EP2978997A1 - Transmission pour un véhicule automobile - Google Patents

Transmission pour un véhicule automobile

Info

Publication number
EP2978997A1
EP2978997A1 EP14705807.7A EP14705807A EP2978997A1 EP 2978997 A1 EP2978997 A1 EP 2978997A1 EP 14705807 A EP14705807 A EP 14705807A EP 2978997 A1 EP2978997 A1 EP 2978997A1
Authority
EP
European Patent Office
Prior art keywords
transmission according
planetary
planetary gear
gear
transmission
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Withdrawn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
EP14705807.7A
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 EP2978997A1 publication Critical patent/EP2978997A1/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Withdrawn legal-status Critical Current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
    • 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
    • F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with intermeshing 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
    • 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 transmission, in particular multi-clutch transmission, for a motor vehicle, comprising the elements drive shaft, a plurality of planetary gear sets, wherein a planetary gear planetary sun gear, one or more planetary gears, a web and a ring gear, N switching elements, comprising a plurality of clutches, where N is a Whole number is greater than four, and an output shaft, wherein by means of at least one of the N switching elements, the drive shaft with the output shaft for displaying different gear ratios by means of at least one of the planetary gear is connectable.
  • WO 2012/052284 A1 a multistage transmission with six forward gears and one reverse gear is shown, which comprises four planetary gear sets, seven rotatable shafts and five shift elements, wherein the sun gear of the first planetary gear set is connected to the sixth shaft, which via a first brake to the Housing of the transmission can be coupled, wherein the web of the first planetary gear set is connected to the fifth shaft, which is connected to the sun gear of the second planetary gear set and coupled via a second brake to the housing, wherein the drive shaft with the ring gear of the first planetary gear set and the sun gear connected to the third planetary gear set and via a clutch with the connected to the web of the third planetary and the ring gear of the fourth planetary gear seventh shaft is detachably connected, wherein the fourth shaft connected to the ring gear of the third planetary gear set and the web of the second planetary gear set and a third brake is coupled to the housing, wherein the output shaft is connected
  • the disadvantage here is that switching elements such as multi-plate clutches or brakes are hydraulically actuated. This hydraulic actuation leads to high hydraulic losses. To avoid these actuation losses, It has been proposed to provide electromechanical or electrohydraulic actuations. The disadvantage here is again that the switching elements, especially the couplings are difficult to access.
  • An object of the present invention is therefore to provide a transmission for a motor vehicle, which has a good efficiency, low component load and low construction costs. Moreover, it is an object of the present invention to provide a transmission for a motor vehicle, which has good accessibility of switching elements from the outside. Another object of the present invention is to provide an alternative transmission for a motor vehicle.
  • the present invention solves the problems in a transmission, in particular multiple clutch transmissions, for a motor vehicle, comprising the elements drive shaft, a plurality of planetary gear sets, wherein a planetary gearset includes the planetary sun gear, one or more planetary gears, a web and a ring gear, N switching elements, comprising a plurality of clutches , wherein N is an integer greater than four, and an output shaft, wherein by means of at least one of the N shift elements, the drive shaft to the output shaft for displaying different gear ratios by at least one of the planetary gear is connectable, characterized in that the N switching elements at least M brakes and NM Couplings include, where M is an integer greater than or equal to one, and that at least (NM) / 2 couplings cooperate with the drive shaft and / or output shaft.
  • the invention solves the tasks also in a motor vehicle, in particular in a passenger or truck with a transmission according to one of claims 1 to 23.
  • switching element is preferably to be understood in the description, in particular in the claims, a device which comprises at least one opened and a closed state, wherein in the open state, the device no torque, and wherein in the closed state, the device can transmit a torque between two devices cooperating with this device or the switching element devices, such as shafts.
  • ring gear shaft is to be understood preferably in the specification, in particular in the claims, as meaning a shaft which is connected to a ring gear of a planetary gear set for transmitting force and torques is connected to a sun gear of a planetary gear set for transmitting power and torques.
  • the majority of the couplings cooperate with the drive shaft. If the majority of the clutches are arranged in the region of the drive shaft, a particularly easy accessibility or accessibility of the clutches from the outside is possible. In addition, these can be arranged in a particularly simple manner in the transmission.
