EP2864668A1 - Boîte de vitesses multi-étagée - Google Patents

Boîte de vitesses multi-étagée

Info

Publication number
EP2864668A1
EP2864668A1 EP13723097.5A EP13723097A EP2864668A1 EP 2864668 A1 EP2864668 A1 EP 2864668A1 EP 13723097 A EP13723097 A EP 13723097A EP 2864668 A1 EP2864668 A1 EP 2864668A1
Authority
EP
European Patent Office
Prior art keywords
planetary gear
clutch
closing
brake
gear set
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Withdrawn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
EP13723097.5A
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 EP2864668A1 publication Critical patent/EP2864668A1/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Withdrawn legal-status Critical Current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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0073—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eleven 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
    • 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, in the prior art, planetary gear sets that are switched by means of friction elements, such as clutches and brakes, and usually with a slip element and optionally a lockup clutch, such as a hydrodynamic torque converter or a fluid coupling connected.
  • friction elements such as clutches and brakes
  • slip element such as clutches and brakes
  • lockup clutch such as a hydrodynamic torque converter or a fluid coupling connected.
  • A1 discloses a transmission arrangement of an automatic transmission for a vehicle comprising ten forward gears, which has a first planetary gear, which is designed as a simple planetary gear and a first rotary element, which acts as a fixed element, a second rotary element, the one reduced rotational speed provides, and a third rotary element, which is directly connected to an input shaft and has as input element acts.
  • the known transmission further comprises a second simple planetary gear, which is a fourth rotary member, which is directly connected to the second rotary member, a fifth rotary member which is selectively connected by inserting a first brake with a transmission housing and a sixth rotary member, optionally by inserting a second brake is connected to a transmission housing, wherein a first clutch selectively connects at least two rotational elements of the fourth, fifth and sixth rotational elements.
  • a third of a planetary gear with a single pinion and a planetary gear with double pinion planetary gear is provided, which is a seventh rotary member which is directly connected to the sixth rotary member, an eighth rotary member which is selectively connected by inserting a second clutch to the drive shaft and selectively connected to the transmission housing by inserting a third brake, a ninth rotary element connected to an output shaft, and a tenth rotary element connected to the fourth rotary element by inserting a third clutch, wherein a fourth clutch is interposed between the third Seventh rotary element and the eighth rotary element is arranged.
  • the present invention has for its object to propose a multi-speed transmission of the type mentioned, which has at least eleven forward gears and a reverse gear and a high spread, in which the construction cost, component load and size are optimized and also the efficiency in terms of drag and Gear losses is improved.
  • This object is achieved by the features of claim 1. Further advantages and advantageous embodiments will become apparent from the dependent claims.
  • a multi-speed transmission according to the invention is proposed in planetary construction, 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 eleven forward gears and one reverse gear can be realized.
  • the planetary gear sets of the transmission are preferably designed as negative planetary gear sets.
  • the ring gear at a fixed web has a direction of rotation opposite to the sun and it results in a negative stationary gear ratio.
  • 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, all inner planetary gears mesh with the sun gear and all outer planet gears with the ring gear, each inner planetary gear, each with 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 set is connected to the seventh shaft, which via a first clutch with the third shaft solves bar is connected, which is connected to the sun gear of the second planetary gear set and the web of the third planetary gear and coupled via a first brake to the housing.
  • the seventh shaft is also detachably connectable via a second clutch with the fifth shaft, which is connected to the ring gear of the third planetary gear and releasably connectable via a third clutch with the eighth shaft connected to the web of the second planetary gear set, wherein the eighth shaft via a fourth clutch with the connected to the sun gear of the third planetary gear set and the sun gear of the fourth planetary gear set sixth shaft of the transmission is detachably connectable.
  • the drive shaft of the transmission is connected to the web of the first planetary gear set and the ring gear of the second planetary gear set, wherein the fourth shaft connected to the ring gear of the fourth planetary gear set can be coupled to the housing via a second brake and the output shaft of the transmission with the ring gear of the first planetary gear set and the web of the fourth planetary gear set is connected.
  • the inventive design of the multi-speed transmission results in particular for passenger cars suitable translations and increased total spread of the multi-speed transmission, whereby an improvement in ride comfort and a significant consumption reduction can be effected.
  • the construction cost is significantly reduced with the multi-stage transmission according to the invention by a small number of switching elements.
  • a switching element which is actuated in the first forward gear and in reverse is suitable.
  • the transmission according to the invention is designed such that an adaptability to different drive train configurations is made possible both in the power flow direction as well as in space.
  • the transmission can be installed, for example, in front-transverse design or in the context of a standard drive.
  • Figure 1 is a schematic view of a 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.
  • 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 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 two brakes 03, 04 and four clutches 37, 57, 58, 68 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 seventh shaft 7, which is detachably connected via a first clutch 37 to the third shaft 3, which with the sun gear of the second planetary gear set P2 and the Web of the third planetary gear set P3 and coupled via a first brake 03 to the housing G can be coupled.
  • the seventh shaft 7 via a second clutch 57 to the fifth shaft 5 detachably connected, which is connected to the ring gear of the third planetary gear set P3 and via a third clutch 58 with the with the Web of the second planetary gearset P2 connected eighth shaft 8 is detachably connectable, which is detachably connectable via a fourth clutch 68 with the connected to the sun gear of the third planetary gear P3 and the sun gear of the fourth planetary gear set P4 sixth shaft 6 of the transmission.
  • the drive shaft 1 is connected to the web of the first planetary gear set P1 and the ring gear of the second planetary gear set P2, wherein the fourth shaft 4 connected to the ring gear of the fourth planetary gear set P4 can be coupled to the housing G via a second brake 04; the output shaft 2 of the transmission is connected to the ring gear of the first planetary gear P1 and the web of the fourth planetary gear set P4.
  • FIG. 2 shows an exemplary circuit diagram of a multistage transmission according to FIG. For each gear three switching elements are closed. The shift pattern, the respective ratios i of the individual grades and the step to be determined therefrom or increments ⁇ are taken to the next higher gear example, the value 1 1, 095 represents the spread of the transmission.
  • the values for the stationary gear ratios of the planetary gear sets P1, P2, P3, P4 which are designed as minus planetary gear sets are -1, 91, -1, 60, -1, 60 and -2.96, respectively. From Figure 2 it is seen that in sequential switching mode only one switching element switched on and a switching element must be switched off because two adjacent gear stages use two switching elements together. Further, it will be seen that a large spread is achieved with small gear jumps.
  • the first forward gear is obtained by closing the first and second brakes 03, 04 and the fourth clutch 68, the second forward gear by
  • the eighth forward gear can be switched by further switching combinations, which are denoted in Figure 2 with 8.1, 8.2 and 8.3.
  • the eighth forward speed may be achieved by closing the first, second and third clutches 37, 57, 58 or closing the first, second and fourth clutches 37, 57, 68 or closing the first, third and fourth clutches 37, 58, 68 result.
  • the tenth forward gear can be switched by further switching combinations, which are designated in FIG. 2 as 10.1, 10.2 and 10.3. Accordingly, the tenth forward speed can be achieved by closing the first brake 03 and the first and fourth clutches 37, 68, or by closing the first brake 03 and the first and third clutches 37, 58 or by closing the first and second brakes 03, 04 and the first clutch 37 result.
  • an axle differential and / or a distributor differential can be arranged on the drive side or on the output side.
  • the drive shaft 1 can be separated by a coupling element of a drive motor as needed, with a hydrodynamic converter, a hydraulic clutch, a dry starting clutch, a wet starting clutch, a magnetic powder clutch or a centrifugal clutch can be used as the coupling element , It is also possible to arrange such a starting element in the power flow direction behind the transmission, in which case the drive shaft 1 is constantly connected to the crankshaft of the drive motor.
  • the multistage transmission according to the invention also allows the arrangement of a torsional vibration damper between the drive motor and transmission.
  • a wear-free brake such. a hydraulic or electric retarder or the like, be arranged, which is particularly important for use in commercial vehicles of particular importance.
  • a power take-off may be provided to drive additional units on each shaft, preferably on the drive shaft 1 or the output shaft 2.
  • the friction shift elements used can be designed as power shift clutches or brakes.
  • non-positive clutches or brakes such as multi-disc clutches, band brakes and / or cone clutches.
  • Another advantage of the multistage transmission presented here is that an electric machine can be mounted on each shaft as a generator and / or as an additional drive machine.

