EP2841802A1 - Boîte de vitesses multi-étagée - Google Patents

Boîte de vitesses multi-étagée

Info

Publication number
EP2841802A1
EP2841802A1 EP13709419.9A EP13709419A EP2841802A1 EP 2841802 A1 EP2841802 A1 EP 2841802A1 EP 13709419 A EP13709419 A EP 13709419A EP 2841802 A1 EP2841802 A1 EP 2841802A1
Authority
EP
European Patent Office
Prior art keywords
clutch
planetary gear
gear
gear set
web
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Withdrawn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
EP13709419.9A
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 EP2841802A1 publication Critical patent/EP2841802A1/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Withdrawn legal-status Critical Current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
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
    • F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2094—Transmissions using gears with orbital motion using positive clutches, e.g. dog clutches

Definitions

  • the invention relates to a multi-speed planetary gear, in particular for a motor vehicle.
  • Such multistage transmissions are preferably used as automatic transmissions of motor vehicles, wherein the power flow which is effective in the respective gear ratio within the planetary gear sets is defined by a specific actuation of the shifting elements.
  • the planetary gear sets are usually also connected in an automatic transmission with a slipping action underlying and optionally provided with a lock-up clutch starting element, such as about a hydrodynamic torque converter or a fluid coupling.
  • a multi-speed transmission in planetary construction in which four planetary gear sets, and a total of eight rotatable shafts are arranged, one of which represents the drive shaft and another the output shaft of the multi-speed transmission. Furthermore, at least six switching elements are provided in the region of the shafts, by means of whose targeted actuation the power flow within the four planetary gear sets varies and thus different gear ratios between the input and output shafts can be defined. Altogether this means nine forward gears and one reverse gear can be engaged.
  • the object of the invention is to provide an alternative multi-step transmission, preferably with improved efficiency and sufficiently large and sufficiently uniformly distributed translation series.
  • a multistage transmission comprising at least four planetary gear sets, a housing, a drive shaft and an output shaft, wherein a ring gear of a first planetary gear set with a sun gear of a four-wheel drive th planetary gear set is constantly connected,
  • a ring gear of the fourth planetary gear set is continuously connected to the output shaft
  • a sun gear of the first planetary gear set and a web of a second planetary gear set can be coupled to the housing via a first brake
  • a web of the first planetary gear set can be coupled to the housing via a second brake
  • the web with the sun gear, the ring gear with the sun gear or the ring gear with the web of each of the third planetary gear set or the drive shaft with the web of the fourth planetary gear set can be coupled via a first clutch, a ring gear with the sun gear or the ring gear with the web or Sun gear to the web of each of the fourth planetary gear set can be coupled via a second clutch and three of the following five compounds constantly and two of said compounds by means of at least one switching element are designed to be detachable:
  • a planetary gear set is understood to mean, in particular, a wheel set which comprises at least one sun gear, in that one or more planetary gears mesh, a web which determines the axes of the planetary gears and a ring gear in which the planetary gears mesh.
  • the ring gear has an internal toothing and the sun gear has an external toothing.
  • switching element in its respective current operating state, ie open or closed, for example, because short lines and the pressure losses are lower. It is also possible to arrange switching elements on the housing and thus at least partially against rotation, whereby seals which connect a stationary line with a rotating line, can be avoided in whole or in part.
  • the spatial arrangement of the easily accessible switching elements simplifies the replacement of the usual hydraulically actuated multi-plate clutches or - brakes by, for example, electro-mechanical or electro-hydraulically actuated brakes and clutches, which are comparatively easy to use driven.
  • Well achievable switching elements are on the one hand brakes, which rotatably couple a shaft with the housing, but also switching elements on outer shafts of the multi-speed transmission, preferably on input or output shaft, which can be supplied comparatively easy to operate hydraulic fluid.
  • the multi-speed transmission also has a good toothing efficiency, only small loads on the components, in particular low Planetenensatz- and switching element moments, low absolute and relative speeds and / or low construction costs. The latter allows the realization of the multi-speed transmission with only low weight and low cost. Finally, the multi-speed transmission also allows a good translation series, so a well usable gradation of the gears.
  • a preferred embodiment of the multi-speed transmission includes four planetary gear sets, four clutches, two brakes, and no fixed housing coupling. By pressing two switching elements (brakes and / or clutches), nine forward gears and one reverse gear can be shifted, with another alternative shift position being available for the fifth gear. In addition, the transmission allows the circuit of an additional forward gear and an additional reverse gear.
  • a hydrodynamic torque converter As starting elements, a hydrodynamic torque converter, a hydrodynamic clutch, an additional starting clutch, an integrated starting clutch or brake and / or an additional electric motor can be used.
  • an electric motor or another power / power source can be arranged on each shaft.
  • Des shimmerern can be arranged on each shaft in principle a freewheel to the housing or to another shaft.
  • the multi-speed transmission is realized as a standard drive, but also conceivable is a front-transverse construction.
  • All switching elements can act frictionally or positively.
  • the second clutch and / or the fourth clutch in other transmission variants, the fifth or sixth clutch instead of the fourth clutch
