EP2089636A1

EP2089636A1 - Friction clutch for the drivetrain of a vehicle

Info

Publication number: EP2089636A1
Application number: EP07846773A
Authority: EP
Inventors: Jörg SUDAU
Original assignee: ZF Friedrichshafen AG
Current assignee: ZF Friedrichshafen AG
Priority date: 2006-12-13
Filing date: 2007-11-23
Publication date: 2009-08-19
Also published as: DE102006058666A1; WO2008071302A1

Abstract

A friction clutch for the drivetrain of a vehicle comprises a housing arrangement (12) which is to be coupled to a drive element for common rotation about a rotational axis (A) and which is or can be at least partially filled with fluid, a first group (30) of friction elements which are coupled by means of a first friction element carrier (26) to the housing arrangement (12) for common rotation about the rotational axis (A), a second group (34) of friction elements which can be placed in frictional engagement with the friction elements (28) of the first group (30) of first friction elements by means of a piston element (64) and which are coupled by means of a second friction element carrier (38) to a primary side (40) of a torsional vibration damper arrangement (42) for common rotation about the rotational axis (A), wherein the torsional vibration damper arrangement (42) has a secondary side (54) which is to be coupled to a drive element for common rotation about the rotational axis (A) and which is coupled to the primary side (40) by means of a damper element arrangement (52) for torque transmission and for relative rotation with respect to one another about the rotational axis (A), wherein the damper element arrangement (52) is arranged radially at the inside or radially at the outside with respect to the two groups (30, 34) of friction elements, wherein the piston element (64) serves to divide the interior space (66) of the housing arrangement (12) into a first partial space (68) which contains the torsional vibration damper arrangement (42) and a second partial space (70) in which the fluid pressure is to be increased in relation to the fluid pressure in the first partial space (68) in order to produce the frictional engagement of the friction elements (28, 36) of the two groups (30, 34) of friction elements, wherein there is no fluid-exchanging connection between the first partial space (68) and the second partial space (70) and wherein the torsional vibration damper arrangement (42) divides the first partial space (68) into a first space region (76), which contains the two groups (30, 34) of friction elements, and a second space region (78), and a fluid supply duct arrangement (72) is open to one of the two space regions (76, 78) and a fluid discharge duct arrangement (84) is open to the other of the two space regions (76, 78).

Description

Friction clutch for the drive train of a vehicle

(Description)

Technical area

The present invention relates to a friction clutch for the drive train of a vehicle. By means of such a friction clutch, in a 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.

State of the art

Such friction clutches known for example from DE 10 2005 030 192 A1, also referred to as wet running friction clutches, generally have two groups of friction elements, also referred to as lamellae. A first of this group of friction elements is coupled to a housing assembly for common rotation. A second group of friction elements is torque-coupled to the output member or coupled. Serve respective Reibelemententräger. By 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. In order to produce this frictional engagement, 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.

In order to be able to dampen rotational irregularities occurring in the torque transmission path in the arrangement known from DE 10 2005 030 192 A1, a torsional vibration damper arrangement is provided 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. In the former case, 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. In the second-mentioned case, in particular, 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. This means that the 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.

Presentation of the invention

It is the object of the present invention to provide a friction clutch, which improved in particular axially compact design Operating behavior has.

According to a first aspect of the present invention, this object is achieved by 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 Reibelemententrägers with a primary side of a Torsionsschwingungsdämpferanordnung to common rotation about the axis of rotation are coupled, wherein the Torsionsschwingungsdämpferanordnung 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 two groups of friction elements, wherein the interior of the housing arrangement is divided into a first subspace by the piston element; which is the torsional vibration damper assembly, and a second subspace is divided, in which for establishing the frictional engagement of the friction elements of the two groups of friction elements to increase the fluid pressure compared to the fluid pressure in the first subspace, wherein between the first subspace and the second subspace no Fluid exchange connection arrangement consists and wherein the Torsionsschwingungsdämpferanordnung divides the first subspace into a first space region containing the two groups of friction elements and a second space region and a Fluidzuführkanalanordnung to e inem of the two space areas is open and a Fluidabführkanalanordnung is open to the other of the two space areas. In this inventive construction of a wet-running friction clutch so basically a so-called three-line structure is present. In this structure, the fluid supply or fluid discharge to the second compartment is completely independent of the fluid flow of the first compartment. This is induced solely by utilizing the Fluidzuführkanalanordnung and the Fluidabführkanalanordnung, while a fluid exchange between the two subspaces is not possible in principle. In this way, completely independent of the desired pressure differences between the two subspaces, a sufficient flow through the first subspace and, in particular, the first spatial area thereof is provided, without having to provide comparatively expensive skimming mechanisms acting on the type of conveying blades.

