WO2012072392A1 - Transmission à plusieurs étages - Google Patents

Transmission à plusieurs étages Download PDF

Info

Publication number
WO2012072392A1
WO2012072392A1 PCT/EP2011/069798 EP2011069798W WO2012072392A1 WO 2012072392 A1 WO2012072392 A1 WO 2012072392A1 EP 2011069798 W EP2011069798 W EP 2011069798W WO 2012072392 A1 WO2012072392 A1 WO 2012072392A1
Authority
WO
WIPO (PCT)
Prior art keywords
planetary gear
clutch
shaft
gear set
gear
Prior art date
Application number
PCT/EP2011/069798
Other languages
German (de)
English (en)
Inventor
Gerhard Gumpoltsberger
Christian Sibla
Stefan Beck
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 WO2012072392A1 publication Critical patent/WO2012072392A1/fr

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
    • F16H2200/0047—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising five forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2041—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with four 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
    • F16H2200/2097—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 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 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. Further multi-speed transmissions are for example from the
  • 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 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, 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 Set by means of the third shaft via a first brake to a housing of the transmission can be coupled and releasably connected via a second clutch to the drive shaft, wherein the ring gear of the 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 present invention has for its object to propose a multi-speed transmission of the type mentioned, which has five forward gears and one reverse gear with sufficient translation, in which the construction cost and size, especially the overall length, or the weight can be optimized and also the efficiency in terms the drag and gearing losses is improved.
  • the multistage transmission according to the invention small supporting moments act on the shifting elements.
  • the transmission should be suitable both for a coaxial and for a front-transverse construction. This object is achieved by the features of claim 1. Further advantages and advantageous embodiments will become apparent from the dependent claims.
  • a multi-speed transmission is proposed in planetary construction, which has a drive and an output, which are arranged in a housing. Furthermore, at least three planetary gear sets, referred to below as the first, second and third planetary gear set, six rotatable shafts - hereinafter referred to as the drive shaft, output shaft, third, fourth, fifth and sixth shaft - and at least four preferably as a plate switching elements or as positive Switching elements executed switching elements, comprising a brake and three clutches, provided, the selective engagement causes different ratios between the drive and the output, so that preferably five forward gears and one reverse gear can be realized.
  • the first, second and third planetary gear set six rotatable shafts - hereinafter referred to as the drive shaft, output shaft, third, fourth, fifth and sixth shaft - and at least four preferably as a plate switching elements or as positive Switching elements executed switching elements, comprising a brake and three clutches, provided, the selective engagement causes different ratios between the drive and the output, so that preferably five
  • the planetary gear sets are preferably arranged axially in the order of the first planetary gear set, second planetary gearset, third planetary gearset or second planetary gearset, first planetary gearset, third planetary gearset, and are preferably configured as minus planetary gear sets.
  • the axial order of the planetary gear sets may be arbitrary.
  • 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 rotational direction when the web is held stationary. tion as the sun gear and there is a positive gear ratio translation.
  • the sun gear of the first planetary gear set is connected to the third shaft, which is coupled via a brake to the housing of the transmission and via a first clutch to the connected to the web of the second planetary gear sixth shaft is detachably connectable, which via a second Clutch is releasably connected to the output shaft of the transmission connected to the ring gear of the third planetary gear set.
