EP2978998A1 - Train planétaire à plusieurs étages - Google Patents

Train planétaire à plusieurs étages

Info

Publication number
EP2978998A1
EP2978998A1 EP14706053.7A EP14706053A EP2978998A1 EP 2978998 A1 EP2978998 A1 EP 2978998A1 EP 14706053 A EP14706053 A EP 14706053A EP 2978998 A1 EP2978998 A1 EP 2978998A1
Authority
EP
European Patent Office
Prior art keywords
planetary gear
clutch
gear
housing
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Withdrawn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
EP14706053.7A
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 EP2978998A1 publication Critical patent/EP2978998A1/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Withdrawn legal-status Critical Current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
    • F16H2200/20—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
    • F16H2200/2097—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 invention relates to a multi-stage planetary gear, in particular an automatic transmission for a motor vehicle.
  • a transmission is arranged for example in a motor vehicle between a drive and the drive wheels.
  • Such a multi-stage planetary gear has a plurality of individual planetary gear, which are interconnected by means of switching elements in the form of clutches and / or brakes.
  • a multi-stage planetary gear often switching elements are used, which are hydraulically operated. If now such switching elements in the interior of the transmission, in particular arranged to be moving relative to the transmission housing, the hydraulic lines must have transitions to a rotating component. In such transitions, a pressure loss often occurs, so that the pressure within the hydraulic line must be actively maintained. This happens e.g. via a hydraulic pump. The same applies to the use of electrically, pneumatically or mechanically actuated switching elements.
  • the object of the invention is to provide a multi-stage planetary gear, which has the highest possible proportion of easily accessible switching elements.
  • a multi-stage planetary gear according to the features of claim 1 is given.
  • this multi-stage planetary gear shift elements which are designed as four clutches and two brakes, easily accessible.
  • the multi-stage planetary gear has four arranged between a drive shaft and an output shaft single planetary gear.
  • Each individual planetary gear each includes a sun gear, a ring gear and a plurality of planetary gears each associated with a web.
  • the multi-stage planetary gear can advantageously be designed in standard construction, so that the drive shaft and the output shaft are arranged coaxially in the housing. It is alternatively possible, the multi-stage planetary gear in To perform front-transverse construction, so that the output shaft can be arranged offset in axial direction to the drive shaft.
  • the drive shaft can be made connectable via the drive clutch to the drive train of the motor vehicle.
  • the drive clutch is designed in particular as a hydrodynamic torque converter, as a hydrodynamic clutch, an additional starting clutch, an integrated starting clutch, an integrated starting brake, or as an additional electric motor.
  • the inventive multi-stage planetary gear is characterized by a reduced construction or assembly costs. Both cost and weight of the multi-stage planetary gear are reduced.
  • the coupling elements are arranged on au outer shafts, in particular on the drive shaft and / or on the output shaft.
  • the outer shafts are particularly accessible from outside, so that access to all coupling elements in case of need with little effort is possible.
  • the fourth clutch is arranged on the output shaft and thus easily accessible from outside.
  • the individual planetary gear can be connected by means of the switching elements, that the multi-stage planetary gear has a good gear ratio.
  • the individual planetary gear are each designed as a so-called minus planetary gear.
  • the respective stand ratio of the respective single planetary gear has a negative value.
  • the coaxially arranged central wheels, ie the inner sun gear and the concentrically arranged, outer ring gear have opposite directions of rotation.
