WO2002042106A1 - Transmission integrale a repartition pour vehicule a moteur - Google Patents

Transmission integrale a repartition pour vehicule a moteur Download PDF

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Publication number
WO2002042106A1
WO2002042106A1 PCT/EP2001/013503 EP0113503W WO0242106A1 WO 2002042106 A1 WO2002042106 A1 WO 2002042106A1 EP 0113503 W EP0113503 W EP 0113503W WO 0242106 A1 WO0242106 A1 WO 0242106A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
differential
wheel transfer
synchronization
ring gear
Prior art date
Application number
PCT/EP2001/013503
Other languages
German (de)
English (en)
Inventor
Bernhard Drerup
Ünal GAZYAKAN
Detlef Baasch
Gerhard Gumpoltsberger
Michael Ebenhoch
Barbara Schmohl
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 WO2002042106A1 publication Critical patent/WO2002042106A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
    • B60K17/344—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear
    • B60K17/346—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear
    • B60K17/3467—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear combined with a change speed gearing, e.g. range gear
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K23/00—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for
    • B60K23/08—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles
    • B60K23/0808—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles for varying torque distribution between driven axles, e.g. by transfer clutch

Definitions

  • the invention relates to an all-wheel transfer gearbox for a motor vehicle with a transmission stage and a differential.
  • a transmission unit is known from US Pat. No. 4,667,538, which is arranged in a drive train on an output side of a main transmission of a motor vehicle.
  • This gear unit has a planetary gear set with a sun gear arranged on a transmission input shaft and planet bodies engaged therewith.
  • the planetary bodies are mounted on a planet carrier, which is connected to a transmission output shaft of this transmission unit, and are in engagement with a ring gear.
  • the ring gear is connected in a rotationally fixed manner to a housing of the gear unit or to the gear output shaft of the gear unit.
  • the sliding sleeve is pushed onto the ring gear and connected to it in a rotationally fixed manner, the sliding sleeve being arranged on the ring gear so as to be displaceable in the axial direction of the ring gear.
  • the ring gear In a first axial position of the sliding sleeve, the ring gear is connected in a rotationally fixed manner to the output shaft of the gear unit via the sliding sleeve.
  • a rotationally fixed connection between the ring gear and the housing of the gear unit is established via the sliding sleeve.
  • the sliding sleeve is brought into contact with an annular body in each case.
  • the ring bodies each have a conical surface, the conical surface producing a speed compensation between the sliding sleeve and the housing or the transmission output shaft during pressing of the sliding sleeve on the ring body with increasing contact pressure.
  • the disadvantage here is that the synchronization comprising the sliding sleeve and the ring body has a large diameter due to the arrangement of the sliding sleeve on the ring gear, which leads overall to large dimensions of the gear unit, which takes up a large amount of space in a motor vehicle.
  • a sliding sleeve of a synchronization which is provided for setting a first or a second transmission ratio, is formed in one piece with a ring gear of a planetary gear set.
  • the planetary gear set is arranged between a gearbox input shaft and a gearbox output shaft, the gearbox output shaft being driven in a first axial position of the sliding sleeve or the ring gear of the planetary gearset at the same speed as the gearbox input shaft.
  • the transmission output shaft In a second axial position of the sliding sleeve, the transmission output shaft is driven at a speed different from the speed of the transmission input shaft, which is dependent on the gear ratio of the transmission.
  • the ring gear which engages with planet bodies of the planetary gear set, has to be displaced in the axial direction of the transmission.
  • transfer cases are provided after a main transmission in order to distribute a drive power supplied by the engine to the individual drive axles.
  • Such transfer cases have, among other things, a so-called range group or a gear stage designed as a planetary gear set, which is provided for switching between an off-road gear and a road gear, with which a desired increase in torque in the off-road gear takes place in the drive train only after the main gear.
  • an all-wheel transfer gearbox which has a gear ratio and a synchronization for switching the gear ratio.
