DE10125628A1 - clutch assembly - Google Patents

Abstract

A clutch arrangement, especially for a motor vehicle, comprising a housing arrangement (12) which is filled or which can be filled with fluid, at least one first friction element (22) which can be jointly rotated with the housing arrangement (12) and at least one second friction organ (24) which can be jointly rotated with an output element (18) and which can be brought to rest against the at least one first friction element (22) in order to produce at least one interactive friction effect. At least one friction element (22,24) is embodied in such a way that fluid can circulate around at least certain areas of the friction elements (22,24).

Description

The present invention relates to a clutch arrangement, in particular for a motor vehicle, comprising a fluid filled or fillable Ge housing arrangement, at least one in common with the housing arrangement rotatable first friction member and at least one with an output member jointly rotatable second friction member, which is used to produce a Friction interaction in contact with at least one first friction element is feasible.

Such a generally known as a wet clutch Coupling arrangement is known for example from DE 199 17 893 A1. This clutch assembly includes several in frictional interaction other friction elements, generally referred to as lamellae. By a clutch piston, these disks can be pressed against each other be so that between the housing assembly and an output shaft receive a torque transmission generated by Coulomb friction can be. Especially in slip operation, for example when Starting off is due to the friction elements sliding against each other at least part of the drive torque of the drive unit in heat implemented. Especially with longer lasting slip conditions, such as. B. when starting on a mountain, this can lead to overheating in the area Lead friction elements and possibly damage to the same friction linings. To provide cooling, a fluid flow arrangement is provided by which, for example, by one in the gear arrangement seen fluid feed pump fluid introduced into the housing assembly can be and can be withdrawn from the housing arrangement. The Fluid flows along the friction elements, absorbs heat and trans  port this heat out of the area of the clutch assembly. The fluid heated when flowing through the clutch arrangement can can then be cooled again, for example in a gearbox cooler. The fluid flow established in this way is comparative slow and causes, for example, the various friction elements with a fluid flow of about 10 l / min. With very strong ones Loads with this flow can often not be the required heat dissipation can be achieved.

It is the object of the present invention to provide a wet clutch arrangement, in particular for a motor vehicle, to provide which, even with heavy loads, the risk of at least local Overheating can largely be excluded.

According to the invention, this object is achieved by a coupling arrangement tion, in particular for a motor vehicle, comprising a fluid-filled or fillable housing arrangement, at least one with the housing arrangement tion jointly rotatable first friction member and at least one with one Output member jointly rotatable second friction member, which to the Her position of a friction interaction in contact with at least one first Friction member can be brought.

It is then further provided that at least one friction element for Generation of a flow around the friction elements at least in regions Fluid circulation is formed.

Since in the clutch assembly according to the invention by the friction organs themselves a fluid circulation flowing around this is induced, whereby it should not be ruled out that other elements for generation contributing to fluid circulation is achieved in the housing arrangement existing fluid before it is under the general existing Fluid flow is exchanged several times along the friction elements  flows and thus due to the existing heat storage capacity of the Fluids with this can also dissipate significantly more heat than this would be possible with only one flow along the friction elements. This arrangement is particularly useful for short-term, heavy loads advantageous, which then leads to an increase in the temperature of the fluid to lead. As part of the generally existing fluid exchange this fluid brought to significantly higher temperatures from the Housing arrangement deducted and in the transmission cooler or another Cooler brought back to normal temperature. It can be done through the fluid circulation according to the invention, induced by means of the friction elements themselves tion induce currents in which the friction elements or at least one Part of the same flow around with a fluid volume of 3000 l / min.

A measure by which a very high fluid delivery efficiency can be set is that at least a first friction member and at least one second friction element for generating the fluid circulation forms are. It can preferably be provided that at least one first friction member has at least one fluid delivery surface and that at least one second friction element on at least one fluid delivery surface has. It should be pointed out here that in the sense of the present Invention a fluid delivery surface is such an area, which on the fluid to be excited to circulate acts to keep it moving offset, for example around the fluid at a flow rate to give circumferential direction and thus to ensure that flee due to the force this fluid will move radially outwards. nevertheless is a fluid conveying surface such an area, for example in the manner of a turbine wheel for torque support, one for flow excited fluid and thus ultimately in particular Due to the existing speed difference between two fluid delivery surfaces to promote the fluid and thus to generate the fiction, the moderate cooling effect inducing fluid circulation contributes. Another meaningful aspect in the present invention is that by the  built up fluid circulation not only improves heat from the area the thermally exposed surfaces can be removed, but that by torque support this fluid circulation also according to Art a pump / turbine arrangement for torque transmission. This means that with such wet-running clutches the torque transmission capacity can be increased. Furthermore, this is through Fluid circulation creates torque transmission already in one state effective by being able to interact with each other Surface areas are not yet in contact.

In order to be able to provide the best possible fluid delivery efficiency, be provided according to the present invention that the at least a fluid delivery surface, a radial extension component and an axial has extension component.

For example, it can be provided that the at least one fluid conveyor area at least in regions with an essentially tangential oriented surface normals is formed.