According to a further aspect of the present invention, the object mentioned at the outset is achieved by 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 Reibelemententrägers 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 Reibelemententrägers with a primary side a torsional vibration damper assembly for common rotation about the axis of rotation are coupled, wherein the Torsionsschwingungsdämpferanordnung 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, wherein the damper element arrangement is arranged radially outwardly with respect to the two groups of friction elements.

In this construction of a wet-running friction clutch, therefore, 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. This ensures that, above all, due to the tendency of the fluid occurring under centrifugal force to move radially outwards, adequate lubrication and additional damping functionality are achieved by the fundamentally existing embedding of the damper element arrangement in the fluid present on the outside. Another essential aspect is that by arranging the damper element arrangement comparatively far radially outward, a considerably larger damping volume can be provided in comparison to the arrangement known from the prior art.

Due to the radial staggering of the damper element arrangement and the two groups of friction elements, it is possible to position these two assemblies at least partially axially overlapping, which is particularly beneficial for an axially short design.

In the structure according to the invention, 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 Torsionsschwingungsdämpferanordnung, are preferably radially outside of the second Reibelemententrägers 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.

In this case, it is particularly advantageous if 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.

In particular, 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.

In order to obtain a reaction force support, it is further proposed that the Torsionsschwingungsdämpferanordnung is supported axially relative to the housing assembly.

In an alternative design which is structurally very simple to implement, it is proposed that the housing arrangement form an abutment for the two groups of friction elements when they are acted upon by the piston element.

Furthermore, it is possible for 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. In a corresponding manner, 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.

Brief description of the drawings

The present invention will be described below with reference to the accompanying drawings. It shows:

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;

4 is a partial longitudinal sectional view of a wet-running friction clutch according to a fourth embodiment.

Best way to carry out the invention

In Fig. 1, a wet-running friction clutch according to a first embodiment is generally designated by the reference numeral 10. The

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

Welding connected together. With a drive unit, so for example an internal combustion engine to be positioned opposite

Housing part 14 is radially inward, for example by welding a

Housing hub 18 firmly connected to a bearing lug 20 for radial Abstϋtzung 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.

With the housing part 14 of the housing assembly 12, for example, by welding a substantially annularly shaped first Reibelemententräger 26 is firmly connected. 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. It goes without saying that 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. Furthermore, it goes without saying that 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. In the example illustrated, 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. Radially outwardly, 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 Torsionsschwingungsdämpferanordnung 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 Torsionsschwingungsdämpferanordnung 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. By increasing the fluid pressure in the second subspace 70 in comparison to the fluid pressure present in the first subspace 68, 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 Torsionsschwingungsdämpferanordnung 42 and the output hub 60 transmitted.

In order to be able to set this pressure or these pressure ratios, 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. In the representation of FIG. 1, 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. It can be seen that 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 Torsionsschwingungsdämpferanordnung 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. Thus via the channel or channels 82 in the first spatial region 76 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.

It can thus be seen that 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. However, since the 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.

At the same time, however, in the embodiment shown in Fig. 1 by the radial staggering of the two groups 30, 34 of friction elements on the one hand and the damper element assembly 52 on the other hand created for an axially compact design, since at least a small axial overlap is present. Since the damper element assembly 52, although arranged on the output side in the friction clutch 10, radially outward, at the same time a comparatively large volume for the damper springs or other damper elements is provided.

A modified embodiment is shown in FIG. Here, 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".