  • the synchronization comprises a sliding sleeve, which is connected in a rotationally fixed manner to a ring gear of the gear stage designed as a planetary gear set and can be displaceably guided on the ring gear.
  • An off-road gear or a gear ratio intended for permanent road operation is set via the sliding sleeve.
  • a non-rotatable connection is made between a housing of the all-wheel transfer gearbox and the sliding sleeve
  • Ring gear of the gear stage or a planet carrier of the gear stage and the ring gear is equipped with a planet carrier. ger one of the translation stage connected in a driveline downstream differential.
  • This differential has a double planetary body set, the planetary bodies of which each engage one of two sun gears of the differential.
  • the drive torque of the transmission input shaft of the all-wheel transfer case is fed to a first or a second transmission output shaft via the two sun gears.
  • the all-wheel transfer gearbox has a controllable lock for locking the two output shafts, the two gearbox output shafts being driven at the same speed when the lock is locked.
  • the object of the present invention is to provide an all-wheel transfer gearbox for a motor vehicle which has a small space requirement and a low overall weight.
  • the space requirement and the weight of an all-wheel transfer gearbox are advantageously reduced by the fact that the synchronization is arranged as a spatial, separate unit directly on the transmission input shaft and is therefore smaller and less in comparison to designs known from the prior art Material use is carried out.
  • the synchronization is not formed in one piece with the transmission input shaft, but is displaceably and / or rotatably arranged concentrically surrounding the transmission input shaft.
  • Another advantage is that due to the connection of the planet carrier of the gear ratio with the ring gear of the differential, a torque distribution between a front axle and a rear axle of a motor vehicle or a degree of reduction can advantageously be carried out more simply and variably.
  • the arrangement or connection according to the invention there is advantageously the possibility of flexibly adapting the all-wheel transfer gearbox to different requirement profiles or applications without having to make any special structural changes.
  • the all-wheel-drive transfer case according to the invention it is advantageously possible to drive off-road or on a street, the off-road allowing high pulling forces at low speeds and driving at very low speeds without a sliding clutch.
  • a motor vehicle with the concept presented can be used conventionally in road operation without disadvantages in road operation.
  • Another advantage is that with the synchronization provided for switching the transmission stage, an automated and a manual switching can be carried out at a standstill and also while the motor vehicle is traveling.
  • the four-wheel transfer gearbox has the advantage that, when the road gear is engaged, only low losses and low relative speeds occur in the gear ratio.
  • the figure shows an all-wheel transfer gear 1, which in the assembled state is connected via a transmission input shaft 2 to a main transmission or its transmission output shaft.
  • the all-wheel transfer case 1 is one on the output side of the main transmission Motor vehicle arranged and leads an incoming drive torque via the transmission input shaft 2, a first planetary gear set 3 as a gear ratio for an off-road gear or a road gear and a second planetary gear set 4 connected to this on a front axle 5 and a rear axle 6 of the motor vehicle.
  • the first planetary gear set or the gear ratio 3 is operatively connected to a corresponding synchronization 7 in such a way that a gear ratio corresponding to the off-road gear can be set from a road gear or a neutral position as required or based on a request from a driver of the motor vehicle in the all-wheel-drive transfer case 1.
  • the second planetary gear set is designed as a differential 4 with variable division for distributing the incoming drive torque to the front axle 5 and the rear axle 6 of the motor vehicle.
  • the translation stage is preferably carried out with helical teeth in order to minimize noise during operation of the all-wheel transfer case.
  • helical teeth it is at the discretion of the person skilled in the art, depending on the respective application, to provide a different configuration of the toothing of the gear ratio.
  • the synchronization 7 is arranged as a spatial unit directly on the transmission input shaft 2 and is in operative connection with a ring gear 8 of the transmission stage 3.
  • a planet carrier 9 of the translation tion stage 3 connected to a ring gear 10 of the differential 4, the differential 4 having a plurality of double planet bodies 12A, 12B of a plus planetary gear set mounted on a planet carrier 11 of the differential 4.