In a particularly simple to construct configuration according to the invention tion form, the at least one fluid delivery surface can thereby be provided be that the at least a first friction element and / or the little tens a second friction member on at least one axial side at least one fluid delivery surface providing friction lining arrangement having. This can be achieved, for example, by the at least a fluid delivery surface at least one a groove-like channel in the Reibbe comprises bearing arrangement in the circumferential direction delimiting wall.

In order to further increase the fluid delivery efficiency, it is proposed that that the at least one first friction element and / or the at least one second friction member on both axial sides of the fluid delivery surfaces has friction lining arrangements.  

The friction load on different friction elements is particularly good distributing embodiment can be provided that the little at least one first friction element and / or the at least one second friction element At least one fluid delivery surface is only available on one axial side has a friction lining arrangement and that the other axial side a friction lining arrangement of another friction member is opposite.

In an alternative embodiment, which has a high fluid delivery can provide efficiency, it can be provided that at least a first friction element and / and the at least one second friction element one Has friction lining carrier, which preferably on at least one axial side carries a friction lining arrangement, and that at least one Fluid delivery surface is provided by the friction lining carrier. This can can be achieved, for example, in that the friction lining carrier in um Lining successively, axially offset to each other has support sections, which by connecting sections with each other are connected, and that the at least one fluid delivery surface through a connecting portion is provided.

In order to make the construction as simple as possible, is before struck that the friction lining carrier by reshaping an essentially Chen ring-like sheet metal blank is formed.

It can further be provided that on the axially offset from each other Covering sections at their axia, each facing away from each other len side lining segments of respective friction lining arrangements are provided are.

A very high fluid delivery efficiency can be obtained if more number of successive fluid conveying surfaces in the circumferential direction the at least one first friction element and / or the at least one second friction member is provided.  

In the coupling arrangement according to the invention, a pressing element can be used be provided, through which the first and second friction members in Frictional interaction can be brought together, with the pressure element an interior area of the housing arrangement in a the friction organs containing first room area and a second room area is divided.

As already mentioned, it is advantageous for an almost permanent one To ensure replacement of the fluid present in the housing arrangement, to be able to dissipate the heat stored in it. It will therefore proposed that a fluid flow arrangement is provided for Supply of fluid in the first area and for the removal of fluid the first spatial area is essentially independent of the fluid circulation tion.

In an alternative embodiment, it can be provided that the first space area against fluid exchange is essentially complete is completed.

To set a torque-transmitting state can pre can be seen that in the second room area fluid for acting on the Pressure element for generating the friction interaction of the friction elements can be initiated.

In an alternative embodiment, the torque transmitted state can be obtained in that the pressing element to generate the frictional interaction by essentially excluding Provided actuation arrangement half of the housing arrangement is beatable.

For the best possible heat dissipation from the area of rubbing together on the interacting surfaces is the strongest possible fluid circulation  lation advantageous. Therefore, according to a further advantageous aspect be provided in the present invention that the at least one first friction element and / or the at least one second friction element one Friction lining carrier with one contributing to the generation of the fluid circulation flap-like turn.

Furthermore, in the clutch arrangement according to the invention to obtain efficient fluid circulation, it is advantageous that the number of fluid delivery surfaces provided on the at least one first friction member and / or the number of fluid delivery surfaces provided on the at least one second friction member is in the range of 6-48, preferably 24 , lies and / or that in the at least one first friction element and / or in the at least one second friction element:

• - A fluid delivery surface inside dimension to a fluid delivery surface outside dimension a ratio in the range of 0.35-0.85 preferably about 0.6, or / and
• - An outer dimension of an outer fluid deflection space a fluid delivery surface outer dimension a ratio in the range of 1.03-1.2, preferably about 1.1, and / or
• - An inner dimension of an inner fluid deflection space to one Fluid delivery area inside dimension a ratio of 0.4-0.9, preferably about 0.7.

In a further preferred embodiment, it can be provided that that an axial dimension is one that contributes to fluid circulation the first friction elements occupy an axial extent Axial dimension of one through the second contributing to fluid circulation Friction organs occupied axial extent a ratio in the Range of 0.5-1.2, preferably about 1. Combined with the generation of a fluid circulation, it has proven to be advantageous provides if at least a first friction member and / or at least a second friction element, a friction lining is provided, the interior of which  measurement to its outer dimension a ratio in the range of 0.6-0.9, preferably 0.75.

According to a further aspect, the present invention relates to a Coupling arrangement, in particular for a motor vehicle, comprising a fluid-filled or fillable housing arrangement, at least one with the Housing arrangement jointly rotatable first friction member, at least one with an output member rotatable second friction member, which for producing a frictional interaction in contact with at least one first friction member can be brought, and a ver in the housing arrangement The pressure element, which can be stored, through which the first and second friction elements can be brought into mutual frictional interaction.

According to the invention it is further provided that the pressing element by one provided essentially outside the housing arrangement Actuating arrangement for generating the friction interaction is beatable.

