EP3033550A1 - Engrenage différentiel pour essieu moteur d'un véhicule automobile - Google Patents

Engrenage différentiel pour essieu moteur d'un véhicule automobile

Info

Publication number
EP3033550A1
EP3033550A1 EP14745086.0A EP14745086A EP3033550A1 EP 3033550 A1 EP3033550 A1 EP 3033550A1 EP 14745086 A EP14745086 A EP 14745086A EP 3033550 A1 EP3033550 A1 EP 3033550A1
Authority
EP
European Patent Office
Prior art keywords
differential
differential gear
actuator
gear according
coupling
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Withdrawn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
EP14745086.0A
Other languages
German (de)
English (en)
Inventor
Christian Meixner
Karin VOGTHERR
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.)
Audi AG
Original Assignee
Audi 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 Audi AG filed Critical Audi AG
Publication of EP3033550A1 publication Critical patent/EP3033550A1/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Withdrawn legal-status Critical Current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
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/22—Arrangements for suppressing or influencing the differential action, e.g. locking devices using friction clutches or brakes
    • 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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel 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
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable 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
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
    • F16H48/32—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using fluid pressure actuators
    • 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
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
    • F16H48/34—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators
    • 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
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/295—Arrangements for suppressing or influencing the differential action, e.g. locking devices using multiple means for force boosting

