EP2841806A1 - Boîte de vitesses multi-étagée - Google Patents

Boîte de vitesses multi-étagée

Info

Publication number
EP2841806A1
EP2841806A1 EP13709881.0A EP13709881A EP2841806A1 EP 2841806 A1 EP2841806 A1 EP 2841806A1 EP 13709881 A EP13709881 A EP 13709881A EP 2841806 A1 EP2841806 A1 EP 2841806A1
Authority
EP
European Patent Office
Prior art keywords
planetary gear
clutch
gear set
shaft
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Withdrawn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
EP13709881.0A
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 EP2841806A1 publication Critical patent/EP2841806A1/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Withdrawn legal-status Critical Current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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2064—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using at least one positive clutch, e.g. dog clutch
    • 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 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 12 480 B4 of the Applicant. It comprises three single planetary gear sets and three brakes and two clutches for shifting six forward gears and one reverse gear, a drive shaft and an output shaft, wherein the web of the first planetary gear set with the ring gear of the second planetary gear set and the bridge of the second planetary gear set with the ring gear of the third Planetenradsatzes is constantly connected and the drive shaft is connected directly to the sun gear of the second planetary gear set.
  • the drive shaft via the first clutch to the sun gear of the first planetary gear and the second clutch to the web of the first planetary gear set is connectable, wherein the sun gear of the first planetary gear set via the first brake with a housing of the transmission is connectable and the web of the first planetary gear set via the second brake to the housing of the transmission is connectable, wherein the sun gear of the third planetary gear set via the third brake to the housing of the transmission is connectable.
  • the output shaft of the transmission is permanently connected to the web of the third planetary gear set and the ring gear of the first planetary gear set.
  • 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.
  • 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 as drive shaft, output shaft, third, fourth, fifth, sixth, seventh and eighth shaft
  • 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 by means of the third shaft via a first brake to a housing of the transmission is coupled and releasably connectable via a second clutch to the drive shaft, wherein the ring gear of second planetary gear set 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 switching elements of such executed multi-step transmission which are usually designed as multi-plate clutches or brakes, hydraulically actuated, which disadvantageously to high hydraulic see losses leads.
  • the use of demand-actuated switching elements would be particularly advantageous.
  • switching elements are understood in which the maintenance of the switching state requires little or no energy compared to the change of a switching state, so for example. from an open switching state to a closed switching state or from a closed to an open switching state.
  • the switching elements in particular the clutches should be easily accessible from the outside.
  • the present invention has for its object to propose a multi-speed transmission of the type mentioned, which has nine forward gears and one reverse gear with sufficient translation, in which the construction cost, component load and size are optimized and also the efficiency is improved. Furthermore, the switching elements of the transmission should be easily accessible from the outside, whereby the installation of demand-actuated switching elements is made possible. In addition, the transmission should be suitable for both a standard and a front-transverse construction.
  • a multi-speed transmission which has a drive and an output, which are arranged in a housing. Furthermore, at least four planetary gear sets, hereinafter referred to as the first, second, third and fourth planetary gear set, eight rotatable shafts - hereinafter referred to as drive shaft, output shaft, third, fourth, fifth, sixth, seventh and eighth shaft - and six preferably as a lamellae switching elements or executed as a form-locking switching elements 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, second, third and fourth planetary gear set eight rotatable shafts - hereinafter referred to as drive shaft, output shaft, third, fourth, fifth, sixth, seventh and eighth shaft - and six preferably as a lamellae switching elements or executed as a form-locking switching elements
  • Switching elements comprising brakes and clutches, provided, the selective intervention causes different
  • the planetary gear sets of the transmission are preferably designed as negative planetary gear sets.
  • 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 direction of rotation when the web is held on as the sun gear and there is a positive stationary gear ratio.
  • the sun gear of the first planetary gear is connected to the fifth shaft, which is coupled via a third brake to the housing, wherein the drive shaft via a first clutch to the fourth shaft is detachably connected, which with the ring gear of the first Planetenradsatzes and the web of the second planetary gear set and coupled via a second brake to the housing can be coupled.
  • the drive shaft via a second clutch with the connected to the web of the fourth planetary and the ring gear of the third planetary gear seventh shaft is releasably connectable and connected via a third clutch with the connected to the sun gear of the second planetary eighth shaft releasably connectable.