  • at least one of the negative planetary gear is designed as a so-called plus planetary gear. This is possible, for example, in the case of a single planetary gearbox, in which the connection between web and ring gear is exchanged, and at the same time the amount of stand ratio is increased by the value of one.
  • the arrangement of the individual planetary gear in the housing, in particular along the drive shaft and / or output shaft is variable.
  • the geometric position of the respective individual planetary gear, in particular their order along the drive shaft and / or output shaft, is arbitrary.
  • the switching elements can be arranged freely selectable with respect to their geometric position in the housing.
  • the connecting shafts, the drive shaft and / or the output shaft are each connected to the housing and / or each other by means of a freewheeling element. This results in additional degrees of freedom for the interconnection of the individual planetary gear and their coupling in the housing.
  • a drive mounted on the connecting shaft, the drive shaft and / or the output shaft can be provided.
  • the additional drive can be designed for example as an electric motor. It is also conceivable to use other power and / or power sources as a drive.
  • the switching elements are frictionally and / or positively designed.
  • the second brake, the second coupling element and the fourth coupling element are designed as claw circuit elements. Due to the characteristic of the multi-stage planetary gear, the execution of said switching elements as claw circuit elements leads to a significantly reduced fuel consumption.
  • Fig. 3 shows a second embodiment of a multi-stage planetary gear according to FIG. 1 with a modified arrangement of the switching elements
  • FIG. 4 shows a third embodiment of a multi-stage planetary gear according to FIG. 1 with a different arrangement of the switching elements. Corresponding parts are provided in FIGS. 1 to 4 with the same reference numerals. Also details of the embodiments explained in more detail below can constitute an invention in itself or be part of an inventive subject matter.
  • a multi-stage planetary gear 1 is shown schematically.
  • the multi-stage planetary gear 1 is designed in particular as a transmission for a motor vehicle.
  • the multi-stage planetary gear 1 is shown in simplified form in FIG. 1 in that only one part of the multi-stage planetary gear 1 arranged above with respect to a transmission longitudinal axis 2 is shown.
  • the multi-stage planetary gear 1 has a housing 3. Within the housing 3, six switching elements, namely a first clutch 4, a second clutch 5, a third clutch 6 and a fourth clutch 7 and a first brake 8 and a second brake 9 are arranged. Furthermore, the multi-stage planetary gear has a drive shaft 10 for transmitting a drive torque from a drive, not shown, to the multi-stage planetary gear 1. Accordingly, the multi-stage planetary gear 1 has an output shaft 1 1. The drive shaft 10 and the output shaft 1 1 are arranged coaxially with respect to the housing longitudinal axis 2. Both the drive shaft 10 and the output shaft 1 1 are each led out of the housing 3.
  • the multi-stage planetary gear further has four along the housing longitudinal axis 2 arranged planetary gear sets 12 to 15. As shown in FIG. 1, the first planetary gear set 12, the second planetary gear set 13, the third planetary gear set 14 and the fourth are along a reference direction 1 6, which is oriented from the drive shaft 10 to the output shaft 1 1 parallel to the transmission longitudinal axis 2 Planetary gear 15 is arranged.
  • the first brake 8 and the second brake 9 are fixedly arranged on an inner wall of the housing 3. Furthermore, along the reference direction 1 6, the first Clutch 4, the second clutch 5 and the third clutch 6 arranged directly next to each other. With the embodiment shown, the three clutches 4 to 6 have a common outer plate carrier 17. The clutches 4, 5 and 6 are arranged on the outer drive shaft 10. The fourth clutch 7 is arranged on the likewise outer output shaft 1 1.
  • each of the planetary gear sets 12 to 15 each have an inner, externally toothed sun gear, an outboard, internally toothed and in particular concentric with the transmission longitudinal axis 2 arranged ring gear and a plurality of each having a web, arranged between the sun gear and the ring gear Planet wheels on.