In such an arrangement, the actuation from outside the Made housing ago, for example by a conventional Engagement or disengagement mechanism, a diaphragm spring-like force memory or the like. Fluid lines, via which fluid for controlling the Coupling must be passed into the housing arrangement are not required sary. Such a configuration is particularly in connection with the further principles of the present invention, in particular the Generation of fluid circulation in the area of rubbing against each other surfaces, advantageous because there is no external fluid supply to the Cooling of the thermally exposed areas is required.

For example, it can be provided that the housing arrangement against Fluid exchange is essentially complete.  

It is also preferred in the clutch arrangement according to the invention a torsional vibration damping arrangement is provided, which in rotation Torque transmission path between one with the housing arrangement coupling drive member and the at least one first friction member can be provided and / or in the torque transmission path between vorese the at least a second friction member and the output member hen can be.

Furthermore, in the clutch arrangement according to the invention, a starter Generator arrangement can be provided, preferably a perma Rotor arrangement of the starter-generator arrangement carrying the magnet is coupled to the housing assembly for common rotation.

The present invention further relates to a friction element for a clutch Arrangement comprising a friction lining carrier, which on at least one axial side carries a friction lining arrangement, and that at least one Fluid delivery surface is provided by the friction lining carrier.

It can again be provided that the friction lining carrier is circumferential in the direction of successive, axially offset facing has cuts, which ver by connecting sections are bound, and that the at least one fluid delivery surface by a Connection section is provided.

The friction lining carrier can, for example, be formed from an im Be essentially annular sheet metal blank.

It is also advantageous if the wear is on axially offset linings cut on their axial sides facing away from each other Lining segments of respective friction lining arrangements of the friction member are provided hen are.

The present invention will hereinafter be described with reference to the accompanying Drawings based on preferred embodiments in detail wrote. Show it:

Fig. 1 is a partial longitudinal sectional view of a hitch be arrangement according to the invention;

FIG. 2 is a partial axial view of a friction element used in the clutch arrangement of FIG. 1;

Fig. 3 is a view of the friction member shown in Figure 2 from the radially outside.

Figure 4 is a partial axial view of an alternatively designed friction organ.

FIG. 5 shows a modification of the friction element shown in FIG. 4;

Fig. 6 shows an alternative embodiment of the coupling arrangement of the invention;

FIG. 7 is a partial axial view of a friction element used in the clutch arrangement of FIG. 6;

FIG. 8 is a view corresponding to FIG. 6 of a further alternative embodiment of the coupling arrangement according to the invention;

Fig. 9 shows a further view of an alternative Ausgestaltungs form of the coupling assembly according to the invention;

Fig. 10 is a partial axial view of a ge in the embodiment of Figure 9 Mäss friction element employed.

FIG. 11 is a partial axial view of another friction element used in the embodiment according to FIG. 9;

Fig. 12-15 different embodiments of friction lining carriers for outer and inner plates;

FIG. 16 is a partial sectional view of an alternative type of configuration of a clutch assembly according to the invention;

FIG. 17 shows a perspective view of a fluid conveying surface element which can be used in the embodiment according to FIG. 16;

Fig. 18 is a sectional view of a friction element;

Fig. 19-21 partial longitudinal sectional views of coupling arrangements according to the invention, which represent the various possibilities of fluid flow;

Fig. 22 is a partial longitudinal sectional view of a hitch be arrangement according to the invention, based on which different dimensions are shown;

Fig. 23 is a partial longitudinal sectional view of an outer plate carrier;

FIG. 24 is a partial longitudinal sectional view of an inventive lung Kupp arrangement according to an alternative form Ausgestaltungs;

Fig. 25-30 further embodiments of the coupling arrangement according to the invention in connection with a torsional vibration damper or a starter-generator arrangement.

In Fig. 1, a clutch assembly according to the invention is generally designated 10 . This wet-running clutch arrangement 10 comprises a housing arrangement 12 , which via a plurality of fastening elements and a coupling element, not shown, such as. B. flex plate, can be coupled to a drive shaft, for example crankshaft of an internal combustion engine, for common rotation. On the axial side remote from the coupling with the drive shaft, the housing arrangement 12 has a housing hub 16 which, for example, engages in a gear arrangement (not shown) and drives a fluid feed pump there for rotation. Arranged concentrically with the housing hub 16 is an output shaft 18 which projects with its free end into the interior 20 of the housing arrangement 12 . This output shaft 18 can be a transmission input shaft, for example.