  • the web of the first planetary gear set is connected to the connected to the ring gear of the second planetary gear fourth shaft of the transmission, wherein the ring gear of the first planetary gear set is connected to the fifth shaft, which is connected to the web of the third planetary gear set and wherein the sun gear of the third planetary gear set is coupled to the housing.
  • the drive shaft of the transmission is connected to the sun gear of the second planetary gear set, wherein according to the invention a further clutch is provided by the closing of the second planetary gear set is blockable.
  • the further coupling is designed as a coupling which releasably connects the drive shaft with the sixth shaft, so that the blocking of the second planetary gear set can be effected by a coupling of the sun gear of the second planetary gear set with the web of the second planetary gear set.
  • the further coupling can be designed as a coupling which removably connects the fourth shaft to the sixth shaft, so that the blocking of the second planetary gear set can take place by coupling the web of the second planetary gear set with the ring gear of the second planetary gear set ,
  • 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 significantly reduced with the multi-stage transmission according to the invention by a small number of switching elements.
  • a start with a hydrodynamic converter, an external starting clutch o- perform well with other suitable external starting elements. It is also conceivable to allow a starting operation with a start-up element integrated in the transmission.
  • 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 and FIG. 2;
  • FIG. 4 shows a schematic view of a third preferred embodiment of a multistage transmission according to the invention.
  • FIG. 5 shows a schematic view of a fourth preferred embodiment of a multistage transmission according to the invention.
  • FIG. 6 shows an exemplary circuit diagram for a multistage transmission according to FIG. 4 and FIG. 5.
  • FIG. 1 shows a multi-speed transmission according to the invention with a drive shaft 1, an output shaft 2 and three planetary gear sets P1, P2 and P3, which are arranged in a housing G.
  • the planetary gear sets P1, P2, P3 are formed in the example shown in Figure 1 as negative planetary gear sets.
  • at least one planetary gear set 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 are arranged axially in the order P1, P2, P3.
  • switching elements namely a brake 03 and three clutches 16, 26, 36 are provided.
  • the spatial arrangement of the switching elements can be arbitrary and is only by the dimensions and the outer Shaping limited.
  • the clutches and the brake of the transmission are preferably designed as Reibschaltemia or lamellar switching elements.
  • the multistage transmission according to the invention has a total of six rotatable shafts, namely the shafts 1, 2, 3, 4, 5 and 6, wherein the drive shaft, the first shaft 1 and the output shaft forms the second shaft 2 of the transmission.
  • the sun gear of the first planetary gear P1 is connected to the third shaft 3, which is coupled via a brake 03 to the housing G of the transmission and a first clutch 36 with the with the web of the second planetary gear set P2 connected to the sixth shaft 6 is detachably connectable, which is releasably connectable via a second clutch 26 to the output shaft 2 connected to the ring gear of the third planetary gear P3.
  • the web of the first planetary gearset P1 is connected to the fourth shaft 4 connected to the ring gear of the second planetary gearset P2; Further, the ring gear of the first planetary gear P1 is connected to the fifth shaft 5, which is connected to the web of the third planetary gear set P3, wherein the sun gear of the third planetary gear set P3 is coupled to the housing G (shaft 0).
  • the drive shaft 1 of the transmission is connected to the sun gear of the second planetary gear set P2, wherein a third clutch 16 is provided which removably connects the drive shaft 1 with the sixth shaft 6, so that when the third clutch 16 is closed a blocking of the second planetary gear set P2 is effected by the coupling of the sun gear of the second planetary gear set P2 with the web of the second planetary gear set P2.
  • the first clutch 36 and the third clutch 16 can be arranged axially next to one another and have a common outer disk carrier.
  • the embodiment of Figure 1 is particularly suitable due to the arrangement of the drive and the output for a coaxial design (standard design).
