WO2008071302A1 - Embrayage à friction pour la chaîne cinématique d'un véhicule - Google Patents

Embrayage à friction pour la chaîne cinématique d'un véhicule Download PDF

Info

Publication number
WO2008071302A1
WO2008071302A1 PCT/EP2007/010172 EP2007010172W WO2008071302A1 WO 2008071302 A1 WO2008071302 A1 WO 2008071302A1 EP 2007010172 W EP2007010172 W EP 2007010172W WO 2008071302 A1 WO2008071302 A1 WO 2008071302A1
Authority
WO
WIPO (PCT)
Prior art keywords
friction
friction elements
arrangement
rotation
fluid
Prior art date
Application number
PCT/EP2007/010172
Other languages
German (de)
English (en)
Inventor
Jörg SUDAU
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
Priority to EP07846773A priority Critical patent/EP2089636A1/fr
Publication of WO2008071302A1 publication Critical patent/WO2008071302A1/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
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
    • F16D13/52—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member
    • 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
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/72—Features relating to cooling
    • 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
    • F16D25/123—Details not specific to one of the before-mentioned types in view of cooling and lubrication

Definitions

  • the present invention relates to a friction clutch for the drive train of a vehicle.
  • a friction clutch for the drive train of a vehicle.
  • a torque transmission connection can be produced between a drive unit having a drive element, for example an internal combustion engine, and a transmission providing an output device or another module following in the torque flow.
  • a piston member which divides the interior of the housing assembly into two subspaces, the friction elements can be frictionally engaged and thus a torque between the housing assembly and a driven hub to be coupled to an output hub are produced.
  • a subspace of the inner space substantially formed between the piston element and a part of the housing arrangement can be supplied with fluid under elevated pressure, so that the piston element is displaced by the increased fluid pressure.
  • a torsional vibration damper arrangement which in the Torque flow between the housing assembly and a first group of friction elements may lie or may lie in the torque flow between a second group of the friction elements and the output hub and thus the output member.
  • the torsional vibration damper arrangement with its essential components in particular also the damper element arrangement of the same, is arranged in the radially outer region of the housing arrangement, ie radially outside the two groups of friction elements.
  • the damper element arrangement of the torsional vibration damper arrangement is arranged lying radially between the two groups of friction elements and the output hub.
  • This known wet-running friction clutch assembly is also of the so-called two-line type. That is, there is only a first conduction path, via which fluid is fed into the interior of the housing assembly, and a second conduction path, via which fluid is withdrawn from the interior of the housing assembly.
  • the first conduction path is formed in a serving as output member output shaft, generally a transmission input shaft, as a central opening and opens radially inward in the above-mentioned subspace a.
  • One or a plurality of connection openings is created in the piston element, which forms a fluid exchange connection between this part space and the other subspace containing the two groups of friction elements.
  • pressurized fluid first flows into the first-mentioned subspace and via the openings provided in the piston element into the second subspace, where it can flow around the friction elements and is conveyed via a skimming mechanism from the radially outer region radially inward and then out of there Interior of the housing assembly deducted.
  • a friction clutch for the drive train of a vehicle comprising a housing assembly to be coupled to a drive member for common rotation about a rotation axis and at least partially filled or filled with fluid, a first group of friction elements a second group of friction elements, which are frictionally engageable by a piston element with the friction elements of the first group of first friction elements and by means of a second Reibelementenoughs with a primary side of a Torsionsschwingungsdämpferan extract to common rotation about the axis of rotation are coupled, wherein the Torsionsschwingungsdämpferan Aunt has a secondary side, which is to be coupled with a driven member for common rotation about the axis of rotation u nd is coupled to the primary side via a damper element arrangement for transmitting torque and for relative rotation with respect to each other about the rotation axis, wherein the damper element arrangement is arranged radially inwardly or radially outwardly with respect to the