Definitions

  • the present invention relates to a differential gear for a drive axle of a motor vehicle according to the preamble of patent claim 1.
  • a generic differential gear is known, for example, from WO / 2013 / 056691A1, in which two multi-plate clutches are integrated in the differential housing which generate a self-locking effect "torque-sensing.”
  • an electromechanical actuator attached to the differential housing is provided by the software This results in further, in particular driving dynamics advantageous control intervention options regardless of the applied drive torque.
  • the at least one actuator is arranged in the region of one of the output shafts, preferably arranged on a flange of an output shaft of the differential gear designed as a driving flange shaft, and acts on the clutch device with at least one transmission medium.
  • a rod preferably a pull rod, and radially outwardly thereto a support tube may be provided as a transmission means indirectly acted upon by the actuator directly or indirectly on a support disk of the coupling device on the one hand and on the driver formed for example by a driving pin on the other Act.
  • the preferably designed as a pull rod rod and the support tube can be actuated via a, for example, electromagnetically adjustable, ball-ramp system with adjusting discs, resulting in relatively low actuating forces, which can be applied for example by means of a small, low-weight electromagnet.
  • the preferably designed as a pull rod rod and the support tube for example hydraulically or optionally pneumatically, via a linear adjustment, for example, a piston-cylinder unit, in opposite directions be acted upon.
  • an already existing in the motor vehicle pressure medium source may be used with the interposition of a corresponding control valve or it may be used a self-sufficient, electrically driven hydraulic pump.
  • the actuator may be connected to an electronic driving program control of the motor vehicle and superimposed on the driving torque activate the locking device in defined driving conditions of the motor vehicle to a defined extent.
  • Control parameters may be, in particular, the starting of the motor vehicle and / or the passing through of Kuryen, whereby already existing parameters such as vehicle speed, steering angle, lateral acceleration, load request, etc. can be taken into account in the driving program control.
  • Fig. 1 in sketchy, half-tone representation of a differential gear for a
  • Fig. 3 is a schematically and in a longitudinal section through the flange shafts shown bevel differential gear with both sides of the bevel gears and a drive pin arranged multi-plate clutches and a hydraulically actuated actuator.
  • FIG. 1 shows a sketch of a bevel gear differential 10 for a drive axle (front or rear axle) of a motor vehicle, which is rotatably mounted in a differential housing, not shown, and a fixed to a differential housing 12 ring gear 14 as a drive element and two stub shafts 16, Having 18 as output elements.
  • the stub shafts 16, 18 are connected via flanges 16a, 18a with abreibendem drive shafts or the wheels of the drive axle. Furthermore, bear in the differential housing 12 projecting stub shafts 16, 18, the axle bevel gears 20 of the differential 10, which in turn mesh with the planetary gears 22 designed as bevel gears.
  • the planet gears 22 are rotatably mounted on a driving pin 24 which is fixed diametrically opposite in a drum-shaped coupling block 26.
  • the coupling block 26 is axially displaceably guided in the differential housing 12 via axially parallel toothings (at 30) and acts with a pressure disk 26a on a coupling 28 positioned within the differential housing 12, here and below by way of example Multi-plate clutch 28.
  • 12 multi-plate clutches 28 could be provided on both sides of the differential housing.
  • the lamellae (without reference numeral) of the multi-plate clutch 28 acting as a blocking device are positively connected in an alternating manner with the differential housing 12 or a hub portion 20a of the corresponding axle bevel gear 20 and are supported on the end wall 12a of the differential housing via axially parallel gears.
  • the driving differential housing 12 is coupled to the Achskegelrad 20 of the flange 18 and thus canceled the differential effect or the locking device active.
  • the electromagnetic actuator 34 is provided with an electromagnet 36 cooperating with a setting disk 34b, a ball-ramp system 34c and a
  • the electromagnet 36 here consists of a co-rotating armature 36a and a housing-fixed coil 36b. Between these two halves of the electromagnet 36 there is a primary clutch or multi-disc clutch 37, the outer disks 37a of which the left in the image plane flange 17 and thus also connected to the left in the image plane Achskegelrad 20 are. It is understood that this arrangement can just as well be formed at any other suitable location.
  • the inner disks 37b are rotatably connected, for example, by means of splines of the adjusting disk 34 with the arranged inside the stub shaft 16 tie rod 38 and via this with the differential or driving pin 24 and thus the differential housing.
  • the balls of the ball ramp 34 roll within the ramp and cause a spreading action between the right adjusting disc 34b and the left adjusting disc 34a.
  • This spreading force acts on the coupling 28 in the differential from the left adjusting disk 34a via the pull rod 38, the driving pin 24 and the pressure disk 26a. Due to the torque-sensing effect of the differential, this disk set of the clutch 28 is already impressed on the input torque and is additionally pressed more strongly by the actuation force from the ball ramp. This allows the non-ideal driving condition to be driven through even more dynamically.
  • FIG. 1 various bearings are shown in FIG. 1, for example the bearings 39a for mounting the differential housing in the differential flange cover.
  • the storage 39b for storage of the left flange shaft in the housing.
  • the bearings 39c are each thrust bearings, while the bearing 39d is a radial bearing.
  • adjusting disc 34a is still acted upon by a return spring 41. 2 differs from FIG. 1 in particular in that in the differential gear 10 ', the actuator 44 (see also FIG. 3) is hydraulically actuated and actuated, wherein two relatively displaceable and a common cylinder chamber 44c delimiting Ring piston 44a, 44b of a corresponding piston-cylinder Unit are provided, which act on the tie rod 38 and the support tube 40 as described above.
  • Fig. 3 there is shown in greater detail a differential gear 10 " substantially corresponding to Fig. 2 and described only insofar as is necessary for the understanding of the present invention.
  • FIG. 3 partially shows the axle housing 46 in which the differential housing 12 of the bevel gear differential 10 "is axially non-displaceably mounted on both sides tapered roller bearings 48.
  • the flange shafts 16, 18 carrying the axle bevel gears 20 are also provided on the output side via ball bearings 50 are rotatably supported in the axle housing 46.
  • two multi-plate clutches 28 are arranged, the fins of which are connected to the clutch block 26 on the one hand and to the hub sections 20a of the axle bevel gears 20 on the other hand via corresponding gears as described above.
  • the left-side multi-disc clutch 28 can also be acted upon by means of the hydraulically actuatable actuator 44 as follows:
  • actuator 44 is composed analogous to FIG. 2 of two mutually displaceable on the stub shaft 16 and in the axle housing 46 and directly to the flange 16a adjacent annular piston 44a and 44b together, which are axially displaceably guided in the axle housing 46 and delimit a common cylinder space 44c.
  • the cylinder chamber 44c can over in the Axle housing 46 integrated channels (not shown) are supplied with hydraulic fluid.
  • the annular piston 44a is mounted on the stub shaft 16 and acts via a first thrust bearing 42 on the flange 16a and via this via a second thrust bearing 42 on a cup 38a within the flange 16a, which in turn form-fitting with the in the stub shaft 16 in a central bore 16b axially displaceably guided Zügstange 38 cooperates.
  • the pull rod 38 acts with the interposition of a pressure piece 54 on the driving pin 24 of the bevel gear differential or of the coupling block 26.
  • annular piston 44b acts indirectly via a first thrust bearing 42 on the support tube 40, which abuts via a further thrust bearing 42 at a hub-shaped coupling body 52 acting on the left multi-disc clutch 28 as a support disc.
  • the radially outer support tube 40 can rotate with the stub shaft 16 and supports the pressure forces occurring during actuation of the left multi-plate clutch 28 via the coupling body 52, while the drew-coupled to the stub shaft 16 tie rod 38 via the axially displaceable relative to the differential housing 2 coupling block 26 the left multi-plate clutch 28 acted upon.
  • the two multi-plate clutches 28 can thus be "torque sensing" applied via the coupling block 26 at different input and output torques and it can additionally or alternatively the left multi-plate clutch 28 via the actuator 44 with the support tube 40 and the Pull rod 38 are activated as a transmission means more or less to block the differential action.
  • the electric or hydraulic actuation of the actuator 34 or 44 may preferably take place via an electronic driving stability program (not shown) of the motor vehicle which controls the additional actuation of the multi-plate clutch 28 in accordance with driving-specific data such as vehicle speed, load signal, steering angle, lateral acceleration.
  • driving-specific data such as vehicle speed, load signal, steering angle, lateral acceleration.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid Mechanics (AREA)
  • Electromagnetism (AREA)
  • Retarders (AREA)