  • the number of planet gears may vary.
  • the first planetary gear set 12 comprises a sun gear 18, a ring gear 19 and at least one planetary gear 21 having a web 20.
  • the second planetary gear set 13 comprises a sun gear 22, a ring gear 23 and at least one planetary gear 25 with a web 24.
  • the third planetary gear set 14 comprises a sun gear 26, a ring gear 27 and at least one planetary gear 29 with a web 28.
  • the fourth planetary gear set 1 5 includes a sun gear 30, a ring gear 31 and at least one planetary gear 33 with a web 32nd
  • the drive shaft 10 is connected via the first clutch 4 with the web 28 of the third planetary gear set 14.
  • the drive shaft 10 is connected via the second clutch 5 with the ring gear 19 of the first planetary gear set 12.
  • the drive shaft 10 via the second coupling element 5 with the sun gear 22 of the second planetary gear set 13 is connectable.
  • the drive shaft 10 is connected via the third clutch 6 with the sun gear 18 of the first planetary gear set 12.
  • the drive shaft 10 via the third coupling element 6, with the first brake 8 connectable.
  • the output shaft 1 1 is connected to the ring gear 27 of the third planetary gear set 14.
  • the output shaft is connectable via the fourth coupling element 7 with the web 32 of the fourth planetary gear set 1 5.
  • the web 20 of the first planetary gear set 12 is connected to the web 24 of the second planetary gear set 13.
  • the ring gear 23 of the second planetary gear set 13 is connected to the second brake 9.
  • the web 24 of the second planetary gear set 13 is connected to the ring gear 31 of the fourth planetary gear set 15.
  • the web 24 of the second planetary gear set 13 is connected to the sun gear 26 of the third planetary gear set 14.
  • the sun gear 30 of the fourth planetary gear set 1 5 is connected to the housing 3 via an eighth connecting shaft 41.
  • FIG. 2 shows a shift matrix for the gear steps G to be shifted.
  • the gear steps are listed in ascending order in the shift matrix beginning with the first gear G1 to the ninth gear G9 and one reverse gear R.
  • the switching matrix reveals a ratio i to each ratio.
  • a respective gear jump j is listed.
  • the gear gap j between the first gear stage G1 and the second gear stage G2 is 1, 709. This numerical value corresponds to the ratio of the ratio of the first gear stage, namely 4.348, to the gear ratio of the second gear G2, namely 2.545.
  • the alternative fourth gear ratios G4a to G4c have an identical ratio i of 1, 267. This means that an alternative shift position for the fourth gear G4a to G4c does not lead to a change in the gear jumps j, in particular between the third and the fourth gear and the fourth and fifth gear.
  • FIG. 3 an embodiment of another multi-stage planetary gear is shown.
  • the multi-stage planetary gear differs from the multi-stage planetary gear 1 shown in FIG. 1 by a modified arrangement of the clutches.
  • the second clutch 5 and the third clutch 6 are arranged analogously to the multi-stage planetary gear 1 on the drive shaft 10 and interconnected accordingly.
  • the fourth clutch 7 is identical to the multi-stage planetary gear 1 of FIG. 1 arranged on the output shaft 1 1 and interconnected.
  • the first coupling element 4a is not arranged on the drive shaft 10 but on the output shaft 11 and allows the output shaft 11 to be connected to the ring gear 27 of the third via the fourth connecting shaft 37 Planetary gear set 14.
  • All couplings 4 a, 5, 6, 7 are on the outer shafts 10, 1 1 arranged.
  • the brakes 8, 9 are fixed to the housing 3. All switching elements 4a, 5 to 9 are easily accessible from outside.
  • the multi-stage planetary gear according to FIG. 4 differs from the multi-stage planetary gear 1 according to FIG. 1 in that the first clutch 4 b is not arranged directly on the drive shaft 1 1 but on the seventh connecting shaft 40. Accordingly, the first clutch 4b via the seventh connecting shaft 40 allows a connection of the web 38 of the second planetary gear set 13 with the sun gear 26 of the third planetary gear set 14th