  • a sun shaft is designed as a common sun shaft of at least two planetary gear sets. In this way, a more compact Construction of the gearbox achieved. At the same time, a sufficient number of gear ratios can be represented by the transmission.
  • a ring gear is formed as a common ring gear of at least two planetary gear sets.
  • One of the advantages is that it achieves a sufficiently compact design while at the same time providing sufficient flexibility with regard to the provision of gear ratios by the transmission.
  • the common Hohlradwelle at least two planetary gear sets is designed as a sun shaft for at least one other planetary gear. In this way, a particularly simple and reliable power and torque transmission between two planetary gears and at least one other planetary gear is possible.
  • a ring gear is formed as an output shaft.
  • a reliable transmission of force and torques from the ring gear of one of Planentenrad accounts can be done on the output shaft.
  • the web of at least one planetary gear set is connectable to the housing by means of one of the brakes and / or the web of at least one planetary gear set is fixedly connected to the housing. Due to the fixed connection of the web at least one planetary gear to the housing, a reliable support can be made on the housing. Using a brake, this support can also be repealed, so that the flexibility of the transmission is further increased overall.
  • At least one sun shaft is fixedly connectable to the housing by means of one of the brakes.
  • At least one planetary gear set in particular its ring gear, can be connected to the output shaft by means of at least one clutch.
  • a planetary element of a planetary gear In order to can be connected to the output shaft in a flexible and reliable manner, a planetary element of a planetary gear.
  • the majority of the planetary gear sets in particular at least three quarters of the planetary gear sets, expediently have a negative stand ratio.
  • the ring gear at a fixed web to the sun gear opposite direction of rotation, which allows reliable transmission of power and torque between the sun gear and the ring gear.
  • the force and torque of the drive shaft can be decoupled from further elements of the transmission by means of a clutch, which is arranged torque-up or - down of a planetary element of a planetary gear.
  • the clutch can be arranged according to external requirements at different positions in the transmission, which increases the flexibility of the transmission when installed in different vehicles, and this without this reduces the number of gear stages, which are represented by the transmission, reduced.
  • sun shafts of two planetary gear sets are connectable to a common sun shaft by means of a clutch.
  • This increases the flexibility of the transmission, since, depending on requirements, a second planetary gear can be acted upon with the same sun shaft with force and torque, so that more gear ratios can be displayed.
  • a planetary element of a planetary preferably planetary elements different planetary gear sets, connectable to the output shaft, preferably wherein the planetary element is a ring gear.
  • one or more planetary gear sets are coupled to the output shaft.
  • a web of a planetary gear set with one, in particular common sun shaft connectable is advantageously, by means of at least one coupling.
  • At least one planetary gear set has a positive state ratio.
  • One of the advantages achieved with this is that, for example, with the bridge fixed, the ring gear of the planetary gear set has the same direction of rotation as the sun gear.
  • a planetary element of the planetary gear set in particular its ring gear, with positive stand ratio by means of a coupling with the output shaft connectable. Due to the positive state ratio, for example, the planetary gear set can be coupled by means of the clutch to the output shaft, so that the output shaft has the same direction of rotation as the sun shaft of the planetary gear set.
  • At least two of the M brakes preferably all brakes, interact with planetary elements of a same planetary gearset.
  • the construction space of the transmission can be further reduced and at the same time the accessibility of the brakes can be improved, since these are then located or arranged in the region of the corresponding planetary gear.
  • At least ten gear ratios can be displayed, in particular at least nine forward gears and at least one reverse gear.
  • a sufficient number of forward gear ratios and reverse gear ratios are provided by the transmission, so that the transmission can be used flexibly in a wide variety of vehicles.
  • at least one gear in particular a forward gear by at least two, in particular four different operations of the N switching elements can be displayed. In this way, a redundancy of at least one gear stage is ensured, so that even with a failure of one of the switching elements, the gear can be represented by other switching elements.
  • all brakes of a representation of the at least one gear ratio are open.
  • the wear of the brakes can be reduced because no operation of the brakes must be done when operating this gear.
  • At least one switching element in particular at least half of the switching elements are designed as claw switching elements, preferably comprising at least one brake and at least one clutch. This leads to significant fuel consumption advantages of a motor vehicle provided with the transmission.
  • FIG. 1 shows a transmission according to a first embodiment of the present invention
