18 |
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