  • a first planetary body 12A shown in the figure is in engagement with the ring gear 10 of the differential 4 and a second planetary body 12B shown in the figure.
  • the second planetary body 12B transmits the drive torque arriving via the ring gear 10 of the differential 4 to a sun gear 13 of the differential 4 and is in engagement with the first planetary body 12A and the sun gear 13.
  • the drive of the rear axle 6 or the transmission of the drive torque from the differential 4 to the rear axle 6 takes place via the planet carrier 11 of the differential 4, which is operatively connected to the rear axle 6.
  • the drive of the front axle 5 or the transmission of the drive torque from the differential 4 to the front axle 5 takes place via the sun gear 13 of the differential 4, the drive torque supplied to the sun gear 13 being supplied to the front axle 5 via a chain drive 21.
  • the differential 4 is followed by a locking device 22, by means of which the sun 13 and the web 11 can be locked.
  • the barrier ⁇ device 22 is executed in the present embodiment as a multi-disc lock and an
  • hablet- device 23 driven as a function of the respective operating state, that is opened or closed, wherein in the closed state of the locking device 22, the driving torque is distributed to the front axle 5 and the rear axle 6 in equal proportions.
  • the synchronization 7 is connected upstream of the transmission input shaft 2 of the transmission stage 3 and is operatively connected via a carrier 14 connected to the ring gear 8 of the transmission stage 3.
  • the carrier 14 has an annular disk-shaped base part and an adjoining, at least approximately cylindrical collar, a fixed connection being provided between an inside of the ring gear 8 of the transmission stage 3 and an outside of the collar of the carrier 14 facing this.
  • the fixed connection is designed as a positive connection, the carrier 14 and the ring gear 8 of the transmission stage 3 each having an interlocking tooth profile.
  • a locking ring (not shown in detail) is preferably used in the region of the toothing, which secures the ring gear 8 and the carrier 14 in the axial direction to one another.
  • a non-rotatable connection is formed between an inner side of the base part of the carrier 14 facing the transmission input shaft 2 and a sliding sleeve 15 of the synchronization 7 which can be displaced in the axial direction of the transmission input shaft 2, so that a rotationally fixed connection between the planet carrier 9 depending on an axial position of the sliding sleeve 15 of the transmission stage 3 and the ring gear 8 of the transmission stage 3 can be produced via the synchronization 7 or that via the synchronization Chronization 7 a non-rotatable connection between a stationary component 16 of the all-wheel transfer case 1 and the ring gear 8 of the transmission stage 3 can be established.
  • the stationary component 16 is formed in one piece with a housing of the all-wheel distributor gearbox, it naturally being within the discretion of the person skilled in the art to design the stationary component as a separate component that is firmly connected to the housing.
  • the sliding sleeve 15 is shifted into a third axial position, so that the ring gear 8 of the transmission stage 3 via the sliding sleeve 15 and one between the sliding sleeve and one Part of the planet carrier 9 of the translation stage 3 arranged synchronization body is non-rotatably coupled to the planet carrier 9 of the translation stage 3.
  • a linear drive 17 is provided, by means of which the off-road gear or the road gear is engaged depending on a request from a driver of the motor vehicle.
  • the linear drive 17 engages in a guide groove 18 of the sliding sleeve 15 via a driver 19, which is moved in the axial switching direction of the sliding sleeve 15 by an actuating unit of the linear drive 17, which is not shown in detail.
  • the driver for the adjustment of the sliding sleeve is tiltably mounted in a housing of the all-wheel distributor transmission and is actuated with its end facing away from the sliding sleeve by the linear drive, a deflection of its end facing away from the linear drive causing the sliding sleeve to be displaced into axial switching direction.
  • connection between the planet carrier 9 of the gear ratio 3 and the ring gear 10 of the differential 4 is realized via an annular connecting part 20, which is S-shaped in longitudinal section and with its ends facing the gear ratio 3 and the differential 4 a rotationally fixed connection with the planet carrier 9 of the gear ratio 3 and the ring gear 10 of the differential 4.
  • the non-rotatable connection is in The present exemplary embodiment is formed via a positive connection, the connection also being able to be provided via other suitable connection types.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Arrangement And Driving Of Transmission Devices (AREA)