In the housing assembly 12 is a plurality of first friction elements 22, which are coupled to the housing assembly 12 for joint rotation, is provided. Furthermore, a plurality of second friction elements 24 are provided, which are coupled to the output shaft 18 for common rotation via a coupling element 26 and an output hub 28 . An abutment element 30 is provided on the coupling element 26 in a rotationally fixed manner and at least in an axial direction by means of a locking ring 31 . Between this abutment element 30 and a clutch piston 32 are the first friction members 22 and second friction members 24th By the clutch piston 32 , the interior 20 of the housing assembly 12 is divided into a first space 34 , which contains the friction organs 22 , 24 , and a second space 36 . Fluid can be introduced into the second spatial region 36 via a central opening 38 provided in the output shaft 18 . In order to seal this second space area 36 with respect to the first space area 34 , the coupling piston 32 , which is designed essentially in the form of a ring, is fluid-tight, radially outside and radially inside on respective bearing elements 40 , 42 with the interim storage of sealing elements, but is axially displaceable. In the radially inner bearing element 42 , a plurality of fluid flow channels 44 are provided, which allow the supply of fluid into the space 36 .

Fluid can also be introduced into the first spatial region 34 or fluid can be derived therefrom. For this purpose, a hollow cylindrical separating element 46 is provided, for example, in the space region formed between the output shaft 18 and the housing hub 16 , which forms a flow space 48 between the housing hub 16 and itself and which further forms a flow space region 50 between the output shaft 18 and itself , For example, working fluid can be introduced from the fluid delivery pump provided in the gear arrangement through the flow space region 48 into the space region 34 , so that it flows radially outward at the right end of the housing arrangement 12 . The fluid then flows around the friction elements 22, 24, passes radially inwardly and is gen again abgezo via the flow space section 50th In this manner, which, as exchanged in more beschrie ben, heated in the housing assembly 12 fluid discharged continuously and by cooler fluid to be replaced.

At least some of the first friction elements 22 and part of the second friction elements 24 each have friction lining arrangements 52 , 54 on their two axial sides. These friction lining arrangements 52 and 54 are then each axially opposed to another friction element for the frictional interaction. The various friction elements 22 , 24 are on the housing assembly 12 and the coupling element 26 rotatably supported by axial gear-like engagement and axially displaceable in the direction of the axis of rotation A. The structure of such a friction element provided with friction lining arrangements 52 , 54 is described below with reference to FIGS . 2 and 3 with reference to a first friction element 22 . It should be pointed out that the basic structure also applies to the second friction elements 24 provided with friction lining arrangements 52 , 54 .

It can be seen in Fig. 2 that this first friction member 22 has a friction lining carrier 56 with a substantially ring-like contour. When viewed radially from the outside, it can be seen that the friction lining carrier 56 is designed with an inducted structure and has lining-carrying sections 58 , 60 which are offset from one another in the direction of the axis of rotation A. On their axially opposite sides, the lining support sections 58 , 60 carry respective lining segments 62 and 64 of the friction lining arrangements 52 , 54 . In the area of each of the pad support sections 58 , 60 , a coupling projection 66 or 68 is provided radially on the outside, through which the rotationally fixed coupling to corresponding coupling projections 70 of the housing arrangement 12 takes place.

It can also be seen in FIG. 3 that the lining support sections 58 , 60 which are axially offset from one another are connected to one another by connecting sections 72 . These connecting sections 72 , as can also be seen in FIG. 2, extend approximately from radially inside to radially outside and lie essentially in a plane containing the axis of rotation A. For example, the respective connecting sections can be formed with surface normals that are tangential to a circumferential circular line. On their surface regions pointing in the circumferential direction, these connecting sections 72 form fluid conveying surfaces 74 , 76 . The fluid conveying surfaces 74 , 76 of the first friction elements 22 , which are coupled to the housing arrangement 12 for common rotation, act, for example, during a clutch engagement process, in which the first friction elements 22 have a significantly higher speed than the second friction elements 24 , as pump blade surfaces and ensure that a radially outward flow of fluid is generated in their area. In the same way, the fluid delivery surfaces provided on the second friction members 24 in a corresponding manner act as turbine blade surfaces which, due to the existing speed difference between the first friction members 22 and the second friction members 24 , are set in motion by the fluid delivery surfaces 74 , 76 of the first friction members 22 Serve fluid for torque support and thereby guide this fluid radially inward or serve to promote the fluid radially inward. This by means of the fluid conveying surfaces of the second friction elements 24 directed or conveyed radially inward fluid thus replaces the fluid conveyed by the fluid conveying surfaces 74 , 76 of the first friction elements 22 from radially inward to radially outward. It is thus, as shown by the dashed arrows in Fig. 1, a fluid circulation tion, which ultimately corresponds to the fluid circulation, as generated by a pump wheel and a turbine wheel of a hydrodynamic torque converter or a fluid coupling. The fluid circulation generated in the clutch assembly 10 according to the invention leads to the fact that, regardless of the exchange of the fluid present in the housing assembly 12 , which fluid exchange can take place at a rate of 10 l / min, for example, a permanent fluid circulation and flow around the friction elements 22 , 24 is induced, which can for example generate a flow around these friction elements 22 , 24 with a liquid quantity of 3000 l / min. In this way, the frictional heat generated in the friction or slip operation in the various friction elements 22 , 24 can be absorbed significantly better in the fluid, especially with these friction elements. The fluid circulation constructed according to the invention is superimposed on the comparatively slow fluid exchange, so that the fluid brought to a comparatively high temperature by the circulation is continuously drawn off and replaced by cooler fluid.