  • FIG. 2 shows a shift matrix for a transmission according to the first embodiment of the present invention
  • FIG. 10 shows a transmission according to a ninth embodiment of the present invention.
  • Fig. 1 1 shows a transmission according to a tenth embodiment of the present invention; and a transmission according to an eleventh embodiment of the present invention.
  • Fig. 1 shows a transmission according to a first embodiment of the present invention.
  • reference numeral 1 denotes a multi-stage transmission.
  • the multistage transmission 1 has six powershift elements in the form of four clutches K1, K2, K3, K4 and two brakes B1, B2.
  • the drive side can be coupled or connected to the output side of the transmission 1 for the transmission of force and torques.
  • the first clutch K1, the second clutch K2 and the third clutch K3 are connected to the drive shaft ANW on the drive side.
  • the first clutch K1 is further connected to a first shaft W1, so that the clutch, when actuated, transmits power and torque from the drive shaft ANW to the first shaft W1.
  • the second clutch K2 When the second clutch K2 is closed, power is transmitted from the drive shaft ANW to the second shaft W2, and when the third clutch K3 is closed, power and torque are transmitted from the drive shaft ANW to the third shaft W3.
  • the transmission 1 further four planetary gear sets GP1, GP2, GP3 and GP4 and seven waves W1, W2, W3, W4, W5, W6 and W7 are arranged.
  • the general structure of the first planetary gearset GP1, the second planetary gearset GP2 and the fourth planetary gearset GP4 will now be described below.
  • the above-mentioned planetary gear sets GP1, GP2 and GP4 are constructed in a conventional manner and each have a central sun gear 10 which cooperates with one or more planet gears 1 1 for the transmission of force and torques.
  • the one or more planet wheels 1 1 are rotatably mounted on a web 12.
  • a ring gear 13 is arranged, in which the or the planetary gears 1 1 engage for the transmission of force and torques.
  • the web or planet carrier 12 is further connected in each case with a shaft.
  • the structure of the third planetary gear set GP3 is as follows:
  • the third planetary gear set is constructed in the usual way as well as the other planetary gear sets GP1, GP2 and GP4 in a conventional manner and comprises a central sun gear 10, in which at least one planet gear 1 1 a engages.
  • In the first planetary gear 1 1 a now engages at least a second planetary gear 1 1 b for the transmission of force and torques.
  • the planet gears 1 1 a and 1 1 b are rotatably mounted on a common web 12.
  • a ring gear 13 is arranged, in which the or the planetary gears 1 1 b engage.
  • the web 12 or planet carrier is fixedly connected to the housing G of the transmission 1 via the sixth shaft W6.
  • the first shaft W1 connects the first clutch K1 and the bridge of the fourth planetary gear set GP4 for transmitting power and torques.
  • the second shaft W2 connects the second clutch K2 and the ring gear of the second planetary gear set GP2 for transmitting force and torques.
  • the third shaft W3 connects the third clutch K3 with the sun gears 10 of the first planetary gear set GP1 and the second planetary gear set GP2.
  • the fourth wave W4 connects the ring gear of the first planetary gear set GP1 and the land of the second planetary gear set GP2 with the sun gear of the third planetary gear set GP3 and the fourth planetary gear set GP4.
  • the fifth shaft W5 is connected on the one hand via the second brake B2 to the housing G, on the other hand, it is connected to the web of the first planetary GP1.
  • the sixth shaft W6 is fixedly connected to the web of the third planetary GP3 on the one hand and with the housing G on the other hand.
  • the seventh shaft W7 is connected on the one hand to the third shaft W3, on the other hand firmly connected to the housing G via the first brake B1.
  • the output shaft AW is connected on the one hand via a fourth clutch K4 to the ring gear of the third planetary GP3, on the other hand with the ring gear of the fourth planetary GP4.
  • Fig. 2 shows a shift matrix for a transmission according to the first embodiment of the present invention.
  • FIG. 2 shows a switching matrix for a transmission 1 according to FIG. 1.
  • the entries released in the switching matrix indicate that the corresponding switching element or the brake or the clutch is open, i. that the switching element in this case transmits no forces or no torque from the connected to the switching element or connected to this respective shafts or elements of the transmission.
  • An entry in the switching matrix provided with a cross designates a correspondingly actuated or closed switching element, that is to say in the switching matrix, for example in the forward gear stage V1 in the clutch K2 and K4 and in the brake B2.
  • the gear ratio i is 4.398.
  • the gear ratio i is 2.634.
  • the gear ratio i is 1, 819.
  • the gear ratio i is 1, 328.
  • the gear ratio i is 1, 000.
  • the gear ratio i is 0.829.
  • the gear ratio i is 0.719.
  • the gear ratio i is 0.600.
  • the brake B2 and the clutches K1 and K3 are closed.
  • the gear ratio i is 0.506.
  • the brake B2 and the clutches K3 and K4 are closed.
  • the gear ratio i is -3,932.
  • the gear ratio i is 1, 328.
  • the gear gap ⁇ between the first forward gear V1 and the second forward gear V2 is 1, 669, between the second forward gear V2 and the third forward gear V3 1, 448th
