WO2009021582A1 - Dispositif d'embrayage avec compensation des fuites d'huile améliorée - Google Patents

Dispositif d'embrayage avec compensation des fuites d'huile améliorée Download PDF

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Publication number
WO2009021582A1
WO2009021582A1 PCT/EP2008/005414 EP2008005414W WO2009021582A1 WO 2009021582 A1 WO2009021582 A1 WO 2009021582A1 EP 2008005414 W EP2008005414 W EP 2008005414W WO 2009021582 A1 WO2009021582 A1 WO 2009021582A1
Authority
WO
WIPO (PCT)
Prior art keywords
actuating piston
coupling device
sealing element
pressure chamber
disk
Prior art date
Application number
PCT/EP2008/005414
Other languages
German (de)
English (en)
Inventor
Frank GÜNTER
Reinhard Kappel
Original Assignee
Borgwarner Inc.
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 Borgwarner Inc. filed Critical Borgwarner Inc.
Priority to DE112008002026.4T priority Critical patent/DE112008002026B4/de
Publication of WO2009021582A1 publication Critical patent/WO2009021582A1/fr

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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/12—Details not specific to one of the before-mentioned types
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F16D2021/0661—Hydraulically actuated multiple lamellae clutches

Definitions

  • the present invention relates to a coupling device with a compressible disk set, a disk carrier associated with the disk carrier and an axially displaceable actuating piston for compressing the disk set, wherein by rotation of the coupling means a radially extending first
  • Coupling devices in particular multi-disc clutches, are known from the prior art, which have a compressible disk set, a disk carrier associated with the disk set and an axially displaceable actuating piston for compressing the disk pack.
  • a first pressure chamber On the one side of the actuating piston, a first pressure chamber is provided, which can be pressurized in such a way that the actuating piston can be displaced in the axial direction.
  • a first compensation chamber is provided which is delimited by the actuating piston and the disk carrier.
  • Centrifugal oil column acting on the actuating piston generated opposite axial force.
  • the actuating piston and the plate carrier are pushed into each other in the axial direction or nested in the radial direction such that the first Fliehölklale in the first pressure chamber and the second Fliehölklale in the first expansion chamber have different lengths.
  • This results in rotation of the known coupling means that either the axial force in one direction or the axial force in the other direction is greater, so that the actuating piston is always urged in one of the two axial directions during operation of the known coupling devices.
  • a stronger spring element must be provided for returning the piston to its starting position.
  • the coupling device according to the invention which is preferably a double clutch, has a compressible disk set.
  • a compressible disk set may, for example, be understood to mean a disk set consisting of outer disk or driven-side outer disk and inner disk or drive-side disk.
  • the coupling device further comprises a plate carrier associated with the plate carrier, at which may be, for example, an outer or inner plate carrier.
  • the coupling device has an axially displaceable actuating piston for compressing the disk pack. On the one side of the actuating piston, a first pressure chamber is provided, which can be pressurized in such a way that the actuating piston can be displaced in the axial direction.
  • a first compensation chamber is provided which is delimited by the actuating piston and the disk carrier.
  • the first pressure chamber and the first compensation chamber can be filled with oil, wherein by rotation of the coupling device in the first pressure chamber by a radially extending first Fliehölklale acting on the actuating piston axial force and in the first compensation chamber by a radially extending second Fliehölklakulle acting on the actuating piston opposite axial force can be generated.
  • an overflow channel or an overflow opening for partial removal of the oil from the first compensation chamber opens into the first compensation chamber such that the length of the second centrifugal oil column is shortened in the radial direction such that the opposing axial forces acting on the actuating piston equalize.
  • the invention has the advantage that on the one hand a complete centrifugal oil balance is achieved and on the other hand, the axial length of the coupling device can be low.
  • the latter can be attributed to the fact that the first pressure chamber and the first compensation chamber can be of different lengths in the radial direction in order to achieve optimized nesting of actuating piston and plate carrier, especially since centrifugal oil compensation is achieved by a simple, appropriately positioned overflow channel or an overflow opening. is enough.
  • centrifugal oil compensation is achieved by a simple, appropriately positioned overflow channel or an overflow opening. is enough.
  • a low restoring force spring element is required to hold the actuating piston in its initial position.
  • a sealing element is provided between the actuating piston and the plate carrier, which is arranged on the actuating piston such that the overflow channel is formed between the actuating piston and the sealing element.
  • the overflow opening can be provided in the sealing element, wherein said overflow channel is preferred.
