EP2841807A1 - Boîte de vitesses multi-étagée - Google Patents

Boîte de vitesses multi-étagée

Info

Publication number
EP2841807A1
EP2841807A1 EP13709882.8A EP13709882A EP2841807A1 EP 2841807 A1 EP2841807 A1 EP 2841807A1 EP 13709882 A EP13709882 A EP 13709882A EP 2841807 A1 EP2841807 A1 EP 2841807A1
Authority
EP
European Patent Office
Prior art keywords
planetary gear
gear set
clutch
shaft
brake
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP13709882.8A
Other languages
German (de)
English (en)
Inventor
Stefan Beck
Christian Sibla
Wolfgang Rieger
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
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 ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of EP2841807A1 publication Critical patent/EP2841807A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • 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
    • F16H2003/445—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion without permanent connection between the input and the set 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
    • F16H2200/003—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—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
    • 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
    • F16H2200/2094—Transmissions using gears with orbital motion using positive clutches, e.g. dog clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing

Definitions

  • the present invention relates to a planetary gear multi-speed transmission, in particular an automatic transmission for a motor vehicle, according to the preamble of patent claim 1.
  • Automatic transmissions particularly for motor vehicles, include, according to the prior art, planetary gear sets that are switched by means of friction elements, such as clutches and brakes, and usually with a slipping action and optionally a lockup clutch, such as a hydrodynamic torque converter or a fluid coupling connected.
  • friction elements such as clutches and brakes
  • lockup clutch such as a hydrodynamic torque converter or a fluid coupling connected.
  • Such an automatic transmission is known for example from DE 199 12 480 B4 of the Applicant. It comprises three single planetary gear sets and three brakes and two clutches for shifting six forward gears and one reverse gear, a drive shaft and an output shaft, wherein the web of the first planetary gear set with the ring gear of the second planetary gear set and the bridge of the second planetary gear set with the ring gear of the third Planetenradsatzes is constantly connected and the drive shaft is connected directly to the sun gear of the second planetary gear set.
  • the drive shaft via the first clutch to the sun gear of the first planetary gear and the second clutch to the web of the first planetary gear set is connectable, wherein the sun gear of the first planetary gear set via the first brake with a housing of the transmission is connectable and the web of the first planetary gear set via the second brake to the housing of the transmission is connectable, wherein the sun gear of the third planetary gear set via the third brake to the housing of the transmission is connectable.
  • the output shaft of the transmission is permanently connected to the web of the third planetary gear set and the ring gear of the first planetary gear set.
  • a 9-speed multi-speed transmission known; it comprises eight switching elements and four planetary gear sets, one planetary gear set serving as a primary gear and the main gear has a Simpson set and another serving as a reverse gear planetary gear.
  • a multi-speed planetary gear transmission which has a drive and an output, which are arranged in a housing.
  • the known transmission at least four planetary gear sets, hereinafter referred to as the first, second, third and fourth planetary gear set, at least eight rotatable shafts - hereinafter as drive shaft, output shaft, third, fourth, fifth, sixth, seventh and eighth shaft
  • the selective intervention causes different ratios between the drive and the output, so that preferably nine forward gears and one reverse gear can be realized.
  • the first and the second planetary gear set which are preferably designed as negative planetary gear sets, that is to say with a negative stationary gear ratio, form a shiftable transfer gearset, the third and the fourth planetary gear set forming a main gearset.
  • the webs of the first and second planetary gear sets are coupled to each other via the fourth shaft, which is connected to an element of the main gearset that the ring gear of the first planetary gear set coupled to the sun gear of the second planetary gear via the eighth shaft is, which is releasably connectable via a first clutch to the drive shaft and that the sun gear of the first planetary gear by means of the third shaft via a first brake to a housing of the transmission is coupled and releasably connectable via a second clutch to the drive shaft, wherein the ring gear of second planetary gear set by means of the fifth shaft via a second brake to a housing of the transmission can be coupled.
  • the seventh shaft with at least one element of the main gearset is constantly connected and coupled via a third brake to the housing of the transmission
  • the sixth shaft is continuously connected to at least one further element of the main gear and releasably connected via a third clutch to the drive shaft
  • the output shaft is permanently connected to at least one further element of the main gearset.
  • the fourth shaft is constantly connected to the ring gear of the third planetary gear set, wherein the sixth shaft is continuously connected to the ring gear of the fourth planetary gear set and the web of the third planetary gear and releasably connectable via the third clutch to the drive shaft.
  • the seventh shaft is constantly connected to the sun gears of the third and fourth planetary gear set and can be coupled via the third brake to a housing of the transmission. The output takes place here via the output shaft permanently connected to the web of the fourth planetary gear set.