  • the fifth or sixth clutch instead of the fourth clutch
  • the fifth or sixth clutch as positive clutches, in particular as jaw clutches executed, resulting in a significantly improved efficiency and thus significant fuel consumption.
  • the second and the fourth clutch must be actuated only once when switching from the first to the ninth gear and therefore that these switching elements are particularly suitable to be designed as a dog clutch. It has thus been further recognized that the advantage of better efficiency outweighs the disadvantage of more difficult handling in these switching elements due to their comparatively rare operation.
  • the geometric position (order) of the individual wheelsets and switching elements is freely selectable, as long as it allows the bindability of the elements. Thus, individual elements can be moved arbitrarily in their position.
  • FIG. 1 shows a first schematically illustrated exemplary variant of a multi-speed transmission according to the invention
  • FIG. 2 shows a second schematically illustrated exemplary variant of a multistage transmission according to the invention
  • FIG. 3 shows a third schematically illustrated exemplary variant of a multistage transmission according to the invention
  • FIG. 4 shows a fourth schematically illustrated exemplary variant of a multistage transmission according to the invention
  • FIG. 5 shows a fifth schematically illustrated exemplary variant of a multistage transmission according to the invention
  • 6 shows a sixth exemplary illustrated variant of a multi-speed transmission according to the invention
  • 7 shows a seventh schematically illustrated exemplary variant of a multi-speed transmission according to the invention
  • FIG. 8 shows an eighth schematically illustrated exemplary variant of a multistage transmission according to the invention.
  • FIG. 9 shows a ninth schematically illustrated exemplary variant of a multistage transmission according to the invention.
  • Fig. 10 shows a tenth schematically illustrated exemplary variant of a multi-speed transmission according to the invention.
  • Fig. 1 1 is a table which indicates the closed switching elements for the transmission variants shown in Figures 1 to 3 in each gear stage.
  • FIG. 1 shows a multi-speed transmission comprising four planetary gear sets 1, 2, 3, 4, a drive shaft 70, an output shaft 71, six further rotatable shafts 73, 74, 75, 76, 77, 78, six switching elements 51, 52, 61, 62, 63, 64, of which two brakes 51, 52 and four clutches 61, 62, 63, 64.
  • the four planetary gear sets 1, 2, 3, 4 are fourth in the order of the first planetary gear set 1, second planetary gear set 2, third planetary gear set 3 Planetary gear 4 arranged one behind the other.
  • the first Planetary gear set 1 is a Plusplanetenradsatz
  • the second planetary gear set 2 the third planetary gear set 3 and the fourth planetary gear set 4 are formed as minus planetary gear set.
  • the planetary gear sets 1, 2, 3, 4, are jointly surrounded by a housing 72.
  • a ring gear 13 of a first planetary gear set 1 is continuously connected to a sun gear 41 of a fourth planetary gear set 4,
  • a ring gear 43 of the fourth planetary gear set 4 is continuously connected to the output shaft 71,
  • a sun gear 1 1 of the first planetary gear set 1 and a web 22 of a second planetary gear set 2 can be coupled to the housing 72 via a first brake 51, a web 12 of the first planetary gear set 1 can be coupled to the housing 72 via a second brake 52,
  • the web 32 of the third planetary gear set 3 or the drive shaft 70 can be coupled to the web 42 of the fourth planetary gear set 4 with the output shaft 70 via a first coupling 61,
  • a ring gear 43 can be coupled to the sun gear 41 of the fourth planetary gearset 4 via a second clutch 62,
  • the drive shaft 70 can be coupled to the sun gear 21 of the second planetary gear set 2 via a third clutch 63,
  • the drive shaft 70 can be coupled to the sun gear 31 of the third planetary gear set 3 via a fourth clutch 64,
  • the ring gear 33 of the third planetary gear set 3 is permanently connected to the web 22 of the second planetary gear set 2,
  • Fig. 2 shows a multi-stage transmission which is very similar to the multi-speed transmission of Fig. 1 and differs in the following points from the embodiment of Fig. 1:
  • the sun gear 41 of the fourth planetary gear set 4 is not connected to the hollow Rad 43 of the fourth planetary gear set 4 but with the web 42 of the fourth planetary gear set 4 via a second clutch 62 coupled.
  • FIG. 3 shows a multi-stage transmission, which is very similar to the multi-stage transmission of FIG. 1 and differs from the embodiment of FIG. 1 in the following points:
  • the ring gear 43 of the fourth planetary gear 4 is not coupled to the sun gear 41 of the fourth planetary gear 4 but with the web 42 of the fourth planetary gear set 4 via a second clutch 62.
  • the variants shown in FIGS. 2 and 3 with regard to the position of the second clutch 62 are also applicable to the following transmission variants. That is, the second clutch 62 is not necessarily arranged between the ring gear 43 and the sun gear 41 in the following transmission variants, but may also be arranged between the sun gear 41 and the web 42 or between the ring gear 43 and the web 41.
  • FIG. 4 shows a multistage transmission, which is very similar to the multistage transmission of FIG. 1 and differs from the embodiment of FIG. 1 in the following points:
  • the drive shaft 70 is permanently connected to the sun gear 31 of the third planetary gear set 3 and
  • the ring gear 33 of the third planetary gear set 3 can be coupled to the web 22 of the second planetary gear set 2 via a fifth clutch 65.
  • FIG. 5 shows a multistage transmission, which is very similar to the multistage transmission of FIG. 4 and differs from the embodiment of FIG. 4 in the following points:
  • the sun gear 31 of the third planetary gear set 3 can not be coupled to the web 32 of the third planetary gear set 3 but to the ring gear 33 of the third planetary gear set 3 via a first clutch 61.
  • Fig. 6 shows a multi-speed transmission, which is the multi-speed transmission 4 is very similar and differs from the embodiment of FIG. 4 in the following points:
  • the web 32 of the third planetary gear set 3 can not be coupled to the sun gear 31 of the third planetary gear set 3 but to the ring gear 33 of the third planetary gear set 3 via a first clutch 61.