Abstract

L'invention concerne un train planétaire à plusieurs étages, en particulier une transmission automatique pour un véhicule automobile, comprenant : un carter (3) présentant un axe longitudinal (2) ; un arbre d'entraînement (10) pouvant être relié à une ligne d'entraînement pour la transmission d'un couple d'entraînement de la ligne d'entraînement sur le train planétaire à plusieurs étages (1) ; un arbre de sortie (11) pouvant être relié à une ligne d'entraînement pour la transmission d'un couple de sortie du train planétaire à plusieurs étages (1) sur la ligne de sortie ; quatre engrenages planétaires individuels (12, 13, 14, 15) qui sont disposés le long de l'axe longitudinal (2) du carter et qui comprennent chacun une roue solaire (18, 22, 26, 30), une couronne (19, 23, 27, 31) et au moins une roue planétaire (21, 25, 29, 33) comprenant chacune au moins un plan fixe (20, 24, 28, 32) ; six éléments de commande qui sont disposés à l'intérieur du carter (3) et qui sont réalisés sous la forme de quatre éléments de couplage (4, 5, 6, 7) et de deux freins (8, 9) ; et des arbres de liaison (34, 35, 36, 37, 38, 39, 40, 41, 44) pour des liaisons entre les trains planétaires individuels (12, 13, 14, 15), l'arbre d'entraînement (10), l'arbre de sortie (11), les éléments de couplage (4, 5, 6, 7) et/ou les freins (8, 9). Les trains planétaires individuels (12, 13, 14, 15) peuvent être commandés au moyen des éléments de commande (4, 5, 6, 7, 8, 9) d'une manière telle que des rapports de transmission différents (i) agissent entre l'arbre d'entraînement (10) et l'arbre de sortie (11) de sorte que le train planétaire à plusieurs étages (1) présente neuf vitesses avant (G1, G2, G3, G4, G4a, G4b, G4c, G5, G6, G7, G8, G9) et une vitesse arrière (R), et que les éléments de commande (4, 5, 6, 7, 8, 9) sont disposés de manière bien accessible depuis l'extérieur du carter (3).
EP14706053.7A 2013-03-27 2014-02-25 Train planétaire à plusieurs étages Withdrawn EP2978998A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013205377.0A DE102013205377A1 (de) 2013-03-27 2013-03-27 Mehrstufen-Planetengetriebe
PCT/EP2014/053569 WO2014154411A1 (fr) 2013-03-27 2014-02-25 Train planétaire à plusieurs étages

Publications (1)

Publication Number Publication Date
EP2978998A1 true EP2978998A1 (fr) 2016-02-03

Family

ID=50156779

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14706053.7A Withdrawn EP2978998A1 (fr) 2013-03-27 2014-02-25 Train planétaire à plusieurs étages

Country Status (6)

Country Link
US (1) US9856947B2 (fr)
EP (1) EP2978998A1 (fr)
JP (1) JP6374946B2 (fr)
CN (1) CN105074276B (fr)
DE (1) DE102013205377A1 (fr)
WO (1) WO2014154411A1 (fr)

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013205384A1 (de) * 2013-03-27 2014-10-02 Zf Friedrichshafen Ag Getriebe für ein Kraftfahrzeug
DE102015223297A1 (de) * 2015-11-25 2017-06-01 Zf Friedrichshafen Ag Getriebe für ein Kraftfahrzeug, sowie Antriebsstrang für ein Kraftfahrzeug mit einem solchen Getriebe
KR101916068B1 (ko) * 2016-09-13 2018-11-07 현대자동차 주식회사 차량용 자동 변속기의 유성기어트레인
US10451147B2 (en) 2016-09-28 2019-10-22 Allison Transmission, Inc. Multi-speed planetary transmission
US10234001B2 (en) 2016-09-28 2019-03-19 Allison Transmission, Inc. Multi-speed planetary transmission
US10260599B2 (en) 2016-09-28 2019-04-16 Allison Transmission, Inc. Multi-speed planetary transmission
US10302173B2 (en) 2016-09-28 2019-05-28 Allison Transmission, Inc. Multi-speed planetary transmission
US10161486B2 (en) 2016-09-28 2018-12-25 Allison Transmission, Inc. Multi-speed planetary transmission
US10161484B2 (en) 2016-09-28 2018-12-25 Allison Transmission, Inc. Multi-speed planetary transmission
US10323722B2 (en) 2016-09-28 2019-06-18 Allison Transmission, Inc. Multi-speed planetary transmission
US10174814B2 (en) 2016-09-28 2019-01-08 Allison Transmission, Inc. Multi-speed planetary transmission
US10323723B2 (en) 2016-09-28 2019-06-18 Allison Transmission, Inc. Multi-speed planetary transmission
US10060512B2 (en) 2016-09-28 2018-08-28 Allison Transmission, Inc. Multi-speed planetary transmission
US9933045B1 (en) 2016-09-28 2018-04-03 Allison Transmission, Inc. Multi-speed planetary transmission
US10316940B2 (en) 2016-09-28 2019-06-11 Allison Transmission, Inc. Multi-speed planetary transmission
US10473190B2 (en) 2016-09-28 2019-11-12 Allison Transmission, Inc. Multi-speed planetary transmission
US10533644B2 (en) 2016-09-28 2020-01-14 Allison Transmission, Inc. Multi-speed planetary transmission
US10060511B2 (en) 2016-09-28 2018-08-28 Allison Transmission, Inc. Multi-speed planetary transmission
US10364867B2 (en) 2016-09-28 2019-07-30 Allison Transmission, Inc. Multi-speed planetary transmission
US10253850B2 (en) 2016-09-28 2019-04-09 Allison Transmission, Inc. Multi-speed planetary transmission
KR102417359B1 (ko) * 2017-09-20 2022-07-05 현대자동차 주식회사 차량용 자동변속기의 유성기어트레인
CN108843753A (zh) * 2018-08-21 2018-11-20 盛瑞传动股份有限公司 多级变速器
DE102018127710A1 (de) * 2018-11-07 2020-05-07 Schaeffler Technologies AG & Co. KG Elektrische Antriebseinheit sowie Antriebsanordnung für eine elektrische Antriebseinheit