  • the gear gap ⁇ between the third forward speed V3 and the fourth forward speed V4 is 1, 370, between the fourth forward speed V4 and the fifth forward speed V5 1, 328.
  • the total jump is 8.685.
  • Fig. 3 shows a transmission according to a second embodiment of the present invention.
  • a transmission 1 according to FIG. 1 is shown.
  • two positions A and B can be seen for the clutch K1, in which the first clutch K1 can be arranged to have the same effect as the position according to FIG.
  • the first alternative position A for the first clutch K1 is between the ring gear of the fourth planetary gear set GP4 and the output shaft AW
  • the second position B for the first clutch K1 is between the sun gear of the third planetary gear set GP3 and the sun gear of the fourth planetary gear set GP4 on the fourth shaft W4, so that ring gear and output shaft and the two sun gears can be coupled to each other by means of the first clutch K1.
  • FIG. 4 a transmission 1 according to FIG. 1 is shown.
  • two positions C and D for the clutch K2 can be seen, in which the second clutch K2 can be arranged with the same effect.
  • the first alternative position C for the second clutch K2 is between the bridge of the second planetary gearset GP2 and the fourth shaft W4
  • the second position D for the second clutch K2 is between the sun gear of the first planetary gearset GP1 and sun gear of the second planetary gearset GP2 on the third shaft W3, so that the bridge and the fourth shaft or the two sun gears can be coupled together.
  • Fig. 5 shows a transmission according to a fourth embodiment of the present invention.
  • the drive shaft ANW is thus directly connected to the web of the fourth planetary gearset GP4 via the first shaft W1.
  • Fig. 6 shows a transmission according to a fifth embodiment of the present invention.
  • the drive shaft ANW is connected directly to the web of the fourth planetary gear set GP4 via the first shaft W1 K1 is disposed on the fourth shaft W4 between the sun gear of the third planetary gear set GP3 and the sun gear of the fourth planetary gear set GP4.
  • Fig. 7 shows a transmission according to a sixth embodiment of the present invention.
  • the second clutch K2 is now at the position C of FIG. 4, now designated by reference K2 ' , arranged.
  • the drive shaft ANW is thus connected via the second shaft W2 directly to the ring gear of the second planetary gearset GP2.
  • the web of the second planetary gear GP2 is connectable via the second clutch K2 with the fourth wave W4.
  • Fig. 8 shows a transmission according to a seventh embodiment of the present invention.
  • Fig. 9 shows a transmission according to an eighth embodiment of the present invention.
  • FIG. 10 shows a transmission according to a ninth embodiment of the present invention.
  • the second clutch K2 is disposed at the position D shown in Fig. 4, here denoted by reference numeral K2 ", thus the second clutch K2" is interposed between the sun gear of the first planetary gear set GP1 and the sun gear of the second planetary gear set GP2 arranged third wave W3 and allows a connection for transmission of force and torque between the sun shaft of the first and second planetary GP1, GP2.
  • Fig. 11 shows a transmission according to a tenth embodiment of the present invention.
  • Fig. 12 shows a transmission according to an eleventh embodiment of the present invention.
  • the transmission 1 comprises four tarpaulin wheel levels GP1, GP2, GP3, GP4, six shift elements B1, B2, K1, K2, K3, K4, the shift elements being in the form of four clutches K1, K2, K3 , K4 and two brakes B1, B2 are formed. Furthermore, a solid housing coupling in Form of the sixth wave W6 available. Finally, two switching elements to be switched at the same time are arranged.
  • a hydrodynamic torque converter As a starting element for the transmission 1, a hydrodynamic torque converter, a hydrodynamic clutch, an additional starting clutch, an integrated starting clutch or brake and / or an additional electric machine can be arranged.
  • an electric machine or other power / power source On each of the shafts W1 to W7, an electric machine or other power / power source can be arranged.
  • a freewheel to the housing G or to another wave W1, W2, W3, W4, W5, W6, W7 are arranged.
  • the transmission 1 can preferably be installed in standard drive construction or in front / transverse design in a motor vehicle. As switching elements frictional and / or positive switching elements are possible.
  • the second brake B2, the second clutch K2 and the fourth clutch K4 can be designed as claw switching elements, which leads to significant fuel consumption advantages of a motor vehicle provided with the transmission.
  • the present invention has the advantage that a low construction cost for the transmission is required, which results in lower manufacturing costs and lower weight of the transmission.
  • the transmission offers a good gear ratio, low absolute and relative speeds as well as low planententate and switching element moments.
  • the present invention provides good gearing efficiencies and a very good accessibility of all switching elements, in particular for their maintenance.
  • the geometric position / sequence of the individual planetary gear sets GP1, GP2, GP3, GP4 and the individual switching elements K1, K2, K3, K4, B1, B2 taking into account the bondability of the respective transmission elements are freely chosen among each other.
  • Individual transmission elements can be moved as desired in their position / position within the transmission 1.