  • the variants shown in FIGS. 5 and 6 with regard to the position of the first clutch 61 can also be applied to the transmission variant illustrated in FIG. 9. That is, the first clutch 61 is not necessarily arranged in this transmission variant between the sun gear 31 and the web 32, but may also be arranged between the sun gear 31 and the ring gear 33 or between the ring gear 33 and the web 32.
  • Fig. 7 shows a multi-stage transmission, which is very similar to the multi-stage transmission of Fig. 1 and differs in the following points from the embodiment of Fig. 1:
  • the drive shaft 70 is permanently connected to the sun gear 31 of the third planetary gear set 3 and
  • the web 32 of the third planetary gear set 3 can be coupled to the web 42 of the fourth planetary gear set 4 and the shaft 78 via a sixth clutch 66.
  • FIG. 8 shows a multistage transmission comprising four planetary gear sets 1, 2, 3, 4, a drive shaft 70, an output shaft 71, three further rotatable shafts 73, 74, 75, six shift elements 51, 52, 61, 62, 63, 64 thereof two brakes 51, 52 and four clutches 61, 62, 63, 64.
  • the four planetary gear sets 1, 2, 3, 4 are arranged one behind the other in the order of the first planetary gear set 1, second planetary gear set 2, third planetary gear set 3, fourth planetary gear set 4.
  • the first planetary gear set 1 is a plus planetary gear set
  • the second planetary gear set 2 the third planetary gear set 3 and the fourth planetary gear set 4 are designed as a minus planetary gearset.
  • the planetary gear sets 1, 2, 3, 4, are jointly surrounded by a housing 72.
  • a ring gear 13 of a first planetary gear set 1 is continuously connected to a sun gear 41 of a fourth planetary gear set 4
  • a ring gear 43 of the fourth planetary gear set 4 is continuously connected to the output shaft 71
  • a sun gear 1 1 of the first planetary gear set 1 and a web 22 of a second planetary gear set 2 can be coupled to the housing 72 via a first brake 51, a web 12 of the first planetary gear set 1 can be coupled to the housing 72 via a second brake 52,
  • the drive shaft 70 is continuously connected to the sun gear 21 of the second planetary gear set 2,
  • the drive shaft 70 can be coupled to the sun gear 31 of the third planetary gear set 3 via a fourth clutch 64,
  • the ring gear 33 of the third planetary gear set 3 is permanently connected to the web 22 of the second planetary gear set 2,
  • the ring gear 13 of the first planetary gear set 1 can be coupled to the ring gear 23 of the second planetary gear set 2 via a seventh clutch 67.
  • FIG. 9 shows a multistage transmission, which is very similar to the multistage transmission of FIG. 8 and differs from the embodiment of FIG. 8 in the following points:
  • the drive shaft 70 is permanently connected to the sun gear 31 of the third planetary gear set 3 and
  • FIG. 10 shows a multistage transmission, which is very similar to the multistage transmission of FIG. 8 and differs from the embodiment of FIG. 8 in the following points:
  • the drive shaft 70 is permanently connected to the sun gear 31 of the third planetary gear set 3 and
  • the web 32 of the third planetary gear set 3 can be coupled to the web 42 of the fourth planetary gear set 4 and the shaft 78 via a sixth clutch 66.
  • a first gear can be realized by the closed first brake 51, the closed second clutch 62 and the closed fourth clutch 64.
  • a second gear can be realized by the closed first brake 51, the closed second brake 52 and the closed fourth clutch 64.
  • a third gear can be realized by the closed first brake 51, the closed third clutch 63 and the closed fourth clutch 64.
  • a fourth gear can be realized by the closed second brake 52, the closed third clutch 63 and the closed fourth clutch 64.
  • a fifth gear is through the closed first clutch 61, the closed third clutch 63 and the closed fourth clutch 64, or
  • a sixth gear can be realized by the closed second brake 52, the closed first clutch 61 and the closed fourth clutch 64.
  • a seventh gear can be realized by the closed second brake 52, the closed first clutch 61 and the closed third clutch 63.
  • An eighth gear can be realized by the closed first brake 51, the closed second brake 52 and the closed first clutch 61.
  • a ninth gear can be realized by the closed first brake 51, the closed first clutch 61 and the closed third clutch 63.
  • a reverse gear can be realized by the closed first brake 51, the closed second clutch 62 and the closed third clutch 63.
  • An additional forward gear is provided by the closed second brake 52, which is closed.
  • second clutch 62 and the closed third clutch 63 feasible.
  • An additional return gear can be realized by the closed second brake 52, the closed second clutch 62 and the closed fourth clutch 64.
  • the shift positions of the multi-speed transmission illustrated in FIG. 7 are similar to those of the multi-speed transmission shown in FIGS. 1 to 3, but the sixth clutch 66 takes the place of the fourth clutch 64.
  • the shift positions of the multi-speed transmission illustrated in FIG. 8 are similar to those of the multi-speed transmission shown in FIGS. 1 to 3, but the seventh clutch 67 replaces the third clutch 63.
  • the shift positions of the multi-speed transmission illustrated in FIG. 9 are similar to those of the multi-speed transmission shown in FIG. 8, but the fifth clutch 65 replaces the fourth clutch 64.
  • the shift positions of the multi-speed transmission shown in FIG. 10 are quite similar to those of the multi-speed transmission shown in FIG. 8, but the sixth clutch 66 takes the place of the fourth clutch 64.
  • the first wheel set 1 is designed as a plus wheel set and the remaining wheel sets 2, 3, 4 as minus wheel sets.
  • the transmission ratio is:
  • this wheelset 1, 2, 3, 4 instead of a minus wheel as a plus wheel or instead as plus wheel as a negative wheel is executed.
  • connection / couplings to the web 12, 22, 32, 42 and the ring gear 13, 23, 33, 43 of a wheelset 1, 2, 3, 4 exchanged and the direction of rotation between the sun gear 1 1, 21, 31, 41 and ring gear 13, 23, 33, 43 of this wheel 1, 2, 3, 4 vice versa.
  • the connection / coupling between the individual transmission elements can be changed without changing the characteristics of the transmission.
  • the mentioned permutation of the connection / coupling is not limited to a wheelset 1, 2, 3, 4, but can also be applied to several wheelsets 1, 2, 3, 4 at the same time.