It should be pointed out here that the principle of producing a fluid circulation shown in FIG. 1 can of course be provided independently of the number of first friction elements or second friction elements. Through the positioning shown in FIG. 1, in which the first friction elements 22 designed for fluid delivery are arranged one after the other, each with an essentially plate-like second friction element 24 lying between them, and then after a transition friction element 22 , which has no friction linings carries, which follow the second friction members 24 designed for fluid conveyance, between which there is a substantially plate-shaped first friction member not provided with friction linings, a global fluid circulation is generated with regard to the entirety of the friction members 22 , 24 . By staggering the arrangement of the first friction elements 22 contributing to the generation of fluid flow and the second friction elements 24 contributing to the generation of fluid flow, a plurality of local fluid circulation areas can be generated in the region of the friction elements 22 , 24 . It is also not absolutely necessary to provide the same number of first friction element 22 and second friction element 24 designed for fluid generation. For example, more first friction elements 22 effective as pump wheels or pump blades can be provided.

It can also be seen that two first friction elements 22 follow one another in the axially central region, so that an ineffective friction surface pairing is created. This can be avoided, for example, by the fact that ultimately no friction linings are provided on the friction lining carriers of the first friction members 22, but instead friction linings are provided on all second friction members 24 , in particular also on the plate-like second friction member 22 shown on the right in FIG. 1. In the sense of the present invention, such a friction surface carrier, which does not carry friction linings, is nevertheless to be regarded as a friction lining carrier, in particular with regard to the structure relevant for fluid delivery.

In FIG. 4 a modified embodiment is shown of a first form Reibor goose 22nd It can be seen in comparison to the embodiment according to FIG. 2 that the projections 66 , 68 which serve for the rotary coupling and are offset from one another are displaced radially further outward and that between the individual friction lining segments of the friction lining arrangements in each case in the circumferential transition region between the lining support sections 58 , 60 fluid passage openings 78 are provided. These fluid passage openings 78 enable the essentially unhindered fluid circulation. In the embodiment according to Fig. 5, these fluid passage openings are provided so that in each case 78 to open radially outwardly, in this case in the radial direction relatively Langge stretched projections 66, 68 for coupling to the corresponding formatter tion 70 of the housing assembly 12. Here, too, the various connecting sections 72 are provided for providing the fluid conveying surfaces which can be seen in FIG. 3.

It should be pointed out that the embodiments according to FIGS. 4 and 5 can also be used with the second friction elements 24 coupled to the output shaft 18 , the various openings or coupling projections then radially inward with respect to the area bearing the friction lining segments extend.

In FIGS. 12-15 different embodiment variants of friction lining are lagträgern 56 also presented for both the with the output shaft 18 to be coupled to second friction elements 24 and for the housing assembly 12 to be coupled to the first friction elements 22nd One can see in FIG. 12 a friction lining carrier 56 for a friction member 24 to be coupled to the output shaft 18 . As already described above, the latter has the different lining support sections 58 , 60 which are axially offset from one another and which are coupled to one another by the connecting sections 72 . The connecting sections 72 in turn form the fluid delivery surfaces 74 , 76 on the surfaces oriented in the circumferential direction. From each of the covering sections 58 , 60 a web section 100 , 102 extends radially inwards. These open into a radially inner ring-like section 104 , which has on its inner circumferential side a toothing, not shown, for rotationally fixed coupling to the coupling element 26 . Since the lining carrying sections 58 , 60 are axially offset from one another, the web sections 100 , 102 respectively emanating from these run in the pattern shown in FIG. 12 inclined with respect to the axis of rotation A or a plane orthogonal thereto. Passage openings 106 are formed between the individual web sections 100 , 102 , through which the fluid excited for circulation can pass in the axial direction.

In the embodiment variant shown in FIG. 13, only one set of the covering support sections 58 , 60 , namely the covering support sections 60 , web sections 100 are used . The pad support sections 58 are not directly connected to the ring section 104 in their radially inner region. This results in a configuration in which the web sections 100 can lie in the same plane as the covering carrying sections 60 and in which, due to the halved number of web sections, which can then have a somewhat greater width, basically those between the individual web sections 100 formed openings 106 have a larger dimension.

In Fig. 14 a friction lining 56 is shown on a radially outer friction element to be coupled, that is, for example, a anzukop to the housing assembly 12 pelndes friction member 22nd Here too, the axially offset lining support sections 58 , 60 and the connecting sections 72 connecting them with the fluid delivery surfaces 74 , 76 provided thereon can be seen. Axially on the outside, sections 60 have web sections 108 which open into an outer ring section 110 . This has an external toothing 112 for rotationally fixed coupling, for example to the coupling projections 70 . Openings 114 are again provided in the circumferential direction between the individual web sections 108 , through which openings the fluid can pass in the axial direction. It should be pointed out here that, of course, web sections 58 can also or additionally extend radially outward from the lining support sections 58 , so that the inclined orientation of the different web sections, which can be seen in the example of FIG. 12, is again provided.