Family Cites Families (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4839686B2 (ja) * 2005-05-16 2011-12-21 トヨタ自動車株式会社 多段変速機
JP4438689B2 (ja) * 2005-05-27 2010-03-24 トヨタ自動車株式会社 車両用駆動装置の制御装置
JP2006349153A (ja) * 2005-06-14 2006-12-28 Hiroki Kawana ９速自動変速機のギヤトレーン
KR100793887B1 (ko) * 2006-08-14 2008-01-15 현대자동차주식회사 자동변속기의 파워 트레인
KR100851829B1 (ko) * 2006-11-06 2008-08-13 현대자동차주식회사 자동변속기의 파워 트레인
US7909726B2 (en) * 2007-02-08 2011-03-22 GM Global Technology Operations LLC Multi-speed transmission
DE102007055808A1 (de) * 2007-12-14 2009-06-18 Zf Friedrichshafen Ag 10-Gang-Automatgetriebe
US7980988B2 (en) * 2008-01-25 2011-07-19 GM Global Technology Operations LLC Multi-speed transmission
US7887453B2 (en) * 2008-01-31 2011-02-15 GM Global Technology Operations LLC 9-speed transmission
DE102008000428A1 (de) 2008-02-28 2009-09-03 Zf Friedrichshafen Ag Mehrstufengetriebe
US8047954B2 (en) * 2009-02-13 2011-11-01 GM Global Technology Operations LLC Multi-speed transmission
DE102009001253B3 (de) * 2009-03-02 2010-06-24 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102009019046A1 (de) 2009-04-28 2010-11-04 Daimler Ag Getriebevorrichtung
DE102009028669A1 (de) * 2009-08-20 2011-02-24 Zf Friedrichshafen Ag Mehrstufengetriebe
JP5024361B2 (ja) * 2009-12-21 2012-09-12 トヨタ自動車株式会社 車両用駆動装置の制御装置
US8425367B2 (en) * 2010-10-05 2013-04-23 GM Global Technology Operations LLC Transmission having at least ten speeds
KR101220387B1 (ko) * 2011-06-22 2013-01-09 현대자동차주식회사 차량용 자동변속기의 유성기어트레인
DE102012202813A1 (de) * 2012-02-24 2013-08-29 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102012203936A1 (de) * 2012-03-14 2013-09-19 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102012206774B4 (de) * 2012-04-25 2021-03-11 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102012206819A1 (de) * 2012-04-25 2013-10-31 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102012206773B4 (de) * 2012-04-25 2021-03-11 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102012206808B4 (de) * 2012-04-25 2021-03-11 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102012206778B4 (de) * 2012-04-25 2021-03-11 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102012206809B4 (de) * 2012-04-25 2021-03-11 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102012207091A1 (de) * 2012-04-27 2013-10-31 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102012207085B4 (de) * 2012-04-27 2021-04-29 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102012207092B4 (de) * 2012-04-27 2022-05-05 Zf Friedrichshafen Ag Mehrstufengetriebe
US9435404B2 (en) * 2012-08-08 2016-09-06 Ford Global Technologies, Llc Multiple speed transmission
DE102012221234A1 (de) * 2012-11-21 2014-05-22 Zf Friedrichshafen Ag Getriebe
DE102013205382A1 (de) * 2013-03-27 2014-10-02 Zf Friedrichshafen Ag Getriebe für ein Kraftfahrzeug
DE102013205376A1 (de) * 2013-03-27 2014-10-02 Zf Friedrichshafen Ag Getriebe für ein Kraftfahrzeug
DE102013205378A1 (de) * 2013-03-27 2014-10-02 Zf Friedrichshafen Ag Getriebe für ein Kraftfahrzeug
DE102013205387A1 (de) * 2013-03-27 2014-10-02 Zf Friedrichshafen Ag Getriebe für ein Kraftfahrzeug
DE102013205380A1 (de) * 2013-03-27 2014-10-02 Zf Friedrichshafen Ag Getriebe für ein Kraftfahrzeug
US9285014B2 (en) * 2013-10-30 2016-03-15 Ford Global Technologies, Llc Multi-speed transmission
KR101683493B1 (ko) * 2014-12-10 2016-12-07 현대자동차 주식회사 차량용 자동변속기의 유성기어트레인