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 à quatre étages, selon laquelle : une couronne (13) d'un premier train planétaire (1) est reliée à un pignon (41) d'un quatrième train planétaire (4) ; une couronne (43) du quatrième train planétaire (4) est reliée à l'arbre de sortie (71) ; un pignon (11) du premier train planétaire (1) et un porte-satellites (22) d'un deuxième planétaire (2) peuvent être accouplés au carter (72) par l'intermédiaire d'un premier frein (51) , un porte-satellites (12) du premier train planétaire (1) peut être accouplé au carter (72) par l'intermédiaire d'un deuxième frein (52) ; l'arbre d'entrée (70) peut être accouplé au porte-satellites (42) du quatrième train planétaire (4) par l'intermédiaire d'un premier embrayage (61) ; et une couronne (43) peut être accouplée au pignon (41) du quatrième train planétaire (4) par l'intermédiaire d'un deuxième embrayage (62). La variation d'autres accouplements à l'intérieur de la boîte de vitesses multi-étage permet d'obtenir un ensemble de boîtes de vitesses aux propriétés semblables.
EP13709419.9A 2012-04-27 2013-03-13 Boîte de vitesses multi-étagée Withdrawn EP2841802A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012207081.8A DE102012207081B4 (de) 2012-04-27 2012-04-27 Mehrstufengetriebe
PCT/EP2013/055058 WO2013159989A1 (fr) 2012-04-27 2013-03-13 Boîte de vitesses multi-étagée