  • the third and the fourth planetary gear set may be combined or reduced to form a Ravigneaux set having a common web and a common ring gear.
  • the switching elements of such executed multi-step transmission which are usually designed as multi-plate clutches or brakes, hydraulically actuated, which disadvantageously to high hydraulic see losses leads.
  • the use of demand-actuated switching elements would be particularly advantageous.
  • switching elements Under demand actuated switching elements can be understood in particular switching elements in which for the maintenance of the switching state no or less energy is necessary, as to change the switching state.
  • the switching elements in particular the clutches should be easily accessible from the outside.
  • the present invention has for its object to propose a multi-speed transmission of the type mentioned, which has nine forward gears and one reverse gear with sufficient translation, in which the construction cost, component load and size are optimized and also the efficiency is improved. Furthermore, the switching elements of the transmission should be easily accessible from the outside, whereby the installation of demand-actuated switching elements is made possible. In addition, the transmission should be suitable for both a standard and a front-transverse construction.
  • a multi-speed transmission which has a drive and an output, which are arranged in a housing. Furthermore, at least four planetary gear sets, hereinafter referred to as the first, second, third and fourth planetary gear set, eight rotatable shafts - hereinafter referred to as drive shaft, output shaft, third, fourth, fifth, sixth, seventh and eighth shaft - and six preferably as a lamellae switching elements or designed as a form-locking switching elements switching elements, comprising brakes and clutches, provided, the selective Intervention causes different ratios between the drive and the output, so that preferably nine forward gears and one reverse gear can be realized.
  • the selective Intervention causes different ratios between the drive and the output, so that preferably nine forward gears and one reverse gear can be realized.
  • the planetary gear sets of the transmission are preferably designed as negative planetary gear sets.
  • the ring gear at a fixed web on a sun gear opposite direction of rotation.
  • a simple plus planetary gear includes a sun gear, a ring gear and a web on which inner and outer planetary gears are rotatably mounted, wherein all inner planetary gears mesh with the sun gear and all outer planetary gears with the ring gear, each inner planetary gear each having an outer Planet wheel meshes.
  • the ring gear has the same direction of rotation when the web is held on as the sun gear and there is a positive stationary gear ratio.
  • the sun gear of the first planetary gear set is connected to the fifth shaft, which is releasably connectable via a first clutch to the drive shaft and can be coupled via a third brake to the housing, wherein the drive shaft via a second clutch with the with the web of the fourth planetary gear set and the ring gear of the third planetary gear set connected seventh shaft is detachably connectable and via a third clutch with the eighth shaft connected to the sun gear of the second planetary gear set is detachably connectable.
  • the sixth shaft is connected to the ring gear of the first planetary gear set, the bridge of the second planetary gear set and the ring gear of the fourth planetary gear set, wherein the third shaft is connected to the sun gear of the third planetary gear set and the sun gear of the fourth planetary gear set and to a first brake Housing can be coupled.
  • the fourth shaft is connected to the web of the first planetary gear set and the ring gear of the second planetary gear set and coupled via a second brake to the housing, wherein the output shaft of the transmission is connected to the web of the third planetary gear set.
  • switching elements of the transmission u.a. be designed as hydraulically actuated switching elements.
  • the construction cost is significantly reduced with the multi-stage transmission according to the invention by a small number of switching elements.
  • a switching element which is actuated in the first forward gear and in reverse is suitable.
  • the multistage transmission according to the invention, a good efficiency in the main drives with respect to the drag and gear losses.
  • there are low torques in the switching elements and in the planetary gear sets of the multi-speed transmission whereby the wear in the multi-speed transmission is advantageously reduced.
  • a correspondingly small dimensioning is made possible by the low torques, whereby the required space and the corresponding costs are reduced.
  • the transmission according to the invention is designed such that an adaptability to different drive train configurations is made possible both in the power flow direction as well as in space.
  • Figure 1 is a schematic view of a preferred embodiment of a multi-speed transmission according to the invention.
  • FIG. 2 shows an exemplary circuit diagram for a multistage transmission according to FIG. 1.
  • FIG. 1 shows a multi-speed transmission according to the invention with a drive shaft 1, an output shaft 2 and four planetary gear sets P1, P2, P3 and P4, which are arranged in a housing G.
  • the planetary gear sets P1, P2, P3, P4 are formed in the example shown in Figure 1 as negative planetary gear sets.
  • at least one of the planetary gear sets P1, P2, P3, P4 can be designed as a positive planetary gear set, if at the same time the web and Hohlradanulation exchanged and the amount of the stationary gear ratio is increased by 1 compared to the design as a minus planetary gear.
