WO2012052285A1 - Boîte de vitesses multiétagée - Google Patents

Boîte de vitesses multiétagée Download PDF

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Publication number
WO2012052285A1
WO2012052285A1 PCT/EP2011/067265 EP2011067265W WO2012052285A1 WO 2012052285 A1 WO2012052285 A1 WO 2012052285A1 EP 2011067265 W EP2011067265 W EP 2011067265W WO 2012052285 A1 WO2012052285 A1 WO 2012052285A1
Authority
WO
WIPO (PCT)
Prior art keywords
planetary gear
gear set
shaft
brake
gear
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.)
Ceased
Application number
PCT/EP2011/067265
Other languages
German (de)
English (en)
Inventor
Gerhard Gumpoltsberger
Christian Sibla
Stefan Beck
Michael Wechs
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 WO2012052285A1 publication Critical patent/WO2012052285A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six 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
    • F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means

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 49 507 A1 of the applicant;
  • two non-switchable front-gear sets are provided on the output side, the output side generate two speeds that are selectively switchable in addition to the speed of the drive shaft to a force acting on the output shaft, switchable Doppelplanetenradsatz by selectively closing the switching elements used that to switch from a Gear in each case the following higher or lower gear from the two currently operated switching elements only one switching element must be switched on or off.
  • 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. Further multi-speed transmissions are for example from the
  • 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 referred to as drive shaft, output shaft, third, fourth, fifth, sixth, seventh and eighth shaft and at least six 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 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 Set by means of the third shaft via a first brake to a housing of the transmission can be coupled and releasably connected via a second clutch to the drive shaft, wherein the ring gear of the 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 present invention has for its object to propose a multi-speed transmission of the type mentioned, which has six forward gears and one reverse gear with sufficient translation, in which the construction cost and size, especially the overall length, or the weight are optimized and also the efficiency in terms the drag and gearing losses is improved.
  • small supporting moments act on the shifting elements.
  • Another object of the invention is to allow easy accessibility of the Scheltiata of the transmission. 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 which has a drive and an output, which are arranged in a housing. Furthermore, at least four planetary gear sets, hereinafter referred to as first, second, third and fourth planetary gear set, seven rotatable shafts - hereinafter referred to as drive shaft, output shaft, third, fourth, fifth, sixth and seventh shaft - and at least five preferably designed as a lamellae switching elements Shift elements, comprising four brakes and a clutch, provided, the selective engagement causes different ratios between the drive and the output, so that preferably six forward gears and one reverse gear can be realized.
  • first, second, third and fourth planetary gear set seven rotatable shafts - hereinafter referred to as drive shaft, output shaft, third, fourth, fifth, sixth and seventh shaft - and at least five preferably designed as a lamellae switching elements Shift elements, comprising four brakes and a clutch, provided, the selective engagement causes different ratios between the drive and the output, so that preferably six forward gears and one
  • the planetary gear sets are preferably arranged axially in the order of the first planetary gearset, second planetary gearset, third planetary gearset, fourth planetary gearset or first planetary gearset, second planetary gearset, fourth planetary gearset, third planetary gearset and are preferably configured as minus planetary gear sets.
  • the axial order of the planetary gear sets may be arbitrary.
  • 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, all inner planetary gears mesh with the sun gear and all outer planetary 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 gear ratio translation.
  • the sun gear of the first planetary gear set is connected to the sixth shaft, which is coupled via a first brake to the housing of the transmission and via a coupling with the connected to the web of the second planetary gear and the sun gear of the third planetary gear set drive shaft of the transmission solvable is connectable, wherein the web of the first planetary gear set is connected to the fourth shaft, which is connected to the ring gear of the second and the ring gear of the third planetary gear and via a second brake to the housing of the transmission can be coupled.
  • the output shaft is connected to the ring gear of the first planetary gear set and the bridge of the fourth planetary gear set, wherein the sun gear of the second planetary gear set is connected to the fifth shaft, which can be coupled via a third brake to the housing of the transmission.
  • the web of the third planetary gear set is connected to the seventh shaft connected to the ring gear of the fourth planetary gear set, wherein the third shaft is connected to the sun gear of the fourth planetary gear set and can be coupled to the housing of the gearbox via a fourth brake.
  • 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.
  • an easy accessibility of these switching elements is ensured by the execution of four switching elements as brakes, since the brakes are arranged on the transmission housing; Furthermore, the execution of four switching elements results as brakes in energy-saving switching operations, as no rotary transformer are required on the brakes.
  • the construction cost is significantly reduced with the multi-stage transmission according to the invention by a small number of switching elements.