  • the sixth shaft is connected to the bridge of the first planetary gear set, the ring gear of the second planetary gear set and the ring gear of the fourth planetary gear set, the third shaft connected to the sun gear of the third planetary gear set and the sun gear of the fourth planetary gear set and to the housing via a first brake can be coupled; the output shaft of the transmission is connected to the web of the third planetary gear set.
  • switching elements of the transmission can be used as u.a. be executed hydraulically actuated switching elements.
  • the construction cost is significantly reduced with the multi-stage transmission according to the invention by a small number of switching elements.
  • a switching element which is actuated in the first forward gear and in reverse is suitable.
  • the multistage transmission according to the invention, a good efficiency in the main drives with respect to the drag and gear losses.
  • there are low torques in the switching elements and in the planetary gear sets of the multi-speed transmission whereby the wear in the multi-speed transmission is advantageously reduced.
  • a correspondingly small dimensioning is made possible by the low torques, whereby the required space and the corresponding costs are reduced.
  • 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 is a schematic view of a first preferred embodiment of a multi-speed transmission according to the invention
  • FIG. 2 shows an exemplary circuit diagram for a multistage transmission according to FIG. 1;
  • Figure 3 is a schematic view of another embodiment of a multi-speed transmission according to the invention.
  • FIG. 4 shows an exemplary circuit diagram for a multistage transmission according to FIG. 3;
  • Figure 5 is a schematic view of two further embodiments of a multi-speed transmission according to the invention.
  • FIG. 6 shows a schematic view of a further embodiment of a multistage transmission according to the invention
  • FIG. 7 shows an exemplary circuit diagram for a multistage transmission according to FIG. 6.
  • FIG. 1 shows a multi-speed transmission according to the invention with a drive shaft 1, an output shaft 2 and four planetary gear sets P1, P2, P3 and P4, which are arranged in a housing G.
  • the planetary gear sets P1, P2, P3, P4 are formed in the example shown in Figure 1 as negative planetary gear sets.
  • at least one of the planetary gear sets P1, P2, P3, P4 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 P1, P2, P3, P4 axially arranged in the order of the first planetary gear set P1, second planetary gear set P2, third planetary gear set P3, fourth planetary gear set P4.
  • the axial order of the individual planetary gear sets and the arrangement of the switching elements are freely selectable, as long as it allows the binding of the elements.
  • switching elements namely three brakes 03, 04, 05 and three clutches 14, 17, 18 are provided.
  • the spatial arrangement of the switching elements can be arbitrary and is limited only by the dimensions and the external shape.
  • the clutches and the brakes of the transmission are preferably designed as Reibschaltemia or lamellar switching elements, but can also be designed as a form-locking switching elements.
  • the multi-speed transmission according to the invention has a total of eight rotatable shafts, namely the waves 1, 2, 3, 4, 5, 6, 7 and 8, wherein the drive shaft, the first shaft 1 and the output shaft form the second shaft 2 of the transmission.
  • the sun gear of the first planetary gear set P1 is connected to the fifth shaft 5, which is coupled via a third brake 05 to the housing G, wherein the drive shaft 1 via a first clutch 14 with the fourth Shaft 4 is releasably connectable, which is connected to the ring gear of the first planetary gear set P1 and the web of the second planetary gear set P2 and can be coupled via a second brake 04 to the housing G.
  • the sixth shaft 6 is connected to the web of the first planetary gear set P1, the ring gear of the second planetary gear P2 and the ring gear of the fourth planetary gear set P4, wherein the third shaft 3 with the sun gear of the third planetary gear set P3 and the sun gear of the fourth Planetary gear set P4 is connected and can be coupled via a first brake 03 to the housing G and wherein the output shaft 2 of the transmission is connected to the web of the third planetary gear set P3.
  • the first brake 03 is suitable for execution as a claw switching element, whereby the consumption is significantly improved.
  • FIG. 2 shows an exemplary circuit diagram of a multistage transmission according to FIG.
  • the shift pattern can be the respective ratios i of the individual gear ratios and the gear jumps or step increments ⁇ to be determined therefrom
  • the higher gear is taken as an example, with the value 9.001 representing the spread of the gearbox.
  • the first forward gear is obtained by closing the first and third brakes 03, 05 and the third clutch 18, the second forward gear by closing the first and third brakes 03, 05 and the first clutch 14, the third forward gear by Closing the first brake 03 and the first and third clutches 14, 18, the fourth forward gear by closing the first brake 03 and the first and second clutches 14, 17, the fifth forward gear in the example shown executed by direct closing the first, second and third clutches 14, 17, 18, the sixth forward gear by closing the third brake 05 and the first and second clutches 14, 17, the seventh forward gear by closing the third brake 05 and the second and third Clutch 17, 18, the eighth forward gear by closing the second and third brakes 04, 05 and the second clutch 17 and the ninth forward speed is obtained by closing the second brake 04 and the second and third clutch 17, 18, wherein the reverse gear by closing the first and second brake 03, 04 and the third clutch 18 results.
