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WO2011020899A1 - Boîte de vitesses multi-étagée - Google Patents

Boîte de vitesses multi-étagée Download PDF

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Publication number
WO2011020899A1
WO2011020899A1 PCT/EP2010/062131 EP2010062131W WO2011020899A1 WO 2011020899 A1 WO2011020899 A1 WO 2011020899A1 EP 2010062131 W EP2010062131 W EP 2010062131W WO 2011020899 A1 WO2011020899 A1 WO 2011020899A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
planetary gear
gear set
planetary
clutch
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.)
Ceased
Application number
PCT/EP2010/062131
Other languages
German (de)
English (en)
Inventor
Gerhard Gumpoltsberger
Christian Sibla
Stefan Beck
Josef Haupt
Gert Bauknecht
Peter Ziemer
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 WO2011020899A1 publication Critical patent/WO2011020899A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2012—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

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 in particular for motor vehicles, comprise in the prior art planetary gear sets which are switched by means of friction elements such as clutches and brakes, and usually with a slipping action and optionally with a lock-up starting element, such as a hydrodynamic torque converter or a fluid coupling connected.
  • Such an automatic transmission is known for example from DE 199 49 507 A1 of the applicant;
  • two non-switchable front-gear sets are provided on the output side, the output side generate two speeds that are selectively switchable in addition to the speed of the drive shaft to a force acting on the output shaft, switchable Doppelplanetenradsatz by selectively closing the switching elements used that to switch from a Gear in each case the following higher or lower gear from the two currently operated switching elements only one switching element must be switched on or off.
  • a multi-speed automatic transmission with eight forward gears and one reverse gear comprising a first input path T1 of a first transmission ratio; an input path T2 having a larger gear ratio than this input path T1; a planetary gear set of the type Ravigneaux with four elements, the four elements a first element, a second element, a third element and a fourth element are in the order of the elements in a speed diagram; a clutch C-2 which transmits rotation of the input path T2 to the first element S3; a clutch C-1 which transmits the rotation from the input path T2 to the fourth element S2; a clutch C-4 which transmits a rotation from the input path T1 to the first element; a clutch C-3 which transmits the rotation from the input path T1 to the second element C3; a brake B-1 which establishes the engagement of the fourth element; a brake B-2 which makes the engagement of the second member; and an output element coupled to the third element S3.
  • a 9-speed multi-speed transmission is also known from DE 29 36 969 A1; it comprises eight shift elements and four sets of wheels, one wheel set serves as a Vorschaltgetriebe and the main gear has a Simpson set and another serving as a reverse gear wheelset.
  • a planetary gear multi-speed 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 - and at least six switching elements, including 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 first and the second planetary gear set which are preferably designed as minus planetary gear sets, form a switchable transfer gearset, wherein the third and the fourth planetary gear set form 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 set on the eighth wave 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 can be coupled by means of the fifth shaft via a second brake to a housing of the transmission.
  • the seventh shaft with at least one element of the main gearset is constantly connected and coupled via a third brake to a 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 constantly connected to the ring gear of the fourth planetary gear set and the web of the third planetary gear set 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 gearset.
  • the third and the fourth planetary gear set to be a Ravigneaux set with a common web and a common ring gear or reduced.
  • the present invention has for its object to propose a multi-speed transmission of the type mentioned, which has nine forward gears and at least one reverse gear with sufficient translation, in which the construction cost and size, in particular the overall length, or the weight can be optimized and also the efficiency is improved in terms of drag and gearing losses.
  • the multistage transmission according to the invention small supporting moments act on the shifting elements.
  • the transmission according to the invention should be suitable for 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 at least six switching elements, comprising brakes and clutches, provided whose selective engagement 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 are arranged axially in the order of the first planetary gearset, second planetary gearset, third planetary gearset, fourth planetary gearset and are preferably designed as minus planetary gear sets.
  • a simple minus planetary set includes known a sun gear, a ring gear and a web on which planet gears are rotatably mounted, each with Combine sun gear and ring gear. In this way, the ring gear at a fixed web on a sun gear opposite direction of rotation.
  • a simple plus planetary gear set includes a sun gear, a ring gear and a web on which inner and outer planetary gears are rotatably mounted, all inner planetary gears with the sun gear and all outer planetary gears with the ring gear, each inner planetary gear with each meshing with an outer planetary gear.
  • the ring gear has the same direction of rotation when holding the web as the sun gear.
  • the sun gear of the first planetary gear set is operatively connected to the drive shaft connected to the land of the fourth planetary gear set, the land of the first planetary gear set being connected to the third shaft, which can be coupled to a housing of the transmission via a first brake via a first clutch with the seventh shaft and via a second clutch with the sixth shaft is detachably connectable, wherein the sixth shaft is connected to the ring gear of the second planetary gear set, the sun gear of the third planetary gear set and the sun gear of the fourth planetary gear set.
  • the ring gear of the first planetary gear set is connected to the seventh shaft, which is connected to the web of the second planetary gear set, wherein the ring gear of the third planetary gearset is coupled via a third brake to a housing of the transmission, wherein the sun gear of the second planetary gear set with the fourth shaft is connected, which is coupled via a second brake to a housing of the transmission and wherein the operatively connected to the ring gear of the fourth planetary gear set output shaft is connected to the web of the third planetary gear set.
  • the drive shaft with the web of the fourth planetary gearset via a connected to the web of the fourth planetary gear set eighth shaft and the eighth shaft to the drive shaft releasably connecting the third clutch releasably connectable, wherein the output shaft is directly connected to the ring gear of the fourth planetary gearset.