  • a Approach with a hydrodynamic converter, an external starting clutch o- also to carry out with other suitable external starting 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.
  • Figure 1 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.
  • 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 and P4 are formed in the example shown in Figure 1 as negative planetary gear sets.
  • at least one planetary gear set 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 are arranged axially in the order P1, P2, P3, P4.
  • five switching elements namely four brakes 03, 04, 05, 06 and only one clutch 16 are provided.
  • the spatial arrangement of the switching elements can be arbitrary and is limited only by the dimensions and the external shape.
  • the clutch and the brakes of the transmission are preferably designed as Reibschaltimplantation or lamellar switching elements.
  • the multi-speed transmission according to the invention has a total of seven rotatable shafts, namely the waves 1, 2, 3, 4, 5, 6 and 7, wherein the drive shaft, the first shaft 1 and the output shaft forms the second shaft 2 of the transmission.
  • the sun gear of the first planetary gearset P1 is connected to the sixth shaft 6, which can be released via a clutch 16 to the drive shaft 1 connected to the web of the second planetary gearset P2 and the sun gear of the third planetary gearset P3 connectable and can be coupled via a first brake 06 to the housing G of the transmission; Furthermore, the web of the first planetary gear set P1 is connected to the fourth shaft 4, which is connected to the ring gear of the second planetary gear set P2 and the ring gear of the third planetary gear set P3 and can be coupled via a second brake 04 to the housing G of the transmission.
  • the output shaft 2 is connected to the ring gear of the first planetary gear P1 and the web of the fourth planetary gear set P4, wherein the sun gear of the second planetary gear set P2 is connected to the fifth shaft 5, via a third brake 05 to the housing G of the transmission can be coupled.
  • the web of the third planetary gear set P3 is connected to the connected to the ring gear of the fourth planetary gear set P4 seventh shaft 7, wherein the third shaft 3 connected to the sun gear of the fourth planetary gear set P4 and a fourth brake 03 to the housing G of the transmission can be coupled.
  • the first, second and third brakes 06, 04, 05 may, viewed axially, be arranged next to one another, wherein the single clutch 16 may be arranged axially between the first and the second planetary gear set P1, P2.
  • FIG. 2 shows an exemplary circuit diagram of a multistage transmission according to FIG. For each gear two switching elements are closed.
  • the shift pattern, the respective ratios of the individual gear ratios i and the step to be determined therefrom or increments ⁇ are taken to the next higher gear example, the value of 7.568 represents the spread of the transmission.
  • Typical values for the stationary gear ratios of the planetary gear sets P1, P2, P3 and P4 designed as minus planetary gear sets are respectively -3.330, -3.700, -2.600 and -3.700. It can be seen from FIG. 2 that in sequential switching mode only one switching element is switched on and one switching element has to be switched off since two adjacent gear stages share a switching element. Further, it will be seen that a large spread is achieved with small gear jumps.
  • the first forward gear is obtained by closing the second and fourth brakes 04, 03, the second forward gear by closing the first and fourth brakes 06, 03, the third forward gear by closing the fourth brake 03 and the clutch 16, the fourth forward gear by closing the third and fourth brakes 05, 03, the fifth forward gear by closing the third brake 05 and the clutch 16 and the sixth forward gear results by closing the first and third brakes 06, 05 wherein the reverse gear by closing the second brake 04 and the clutch 16 results.
  • this switching element can be used as a starting element.
  • an axle differential and / or a distributor differential can be arranged according to the invention.
  • 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 a 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 switching 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, or form-locking claw switching elements can be 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.

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

Abstract

Boîte de vitesses multiétagée avec six marches avant et une marche arrière, comportant quatre jeux de satellites (P1, P2, P3, P4), sept arbres (1, 2, 3, 4, 5, 6, 7) rotatifs et cinq éléments de commutation (03, 04, 05, 06, 16), le pignon planétaire du jeu de satellites (P1) étant relié au sixième arbre (6) qui peut être relié de manière libérable par un accouplement (16) à l'arbre d'entraînement (1) relié au porte-satellites du jeu de satellites (P2) et au pignon planétaire du troisième jeu de satellites (P3) et qui peut être couplé par un premier frein (06) au carter (G). Le porte-satellites du jeu de satellites (P1) est relié au quatrième arbre (4) qui est relié à la couronne du jeu de satellites (P2) et à la couronne du jeu de satellites (P3) et qui peut être couplé par un deuxième frein (04) au carter (G). L'arbre de sortie (2) est relié à la couronne du jeu de satellites (P1) et au porte-satellites du jeu de satellites (P4) et le pignon planétaire du jeu de satellites (P2) est relié au cinquième arbre (5) qui peut être couplé par un troisième frein (05) au carter (G). Le porte-satellites du jeu de satellites (P3) est relié au septième arbre (7) qui est relié à la couronne du jeu de satellites (P4). Le troisième arbre (3) est relié au pignon planétaire du jeu de satellites (P4) et il peut être couplé par un quatrième frein (03) au carter (G).
PCT/EP2011/067265 2010-10-20 2011-10-04 Boîte de vitesses multiétagée Ceased WO2012052285A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010042664.4 2010-10-20
DE201010042664 DE102010042664A1 (de) 2010-10-20 2010-10-20 Mehrstufengetriebe