  • the fourth forward gear can be switched by further switching combinations, which are designated in Figure 2 with M. Accordingly, the fourth forward speed can be achieved by closing the first and second brakes 03, 04 and the second clutch 17 or by closing the first brake 03 and the second and third clutches 17, 18 or by closing the first and third brakes 03, 05 and the second coupling 17 result. Characterized in that the first, second and third brake 03, 04, 05 and the third clutch 18 are closed in the first forward gear and / or in reverse, these switching elements can be used as starting elements.
  • FIG. 3 is a further embodiment of the invention, which differs from the exemplary embodiment according to FIG. 1 in that the third clutch 18 is replaced by a fourth clutch 68, which has the eighth shaft 8 connected to the ring gear of the second planetary gearset P2 with the sixth Shaft 6 releasably connects, wherein the drive shaft 1 is connected to the sun gear of the second planetary gear set P2.
  • the first clutch 14 By closing the first clutch 14, the second planetary gear set P2 is blocked.
  • the circuit diagram corresponding to this embodiment is shown in Figure 4, wherein the value 9 represents the spread of the transmission.
  • the values for the stationary gear ratios of the planetary gear sets P1, P2, P3, P4 designed as minus planetary gear sets are -2.317, -2.050, -2.863 and -3.022 in the example shown.
  • the first forward gear is obtained by closing the first and third brakes 03, 05 and the fourth clutch 68, the second forward gear by closing the first and third brakes 03, 05 and the first clutch 14, the third forward gear by Closing the first brake 03 and the first and fourth clutches 14, 68, the fourth forward gear by closing the first brake 03 and the first and second clutches 14, 17, the fifth forward gear in the example shown executed by direct closing the first, second and fourth clutches 14, 17, 68, the sixth forward gear by closing the third brake 05 and the first and second clutches 14, 17, the seventh forward gear by closing the third brake 05 and the second and fourth Coupling 17, 68, the eighth forward gear by closing the second and third brakes 04, 05 and the second clutch 17 and the ninth forward speed is obtained by closing the second brake 04 and the second and fourth clutch 17, 68, wherein the reverse by closing the first and second brake 03, 04 and the fourth clutch 68 results.
  • the fourth forward gear can be switched by further switching combinations, which are designated in Figure 4 with M. Accordingly, the fourth forward speed can be achieved by closing the first and second brakes 03, 04 and the second clutch 17 or by closing the first brake 03 and the first and second clutches 14, 17 or by closing the first and third brakes 03, 05 and the second coupling 17 result.
  • the second planetary gear set P2 can be blocked by a detachable connection of the sun gear with the ring gear or the land with the ring gear.
  • the example shown in the left part of Figure 5 differs from the embodiment of Figure 3 in that the first clutch 14 and thus the detachable connection between the drive shaft 1 and the fourth shaft 4 is omitted, the first clutch 14 by a fifth clutch 18 '. is replaced, which connects the drive shaft 1 releasably connected to the eighth shaft 8 connected to the ring gear of the second planetary gear set P2.
  • the fifth clutch 18 ' By closing the fifth clutch 18 ', the second planetary gearset P2 is locked by the connection of the sun gear with the ring gear.
  • the circuit diagram corresponding to this embodiment corresponds to the circuit diagram of Figure 4, wherein the first clutch 14 is replaced by the fifth clutch 18 '.
  • the embodiment shown in the right part of Figure 5 differs from the embodiment of Figure 3 in that the first clutch 14 and thus the detachable connection between the drive shaft 1 and the fourth Wel- le 4 is omitted, the first clutch 14 is replaced by a sixth clutch 48, which connects the fourth shaft 4 with the connected to the ring gear of the second planetary gear set P2 eighth shaft 8 releasably. By closing the sixth clutch 48, the second planetary gear set P2 is blocked by the connection of the web with the ring gear.
  • the circuit diagram corresponding to this embodiment corresponds to the circuit diagram of Figure 4, wherein the first clutch 14 is replaced by the sixth clutch 48.
  • Figure 6 is another embodiment of a multi-speed transmission according to the invention, which differs from the embodiment of Figure 1 in that the third clutch 18 is replaced by a seventh clutch 48 ', which connected to the web of the second planetary gear P2 eighth shaft 8 with the fourth shaft 4 releasably connects, wherein the drive shaft 1 is connected to the sun gear of the second planetary gear set P2.
  • the circuit diagram corresponding to this embodiment is shown in Figure 7, wherein the value 9 represents the spread of the transmission.
  • the values for the stationary gear ratios of the planetary gear sets P1, P2, P3, P4 designed as minus planetary gear sets are -2.317, -2.050, -2.863 and -3.022 in the example shown.
  • the circuit diagram corresponds to the circuit diagram of Figure 4 with the difference that the fourth clutch 68 is replaced by the seventh clutch 48 '.
  • an axle differential and / or a distributor differential can be arranged on the drive side or on the output side.
  • the drive shaft 1 separated by a coupling element of a drive motor as needed be used as a coupling element, a hydrodynamic converter, a hydraulic clutch, a dry starting clutch, a wet starting clutch, a magnetic powder clutch or a centrifugal clutch or the like. 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 e.g. Multi-plate clutches, band brakes and / or cone clutches are 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. Designation of the first shaft, drive shaft