  • a wet-running friction clutch for the drive train of a vehicle comprising a housing arrangement, which is to be coupled to a drive member for common rotation about an axis of rotation and at least partially filled or filled with fluid Friction elements, which are coupled by means of a first Reibelementenwents with the housing assembly for common rotation about the axis of rotation, a second group of friction elements which are frictionally engageable by a piston member with the friction elements of the first group of first friction elements and by means of a second Reibelementenoughs with a primary side a torsional vibration damper assembly for common rotation about the axis of rotation are coupled, wherein the Torsionsschwingungsdämpferanssen has a secondary side, which with a driven member for rotation together the rotation axis is to be coupled and is coupled to the primary side via a damper element arrangement for transmitting torque and for relative rotation with respect to each other about the axis of rotation,
  • the gate sion vibration damper assembly on the output side that is provided in the torque flow between the second group of friction elements and the output member, while nevertheless the damper element arrangement is arranged in the radially outer region, ie radially outward with respect to the two groups of friction elements.
  • the second friction element carrier can be arranged radially inside the first friction element carrier.
  • the two spatial regions, which are formed in the first subspace by the presence of the Torsionsschwingungsdämpferan extract, are preferably radially outside of the second Reibelementenhovs in fluid communication. This means that the fluid circulation that can be generated in the first subspace must necessarily go as far as radially outward into the area of the two groups of friction elements, so that a sufficient flow around these thermally comparatively heavily loaded subassemblies is ensured.
  • the fluid exchange connection of the two spatial regions is generated only radially outside the two groups of friction elements.
  • This can be achieved, for example, by virtue of the fact that at least one side of the primary side and the secondary side has at least one disk element which generates a substantially fluid-tight separation between the two spatial regions radially outward at least up to the radially further inwardly disposed one of the two friction element carriers.
  • the damper element arrangement when the damper element arrangement is arranged radially outward with respect to the two groups of friction elements and thus components of the primary side and the secondary side of the generally radially inner coupling to an output member into this area radially outward, so also on the radial Extending portion of the two groups of friction, it is advantageous if at the same time the torsional vibration damper assembly forms an abutment for the two groups of friction elements when acted upon by the piston member.
  • the housing arrangement form an abutment for the two groups of friction elements when they are acted upon by the piston element.
  • an abutment element provided on the first friction element carrier to form an abutment for the two groups of friction elements when they are acted upon by the piston element.
  • the first friction element carrier can be fixedly connected to the housing arrangement or integrally formed therewith, ie as integrated into an assembly of the housing arrangement.
  • the second friction element carrier may be fixedly connected to or integral with a disc element of the primary side of the torsional vibration damper arrangement cooperating with the damper element arrangement.
  • FIG. 1 is a partial longitudinal sectional view of a wet-running friction clutch according to a first embodiment
  • FIG. 2 is a partial longitudinal sectional view of a wet-running friction clutch according to a second embodiment
  • FIG. 3 is a partial longitudinal sectional view of a wet-running friction clutch according to a third embodiment
  • FIG. 4 is a partial longitudinal sectional view of a wet-running friction clutch according to a fourth embodiment.
  • a wet-running friction clutch according to a first embodiment is generally designated by the reference numeral 10.
  • Friction clutch 10 includes a housing assembly 12, which is essentially constructed with two formed, for example, as sheet metal parts housing parts 14 and 16. These two housing parts 14 and 16 are radially outward through
  • Housing part 14 is radially inward, for example by welding a
  • Housing hub 18 firmly connected to a bearing lug 20 for radial Abst ⁇ tzung the housing assembly 12, for example, in a corresponding recess of a drive shaft.
  • This drive shaft so for example a crankshaft of an internal combustion engine can be coupled via a flex plate or the like with a plurality of coupling portions 22 on the housing part 14 for common rotation about a rotation axis A.
  • the housing part 16 is fixed radially inside with a pump hub 24, for example by welding.
  • This pump hub 24 can be arranged engaging, for example, in a transmission housing to drive upon rotation of the housing assembly 12 about the axis of rotation A lying in the transmission fluid pump.
  • Friction elements 28 of a first group 30 of friction elements are coupled to the first friction element carrier 26 in meshing engagement and thus coupled therewith for common rotation about the axis of rotation A, but axially movable with respect thereto.
  • This axial movement is limited by a ring-like abutment member 32 to which in FIG. 1 furthest to the right, so furthest from the housing part 14 lying friction element of the first group 30 of friction elements in axial contact.
  • a second group 34 of friction elements comprises a plurality of friction elements 36 which are arranged alternately with respect to the friction elements 28 of the first group 30 of friction elements and are in meshing engagement with a likewise annular second friction element carrier 38.