In the embodiment variant shown in FIG. 15, protrusions 116 projecting radially outward are formed in the transition region between the lining support sections 60 , 58 . Since these projections 116 extend from the pad support sections 60 via the connecting sections 72 and the pad support sections 58 , they have approximately an S-contour or a double-angled contour and are therefore very stiff and suitable for transmitting large torques.

A further modification of the principles presented above can be seen in FIGS. 16-18. In this embodiment, the various friction elements are each constructed from at least one annular disk-like sheet metal element. The first and second friction elements 22 , 24 contributing to the fluid circulation each comprise two sheet metal elements 118 , 120 , 122 , 124 of this type, which are designed in the manner of conventional lamellae. While the sheet metal elements 118 , 120 have the openings 114 for the axial fluid passage radially outside, the sheet metal elements 122 , 124 have the openings 106 for the fluid passage radially inside. Between each of these sheet metal elements 118 , 120 , 122 , 124 an arrangement providing the fluid conveying surfaces is inserted. This can include, for example, the conveying surface element 126 that can be seen in FIG. 17. This again has axially offset sections 58 , 60 , which in the variants described above correspond to the lining support sections and are connected to one another by connecting sections 72 . Each of these connecting portions 72 provides at its two sides in order catch again the fluid-conveying surfaces 74, 76 ready. The conveying surface element 126 can be firmly connected, for example by soldering, gluing or the like, to the associated and, for example, stamped sheet metal elements 118 , 120 or 122 , 124 . It should be pointed out that, of course, other types of conveying surface arrangements composed of a plurality of parts can also be provided here. The friction elements 22 ', 24 ' which do not directly contribute to the fluid circulation are designed in the manner of conventional lamellae, ie also comprise annular disk-like sheet metal elements or the like which carry friction linings on their two axial sides. It should be pointed out that, of course, friction linings can also be provided on the friction elements 22 , 24 which generate the fluid circulation. Above all, friction linings with channel-like depressions provided on their surfaces can be used, so that fluid can also flow in these surface areas for improved heat dissipation. It is further pointed out that in the clutch arrangement according to the invention those friction elements which contribute to the generation of the fluid circulation by appropriate geometry do not necessarily also have to wear the friction linings. For example, the conveying surface element shown in FIG. 17 can be integrated into a coupling arrangement without the friction linings provided thereon, and on both sides of it, counter friction elements can be provided, for example in the form of annular disks and in the circumferential direction, for example, continuous friction linings. It is of course also possible, in an arrangement such as will be described below with reference to FIGS. 6-11, to introduce upper surface channels into friction members constructed, for example, of sheet metal and then to corresponding counter friction members in the circumferential direction either continuously or, for example, likewise also surface channels provided friction linings.

The embodiment shown in FIGS. 16 and 17 is easy to manufacture due to the use of standard components and is therefore also inexpensive. In order to further increase the fluid circulation in a clutch arrangement according to the invention, it can be provided that on the various components formed from sheet metal, for example the lining carriers 56 described above, not only the openings or recesses allowing the passage of fluid radially outside or radially inside the friction linings are provided, but additional conveying or scoop surfaces are provided. As can be seen in the example of FIG. 18, this can happen, for example, in that when a radially outer opening 114 is formed, the sheet metal part is not completely stamped, but instead a U-shaped stamped cut is formed and in this way a laterally or obliquely bent tab 127 is generated. Several such successive lobes in the circumferential direction act in the manner of conveyor blades and reinforce the circulation already provided by the measures according to the invention described above. The angle at which these tabs 127 are bent with respect to a plane substantially orthogonal to the axis of rotation A is preferably in the range of approximately 90 °, but can also be in the angular range of 15-165 °.

A modified embodiment of the clutch arrangement according to the invention is shown in Fig. 6. Components which correspond to the components described above are identified by the same reference signs with the addition of an appendix "a". In the following, only the essential design and functional differences are discussed.

In the embodiment according to FIG. 6, to which the fluid circulation inducing first and second friction elements 22 a, 24 a on both sides again Reibbelaganordnungen 52 a, 54 a provided in the form of, for example, tig ringar formed friction linings. As can be seen, for example, in FIG. 7 from a first friction member 22 a or the friction lining 52 a provided thereon, this has, for example, introduced by punching or embossing, a plurality of preferably substantially radially extending fluid flow channels 80 a. Each of these fluid flow channels 80 a is limited in the circumferential direction by now the fluid conveying surfaces 74 a, 76 a providing walls. In this case, those fluid conveying surfaces 74 a, 76 a which are provided on the first friction members 22 a which can be rotated with the housing arrangement 12 a take over the function of the pump blade surfaces in slip operation, while the corresponding fluid conveying surfaces on the second friction members 24 a again function Provide turbine blade surfaces. In this embodiment, the friction lining carrier 56 a is provided as sheet metal parts which are essentially flat. It can also be seen here that between two first friction elements 22 a and second friction elements 24 a, which induce the fluid circulation, there is in turn a second friction element or first friction element, on which no friction linings are provided.