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

Abstract

Boîte de vitesses multi-étagée comprenant quatre trains planétaires (P1, P2, P3, P4), huit arbres rotatifs (1, 2, 3, 4, 5, 6, 7, 8) et six éléments de commande (03, 04, 05, 14, 17, 8) ; le pignon du premier train planétaire (P1) étant relié au cinquième arbre (5), lequel peut être accouplé au carter (G) par l'intermédiaire d'un troisième frein (05) ; l'arbre d'entrée (1) pouvant être relié de manière libérable par l'intermédiaire d'un premier embrayage (14) au quatrième arbre (4), lequel est relié à la couronne planétaire du premier train planétaire (P1) et au porte-satellites du deuxième train planétaire (P2) et peut être accouplé au carter (G) par l'intermédiaire d'un deuxième frein (04) ; l'arbre d'entrée (1) pouvant être relié de manière libérable par l'intermédiaire d'un deuxième embrayage (17) au septième arbre (7), lequel est relié au porte-satellites du quatrième train planétaire (P4) et à la couronne planétaire du troisième train planétaire (P3), et pouvant être relié par l'intermédiaire d'un troisième embrayage (18) au huitième arbre (8) qui est relié au pignon du deuxième train planétaire (8) ; le sixième arbre (6) étant relié au porte-satellites du premier train planétaire (P1), à la couronne planétaire du deuxième train planétaire (P2) et à la couronne planétaire du quatrième train planétaire (P4) ; le troisième arbre (3) étant relié au pignon du troisième train planétaire (P3) et au pignon du quatrième train planétaire (P4), et pouvant être accouplé par l'intermédiaire d'un premier frein (03) au carter (G) ; l'arbre de sortie (2) de la boîte de vitesses étant relié au porte-satellites du troisième train planétaire (3).
EP13709881.0A 2012-04-25 2013-03-13 Boîte de vitesses multi-étagée Withdrawn EP2841806A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012206819A DE102012206819A1 (de) 2012-04-25 2012-04-25 Mehrstufengetriebe
PCT/EP2013/055076 WO2013160000A1 (fr) 2012-04-25 2013-03-13 Boîte de vitesses multi-étagée