  • the drive shaft is directly connected to the web of the fourth planetary gear set, wherein the output shaft is not directly connected to the ring gear of the fourth planetary gearset but via a further shaft connected to the ring gear of the fourth planetary gear set and the others Shaft with the output shaft releasably connecting further coupling is releasably connectable.
  • the inventive design of the multi-speed transmission results in particular for passenger cars suitable translations and increased total spread of the multi-speed transmission, whereby an improvement in ride comfort and a significant consumption reduction can be effected.
  • the construction cost is considerably 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 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 A schematic view of a first preferred embodiment of a multi-speed transmission according to the invention
  • Figure 2 is a schematic view of a second preferred embodiment of a multi-speed transmission according to the invention.
  • FIG. 3 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 and P4 are formed in the example shown in Figure 1 as a minus planetary gear sets.
  • at least one planetary gear set can be designed as a plus planetary gear set, if at the same time the web and Hohlradanulation exchanged and the amount of stationary translation is increased by 1 compared to the design as a minus planetary gear set.
  • the planetary gear sets are arranged axially in the order P1, P2, P3, P4.
  • 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 forms the first shaft and the output shaft, the second shaft of the transmission.
  • the sun gear of the first planetary gear set P1 is connected to the drive shaft 1, wherein the web of the first planetary gear set P1 is connected to the third shaft 3, which via a first brake 03 to a housing G of Gear can be coupled, via a first clutch 37 with the seventh shaft 7 and a second clutch 36 with the sixth shaft 6 is releasably connectable.
  • the sixth shaft 6 is connected to the ring gear of the second planetary gearset P2, the sun gear of the third planetary gearset P3 and the sun gear of the fourth planetary gearset P4, the drive shaft 1 being connected via the eighth shaft 8 connected to the web of the fourth planetary gearset and a third clutch 18 releasably connecting the eighth shaft 8 to the drive shaft 1 is detachably connectable to the bridge of the fourth planetary gear set P4.
  • the ring gear of the first planetary gear set P1 is connected to the seventh shaft 7, which is connected to the web of the second planetary gear set P2, wherein the ring gear of the third planetary gear set P3 is connected to the fifth shaft 5, which via a third brake 05 to a housing G of the transmission can be coupled and wherein the sun gear of the second planetary gear set P2 is connected to the fourth shaft 4, which can be coupled via a second brake 04 to a housing G of the transmission; the output shaft 2 is directly connected in the embodiment shown with the web of the third planetary gear set P3 and the ring gear of the fourth planetary gear set P4.
  • the first clutch 37 and the second clutch 36 can be viewed axially between the first and second planetary gear sets P1, P2. be arranged, wherein the third clutch 18 may be arranged axially in the power flow direction in the train operation after the fourth planetary gear set P4.
  • the second and third brakes 04, 05 are preferably arranged next to one another when viewed axially.
  • the embodiment shown in Figure 2 differs from the embodiment of Figure 1 in that the detachable connection of the drive shaft 1 with the web of the fourth planetary gear set P4 by means of the drive shaft 1 with the eighth shaft 8 releasably connecting the third clutch 18 and with the web of the fourth planetary gear set P4 eighth shaft 8 is replaced by a direct connection of the drive shaft 1 with the web of the fourth planetary gear set P4, in which case the output shaft with the ring gear of the fourth planetary gear set P4 not directly but via a connected to the ring gear of the fourth planetary gear set P4 another shaft 8 'and a further shaft 8' with the output shaft 2 releasably connecting further coupling 28 is releasably connectable.
  • FIG. 3 shows an exemplary circuit diagram of a multistage transmission according to FIG.
  • the shift scheme, the respective ratios i of the individual grades and the determined therefrom gear jumps or increments phi are taken to the next higher gear example, the value of 9.007 represents the spread of the transmission.
  • Typical values for the stationary ratios of the planetary gear sets P1, P2, P3 and P4, which are designed as minus planetary gear sets, are -1, 953, -2.191, -2.235 and -2.404, respectively. From FIG. 3 it can be seen that in the case of sequential switching, double circuits or group circuits are avoided, since two adjacent gear stages share two switching elements. Further, it will be seen that a large spread is achieved with small gear jumps.
  • the first forward gear is obtained by closing the second and third brakes 04, 05 and the second clutch 36, the second forward gear by Closing the third brake 05 and the first and second clutches 37, 36, the third forward gear by closing the second and third brakes 04, 05 and the first clutch 37, the fourth forward gear by closing the third brake 05 and the first and third clutch 37, 18, the fifth forward gear by closing the second brake 04 and the first and third clutches 37, 18, preferably the sixth forward gear, preferably direct gear, by closing all clutches 37, 36, 18, the seventh forward -Graking by closing the second brake 04 and the second and third clutch 36, 18, the eighth forward gear by closing the first brake 03 and the second and third clutch 36, 18 and the ninth forward gear is obtained by closing the first and the second brake 03, 04 and the third clutch 18, wherein the reverse gear by closing all brakes 03, 04 and 05 results.
  • the third clutch 18 is omitted and replaced by the further clutch 28, i. in the event that the drive shaft 1 directly connected to the web of the fourth planetary gear set P4 and not detachably connectable to the web of the fourth planetary gear set P4 via the eighth shaft 8 and the third clutch 18 and the output shaft 2 with the ring gear of the fourth planetary gear set P4 not directly but via a connected to the ring gear of the fourth planetary gear set P4 further shaft 8 'and the further shaft 8' releasably connected to the output shaft 2 further coupling 28 is detachably connected, in the circuit diagram of Figure 3, the third clutch 18 through the other Clutch 28 replaced.
  • an axle differential and / or a distributor differential can be arranged according to the invention.
  • the drive shaft 1 can be separated by a coupling element of a drive motor as needed, with a hydrodynamic converter, a hydraulic clutch, a dry starting clutch, a wet starting clutch, a magnetic powder clutch or a centrifugal clutch can be used as a coupling element. 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 permanently connected to the crankshaft of the engine.
  • the multistage transmission according to the invention also allows the arrangement of a torsional vibration damper between the engine 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 a load-shifting clutches or brakes.
  • non-positive clutches or brakes such as multi-plate clutches, band brakes and / or cone clutches can be used.
  • Another advantage of the multistage transmission presented here is that an electric machine can be mounted on each shaft as a generator and / or as an additional drive machine.