  • the sealing element is fastened to the actuating piston in a further preferred embodiment.
  • the sealing element can be displaced in the axial direction together with the actuating piston.
  • the sealing element is plugged in a further preferred embodiment of the coupling device according to the invention on the actuating piston.
  • the sealing element can be attached to a protruding bulge of the actuating piston. So that the axial forces, which arise through the second flow column in the first compensation chamber, can be transferred securely to the actuating piston via the sealing element, the sealing element in a further preferred embodiment of the inventive coupling device is in the axial direction on the side of the actuating column facing the plate carrier - Bens truncated.
  • the sealing element is annular.
  • the sealing element can completely surround the hub of the coupling device and furthermore ensure a peripheral seal between the actuating piston, on the one hand, and the disk carrier, so that the first compensating chamber is completely sealed, at least in this area.
  • the inlet opening of the overflow channel is arranged radially further inwards than the outlet opening of the overflow channel.
  • the inlet opening of the overflow channel is preferably provided on the inner diameter of the sealing element, while the outlet opening of the overflow channel is preferably provided on the outer diameter of the sealing element.
  • the annular sealing element has an L-shaped cross-section.
  • one leg of the L-shaped cross-section is at a surface facing in the axial direction and the other leg of the L-shaped cross section is at a radially pointing upper surface. supported surface of the actuating piston. This also makes it possible that the sealing element can be supported and attached in a simple manner to a protruding bulge of the actuating piston.
  • the sealing element on its side facing the actuating piston side protruding support portions for support zen on the actuating piston.
  • the overflow channel can be particularly easily formed between the protruding support portions, the sealing member and the surface of the actuating piston, without a complex processing of the actuating piston itself would be required.
  • the overflow channel has an outlet opening, which opens into a different space than the first pressure chamber.
  • the overflow opening opens into a different space than the first pressure chamber, but here too, the aforementioned overflow channel is preferred. In both cases it is prevented that the pressure or oil pressure within the first pressure chamber is reduced or increased, whereby the control of the actuating piston is simplified.
  • the outlet opening or the overflow opening opens into a further space, which is delimited by the actuating piston and the plate carrier and arranged radially further outward than the compensating space. In this way it is ensured that the centrifugal oil exiting via the overflow channel from the first expansion chamber is safely removed is and the first pressure chamber is not affected by this.
  • the plate carrier is an outer plate carrier.
  • the structure of the coupling device according to the invention also allows a short axial length of the same in this embodiment.
  • the coupling device is designed at least as a double clutch, wherein a second actuating piston is provided for compressing a compressible second plate pack, which is associated with a second pressure chamber, which can be pressurized such that the second actuating piston in axial direction can be moved.
  • a coupling device which is configured as a double clutch to maintain the pressure within the second pressure chamber substantially has the Ü berlaufkanal an outlet opening, which opens into a ⁇ of the space as the second pressure chamber.
  • the overflow opening opens into a different space than the second pressure chamber.
  • the outlet opening or the overflow opening for example, open into the aforementioned further space, which is bounded by the actuating piston and the plate carrier.
  • the first disk pack is a radially outer disk. package and the second disk pack a radially inner disk set.
  • the first or second pressure chamber can be pressurized in such a way that the first or second actuating piston can be displaced in the axial direction counter to the restoring force of a spring element.
  • the spring element only has to apply a small restoring force due to the centrifugal oil compensation according to the invention in order to push the first or second actuating piston back into its starting position.
  • Such a spring element with a lower restoring force thus reduces the weight of the coupling device according to the invention and can also contribute to a shorter axial length of the same. Furthermore, the controllability or sensitivity of the coupling device is improved.
  • FIG. 1 is a side view of an embodiment of the coupling device according to the invention in a sectional representation
  • Fig. 1 shows an embodiment of the coupling device 2 according to the invention in cross section, wherein relative to the longitudinal or rotational axis 4, about which rotate the rotatable parts of the coupling device 2, only the upper part is shown.
  • the coupling device 2 is designed as a multi-plate clutch in the form of a double clutch.
  • the coupling device 2 has a motor-side input hub 6.
  • the input hub 6 is rotatably connected to a drive plate 8.
  • the driver disk 8 is non-rotatably connected to an outer disk carrier 10.