Landscapes

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

Abstract

L'invention concerne une 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 changement de vitesse (03, 04, 37, 57, 58, 68). La roue solaire du premier train planétaire (P1) est reliée au septième arbre (7) qui peut être relié, par l'intermédiaire d'un premier embrayage (37) au troisième arbre (3) qui est relié à la couronne du deuxième train planétaire (P2) et à l'élément de liaison du troisième train planétaire (P3) et peut s'accoupler au carter (G) par l'intermédiaire d'un premier frein (03). Le septième arbre (7) peut être relié, par l'intermédiaire d'un deuxième embrayage (57) au cinquième arbre (5) qui est relié à la couronne du troisième train planétaire (P3) et peut être relié, par l'intermédiaire d'un troisième embrayage (58) au huitième arbre (8) relié à l'élément de liaison du deuxième train planétaire (P2). Le huitième arbre (8) peut être relié, par l'intermédiaire d'un quatrième embrayage (68) au sixième arbre (6) relié à la couronne du troisième train planétaire (P3) et à la couronne du quatrième train planétaire (P4). L'arbre d'entrée (1) est relié à l'élément de liaison du premier train planétaire (P1) et à la couronne du deuxième train planétaire (P2). Le quatrième arbre (4) relié à la couronne du quatrième train planétaire (P4) peut être accouplé au carter (G) par l'intermédiaire d'un deuxième frein (04), et l'arbre de sortie (2) est relié à la couronne du premier train planétaire (P1) et à l'élément de liaison du quatrième train planétaire (P4).
EP13723097.5A 2012-06-26 2013-05-14 Boîte de vitesses multi-étagée Withdrawn EP2864668A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012210840.8A DE102012210840A1 (de) 2012-06-26 2012-06-26 Mehrstufengetriebe
PCT/EP2013/059877 WO2014000942A1 (fr) 2012-06-26 2013-05-14 Boîte de vitesses multi-étagée