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2014154411A1 *

Also Published As

Publication number Publication date
CN105074276A (zh) 2015-11-18
DE102013205377A1 (de) 2014-10-02
CN105074276B (zh) 2017-09-19
US20160053865A1 (en) 2016-02-25
JP2016514808A (ja) 2016-05-23
US9856947B2 (en) 2018-01-02
WO2014154411A1 (fr) 2014-10-02
JP6374946B2 (ja) 2018-08-15

Similar Documents

Publication Publication Date Title
WO2014154411A1 (fr) Train planétaire à plusieurs étages
DE102008035229B4 (de) Mehrganggetriebe
DE102012207081B4 (de) Mehrstufengetriebe
EP2825789B1 (fr) Boîte de vitesses multi-étagée
DE102012207085B4 (de) Mehrstufengetriebe
DE102013205388A1 (de) Getriebe für ein Kraftfahrzeug
DE102010023824B4 (de) Siebengang-Doppelkupplungsgetriebe mit vier Drehachsen
DE102013205379A1 (de) Getriebe für ein Kraftfahrzeug
DE102012207031B4 (de) Mehrstufengetriebe
DE102013205383A1 (de) Getriebe für ein Kraftfahrzeug
DE102013205384A1 (de) Getriebe für ein Kraftfahrzeug
EP2982884A1 (fr) Transmission de groupe de véhicule automobile
DE102014202512B3 (de) Mehrstufengetriebe
DE102016221122A1 (de) Getriebe für ein Kraftfahrzeug
DE102011076382A1 (de) Doppelkupplungsgetriebe
DE102013205378A1 (de) Getriebe für ein Kraftfahrzeug
DE102011077597A1 (de) Zahnräderwechselgetriebe eines Kraftfahrzeuges
DE102013214618A1 (de) Getriebe für ein Kraftfahrzeug
DE102014224089A1 (de) Getriebe für ein Kraftfahrzeug sowie Verfahren zum Betreiben eines solchen
DE102013205382A1 (de) Getriebe für ein Kraftfahrzeug
DE10210348A1 (de) Mehrstufengetriebe
EP2469125B1 (fr) Boîte de vitesses automatique, notamment automatisée, pour un véhicule automobile
DE102017127867B4 (de) Automatisch schaltbares Getriebe für Kraftfahrzeuge
DE102014213690A1 (de) Getriebe
DE102016120601B4 (de) Mehrgängiges Doppelkupplungsgetriebe

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20150827

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20180901