Publications (1)

Publication Number Publication Date
EP2841806A1 true EP2841806A1 (fr) 2015-03-04

Family

ID=47891693

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13709881.0A Withdrawn EP2841806A1 (fr) 2012-04-25 2013-03-13 Boîte de vitesses multi-étagée

Country Status (5)

Country Link
US (1) US9599195B2 (fr)
EP (1) EP2841806A1 (fr)
CN (1) CN104246293B (fr)
DE (1) DE102012206819A1 (fr)
WO (1) WO2013160000A1 (fr)

Families Citing this family (35)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012218687B4 (de) * 2012-10-15 2021-09-30 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102013205377A1 (de) * 2013-03-27 2014-10-02 Zf Friedrichshafen Ag Mehrstufen-Planetengetriebe
KR101655656B1 (ko) * 2015-03-05 2016-09-08 현대자동차주식회사 차량용 다단 변속기
KR101684523B1 (ko) * 2015-05-13 2016-12-08 현대자동차 주식회사 차량용 자동변속기의 유성기어트레인
CN105114559A (zh) * 2015-08-20 2015-12-02 肇庆学院 九速自动变速器
CN107949726B (zh) 2015-09-09 2021-05-14 沃尔沃建筑设备公司 用于车辆的变速器设备
WO2017044019A1 (fr) * 2015-09-09 2017-03-16 Volvo Construction Equipment Ab Agencement de transmission pour un véhicule
WO2017044020A1 (fr) 2015-09-09 2017-03-16 Volvo Construction Equipment Ab Agencement de transmission pour un véhicule
KR101807051B1 (ko) 2016-02-03 2017-12-08 현대자동차 주식회사 차량용 자동변속기의 유성기어트레인
KR101807136B1 (ko) * 2016-02-03 2017-12-07 현대자동차 주식회사 차량용 자동변속기의 유성기어트레인
US10473190B2 (en) 2016-09-28 2019-11-12 Allison Transmission, Inc. Multi-speed planetary transmission
US10253850B2 (en) 2016-09-28 2019-04-09 Allison Transmission, Inc. Multi-speed planetary transmission
US10072735B2 (en) 2016-09-28 2018-09-11 Allison Transmission, Inc. Multi-speed planetary transmission
US10316940B2 (en) 2016-09-28 2019-06-11 Allison Transmission, Inc. Multi-speed planetary transmission
US10234001B2 (en) 2016-09-28 2019-03-19 Allison Transmission, Inc. Multi-speed planetary transmission
US10174814B2 (en) 2016-09-28 2019-01-08 Allison Transmission, Inc. Multi-speed planetary transmission
US9933045B1 (en) 2016-09-28 2018-04-03 Allison Transmission, Inc. Multi-speed planetary transmission
US10060512B2 (en) 2016-09-28 2018-08-28 Allison Transmission, Inc. Multi-speed planetary transmission
US10260599B2 (en) 2016-09-28 2019-04-16 Allison Transmission, Inc. Multi-speed planetary transmission
US10451147B2 (en) 2016-09-28 2019-10-22 Allison Transmission, Inc. Multi-speed planetary transmission
US10323722B2 (en) 2016-09-28 2019-06-18 Allison Transmission, Inc. Multi-speed planetary transmission
US10161486B2 (en) * 2016-09-28 2018-12-25 Allison Transmission, Inc. Multi-speed planetary transmission
US10156283B2 (en) 2016-09-28 2018-12-18 Allison Transmission, Inc. Multi-speed planetary transmission
US10323723B2 (en) 2016-09-28 2019-06-18 Allison Transmission, Inc. Multi-speed planetary transmission
US10364867B2 (en) 2016-09-28 2019-07-30 Allison Transmission, Inc. Multi-speed planetary transmission
US10533644B2 (en) 2016-09-28 2020-01-14 Allison Transmission, Inc. Multi-speed planetary transmission
US10161484B2 (en) 2016-09-28 2018-12-25 Allison Transmission, Inc. Multi-speed planetary transmission
US10060511B2 (en) 2016-09-28 2018-08-28 Allison Transmission, Inc. Multi-speed planetary transmission
US10302173B2 (en) 2016-09-28 2019-05-28 Allison Transmission, Inc. Multi-speed planetary transmission
US10072736B2 (en) 2016-09-28 2018-09-11 Allison Transmission, Inc. Multi-speed planetary transmission
KR102322263B1 (ko) * 2017-08-30 2021-11-04 현대자동차 주식회사 차량용 자동변속기의 유성기어트레인
KR102474354B1 (ko) * 2017-09-12 2022-12-05 현대자동차 주식회사 차량용 자동변속기의 유성기어트레인
KR102463190B1 (ko) * 2017-11-02 2022-11-03 현대자동차 주식회사 차량용 자동변속기의 유성기어트레인
CN113074222A (zh) * 2021-03-23 2021-07-06 中国北方车辆研究所 四自由度多挡位复合行星变速机构
CN113074223A (zh) * 2021-03-23 2021-07-06 中国北方车辆研究所 履带车辆用四自由度多挡行星变速机构