  • the embodiment shown in Figure 2 differs from the embodiment of Figure 1 in that the planetary gear sets are axially arranged in the order P2, P1, P3; In this case, the connections of the individual elements of the planetary gear sets P1, P2, P3 are maintained. As can be seen from Figure 2, the drive and the output of the transmission are close to each other, so that this embodiment is suitable for a front-transverse construction.
  • FIG. 3 shows an exemplary circuit diagram of a multistage transmission according to FIGS. 1 and 2. For each gear two switching elements are closed.
  • the shift scheme the respective ratios of the individual gear ratios i and the step to be determined therefrom or increments ⁇ are taken to the next higher gear example, the value 5.44 represents the spread of the transmission.
  • Typical values for the stationary gear ratios of the planetary gear sets P1, P2 and P3 designed as minus planetary gear sets are respectively -2.300, -3.600 and -2.700. From Figure 3 it will be 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 a switching element in common. Further, it will be seen that a large spread is achieved with small gear jumps.
  • the first forward gear is obtained by closing the brake 03 and the second clutch 26, the second forward gear by closing the first and second clutch 36, 26, the third forward gear by closing the second and third clutch 26, 16, the fourth forward speed by closing the first and third clutches 36, 16 and the fifth forward speed results from closing the brake 03 and the third clutch 16, wherein the reverse gear by closing the brake 03 and the first clutch 36 results.
  • this switching element can be used as a starting element.
  • the multi-stage transmission shown in Figure 4 differs from the multi-stage transmission of Figure 1, characterized in that for blocking the second planetary gear P2 instead of the third clutch 16, a fourth clutch 46 is provided, via which the fourth shaft 4 with the sixth shaft 6 is detachably connectable, so that the blocking takes place by a coupling of the web of the second planetary gear set P2 with the ring gear of the second planetary gear set P2.
  • the third clutch 16 is omitted.
  • the exemplary embodiment according to FIG. 5 differs from the exemplary embodiment shown in FIG. 4 in that the planetary gear sets are arranged axially in the sequence P2, P1, P3, the connections of the individual elements of the planetary gear sets P1, P2, P3 being preserved.
  • this embodiment is suitable for a front-transverse construction.
  • FIG. 6 An exemplary circuit diagram of a multi-speed transmission according to Figures 4 and 5 is the subject of Figure 6. This circuit diagram differs from the circuit diagram of Figure 3 only in that the third clutch 16 is replaced by the fourth clutch 46. According to the invention, it is possible to provide additional freewheels at any suitable location of the multi-speed transmission, for example between a shaft and the housing or, if necessary, to connect two shafts.
  • 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 the 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 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 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 transmission à plusieurs étages présentant six rapports de marche avant et un rapport de marche arrière, comprenant trois trains planétaires (P1, P2, P3), six arbres rotatifs (1, 2, 3, 4, 5, 6) et quatre éléments de changement de vitesse (03, 16, 26, 36, 46), la roue solaire du premier train planétaire (P1) étant reliée au troisième arbre (3) qui peut être accouplé par l'intermédiaire d'un frein (03) au carter (G) et peut être relié de manière amovible par l'intermédiaire d'un premier embrayage (36) au sixième arbre (6) relié au support du deuxième train planétaire (P2), lequel arbre (6) peut être relié de manière amovible par l'intermédiaire d'un deuxième embrayage (26) à l'arbre de sortie (2) relié à la couronne du troisième train planétaire (P3). Le support du premier train planétaire (P1) est relié au quatrième arbre (4) relié à la couronne du deuxième train planétaire (P2) et la couronne du premier train planétaire (P1) est reliée au cinquième arbre (5) qui est relié au support du troisième train planétaire (P3). La roue solaire du troisième train planétaire (P3) est accouplée au carter (G) et l'arbre d'entrée (1) est relié à la roue solaire du deuxième train planétaire (P2), le deuxième train planétaire (P2) pouvant être bloqué par la fermeture d'un troisième embrayage (16) ou d'un quatrième embrayage (46).
PCT/EP2011/069798 2010-12-01 2011-11-10 Transmission à plusieurs étages WO2012072392A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010062248.6 2010-12-01
DE201010062248 DE102010062248A1 (de) 2010-12-01 2010-12-01 Mehrstufengetriebe