  • the planetary gear sets P1, P2, P3, P4 axially arranged in the order of the first planetary gear set P1, second planetary gear set P2, third planetary gear set P3, fourth planetary gear set P4.
  • the axial order of the individual planetary gear sets and the arrangement of the switching elements are freely selectable, as long as it allows the binding of the elements.
  • switching elements namely three brakes 03, 04, 05 and three clutches 15, 17, 18 are provided.
  • the spatial arrangement of the switching elements can be arbitrary and is limited only by the dimensions and the external shape.
  • the clutches and the brakes of the transmission are preferably designed as Reibschaltemia or lamellar switching elements, but can also be designed as a form-locking switching elements.
  • the multi-speed transmission according to the invention has a total of eight rotatable shafts, namely the waves 1, 2, 3, 4, 5, 6, 7 and 8, wherein the drive shaft, the first shaft 1 and the output shaft form the second shaft 2 of the transmission.
  • the sun gear of the first planetary gear P1 is connected to the fifth shaft 5, which is detachably connected via a first clutch 15 to the drive shaft 1 and can be coupled via a third brake 05 to the housing G.
  • the drive shaft 1 is detachably connectable via a second clutch 17 to the seventh shaft 7 connected to the web of the fourth planetary gear set P4 and the ring gear of the third planetary gear set P3 and via a third clutch 18 to the eighth connected to the sun gear of the second planetary gear set P2 Shaft 8 is releasably connectable.
  • the sixth shaft 6 is connected to the ring gear of the first planetary gear set P1, the bridge of the second planetary gear P2 and the ring gear of the fourth planetary gear set P4, wherein the third shaft 3 with the sun gear of the third planetary gear P3 and the sun gear of the fourth Planetary gear P4 connected and can be coupled via a first brake 03 to the housing G.
  • the fourth shaft 4 is connected to the web of the first planetary gear set P1 and the ring gear of the second planetary gear set P2 and coupled via a second brake 04 to the housing G, wherein the output shaft 2 of the transmission is connected to the web of the third planetary gear set P3.
  • first, second and third clutches 15, 17, 18 arranged axially next to one another and designed as a lamellar switching elements and having a common outer disc carrier.
  • first brake 03 and the third clutch 18 are suitable for execution as claw switching elements, whereby the consumption is significantly improved.
  • FIG. 2 shows an exemplary circuit diagram of a multistage transmission according to FIG. For each gear three switching elements are closed.
  • the shift scheme, the respective ratios i of the individual grades and the determined therefrom gear steps or increments ⁇ to the next higher gear are exemplified, the value 9.01 6 represents the spread of the transmission.
  • the values for the stationary gear ratios of the planetary gear sets P1, P2, P3, P4 designed as minus planetary gear sets are -2.366, -1, 600, -3.189 and -2.763 in the example shown. From Figure 2 it is seen that in sequential switching mode only one switching element switched on and a switching element must be switched off because two adjacent gear stages use two switching elements together. Further, it will be seen that a large spread is achieved with small gear jumps.
  • the first forward gear is obtained by closing the first and second brakes 03, 04 and the third clutch 18, the second forward gear by closing the first and third brakes 03, 05 and the third clutch 18, the third forward gear by Closing the first brake 03 and the first and third clutches 15, 18, the fourth forward gear by closing the first brake 03rd and the second and third clutches 17, 18, the fifth forward gear in the shown example by closing the first, second and third clutches 15, 17, 18, the sixth forward gear by closing the third brake 05 and the second and third clutches 17, 18, the seventh forward gear by closing the second brake 04 and the second and third clutches 17, 18, the eighth forward gear by closing the second and third brakes 04, 05 and the second clutches 17 and the ninth forward speed is obtained by closing the second brake 04 and the first and second clutches 15, 17, wherein the reverse gear is obtained by closing the first and second brakes 03, 04 and the first clutch 15.
  • the fourth forward gear can be switched by further switching combinations, which are designated in Figure 2 with M. Accordingly, the fourth forward speed can be achieved by closing the first and second brakes 03, 04 and the second clutch 17 or by closing the first brake 03 and the first and second clutches 15, 17 or by closing the first and third brakes 03, 05 and the second coupling 17 result.
  • an axle differential and / or a distributor differential can be arranged on the drive side or on the output side.
  • the drive shaft 1 can be separated by a coupling element of a drive motor as needed, as a coupling element, a hydrodynamic converter, a hydraulic clutch, a dry starting clutch, a wet starting clutch, a magnetic powder clutch, a centrifugal clutch or the like can be used. It is also possible to arrange such a starting element in the power flow direction behind the transmission, in which case the drive shaft 1 is constantly connected to the crankshaft of the drive motor.
  • the multistage transmission according to the invention also allows the arrangement of a torsional vibration damper between the drive motor and transmission.
  • a wear-free brake such. a hydraulic or electric retarder or the like, be arranged, which is particularly important for use in commercial vehicles of particular importance.
  • a power take-off may be provided to drive additional units on each shaft, preferably on the drive shaft 1 or the output shaft 2.
  • the friction shift elements used can be designed as power shift clutches or brakes.
  • non-positive clutches or brakes such as e.g. Multi-plate clutches, band brakes and / or cone clutches are used.