  • the friction elements 36 of the second group 34 of friction elements are in this way coupled to the second friction element carrier 38 for common rotation about the axis of rotation A, with respect to this, however, to a small extent axially movable.
  • the friction elements of at least one of the groups 30, 34 can be formed by friction elements with friction linings, while the friction elements of the other group then do not have such friction linings.
  • the friction elements are preferably made of Sheet metal material can be formed with the ring-like structure and the toothing on the radially outer or radially inner peripheral region.
  • the second friction element carrier 38 is fixedly connected to a primary side, generally designated 40, of a torsional vibration damper arrangement 42.
  • the primary side 40 has two cover plate elements 46, 48 fixedly connected to one another by rivet bolts 44 and arranged at a defined axial distance.
  • the cover disk element 48 is guided from a region radially outwardly of the first friction element carrier 26 radially inward to the second friction element carrier 38 and fixedly connected thereto by rivet bolts 50.
  • the two cover disk elements 46, 48 form support regions for a damper element arrangement 52, which may comprise a plurality of circumferentially successively arranged damper springs in a known manner.
  • a secondary side 54 of the Torsionsschwingungsdämpferan extract 42 includes a with its radially outer region between the two cover disk elements 46, 48 engaging and cooperating with the damper element assembly central disk element 56 which is fixed radially inside by rivet bolts 58 with an output hub 60 for common rotation about the axis of rotation A.
  • This output hub 60 and thus the entire Torsionsschwingungsdämpferan effet 42 is supported by a ring ball bearing 62 or other bearing assembly with respect to the housing assembly 12 both radially and preferably also axially and rotatably supported.
  • a piston element 64 divides an inner space 66 of the housing arrangement 12 into a first partial space 68 containing the torsional vibration damper arrangement 42 and also the two groups 30 and 34 of friction elements and a second partial space 70 formed essentially between the piston element 64 and the housing part 14.
  • the piston element 64 in the illustration of FIG. 1 can move in the direction of the two Groups 30, 34 are moved by friction elements and thus press them together in frictional engagement with each other. It is then a torque between the housing assembly 12 and an output member, not shown in FIG. 1 via the two groups 30, 34 of friction elements, the Torsionsschwingungsdämpferan extract 42 and the output hub 60 transmitted.
  • At least one channel 72 leading radially outward and open to the second partial space 70 is provided in the housing hub 18.
  • This pressurized fluid can be supplied via an opening shown in the output shaft, not shown.
  • this output shaft is then supported or mounted fluid-tightly to the right of the channel 72 with respect to the housing hub 18.
  • This has the consequence that the fluid supply or the fluid removal for the second subspace 70 can be completely independent of other fluid flows described below. In particular, this also contributes to the fact that there is no fluid exchange connection between the two subspaces 70, 68.
  • the piston element 64 is radially outwardly axially displaceable relative to the housing part 14 and radially inwardly with respect to the housing hub 18 axially displaceable and otherwise also no fluid exchange opening or the like has up.
  • the first subspace 68 is divided by the torsional vibration damper assembly 42 into two spatial regions 76 and 78.
  • the space region 76 which is thus formed in the illustration of FIG. 1 between the housing part 14 and the piston member 64 on the one hand and the Torsionsschwingungsdämpferan Aunt 42 on the other hand, contains the two groups 30, 34 of friction elements.
  • the second space area 78 is substantially flat and disc-shaped, in the radially outer area between the cover disk element 48 and the housing part 16 and in the radially inner area between the central disk element 56 and the housing part 16. A fluid exchange connection exists between these two space areas 76 and 78 essentially only radially outside of Torsional vibration damper assembly 42 in a flow region 80th
  • the fluid which is required in the first subspace 68 and in particular in the first space area 76 thereof in order to dissipate heat out of the area of the friction elements 28, 36 is supplied via one or more channels 82 in the output hub 60.
  • the one or more channels 82 are in communication with a feed channel, which may be formed between an outer surface of the output shaft, not shown, and an inner surface of a support shaft, also not shown, for the output hub 60.
  • radially fluid introduced internally also flows radially outward as a result of centrifugal force and, although the ring ball bearing 62 is not necessarily made fluid-tight, can not reach the region of the channel or channels 72, since, as already stated, the output shaft is sealed with respect to the housing hub 18.