Publications (1)

Publication Number Publication Date
WO2012072392A1 true WO2012072392A1 (fr) 2012-06-07

Family

ID=44925546

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2011/069798 WO2012072392A1 (fr) 2010-12-01 2011-11-10 Transmission à plusieurs étages

Country Status (2)

Country Link
DE (1) DE102010062248A1 (fr)
WO (1) WO2012072392A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104822969A (zh) * 2012-11-21 2015-08-05 腓特烈斯港齿轮工厂股份公司 九挡行星齿轮变速器
CN115325117A (zh) * 2022-10-17 2022-11-11 北京航空航天大学 大速比、多挡位自动变速器

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
DE19949507A1 (de) 1999-10-14 2001-04-19 Zahnradfabrik Friedrichshafen Mehrstufengetriebe
US20030130083A1 (en) * 2002-01-08 2003-07-10 Bucknor Norman Kenneth Family of five-speed transmission mechanisms having three planetary gear sets and four torque-transmitting devices
US20040053727A1 (en) * 2002-09-12 2004-03-18 Usoro Patrick Benedict Family of multi-speed power transmissions with three gearsets
DE102004040597A1 (de) * 2004-08-21 2006-02-23 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102005010210A1 (de) 2005-03-05 2006-09-14 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102006006637A1 (de) 2006-02-14 2007-09-06 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102008000428A1 (de) 2008-02-28 2009-09-03 Zf Friedrichshafen Ag Mehrstufengetriebe

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6695741B2 (en) * 2002-01-08 2004-02-24 General Motors Corporation Family of five-speed transmission mechanisms having three planetary gear sets

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
DE19949507A1 (de) 1999-10-14 2001-04-19 Zahnradfabrik Friedrichshafen Mehrstufengetriebe
US20030130083A1 (en) * 2002-01-08 2003-07-10 Bucknor Norman Kenneth Family of five-speed transmission mechanisms having three planetary gear sets and four torque-transmitting devices
US20040053727A1 (en) * 2002-09-12 2004-03-18 Usoro Patrick Benedict Family of multi-speed power transmissions with three gearsets
DE102004040597A1 (de) * 2004-08-21 2006-02-23 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102005010210A1 (de) 2005-03-05 2006-09-14 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102006006637A1 (de) 2006-02-14 2007-09-06 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102008000428A1 (de) 2008-02-28 2009-09-03 Zf Friedrichshafen Ag Mehrstufengetriebe

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104822969A (zh) * 2012-11-21 2015-08-05 腓特烈斯港齿轮工厂股份公司 九挡行星齿轮变速器
CN104822969B (zh) * 2012-11-21 2018-12-28 腓特烈斯港齿轮工厂股份公司 九挡行星齿轮变速器
CN115325117A (zh) * 2022-10-17 2022-11-11 北京航空航天大学 大速比、多挡位自动变速器
CN115325117B (zh) * 2022-10-17 2023-02-10 北京航空航天大学 大速比、多挡位自动变速器

Also Published As

Publication number Publication date
DE102010062248A1 (de) 2012-06-06

Similar Documents

Publication Publication Date Title
EP2467612B1 (fr) Transmission à plusieurs étages
EP2467620B1 (fr) Transmission à plusieurs étages
EP2467618B1 (fr) Boîte de vitesses multi-étagée
EP2467622B1 (fr) Boîte de vitesses multi-étagée
EP2467616B1 (fr) Boîte de vitesses multi-étagée
EP2467621B1 (fr) Transmission à plusieurs étages
EP2467615B1 (fr) Boîte de vitesses multi-étagée
EP2467613B1 (fr) Transmission à plusieurs étages
EP2467614B1 (fr) Boîte de vitesses multi-étagée
EP2467619B1 (fr) Boite de vitesses multi-etagee
DE102008041192B4 (de) Mehrstufengetriebe
WO2012052284A1 (fr) Boîte de vitesses multiétagée
WO2012052283A1 (fr) Boîte de vitesses multiétagée
DE102010039984A1 (de) Mehrstufengetriebe
WO2011020899A1 (fr) Boîte de vitesses multi-étagée
WO2012072392A1 (fr) Transmission à plusieurs étages
DE102010039993A1 (de) Mehrstufengetriebe
DE102010040002A1 (de) Mehrstufengetriebe
DE102010039995A1 (de) Mehrstufengetriebe
DE102010039991A1 (de) Mehrstufengetriebe
WO2012052286A1 (fr) Boîte de vitesses multiétagée
WO2012052285A1 (fr) Boîte de vitesses multiétagée
DE102010039998A1 (de) Mehrstufengetriebe
DE102010039990A1 (de) Mehrstufengetriebe
DE102010039986A1 (de) Mehrstufengetriebe

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 11781534

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 11781534

Country of ref document: EP

Kind code of ref document: A1