Family Cites Families (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5623059B2 (fr) 1973-12-21 1981-05-28
DE2936969A1 (de) 1979-09-13 1981-04-02 Daimler-Benz Ag, 7000 Stuttgart Planetenraeder-gangwechselgetriebe mit einem vorschalt- und einem hauptgetriebe fuer fahrzeuge
DE19912480B4 (de) 1999-03-22 2006-03-16 Zf Friedrichshafen Ag Automatisch schaltbares Kraftfahrzeuggetriebe
DE10115995A1 (de) 2001-03-30 2002-10-10 Zahnradfabrik Friedrichshafen Mehrstufengetriebe
JP2005098433A (ja) 2003-09-26 2005-04-14 Kyowa Metal Work Co Ltd 多段変速遊星歯車列
JP2005172123A (ja) 2003-12-11 2005-06-30 Kyowa Metal Work Co Ltd 多段変速遊星歯車列
DE102005010210A1 (de) 2005-03-05 2006-09-14 Zf Friedrichshafen Ag Mehrstufengetriebe
JP2006349153A (ja) 2005-06-14 2006-12-28 Hiroki Kawana ９速自動変速機のギヤトレーン
DE102005032001A1 (de) * 2005-07-08 2007-02-01 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102006006637B4 (de) 2006-02-14 2015-02-19 Zf Friedrichshafen Ag Mehrstufengetriebe
US7686730B2 (en) * 2006-11-09 2010-03-30 Ford Global Technologies, Llc Multiple speed automatic transmission
CN101265958B (zh) * 2007-06-07 2010-11-17 黄庆培 多级变速器
US7731625B2 (en) * 2007-07-09 2010-06-08 Gm Global Technology Operations, Inc. 9-speed transmission
US7695398B2 (en) 2007-07-09 2010-04-13 Gm Global Technology Operations, Inc. 9-speed transmission
US7946948B2 (en) 2008-01-31 2011-05-24 GM Global Technology Operations LLC 9-speed transmission
US8038565B2 (en) 2008-02-18 2011-10-18 GM Global Technology Operations LLC Multi-speed transmission
DE102008000429A1 (de) 2008-02-28 2009-09-03 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102008000428A1 (de) 2008-02-28 2009-09-03 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102008041195B4 (de) 2008-08-13 2017-11-30 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102009019046A1 (de) 2009-04-28 2010-11-04 Daimler Ag Getriebevorrichtung
DE102009020442A1 (de) 2009-05-08 2010-11-11 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Getriebe zur Realisierung von mindestens neun Vorwärtsgängen
DE102009028670A1 (de) * 2009-08-20 2011-02-24 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102009028710B4 (de) * 2009-08-20 2019-08-29 Zf Friedrichshafen Ag Mehrstufengetriebe
US8512196B2 (en) * 2010-09-13 2013-08-20 GM Global Technology Operations LLC Multi-speed transmission

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2013160000A1 *

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US20160084353A1 (en) 2016-03-24
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