  • the outer disk carrier 10 has an outer support section 12 and an inner support section 14. While the outer support section 12 is connected in a rotationally fixed manner to the outer lamellae of an outer, compressible first lamella packet 16, the inner support section 14 is connected in a rotationally fixed manner to the outer lamellae of an inner, compressible second lamella packet 18.
  • the coupling device 2 also has an outer inner disk carrier 20 and an inner inner disk carrier 22. At their radially outward-pointing end, both inner disk carriers 20, 22 each have a carrying section 24, 26 which is connected in a rotationally fixed manner to the inner disks of the first disk set 16 or to the inner disks of the second disk pack 18.
  • the outer inner disk carrier 20 is rotatably connected at its radially inwardly facing end to a first output hub 28, while the inner venezlamellen- carrier 22 is rotatably connected at its radially inwardly facing end with a second output hub 30.
  • the coupling device 2 furthermore has an axially displaceable first actuating piston 32 for compressing the first disk set 16 together and an axially displaceable second actuating piston 34 for the purpose of compressing the first disk set 16. mendrucken the second plate pack 18.
  • a first pressure chamber 36 and a second pressure chamber 38 is formed on each side of the first and second actuating piston 32, 34.
  • the pressure spaces 36 and 38 can be filled with oil in the clutch hub 44 via a respective bore 40 or 42 and thus be pressurized such that the first or second actuating piston 32, 34 counteracts the restoring force of a spring element 46 or 48 is moved in the axial direction.
  • FIG. 2 shows the detail A of FIG. 1 enlarged.
  • a first compensation chamber 50 is provided on the other side of the first actuating piston 32.
  • the second actuating piston 34 also has a second compensation chamber 52 (FIG. 1).
  • the first compensation chamber 50 is bounded by the first actuating piston 32, the outer disk carrier 10 and the clutch hub 44, wherein a later explained closer sealing element seals a gap between the Betati ⁇ tion piston 32 and the outer disk carrier 10.
  • a further bore 54 is also provided in the clutch hub 44, which ports into the first compensation chamber 50.
  • the first actuating piston 32 and the outer disk carrier 10 are bulged in an axial direction in the region of the first pressure chamber 36 and the first compensation chamber 50 in such a way that they can be pushed into one another in the axial direction or are arranged nested in the radial direction.
  • the sealing element 56 is annular. forms and attached to the actuating piston 32.
  • the sealing element 56 has an L-shaped cross-section and is plugged onto the first actuating piston 32 in the region of the bulge. In this case, the sealing element 56 is supported in the axial direction on the side of the first actuating piston 32 facing the outer disk carrier 10.
  • an overflow channel 62 is formed between the protruding support sections 60 and is delimited in the axial direction by the first actuating piston 32 on the one hand and the radially extending leg 58 of the L-shaped cross section of the sealing element 56 on the other hand.
  • the overflow channel 62 opens with an inlet opening 64 which is arranged on the inner diameter of the sealing element 56, in the first compensation chamber 50.
  • the overflow channel 62 further points to the outer diameter of the sealing element 56 and thus in the region of the axially extending leg 66 of the L-shaped cross section of the sealing element 56 an outlet opening 68.
  • the outlet opening 68 of the overflow channel 62 opens into a further space 70, which is bounded by the first actuating piston 32 and the outer disk carrier 10 and radially further outside than the first compensation chamber 50, wherein the further space 70 by means of the sealing lip (no reference numeral) of the Sealing element 56 is sealed at least partially against the first compensation chamber 50.
  • the outlet opening 68 of the overflow channel 62 terminates neither in the first pressure chamber 36 nor in the second Pressure chamber 38.
  • the inlet opening 64 within the first compensation chamber 50 thus flows from a portion of the oil from the first compensation chamber 50, so that the fixed, second Fliehölklale only from the inlet opening 64 in the radial direction to the radially outermost boundary of the first compensation chamber 50th extends over a length c in the radial direction, which is smaller than the aforementioned length b.
  • the fixed second flow column with the shortened length c in the radial direction thus generates a fluid pressure within the first compensation chamber 50, which exerts an axial force on the first actuating piston 32 via the radially extending limb 58 of the L-shaped cross section of the sealing element 56, which in FIG. 2 indicated by the arrow 74 and the axial force 72 is opposite.
  • the length of the second flow column is here shortened by appropriate arrangement of Eint ⁇ ttso réelle 64 of the overflow channel 62 within the first compensation chamber 50 such that the opposite axial forces 72, 74 compensate or cancel.
  • This has the advantage, inter alia, that the spring element 46 only has to apply a small restoring force for returning the first actuating piston 32 to its initial position.
  • overflow channel 62 While only one overflow channel 62 has been described above, which is a preferred variant, the removal of the oil can also be effected via a simple overflow opening, which is preferably provided in the sealing element 56.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