  • the fluid thus flows radially outward, can flow around the surfaces of the friction elements 28, 36 and possibly circulate around the area of these surfaces. It then passes even further radially outward into the flow region 80 and from this via the second space region 78 radially inward. There, via one or more channels 84, the fluid can then flow out, between the inner surface of the pump hub 24 shown and an outer surface of the support shaft, not shown.
  • the fluid circulation for the first partial space 68 can be set independently of the engagement state or disengagement state, that is, the respective actuation state of the piston element 64. Due to the fact that the torsional vibration damper 42 is designed so that the two space portions 76, 78 are completely fluid-tightly separated from each other at least up to the radial area of the rivet bolts 44, the fluid flowing into the first space region 76 must also forcibly into the radial region of the two groups 30, 34 of friction elements flow before it can reach the second space area 78.
  • cover plate member 46 is guided in its radially inner end portion to close to the radially outer end portion of the output hub 60 and there continue the cover plate member 46 and as well as the cover plate member 48 are only a small distance from the central disk element 56, practically a substantial fluid exchange is only radially outside in the flow region 80 possible.
  • FIG. 1 A modified embodiment is shown in FIG.
  • components which correspond to components described above in terms of structure and function are denoted by the same reference numerals with the addition of the appendix "a".
  • Output hub 60a on. It can be seen that the cover disk element 46a is also closed in the radial region in which the damper element arrangement 52a lies, in order to ensure that the two spatial regions 76a, 78a extend radially outward to the region of the second friction element support 38a and thus the two groups 30a and 34a are separated from one another by friction elements.
  • the output hub 60a is supported with respect to the housing hub 18a on the one hand and with respect to the housing assembly 12a, in particular of the housing part 16a, on the other hand by respective thrust bearings 86a, 88a in the axial direction. These two bearings 86a, 88a can be designed as Wälz Archiveslager. In the area of the bearing 86a, the channel or channels 82a are formed.
  • the channel or channels 84a are formed.
  • the first friction element carrier 26a forms an integral part of the housing arrangement 12a.
  • the two housing parts 14a, 16a are substantially disk-like and are connected radially outward with a third housing part 90a by welding.
  • This third, approximately cylindrically shaped housing part 90a provides on its inner peripheral side the toothing for coupling with the friction elements 28a of the first group of friction elements 30a.
  • the piston element 64a is located radially inward with respect to the two groups 30a and 34a of friction elements and has a further radially outwardly extending annular or arm-like loading section 92a which engages in the radial region of the friction elements 28a and 36a, respectively, and when the pressure increases in the second Part space 70a presses against each other. In this case, then forms the housing assembly 12a with the housing part 16a, the abutment.
  • FIG. Another embodiment of a friction clutch is shown in FIG.
  • components which correspond to components described above in terms of structure or function, with the same reference numerals below Addition of Annex "b".
  • the two groups 30b and 34b of friction elements are again approximately in the same, central radial region, as in the embodiment shown in Fig. 1.
  • the friction element 110b can also be omitted if the hub part 94b takes over the support of the groups 30b and 34b.
  • Torsional vibration damper assembly 42b is radially outward and axially overlapping with the two groups 30b and 34b of friction elements.
  • the torsional vibration damper arrangement or its primary side 40b here comprises a single disk part 94b, on which the second friction element carrier 38b is fixed by the rivet bolts 50b and which is directly adjacent to the two groups 30b and 34b axially by friction elements.
  • This disk part 94b of the primary side 40b thus forms the abutment for the two groups 30b, 34b of friction elements when they are pressed against each other by the piston element 64b.
  • the disk part 94b is supported radially inwards via a bearing 96b axially on the output hub 60b, which in turn is axially supported by the bearing 88b on the housing arrangement 12b.
  • the secondary side 54b of the torsional vibration damper arrangement 42b here also comprises a single disk part 98b, which is fixed radially inward, for example by welding on the output hub 60b and radially outwardly, the two groups 30b, 34b of friction elements axially overlapping, into the region of the damper element assembly 52b ranges and surrounds there to provide a suitable support area.
  • this disc part 98b of the first subspace 68b is again divided into the two space regions 76b, 78b.
  • the fluid supply into this first subspace 68b takes place via a channel-like intermediate space 100b formed between the housing hub 18b and the output hub 60b, in the flow region of which the ring ball bearing 62b which is generally not formed in a fluid-tight manner lies.
  • the fluid removal from the first subspace 68b takes place again in the between the Housing hub 60b and the housing assembly 12b formed channel-like gap 84b, in the flow region now also not fluid-tight bearing 88b is arranged.