Publications (1)

Publication Number Publication Date
EP2841802A1 true EP2841802A1 (fr) 2015-03-04

Family

ID=47884322

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13709419.9A Withdrawn EP2841802A1 (fr) 2012-04-27 2013-03-13 Boîte de vitesses multi-étagée

Country Status (5)

Country Link
US (1) US9194464B2 (fr)
EP (1) EP2841802A1 (fr)
CN (1) CN104204611B (fr)
DE (1) DE102012207081B4 (fr)
WO (1) WO2013159989A1 (fr)

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DE102014217054B4 (de) * 2014-08-27 2021-09-30 Zf Friedrichshafen Ag Planetengetriebe
KR101664595B1 (ko) 2014-11-26 2016-10-11 현대자동차주식회사 차량용 다단 변속기
KR101655581B1 (ko) 2014-11-26 2016-09-08 현대자동차주식회사 차량용 다단 변속기
KR101655585B1 (ko) 2014-11-26 2016-09-08 현대자동차주식회사 차량용 다단 변속기
KR101664598B1 (ko) 2014-11-26 2016-10-11 현대자동차주식회사 차량용 다단 변속기
KR101664599B1 (ko) * 2014-11-26 2016-10-12 현대자동차주식회사 차량용 다단 변속기
KR101664616B1 (ko) 2014-12-10 2016-10-12 현대자동차주식회사 차량용 다단 변속기
DE102015223297A1 (de) * 2015-11-25 2017-06-01 Zf Friedrichshafen Ag Getriebe für ein Kraftfahrzeug, sowie Antriebsstrang für ein Kraftfahrzeug mit einem solchen Getriebe
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US10364867B2 (en) 2016-09-28 2019-07-30 Allison Transmission, Inc. Multi-speed planetary transmission
US10473190B2 (en) 2016-09-28 2019-11-12 Allison Transmission, Inc. Multi-speed planetary transmission
US10174814B2 (en) 2016-09-28 2019-01-08 Allison Transmission, Inc. Multi-speed planetary transmission
US10451147B2 (en) 2016-09-28 2019-10-22 Allison Transmission, Inc. Multi-speed planetary transmission
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WO2013159989A1 (fr) 2013-10-31
CN104204611A (zh) 2014-12-10
US9194464B2 (en) 2015-11-24
DE102012207081A1 (de) 2013-10-31
DE102012207081B4 (de) 2021-07-01
US20150094185A1 (en) 2015-04-02

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