In order to avoid the blind friction surface between two immediately adjacent first friction elements 22 a, which can also be seen in FIG. 6, an arrangement can be provided as shown in FIG. 8. It can be seen here that a friction lining 52 a (in the case of the first friction members 22 a) or 54 a (in the case of the second friction members 24 a) is provided on only one axial side of the first friction members 22 a and the second friction members 24 a , Each of these friction linings 52 a, 54 a again has the channels 80 a addressed. The abutment element 30 a can carry such a friction lining 54 a with channels 80 a. The local circulations already mentioned above are then generated in this embodiment. While the embodiment shown in FIG. 8 has an improved torque transmission capacity with the same number of friction elements due to the avoidance of an ineffective reactive friction surface, the several local circulations result in a slightly reduced volume flow compared to the global circulation flow in FIG. 6 reached. An axially very compact design is also obtained. Both the embodiment shown in FIG. 6 and the embodiment shown in FIG. 8 have the advantage that an extremely simple constructional construction is present. It can be seen above all that due to the omission of the connecting sections of the embodiment according to FIG. 1, a significantly smaller axial size is achieved, although overall the fluid conveying surfaces provided in the area of the friction lining arrangements provide a smaller total surface and thus there is also a reduced conveying efficiency. To counteract this, the thickness of the various friction linings or the depth of the grooves made therein should be as large as possible using the available axial installation space.

A further modification of the fluid delivery surfaces in the area of the inventive principle using friction linings is shown in FIG. 9. Here too, a plurality of first friction elements 22 a and at least one second friction element 24 a are provided in an axially staggered arrangement. The first friction elements 22 a and the second friction elements 24 a again carry the friction linings or friction lining arrangements 52 a, 54 a on an axial side. In a modification of the embodiments shown above, the second friction elements 24 a, which are coupled to the output shaft via the coupling element 26 a, are now designed as so-called outer plates, ie their rotary driving projections reach radially outwards. The first friction organs 22 a are designed as so-called inner plates and have internal rotary coupling projections for engagement with corresponding formations 70 a on the housing arrangement 12 a. Also shown here is a system of the two-line principle, in which the fluid pressure is increased compared to the fluid pressure in the second space region 36 a by producing an increased fluid supply in order to produce the coupled state in the first space region 34 a. The clutch piston 32 a is thus axially pressed against the friction members 22 a and 24 a. In the clutch piston 32 a at least one passage opening 90 a is provided, which enables a fluid exchange even when the clutch arrangement 10 a is coupled. The hitch be piston 32 a is rotatably coupled via a rotary coupling arrangement 91 a with the housing arrangement 12 a, but with respect to this axially movable bar. In this case, the clutch piston 32 a is also to be regarded as a first friction member rotatable with the housing arrangement 12 a, which ultimately also carries a friction lining 52 a.

In Fig. 10 is a partial axial view of a second friction member 24 a recognizable bar. It can be seen that the friction lining 54 a provided thereon has grooves or channels 80 a closed radially inwards. A radially inner ring-like section 82 a remains. In the radially inner end region of the channels 80 a through openings 84 a are provided in the friction lining carrier 56 a. The friction linings 52 a of the first friction members 22 a, which can be seen in FIG. 11, likewise have a plurality of channels 80 a, which are delimited radially inwards and open into an annular channel area 86 a in their radially inner end region. This ring-like channel region 86 a lies opposite the passage openings 84 a. As with the prior described embodiments prospective the channels 80 a delimiting side walls respective fluid-conveying surfaces 74 form a, 76 a. In the case of the rotatable with the housing arrangement 12 a first friction members 22 a, these fluid conveying surfaces 74 a, 76 a in turn act as the fluid to the radially outward conveying blade surfaces, while the fluid conveying surfaces 74 a, 76 a provided on the second friction members 24 radially flow the fluid support inside and serve to support moments. In the embodiment variants shown in FIG. 9, local circulations are again generated, each of which extends over a lining carrier of a second friction member 24 a, a friction lining 54 a of a second friction member 24 a and a friction lining 52 a of a first friction member 22 a. It should be noted that in this embodiment, the coupling element 26 a, which is located radially outside of the various friction linings 52 a, 54 a, assumes a function for supporting the deflection of the fluid circulation in the radially outer region, while in the embodiments described above this Coupling element has provided a corresponding deflection of the fluid circulation in the radially inner region. The deflection in the radially outer region takes place there through the radially outer sections of the housing arrangement. In particular with reference to the embodiments shown in FIGS . 6-11, it should be pointed out that such friction elements do not of course necessarily have to consist of a separate carrier element and separate friction linings attached to it, for example by gluing. Rather, material made of fiber composite material, e.g. B. carbon fiber composite, one-piece friction elements are provided, which can then be designed as desired in their geometry, but which can also be designed, for example, like the recognizable friction elements in FIG. 8. These friction elements then have on their axial sides in the sense of the present invention on friction linings or friction lining sections, which are formed in one piece with a body arrangement designed for connection to the housing or the output shaft. Of course, it is also possible for such friction elements in which the friction linings or friction lining sections are formed integrally and from the same material as the body regions designed for connection to other components, to provide a meandering structure, as can be seen, for example, in FIG. 17 ,