Landscapes

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

Abstract

Embrayage à friction pour la chaîne cinématique d'un véhicule, comprenant : un ensemble carter (12) à accoupler à un organe d'entraînement en rotation conjointe autour d'un axe de rotation (A) et rempli ou pouvant être rempli au moins partiellement de fluide ; un premier groupe (30) d'éléments de friction qui, au moyen d'un premier porte-éléments de friction (26), sont accouplés à l'ensemble carter (12) en rotation conjointe autour de l'axe de rotation (A) ; un deuxième groupe (34) d'éléments de friction qui, par un élément formant piston (64), peuvent être amenés en engagement de friction avec les éléments de friction (28) du premier groupe (30) d'éléments de friction et qui, au moyen d'un deuxième porte-éléments de friction (38), sont accouplés à un côté primaire (40) d'un ensemble amortisseur de vibrations de torsion (42) en rotation conjointe autour de l'axe de rotation (A). L'ensemble amortisseur de vibrations de torsion (42) présente un côté secondaire (54) qui doit être accouplé à un organe de sortie en rotation conjointe autour de l'axe de rotation (A) et qui est accouplé au côté primaire (40) par l'intermédiaire d'un ensemble (52) d'éléments amortisseurs pour la transmission de couple et pour une rotation relative l'un par rapport à l'autre autour de l'axe de rotation (A). L'ensemble (52) d'éléments amortisseurs est disposé radialement à l'intérieur ou radialement à l'extérieur par rapport aux deux groupes (30, 34) d'éléments de friction. L'élément formant piston (64) divise la chambre intérieure (66) de l'ensemble carter (12) en une première chambre partielle (68) qui contient l'ensemble amortisseur de vibrations de torsion (42), et une deuxième chambre partielle (70) dans laquelle afin de réaliser l'engagement de friction des éléments de friction (28, 36) des deux groupes (30, 34) d'éléments de friction, la pression du fluide doit être augmentée par rapport à la pression du fluide dans la première chambre partielle (68), sachant qu'il n'existe pas de liaison d'échange de fluide entre la première chambre partielle (68) et la deuxième chambre partielle (70). L'ensemble amortisseur de vibrations de torsion (42) divise la première chambre partielle (68) en une première région de chambre (76) contenant les deux groupes (30, 34) d'éléments de friction et une deuxième région de chambre (78), sachant qu'un ensemble canal d'alimentation en fluide (72) est ouvert vers une des deux régions de chambre (76, 78) et qu'un ensemble canal d'évacuation de fluide (84) est ouvert vers l'autre région de chambre (76, 78).
PCT/EP2007/010172 2006-12-13 2007-11-23 Embrayage à friction pour la chaîne cinématique d'un véhicule WO2008071302A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP07846773A EP2089636A1 (fr) 2006-12-13 2007-11-23 Embrayage à friction pour la chaîne cinématique d'un véhicule

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006058666.2 2006-12-13
DE102006058666A DE102006058666A1 (de) 2006-12-13 2006-12-13 Reibungskupplung für den Antriebsstrang eines Fahrzeugs

Publications (1)

Publication Number Publication Date
WO2008071302A1 true WO2008071302A1 (fr) 2008-06-19

Family

ID=39110525

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/010172 WO2008071302A1 (fr) 2006-12-13 2007-11-23 Embrayage à friction pour la chaîne cinématique d'un véhicule

Country Status (3)

Country Link
EP (1) EP2089636A1 (fr)
DE (1) DE102006058666A1 (fr)
WO (1) WO2008071302A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3073786A1 (fr) * 2017-11-22 2019-05-24 Valeo Embrayages Dispositif de transmission pour vehicule hybride