Abstract

L'invention concerne une transmission intégrale à répartition (1) pour véhicule à moteur, comprenant un premier train planétaire (3) constituant un étage de démultiplication pour une traction toutes roues motrices à enclencher, et une synchronisation correspondante (7) pour l'activation de l'étage de démultiplication (3). La transmission intégrale (1) présente en outre un second train planétaire (4) constituant un différentiel à division variable destiné à la répartition d'un couple d'entraînement sur un essieu avant (5) et un essieu arrière (6). La synchronisation (7) est agencée sous la forme d'une unité distincte, directement sur un arbre d'entrée de la transmission (2) et est en liaison coopérante avec une roue à denture intérieure (8) de l'étage de démultiplication (3). Un support planétaire (9) de l'étage de démultiplication (3) est associé à une roue à denture intérieure (10) du différentiel (4).
PCT/EP2001/013503 2000-11-23 2001-11-21 Transmission integrale a repartition pour vehicule a moteur WO2002042106A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2000158203 DE10058203A1 (de) 2000-11-23 2000-11-23 Allradverteilergetriebe für ein Kraftfahrzeug
DE10058203.6 2000-11-23

Publications (1)

Publication Number Publication Date
WO2002042106A1 true WO2002042106A1 (fr) 2002-05-30

Family

ID=7664411

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2001/013503 WO2002042106A1 (fr) 2000-11-23 2001-11-21 Transmission integrale a repartition pour vehicule a moteur

Country Status (2)

Country Link
DE (1) DE10058203A1 (fr)
WO (1) WO2002042106A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011160144A1 (fr) * 2010-06-25 2011-12-29 Paul Roman Oberaigner Boîte de transfert

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004002195A1 (de) * 2004-01-15 2005-08-04 Zf Friedrichshafen Ag Verteilergetriebe mit einer Antriebswelle und zwei Antriebswellen
DE102004002187A1 (de) * 2004-01-15 2005-08-04 Zf Friedrichshafen Ag Getriebe zum Verteilen eines Antriebsmomentes und Verfahren zum Steuern und Regeln eines Getriebes
AT506456B1 (de) * 2008-02-25 2009-09-15 Oberaigner Paul Roman Verteilergetriebe

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4569252A (en) 1983-05-19 1986-02-11 Eaton Corporation Change gear planetary transmission
US4667538A (en) 1983-12-06 1987-05-26 Ab Volvo Range gearbox for motor vehicles having an axially shiftable ring gear
US4920828A (en) * 1988-02-08 1990-05-01 Mazda Motor Corporation Planetary gear type transmission
EP0684153A1 (fr) * 1993-12-16 1995-11-29 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Systeme de transfert
US6022289A (en) 1998-12-16 2000-02-08 New Venture Gear, Inc. Synchronized range shift mechanism for transfer case
EP1036691A2 (fr) * 1999-03-09 2000-09-20 New Venture Gear, Inc. Boíte de transfert avec mécanisme de changement de gamme synchronisée et commande adaptif d'un embrayage

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS56154329A (en) * 1980-04-25 1981-11-28 Nissan Motor Co Ltd Four-wheel-drive vehicle
DE19538661C1 (de) * 1995-10-17 1996-12-05 Steyr Daimler Puch Ag Verteilergetriebe mit zwei Stufen
JP3547582B2 (ja) * 1997-04-21 2004-07-28 本田技研工業株式会社 車両の左右輪間の連結装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4569252A (en) 1983-05-19 1986-02-11 Eaton Corporation Change gear planetary transmission
US4667538A (en) 1983-12-06 1987-05-26 Ab Volvo Range gearbox for motor vehicles having an axially shiftable ring gear
US4920828A (en) * 1988-02-08 1990-05-01 Mazda Motor Corporation Planetary gear type transmission
EP0684153A1 (fr) * 1993-12-16 1995-11-29 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Systeme de transfert
US6022289A (en) 1998-12-16 2000-02-08 New Venture Gear, Inc. Synchronized range shift mechanism for transfer case
EP1036691A2 (fr) * 1999-03-09 2000-09-20 New Venture Gear, Inc. Boíte de transfert avec mécanisme de changement de gamme synchronisée et commande adaptif d'un embrayage

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011160144A1 (fr) * 2010-06-25 2011-12-29 Paul Roman Oberaigner Boîte de transfert
US8795124B2 (en) 2010-06-25 2014-08-05 Paul Roman Oberaigner Transfer gear-box

Also Published As

Publication number Publication date
DE10058203A1 (de) 2002-05-29

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