Abstract

L'invention concerne un engrenage différentiel pour un essieu moteur d'un véhicule automobile. Cet engrenage est pourvu d'un boîtier de différentiel (12) entraîné, lequel agit sur un entraîneur (24), en particulier sur un boulon d'entraînement, par l'intermédiaire d'un bloc d'accouplement (26) guidé de manière solidaire en rotation mais de manière à pouvoir se déplacer par coulissement axialement, et sur lequel des roues planétaires (22) sont montées, lesquelles s'engrènent avec des roues menées (20), les roues menées (20) étant menées sur des arbres de sortie (16, 18) situés des deux côtés. Cet engrenage est également pourvu d'un dispositif de blocage dépendant du couple destiné à déplacer le couple d'entraînement au moyen d'au moins un dispositif d'accouplement (28) intégré dans le boîtier de différentiel (12), ce dispositif pouvant être sollicité en plus par au moins un actionneur (34 ; 44) indépendamment du couple d'entraînement. Selon l'invention, le ou les actionneurs (34 ; 44) sont disposés dans la zone d'au moins un des arbres de sortie (16, 18) et agissent à l'aide d'au moins un moyen de transmission (38, 40) sur le dispositif d'accouplement (28).
EP14745086.0A 2013-08-16 2014-07-30 Engrenage différentiel pour essieu moteur d'un véhicule automobile Withdrawn EP3033550A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013013693.8A DE102013013693B4 (de) 2013-08-16 2013-08-16 Sperrdifferenzialgetriebe für eine Antriebsachse eines Kraftfahrzeugs sowie Verfahren zum Betätigen des Sperrdifferenzialgetriebes
PCT/EP2014/002083 WO2015022053A1 (fr) 2013-08-16 2014-07-30 Engrenage différentiel pour essieu moteur d'un véhicule automobile

Publications (1)

Publication Number Publication Date
EP3033550A1 true EP3033550A1 (fr) 2016-06-22

Family

ID=51260833

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14745086.0A Withdrawn EP3033550A1 (fr) 2013-08-16 2014-07-30 Engrenage différentiel pour essieu moteur d'un véhicule automobile

Country Status (5)

Country Link
US (1) US9945465B2 (fr)
EP (1) EP3033550A1 (fr)
CN (1) CN105452730B (fr)
DE (1) DE102013013693B4 (fr)
WO (1) WO2015022053A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017214916B4 (de) * 2017-08-25 2021-10-07 Audi Ag Differentialgetriebeeinrichtung mit schaltbarer Torque Vectoring-Funktionalität

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DE3212495C2 (de) * 1982-04-03 1985-08-29 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart Sperrbares Differentialgetriebe für Kraftfahrzeuge
DE3313283A1 (de) * 1983-04-13 1984-10-25 Daimler-Benz Ag, 7000 Stuttgart Sperrdifferential mit einer in einem differentialgetriebegehaeuse angeordneten sperrkupplung, die von einem in einem achsgehaeuse angeordneten aeusseren stellglied der axialkolben-zylinder-bauart betaetigt wird
DE3861591D1 (de) 1987-03-21 1991-02-21 Zahnradfabrik Friedrichshafen Anordnung einer elektromagnet-zahnkupplung.
DE3808066A1 (de) * 1987-03-21 1988-09-29 Zahnradfabrik Friedrichshafen Anordnung einer elektromagnet-zahnkupplung
DE3738280A1 (de) 1987-11-11 1989-06-01 Opel Adam Ag Lamellensperrdifferential fuer kraftfahrzeuge, insbesondere frontgetriebene personenkraftwagen
US4976667A (en) * 1988-02-10 1990-12-11 Eaton Corporation Differential clutch and lever actuation system therefor
WO1989010279A1 (fr) * 1988-04-30 1989-11-02 Zahnradfabrik Friedrichshafen Ag Tracteur toutes roues motrices
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US5019021A (en) 1990-07-02 1991-05-28 Eaton Corporation Modulating limited slip differential
US5531653A (en) * 1995-01-13 1996-07-02 Dana Corporation Selectively lockable differential assembly
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DE19929070A1 (de) 1999-06-25 2000-12-28 Zahnradfabrik Friedrichshafen Ausgleichsgetriebe
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DE20312418U1 (de) 2003-08-12 2004-12-23 Offrotec Gmbh Betätigungseinrichtung für ein Sperrdifferentialgetriebe
JP5123893B2 (ja) * 2009-06-03 2013-01-23 本田技研工業株式会社 差動制限機構付き差動装置
CN101737478B (zh) 2010-02-05 2012-06-27 浙江理工大学 一种驱动限滑差速器
JP2011196467A (ja) * 2010-03-19 2011-10-06 Honda Motor Co Ltd 車両の最終減速装置
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DE102012014004A1 (de) 2011-10-17 2013-04-18 Rainer Drexler Lamellensperre mit Differenzialgehäuse
CN102829152B (zh) 2012-09-15 2016-08-17 浙江理工大学 一种回流式液压限滑差速器

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See also references of WO2015022053A1 *

Also Published As

Publication number Publication date
US20160186849A1 (en) 2016-06-30
WO2015022053A1 (fr) 2015-02-19
DE102013013693A1 (de) 2015-02-19
DE102013013693B4 (de) 2020-10-08
CN105452730A (zh) 2016-03-30
US9945465B2 (en) 2018-04-17
CN105452730B (zh) 2018-02-13

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