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019116593A1 (de) * 2019-03-20 2020-09-24 Schaeffler Technologies AG & Co. KG Mehrscheibenkupplung mit optimierter Verschiebereibung; Hybridmodul, Doppelkupplungseinrichtung sowie Antriebsstrang
DE102021001317B4 (de) 2021-03-11 2024-07-04 Mercedes-Benz Group AG Hybridantriebssystem für ein Kraftfahrzeug

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19917893A1 (de) * 1999-04-20 2000-10-26 Mannesmann Sachs Ag Kupplungseinrichtung, insbesondere Anfahrelement, mit einstellbarer Kupplungskühlung für hohe Verlustleistung
EP1584830A1 (fr) * 2004-04-10 2005-10-12 BorgWarner Inc. Dispositif d'embrayage, en particulier dispositif d'embrayage de démarrage
DE102005030192A1 (de) * 2004-07-22 2006-02-16 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Vorrichtung zum Wirkverbinden eines Verbrennungsmotors mit einem Getriebe

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19917893A1 (de) * 1999-04-20 2000-10-26 Mannesmann Sachs Ag Kupplungseinrichtung, insbesondere Anfahrelement, mit einstellbarer Kupplungskühlung für hohe Verlustleistung
EP1584830A1 (fr) * 2004-04-10 2005-10-12 BorgWarner Inc. Dispositif d'embrayage, en particulier dispositif d'embrayage de démarrage
DE102005030192A1 (de) * 2004-07-22 2006-02-16 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Vorrichtung zum Wirkverbinden eines Verbrennungsmotors mit einem Getriebe

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3073786A1 (fr) * 2017-11-22 2019-05-24 Valeo Embrayages Dispositif de transmission pour vehicule hybride

Also Published As

Publication number Publication date
EP2089636A1 (fr) 2009-08-19
DE102006058666A1 (de) 2008-06-19

Similar Documents

Publication Publication Date Title
DE10223780C1 (de) Gangschaltgetriebe für ein Kraftfahrzeug mit hydraulisch betätigbarer Mehrfachkupplung
EP2504597B1 (fr) Dispositif de transfert de couple
DE112010004839B4 (de) Drehmomentübertragungseinrichtung
EP1646799B1 (fr) Systeme d'embrayage dans une boite de vitesses automatique a alimentation de refrigerant a encombrement reduit
EP1339995B1 (fr) Systeme d'embrayage a double disque ou a disques multiples et dispositif de disques associe
EP1637766B1 (fr) Amortisseur de vibrations de torsion
DE10064459B4 (de) Doppelkupplung, insbesondere für Kraftfahrzeuge
DE102010051447A1 (de) Kupplungseinrichtung
EP2123929B1 (fr) Agencement d'accouplement, notamment destiné à l'accouplement rotatif sélectif d'un arbre d'entrée d'un compresseur dans un véhicule doté d'un organe d'entraînement
DE112011100816B4 (de) Anfahreinheit mit Flüssigkeitskupplung
WO2014026685A1 (fr) Module hybride à embrayage de coupure pour une chaîne cinématique d'un véhicule à moteur
WO2012013173A1 (fr) Dispositif d'embrayage
DE102013216333A1 (de) Mehrfachkupplungsvorrichtung, insbesondere Doppelkupplungsvorrichtung
WO2010081451A1 (fr) Ensemble embrayage
WO2010133198A1 (fr) Double embrayage humide
DE102010034128A1 (de) Parallele Doppelkupplungseinrichtung
DE10301405B4 (de) Mehrfach-Kupplungseinrichtung, insbesondere Doppel-Kupplungseinrichtung, mit einer mechanischen, über eine Drehlageranordnung wirkenden Betätigungsanordnung
EP1826459A1 (fr) Convertisseur de couple avec embrayage de pontage
DE102020127039B4 (de) Getriebe
WO2008071302A1 (fr) Embrayage à friction pour la chaîne cinématique d'un véhicule
DE102010023715A1 (de) Doppelkupplung
WO2020052705A1 (fr) Système d'embrayage et unité d'entraînement
EP3759371B1 (fr) Système d'embrayage et unité d'entraînement présentant ce système d'embrayage
WO2009146967A1 (fr) Système de transmission de couple pour la chaîne cinématique d'un véhicule
WO2020052703A1 (fr) Système d'embrayage à actionnement entièrement hydraulique et unité d'entraînement

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 07846773

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 2007846773

Country of ref document: EP