L'invention concerne un dispositif d'embrayage (2) comprenant un paquet de disques compressibles (16), un support de disques (10) associé au paquet de disques (16) et un piston d'actionnement (32) déplaçable axialement pour comprimer le paquet de disques (16). Sur un côté du piston d'actionnement (32) est réalisé un premier espace de pression (36) qui peut être sollicité en pression de telle sorte que le piston d'actionnement (32) puisse être déplacé dans la direction axiale, et de l'autre côté du piston d'actionnement (32) est réalisé un premier espace de compensation (50) qui est limité par le piston d'actionnement (32) et le support de disques (10). Par rotation, la pression est augmentée dans le premier espace de pression (36) à travers une première colonne d'huile de fuite s'étendant radialement, de telle sorte qu'il en résulte une force axiale (72) agissant sur le piston d'actionnement (32). En même temps, par rotation dans le premier espace de compensation (50), la pression est augmentée sur la base d'une deuxième colonne d'huile de fuite s'étendant radialement, de telle sorte qu'une force axiale (74) opposée à la force axiale (72) soit en outre produite sur le piston d'actionnement (32). Conformément à l'invention, un canal de débordement (62) ou une ouverture de débordement débouche dans le premier espace de compensation (50) pour partiellement évacuer l'huile hors du premier espace de compensation (50), de telle sorte que la longueur (c) de la deuxième colonne d'huile de fuite soit raccourcie dans la direction radiale de sorte que les forces axiales (72, 74) agissant de manière opposée sur le piston d'actionnement (32) se compensent mutuellement.
PCT/EP2008/005414 2007-08-13 2008-07-03 Dispositif d'embrayage avec compensation des fuites d'huile améliorée WO2009021582A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112008002026.4T DE112008002026B4 (de) 2007-08-13 2008-07-03 Kupplungseinrichtung mit verbessertem Fliehölausgleich