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

Abstract

L'invention concerne une transmission, en particulier une boîte multi-embrayage, pour un véhicule automobile, comprenant les éléments suivants : l'arbre d'entraînement ; plusieurs trains planétaires, un train planétaire comprenant les éléments planétaires suivants : une roue solaire, un ou plusieurs satellites, une barre et une couronne ; N éléments de commande comprenant plusieurs embrayages, N étant un nombre entier supérieur à quatre ; et un arbre de sortie, lequel peut être relié, au moyen d'au moins un des éléments de commande, à l'arbre de sortie pour représenter différents niveaux de rapports au moyen d'au moins un des engrenages planétaires. Les N éléments de commande comprennent au moins M freins et N-M embrayages, M étant un nombre entier supérieur ou égal à un. Et au moins (N-M)/2 embrayages coopèrent avec l'arbre d'entraînement et/ou l'arbre de sortie.
EP14705807.7A 2013-03-27 2014-02-25 Transmission pour un véhicule automobile Withdrawn EP2978997A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013205376.2A DE102013205376A1 (de) 2013-03-27 2013-03-27 Getriebe für ein Kraftfahrzeug
PCT/EP2014/053567 WO2014154410A1 (fr) 2013-03-27 2014-02-25 Transmission pour un véhicule automobile

Publications (1)

Publication Number Publication Date
EP2978997A1 true EP2978997A1 (fr) 2016-02-03

Family

ID=50151308

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14705807.7A Withdrawn EP2978997A1 (fr) 2013-03-27 2014-02-25 Transmission pour un véhicule automobile

Country Status (6)

Country Link
US (1) US20160053868A1 (fr)
EP (1) EP2978997A1 (fr)
JP (1) JP2016514807A (fr)
CN (1) CN105143719A (fr)
DE (1) DE102013205376A1 (fr)
WO (1) WO2014154410A1 (fr)

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DE102013205377A1 (de) * 2013-03-27 2014-10-02 Zf Friedrichshafen Ag Mehrstufen-Planetengetriebe
DE102013205382A1 (de) * 2013-03-27 2014-10-02 Zf Friedrichshafen Ag Getriebe für ein Kraftfahrzeug
JP6064849B2 (ja) * 2013-09-25 2017-01-25 マツダ株式会社 自動変速機
KR101683501B1 (ko) * 2014-12-11 2016-12-07 현대자동차 주식회사 차량용 자동변속기의 유성기어트레인
EP3347622B1 (fr) * 2015-09-09 2021-01-27 Allison Transmission, Inc. Transmission multivitesse
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CN105143719A (zh) 2015-12-09
JP2016514807A (ja) 2016-05-23
WO2014154410A1 (fr) 2014-10-02
US20160053868A1 (en) 2016-02-25

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