In the structure of a friction clutch 10a shown in Fig. 2, the torsional vibration damper assembly 42a with respect to the two groups 30a and 34a of friction elements radially inwardly and also arranged axially overlapping with this. One of the two cover disk elements of the primary side

40a, namely the cover disk element 46a lying closer to the housing part 14a, is formed radially on the outside integrally with the second friction element support 38a and extends from there to radially inward, and forms a substantially fluid-tight seal for the first space region 76a

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 Wälzkörperlager. In the area of the bearing 86a, the channel or channels 82a are formed. In the area of the bearing 88a, the channel or channels 84a are formed. Thus, it is ensured that, irrespective of whether or to what extent fluid is conducted into the second subspace 70a, a fluid circulation in the first subspace 68a can be adjusted while the torsional vibration damper arrangement 42a and the friction elements 28a, 36a are completely circulated.

It can be seen further that in the friction clutch 10a shown in FIG. 2, 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.

Another embodiment of a friction clutch is shown in FIG. Here, components which correspond to components described above in terms of structure or function, with the same reference numerals below Addition of Annex "b".

In this embodiment, 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. The damper element assembly 52b of

Torsional vibration damper assembly 42b is radially outward and axially overlapping with the two groups 30b and 34b of friction elements. It can be seen that, for example, 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. In order to be able to generate the reaction force, 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. In particular, by 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.

In the modification of this embodiment of Fig. 3 shown in Fig. 4, the previously existing ring ball bearing, which is arranged between the housing hub 18b and the output hub 60b and in particular provides for radial support, not present, so that the channel-like gap 100b here a has larger flow cross-section. Otherwise, this embodiment corresponds to that of FIG. 3.

Claims

claims

A friction clutch for the drivetrain of a vehicle, comprising a drive member for common rotation about a rotation axis (A) to be coupled and at least partially filled or filled with fluid

Housing arrangement (12; 12a; 12b), a first group (30; 30a; 30b) of friction elements, which by means of a first Reibelemententrägers (26; 26a; 26b) with the housing assembly (12; 12a; 12b) for rotation together about the axis of rotation (A) are coupled, a second group (34; 34a; 34b) of friction elements, which by a piston element (64; 64a; 64b) in

Friction engagement with the friction elements (28; 28a; 28b) of the first group (30; 30a, 30b) can be brought by first friction elements and by means of a second friction element carrier (38; 38a; 38b) with a primary side (40; 40a; 40b) of a torsional vibration damper arrangement (42; 42a, 42b) for common rotation about the axis of rotation (A) are coupled, wherein the

A torsional vibration damper arrangement (42; 42a; 42b) has a secondary side (54; 54a; 54b) to be coupled to a driven member for common rotation about the axis of rotation (A) and to the primary side (40; 40a; 40b) via a damper element arrangement (Fig. 52; 52a; 52b) for transmitting torque and for relative rotation with respect to each other about the

Axis of rotation (A) is coupled, wherein the damper element arrangement (52; 52a; 52b) is arranged radially inwardly or radially outwardly of friction elements with respect to the two groups (30,34; 30a; 30b; 34a; 34b), wherein the piston element (64 64a, 64b) the housing (66; 66a; 66b) of the housing assembly (12; 12a; 12b) into a first subspace (68; 68a; 68b) containing the torsional vibration damper assembly (42; 42a; 42b) and a second subspace Subdivision (70; 70a; 70b), in which friction elements (28, 36; 28a; 28b; 36a; 36b) of the two groups (30, 34; 30a; 30b; 34a; 34b) of friction elements are produced for frictional engagement the fluid pressure is to be increased in comparison with the fluid pressure in the first subspace (68; 68a; 68b), wherein no fluid exchange connection exists between the first subspace (68; 68a; 68b) and the second subspace (70; 70a; 70b) and wherein the torsional vibration damper assembly (42; 42a; 42b) divides the first subspace (68; 68a; 68b) into a first space region (76; 76a; 76b.) containing the two groups (30,34; 30a; 30b; 34a; 34b) of friction elements and a second space area (78; 78a; 78b) and a fluid supply channel arrangement (72; 72a; 100a) to one of the two

78b; 76a; 76b; 78a; 78b), and a fluid discharge channel assembly (84; 84a; 84b) is open to the other of the two space regions (76,78; 76a; 76b; 78a; 78b).