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007038208.3 2007-08-13
DE102007038208 2007-08-13

Publications (1)

Publication Number Publication Date
WO2009021582A1 true WO2009021582A1 (fr) 2009-02-19

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PCT/EP2008/005414 WO2009021582A1 (fr) 2007-08-13 2008-07-03 Dispositif d'embrayage avec compensation des fuites d'huile améliorée

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Country Link
DE (1) DE112008002026B4 (fr)
WO (1) WO2009021582A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011023407A1 (fr) 2009-08-28 2011-03-03 Getrag Ford Transmissions Gmbh Système de double embrayage pour une boîte de vitesses munie de deux arbres d'entrée
FR3024511A1 (fr) * 2014-08-01 2016-02-05 Valeo Embrayages Dispositif d'embrayage pour un vehicule automobile
CN105317876A (zh) * 2014-08-01 2016-02-10 Valeo离合器公司 用于机动车辆的离合器装置
CN112594379A (zh) * 2020-12-23 2021-04-02 潍柴动力股份有限公司 充油压强补偿方法及系统、无级变速箱以及车辆
CN112997019A (zh) * 2018-11-12 2021-06-18 戴姆勒股份公司 具有第一离合器和第二离合器的离合设备

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1382875A1 (fr) * 2002-07-18 2004-01-21 BorgWarner Inc. Embrayage humide ou frein à plaque de friction
DE20320467U1 (de) * 2003-07-23 2004-09-16 Zf Friedrichshafen Ag Kupplungsanordnung in einem Automatgetriebe mit bauraumsparender Kühlmittelversorgung
EP1612444A1 (fr) * 2004-06-29 2006-01-04 BorgWarner Inc. Disposition d'embrayage multiple
JP2006125468A (ja) * 2004-10-27 2006-05-18 Koyo Sealing Techno Co Ltd 流体式変速機のクラッチシリンダ

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1988304B1 (fr) * 2007-05-02 2013-02-13 Schaeffler Technologies AG & Co. KG Agencement d'étanchéité et agencement de double couplage par voie humide doté d'un agencement d'étanchéité

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1382875A1 (fr) * 2002-07-18 2004-01-21 BorgWarner Inc. Embrayage humide ou frein à plaque de friction
DE20320467U1 (de) * 2003-07-23 2004-09-16 Zf Friedrichshafen Ag Kupplungsanordnung in einem Automatgetriebe mit bauraumsparender Kühlmittelversorgung
EP1612444A1 (fr) * 2004-06-29 2006-01-04 BorgWarner Inc. Disposition d'embrayage multiple
JP2006125468A (ja) * 2004-10-27 2006-05-18 Koyo Sealing Techno Co Ltd 流体式変速機のクラッチシリンダ

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011023407A1 (fr) 2009-08-28 2011-03-03 Getrag Ford Transmissions Gmbh Système de double embrayage pour une boîte de vitesses munie de deux arbres d'entrée
DE102009039223A1 (de) 2009-08-28 2011-05-26 Getrag Ford Transmissions Gmbh Doppelkupplungsanordnung für ein Getriebe mit zwei Eingangswellen
CN102625884A (zh) * 2009-08-28 2012-08-01 格特拉克·福特传动系统有限公司 用于设有两个输入轴的变速器的双离合器装置
DE102009039223B4 (de) * 2009-08-28 2013-02-21 Getrag Ford Transmissions Gmbh Doppelkupplungsanordnung für ein Getriebe mit zwei Eingangswellen
DE102009039223B8 (de) * 2009-08-28 2013-05-08 Getrag Ford Transmissions Gmbh Doppelkupplungsanordnung für ein Getriebe mit zwei Eingangswellen
US8997961B2 (en) 2009-08-28 2015-04-07 Getrag Ford Trasmissions GmbH Dual clutch assembly for a transmission having two input shafts
FR3024511A1 (fr) * 2014-08-01 2016-02-05 Valeo Embrayages Dispositif d'embrayage pour un vehicule automobile
CN105317877A (zh) * 2014-08-01 2016-02-10 Valeo离合器公司 用于机动车辆的离合器装置
CN105317876A (zh) * 2014-08-01 2016-02-10 Valeo离合器公司 用于机动车辆的离合器装置
EP2990680A3 (fr) * 2014-08-01 2016-07-27 Valeo Embrayages Dispositif d embrayage pour un véhicule automobile
CN105317877B (zh) * 2014-08-01 2019-01-15 Valeo离合器公司 用于机动车辆的离合器装置
CN112997019A (zh) * 2018-11-12 2021-06-18 戴姆勒股份公司 具有第一离合器和第二离合器的离合设备
CN112997019B (zh) * 2018-11-12 2023-05-26 梅赛德斯-奔驰集团股份公司 具有第一离合器和第二离合器的离合设备
CN112594379A (zh) * 2020-12-23 2021-04-02 潍柴动力股份有限公司 充油压强补偿方法及系统、无级变速箱以及车辆

Also Published As

Publication number Publication date
DE112008002026B4 (de) 2019-12-19
DE112008002026A5 (de) 2010-07-15

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