Landscapes

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

Abstract

L'invention concerne une boîte de vitesses multi-étagée, comportant neuf vitesses avant et une marche arrière, comprenant quatre trains planétaires (P1, P2, P3, P4), huit arbres rotatifs (1, 2, 3, 4, 5, 6, 7, 8, 8') et six éléments de commande (03, 04, 05, 13, 18, 28, 36), le planétaire du train planétaire (P1) étant relié à l'arbre d'entrée (1) coopérant avec l'élément de liaison du train planétaire (P4). L'élément de liaison du train planétaire (P1) est relié au troisième arbre (3) pouvant être accouplé à un carter (G) au moyen d'un premier frein (03), et relié de façon amovible au septième arbre au moyen d'un premier embrayage (37) et au sixième arbre (6) au moyen d'un deuxième embrayage (36), le sixième arbre (6) étant relié à la couronne du train planétaire (P2), au planétaire du train planétaire (P3) et au planétaire du train planétaire (P4). Le septième arbre (7) est relié à la couronne du train planétaire (P1) et à l'élément de liaison du train planétaire (P2), le planétaire du train planétaire (P2) étant relié au quatrième arbre (4) pouvant être accouplé à un carter (G) au moyen d'un deuxième frein (04). La couronne du train planétaire (P3) est reliée au cinquième arbre (5) pouvant être accouplé à un carter (G) au moyen d'un troisième frein (05), l'arbre de sortie (2) coopérant avec la couronne du train planétaire (P4) étant relié à l'élément de liaison du train planétaire (P3).
PCT/EP2010/062131 2009-08-20 2010-08-19 Boîte de vitesses multi-étagée Ceased WO2011020899A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009028724A DE102009028724A1 (de) 2009-08-20 2009-08-20 Mehrstufengetriebe
DE102009028724.8 2009-08-20