2. Friction clutch for the drive train of a vehicle, comprising a with a drive member for common rotation about a rotational axis (A) to be coupled and at least partially filled with fluid or fillable housing assembly (12; 12b), a first group (30; 30b) of friction elements coupled by means of a first friction element support (26; 26b) to the housing assembly (12; 12b) for common rotation about the axis of rotation (A), a second group (34; 34b) of friction elements defined by a piston member (64; 64b ) are frictionally engageable with the friction elements (28; 28b) of the first group (30; 30b) of first friction elements and by means of a second friction element carrier (28; 28b) with a primary side (40;

Torsional vibration damper assembly (42; 42b) for common rotation about the axis of rotation (A) coupled to each other, the torsional vibration damper assembly (42; 42b) having a secondary side (54; 54b) coupled to a driven member for common rotation about the axis of rotation (A) and is coupled to the primary side (40; 40b) via a damper element assembly (52; 52b) for rotational transmission and relative rotation about the axis of rotation (A), the damper element assembly (52; 52b) being radially outward of the two groups (30; , 34; 30b; 34b) of friction elements is arranged.

3. Friction clutch according to claim 1 or 2, characterized in that the damper element arrangement (52, 52a; 52b) axially at least partially overlaps with the two groups (30, 34; 30a; 30b; 34a; 34b) of friction elements.

4. friction clutch according to claim 1, characterized in that the second Reibelemententräger (38, 38a;

38b) is radially disposed within the first friction member carrier (24; 24a; 24b) and that the two space portions (76,78; 76a; 76b; 78a; 78b) are in fluid communication with each other radially outward of the second friction member carrier (38; 38a; 38b).

5. Friction clutch according to claim 1 or 4, characterized in that the two space regions (76, 78, 76a, 76b, 78a, 78b) radially outside the two groups (30, 34, 30a, 30b, 34a, 34b) of friction elements in Fluids exchange connection stand.

A friction clutch according to claim 4 or 5, characterized in that at least one side of the primary side (40; 40a; 40b) and the secondary side (54; 54a; 54b) comprises at least one disc element (56; 76a; fluid-tight separation between the two spatial regions (76, 78, 76a;

76b; 78a; 78b) radially outward at least to the radially further inwardly arranged of the two Reibelemententräger (24, 38, 24a, 24b, 38a, 38b) generates.

7. friction clutch according to one of claims 1 to 6, characterized in that the Torsionsschwingungsdämpferanordnung (52b) forms an abutment for the two groups (30b, 34b) of friction elements when acted upon by the piston element (64b).

8. A friction clutch according to claim 7, characterized in that the Torsionsschwingungsdämpferanordnung (52 b) is axially supported relative to the housing assembly (12 b).

9. friction clutch according to one of claims 1 to 6, characterized in that the housing arrangement (12a) forms an abutment for the two groups (30a, 34a) of friction elements upon application of the same by the piston member (64a).

10. Friction clutch according to one of claims 1 to 6, characterized in that on the first Reibelemententräger (24) provided abutment element (32) has an abutment for the two groups (30, 34) of friction elements when acted upon by the piston element (64) forms.

11. Friction clutch according to one of claims 1 to 10, characterized in that the first Reibelemententräger (24, 24b) with the housing assembly (12; 12b) is firmly connected.

12. Friction clutch according to one of claims 1 to 10, characterized in that the first friction element carrier (24a) with the housing assembly (12a) is integrally formed.

13. Friction clutch according to one of claims 1 to 12, characterized in that the second friction element carrier (38; 38b) with a with the damper element arrangement (52; 52b) cooperating disc element (46; 94b) of the primary side (40; 40b) of the Torsionsschwingungsdämpferanordnung ( 52, 52b) is firmly connected.

14. Friction clutch according to one of claims 1 to 12, characterized in that the second Reibelemententräger (38 a) with a with the damper element assembly (52 a) cooperating disc element (46 a) of the primary side (40 a) of the torsional vibration damper assembly (52 a) is integrally formed.