Publications (1)

Publication Number Publication Date
EP2864668A1 true EP2864668A1 (fr) 2015-04-29

Family

ID=48446320

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13723097.5A Withdrawn EP2864668A1 (fr) 2012-06-26 2013-05-14 Boîte de vitesses multi-étagée

Country Status (5)

Country Link
US (1) US9464693B2 (fr)
EP (1) EP2864668A1 (fr)
CN (1) CN104334920B (fr)
DE (1) DE102012210840A1 (fr)
WO (1) WO2014000942A1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015208581A1 (de) * 2015-05-08 2016-11-10 Zf Friedrichshafen Ag Getriebe für ein Kraftfahrzeug
KR101684512B1 (ko) * 2015-05-13 2016-12-08 현대자동차 주식회사 차량용 자동변속기의 유성기어트레인
KR101703580B1 (ko) * 2015-05-13 2017-02-07 현대자동차 주식회사 차량용 자동변속기의 유성기어트레인
KR101703585B1 (ko) * 2015-06-02 2017-02-22 현대자동차 주식회사 차량용 자동변속기의 유성기어트레인
KR101755477B1 (ko) * 2015-09-14 2017-07-10 현대자동차 주식회사 차량용 자동변속기의 유성기어트레인
KR101765604B1 (ko) * 2015-09-14 2017-08-07 현대자동차 주식회사 차량용 자동변속기의 유성기어트레인
KR101896330B1 (ko) * 2016-09-12 2018-09-07 현대자동차 주식회사 차량용 자동 변속기의 유성기어트레인
DE102016220060B3 (de) 2016-10-14 2018-03-22 Schaeffler Technologies AG & Co. KG Antriebsvorrichtung für ein Kraftfahrzeug
CN107524767B (zh) * 2017-09-18 2019-09-10 广州汽车集团股份有限公司 三行星排自动变速器及车辆
CN109764096B (zh) * 2018-11-29 2022-04-08 彭建新 一种自动变速器单元
CN110608270B (zh) * 2019-09-24 2024-05-14 陕西法士特齿轮有限责任公司 一种液力自动变速器

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10221095A1 (de) * 2002-05-11 2004-07-22 Zf Friedrichshafen Ag Mehrstufengetriebe
DE10333434A1 (de) * 2003-07-23 2005-04-14 Zf Friedrichshafen Ag Mehrstufen-Automatgetriebe mit drei Planetenradsätzen
US7704181B2 (en) 2007-04-19 2010-04-27 Gm Global Technology Operations, Inc. Multi-speed transmission
US7722496B2 (en) * 2007-07-31 2010-05-25 Gm Global Technology Operations, Inc. 10-speed transmission
DE102009006587B4 (de) * 2008-02-01 2017-11-30 GM Global Technology Operations LLC (n. d. Ges. d. Staates Delaware) Mehrganggetriebe
JP2009197927A (ja) * 2008-02-22 2009-09-03 Kyowa Metal Work Co Ltd 多段変速遊星歯車列
KR100903340B1 (ko) 2008-04-24 2009-06-16 현대자동차주식회사 차량용 자동 변속기의 기어 트레인
DE102008041205A1 (de) * 2008-08-13 2010-02-18 Zf Friedrichshafen Ag Mehrstufengetriebe
US8002662B2 (en) * 2009-01-26 2011-08-23 GM Global Technology Operations LLC Multi-speed transmissions
DE102010063643A1 (de) * 2010-12-21 2012-06-21 Zf Friedrichshafen Ag Mehrstufengetriebe

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2014000942A1 *

Also Published As

Publication number Publication date
CN104334920A (zh) 2015-02-04
DE102012210840A1 (de) 2014-01-02
US9464693B2 (en) 2016-10-11
US20150167793A1 (en) 2015-06-18
CN104334920B (zh) 2016-11-09
WO2014000942A1 (fr) 2014-01-03

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