Publications (1)

Publication Number Publication Date
WO2011020899A1 true WO2011020899A1 (fr) 2011-02-24

Family

ID=42938577

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/062131 Ceased WO2011020899A1 (fr) 2009-08-20 2010-08-19 Boîte de vitesses multi-étagée

Country Status (2)

Country Link
DE (1) DE102009028724A1 (fr)
WO (1) WO2011020899A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013199958A (ja) * 2012-03-23 2013-10-03 Jatco Ltd 車両用自動変速機
CN116292783A (zh) * 2023-03-30 2023-06-23 中国地质大学（武汉） 一种传动平稳的八挡自动变速器

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014109616B4 (de) * 2014-07-09 2023-07-13 Volkswagen Ag Getriebeanordnung für ein Kraftfahrzeug und Kraftfahrzeug
CN106609818A (zh) * 2015-10-27 2017-05-03 长城汽车股份有限公司 一种自动变速器及汽车

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2936969A1 (de) 1979-09-13 1981-04-02 Daimler-Benz Ag, 7000 Stuttgart Planetenraeder-gangwechselgetriebe mit einem vorschalt- und einem hauptgetriebe fuer fahrzeuge
US4683776A (en) * 1986-02-27 1987-08-04 General Motors Corporation Transmission gearing arrangement
DE19949507A1 (de) 1999-10-14 2001-04-19 Zahnradfabrik Friedrichshafen Mehrstufengetriebe
DE10213820A1 (de) 2001-03-29 2002-10-10 Aisin Aw Co Automatikgetriebe für ein Fahrzeug
JP2005036955A (ja) * 2003-06-23 2005-02-10 Toyota Motor Corp 多段変速機
DE102005010210A1 (de) 2005-03-05 2006-09-14 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102006006637A1 (de) 2006-02-14 2007-09-06 Zf Friedrichshafen Ag Mehrstufengetriebe
WO2010060500A1 (fr) * 2008-11-03 2010-06-03 Daimler Ag Unité de transmission

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10115995A1 (de) * 2001-03-30 2002-10-10 Zahnradfabrik Friedrichshafen Mehrstufengetriebe
JP2006349153A (ja) * 2005-06-14 2006-12-28 Hiroki Kawana ９速自動変速機のギヤトレーン
DE102008016084A1 (de) * 2007-04-02 2008-10-30 GM Global Technology Operations, Inc., Detroit Achtgang-Automatikgetriebe
US7736263B2 (en) * 2007-08-15 2010-06-15 Gm Global Technology Operations, Inc. 9-speed transmission
DE102008000428A1 (de) 2008-02-28 2009-09-03 Zf Friedrichshafen Ag Mehrstufengetriebe

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2936969A1 (de) 1979-09-13 1981-04-02 Daimler-Benz Ag, 7000 Stuttgart Planetenraeder-gangwechselgetriebe mit einem vorschalt- und einem hauptgetriebe fuer fahrzeuge
US4683776A (en) * 1986-02-27 1987-08-04 General Motors Corporation Transmission gearing arrangement
DE19949507A1 (de) 1999-10-14 2001-04-19 Zahnradfabrik Friedrichshafen Mehrstufengetriebe
DE10213820A1 (de) 2001-03-29 2002-10-10 Aisin Aw Co Automatikgetriebe für ein Fahrzeug
JP2005036955A (ja) * 2003-06-23 2005-02-10 Toyota Motor Corp 多段変速機
DE102005010210A1 (de) 2005-03-05 2006-09-14 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102006006637A1 (de) 2006-02-14 2007-09-06 Zf Friedrichshafen Ag Mehrstufengetriebe
WO2010060500A1 (fr) * 2008-11-03 2010-06-03 Daimler Ag Unité de transmission

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013199958A (ja) * 2012-03-23 2013-10-03 Jatco Ltd 車両用自動変速機
CN116292783A (zh) * 2023-03-30 2023-06-23 中国地质大学（武汉） 一种传动平稳的八挡自动变速器

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