Publications (1)

Publication Number Publication Date
WO2012052285A1 true WO2012052285A1 (fr) 2012-04-26

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PCT/EP2011/067265 Ceased WO2012052285A1 (fr) 2010-10-20 2011-10-04 Boîte de vitesses multiétagée

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DE (1) DE102010042664A1 (fr)
WO (1) WO2012052285A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109211160A (zh) * 2018-09-29 2019-01-15 济南大学 一种斜齿轮差动轮系体积的计算方法

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2936969A1 (de) 1979-09-13 1981-04-02 Daimler-Benz Ag, 7000 Stuttgart Planetenraeder-gangwechselgetriebe mit einem vorschalt- und einem hauptgetriebe fuer fahrzeuge
JPS6018351U (ja) * 1983-07-15 1985-02-07 株式会社小松製作所 遊星歯車式変速装置
JPS63195452A (ja) * 1987-02-10 1988-08-12 Mitsubishi Heavy Ind Ltd 変速装置
DE19949507A1 (de) 1999-10-14 2001-04-19 Zahnradfabrik Friedrichshafen Mehrstufengetriebe
DE102005010210A1 (de) 2005-03-05 2006-09-14 Zf Friedrichshafen Ag Mehrstufengetriebe
JP2006307954A (ja) * 2005-04-27 2006-11-09 Jatco Ltd 自動変速機用歯車変速装置
DE102006006637A1 (de) 2006-02-14 2007-09-06 Zf Friedrichshafen Ag Mehrstufengetriebe
JP2009185864A (ja) * 2008-02-05 2009-08-20 Honda Motor Co Ltd 自動変速機
DE102008000428A1 (de) 2008-02-28 2009-09-03 Zf Friedrichshafen Ag Mehrstufengetriebe

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4070927A (en) * 1976-06-04 1978-01-31 General Motors Corporation Planetary gearing arrangement for a transmission
DE19727153C2 (de) * 1997-06-26 1999-05-20 Voith Turbo Kg Mehrganggetriebe, insbesondere Sechsgang-Getriebe
DE19910299C1 (de) * 1999-03-10 2001-04-19 Daimler Chrysler Ag Planetenräder-Wechselgetriebe mit drei Teilgetrieben

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2936969A1 (de) 1979-09-13 1981-04-02 Daimler-Benz Ag, 7000 Stuttgart Planetenraeder-gangwechselgetriebe mit einem vorschalt- und einem hauptgetriebe fuer fahrzeuge
JPS6018351U (ja) * 1983-07-15 1985-02-07 株式会社小松製作所 遊星歯車式変速装置
JPS63195452A (ja) * 1987-02-10 1988-08-12 Mitsubishi Heavy Ind Ltd 変速装置
DE19949507A1 (de) 1999-10-14 2001-04-19 Zahnradfabrik Friedrichshafen Mehrstufengetriebe
DE102005010210A1 (de) 2005-03-05 2006-09-14 Zf Friedrichshafen Ag Mehrstufengetriebe
JP2006307954A (ja) * 2005-04-27 2006-11-09 Jatco Ltd 自動変速機用歯車変速装置
DE102006006637A1 (de) 2006-02-14 2007-09-06 Zf Friedrichshafen Ag Mehrstufengetriebe
JP2009185864A (ja) * 2008-02-05 2009-08-20 Honda Motor Co Ltd 自動変速機
DE102008000428A1 (de) 2008-02-28 2009-09-03 Zf Friedrichshafen Ag Mehrstufengetriebe

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109211160A (zh) * 2018-09-29 2019-01-15 济南大学 一种斜齿轮差动轮系体积的计算方法

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Publication number Publication date
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