Landscapes

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

Abstract

Boîte de vitesses multi-étagée comprenant quatre trains planétaires (P1, P2, P3, P4), huit arbres rotatifs (1, 2, 3, 4, 5, 6, 7, 8) et six éléments de commande (03, 04, 05, 15, 17, 8) ; le pignon du premier train planétaire (P1) étant relié au cinquième arbre (5), lequel peut être accouplé à l'arbre d'entrée (1) par l'intermédiaire d'un premier embrayage (15) et est relié au carter (G) par l'intermédiaire d'un troisième frein (05) ; l'arbre d'entrée (1) pouvant être relié de manière libérable par l'intermédiaire d'un deuxième embrayage (17) au septième arbre (7) qui est relié au porte-satellites du quatrième train planétaire (P4), et pouvant être relié par l'intermédiaire d'un troisième embrayage (18) au huitième arbre (8) qui est relié au pignon du deuxième train planétaire (P2) ; le sixième arbre (6) étant relié à la couronne planétaire du premier train planétaire (P1), au porte-satellites du deuxième train planétaire (P2) et à la couronne planétaire du quatrième train planétaire (P4). le troisième arbre (3) étant relié au pignon du troisième train planétaire (P3) et au pignon du quatrième train planétaire (P4) et pouvant, par l'intermédiaire d'un premier frein (03), être accouplé au carter (G) ; le quatrième arbre (4) étant relié au porte-satellites du premier train planétaire (P1) et à la couronne planétaire du deuxième train planétaire (P2) et pouvant, par l'intermédiaire d'un deuxième frein (04), être accouplé au carter (G) ; l'arbre de sortie (2) étant relié au porte-satellites du troisième train planétaire (P3).
EP13709882.8A 2012-04-25 2013-03-13 Boîte de vitesses multi-étagée Withdrawn EP2841807A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012206809.0A DE102012206809B4 (de) 2012-04-25 2012-04-25 Mehrstufengetriebe
PCT/EP2013/055077 WO2013160001A1 (fr) 2012-04-25 2013-03-13 Boîte de vitesses multi-étagée

Publications (1)

Publication Number Publication Date
EP2841807A1 true EP2841807A1 (fr) 2015-03-04

Family

ID=47891694

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13709882.8A Withdrawn EP2841807A1 (fr) 2012-04-25 2013-03-13 Boîte de vitesses multi-étagée

Country Status (5)

Country Link
US (1) US9267576B2 (fr)
EP (1) EP2841807A1 (fr)
CN (1) CN104246295B (fr)
DE (1) DE102012206809B4 (fr)
WO (1) WO2013160001A1 (fr)

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KR101703580B1 (ko) * 2015-05-13 2017-02-07 현대자동차 주식회사 차량용 자동변속기의 유성기어트레인
KR20170064954A (ko) * 2015-12-02 2017-06-12 현대자동차주식회사 차량용 자동변속기의 유성기어트레인
KR101795388B1 (ko) 2015-12-02 2017-11-09 현대자동차 주식회사 차량용 자동변속기의 유성기어트레인
KR101826560B1 (ko) 2016-03-08 2018-02-07 현대자동차 주식회사 차량용 자동변속기의 유성기어트레인
KR102474354B1 (ko) * 2017-09-12 2022-12-05 현대자동차 주식회사 차량용 자동변속기의 유성기어트레인
KR102451892B1 (ko) * 2017-10-19 2022-10-06 현대자동차 주식회사 차량용 변속장치
KR102463190B1 (ko) * 2017-11-02 2022-11-03 현대자동차 주식회사 차량용 자동변속기의 유성기어트레인
KR102563438B1 (ko) * 2018-08-10 2023-08-03 현대자동차 주식회사 차량용 변속장치
CN114001132A (zh) * 2021-10-26 2022-02-01 中国地质大学（武汉） 一种阶跃比小的九挡自动变速器

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CN104246295B (zh) 2017-10-24
US9267576B2 (en) 2016-02-23
WO2013160001A1 (fr) 2013-10-31
CN104246295A (zh) 2014-12-24
DE102012206809B4 (de) 2021-03-11
DE102012206809A1 (de) 2013-10-31
US20150141195A1 (en) 2015-05-21

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