The embodiments described above and also those described below, in particular the embodiment shown in FIG. 9, are also suitable as a clutch arrangement in a hydrodynamic torque converter or a fluid coupling, that is to say as a so-called lock-up clutch arrangement. Here too, a considerable part of the torque introduced is converted into frictional heat when the bridging state is established, which can then be dissipated quickly by the circulation induced according to the invention. It is of essential advantage in all of the embodiments according to the invention that the amount of fluid conveyed in the context of the fluid circulation increases with increasing speed difference between the various friction elements which abut one another and act as pumps or turbines. That is, especially when there is a strong friction load, ie when there is a large amount of slippage, a large amount of fluid is circulated through the fluid circulation, with the result that the heat generated by friction is significantly improved. The fluid circulation generated in the area of the various frictionally effective surface areas ensures that ultimately fluid can be conveyed very quickly to all thermally exposed surface areas and heat can be dissipated from there.

In the following, the various possibilities of the fluid flow superimposed or superimposable on the fluid circulation according to the invention are presented. Thus, the Fig. 19 generally shows an inventive lung Kupp arrangement 10, wherein the fluid supply or removal in the manner of a 3-line system takes place. While fluid is introduced into the space area 36 for the axial displacement of the clutch piston 32 via the central opening 38 of the output shaft 18 or is discharged from there again, fluid is introduced into the space area 34 via a further line essentially comprising the flow space area 50 . The fluid can be drawn out of the space area 34 again via a further line comprising the flow space area 48 . It should be noted that in the illustration in FIG. 19, the separating element 46 is effective in the manner of a labyrinth-like seal and can basically comprise two sealing elements which can be rotated with respect to one another. The advantage of this arrangement is that the engagement and disengagement process can be made completely independent of any pressure conditions in the area 34 . Excellent heat dissipation can thus be obtained, which can be regulated from the transmission. A very precise displacement of the clutch piston 32 can also be achieved.

The embodiment according to Fig. 20 acts according to the so-called 2-line principle. The fluid is fed into the housing arrangement 12 via the central opening 38 of the output shaft 18 , specifically into the space area 36 . Via one or more openings 130 in the clutch piston 32 , the fluid enters with a throttling effect into the space region 34 and can flow out again through a space region 51 provided between the hub 16 and the output shaft 18 . To engage this clutch arrangement 10 , fluid is therefore increasingly fed into the space region 36 . Due to the increase in the fluid pressure in this space area 36 , the clutch piston 32 is then pressed against the friction elements. Here, it is possible to reverse the fluid flow direction to obtain a faster release. By providing the at least one opening 130 , fluid exchange and corresponding heat dissipation are also permanently possible here in the engaged state. Although the desired fluid leakage (generated through the opening or openings 130 ) results in a reduced efficiency since oil has to be replenished permanently, a permanent fluid exchange is possible with little construction.

The embodiment variant shown in FIG. 21 essentially corresponds to the embodiment variant shown in FIG. 20, in which fluid is fed into the spatial region 36 via the central opening 38 of the output shaft 18 . In the clutch piston 32 , however, no passage opening is provided. There is therefore no direct fluid exchange connection between the two spatial areas 34 , 36 . The space area 34 is prefilled with fluid in this variant. The heat dissipation from the areas subject to friction is only carried out here by the fluid circulation constructed according to the invention in the area of the various friction elements. There is no fluid exchange through which fluid is discharged from the space region 34 . In order to be able to compensate here for the volume change of the space region 34 induced by displacement of the clutch piston 32 , the latter is not completely filled with the working fluid, ie an oil-like liquid or the like, so that a compressible gas volume remains.

In Fig. 22, various dimensions are shown which should be to obtain an efficient circulation of fluid in certain areas. For example, it is advantageous if the ratio of the inner diameter to the outer diameter of the fluid circulation surfaces that ultimately produce the fluid delivery surfaces, that is to say the ratio d / D, is in the range from 0.35-0.85, preferably approximately 0.6. The number of effective fluid delivery areas should be in the range of 6-48, preferably about 24. For the friction linings, it has proven to be advantageous if their diameter ratio d _B / D _{B is} in the range of 0.6-0.9, preferably approximately 0.75.

By providing the above-mentioned various radially outside or inside openings 114 , 106 or through cut-outs between respective coupling projections, the previously mentioned radially outer or radially inner fluid flow spaces 134 , 136 are formed. These can be formed radially outwards or radially inwards by the various previously mentioned ring sections of the friction lining carrier 56 , but, as can also be seen in FIG. 1, for example, can be directly limited by the housing arrangement 12 or the coupling element 26 . For these radially outer or radially inner fluid flow spaces, in which the fluid flows approximately in the axial direction, it has proven to be advantageous to have a value in the range of 1.03-1 as a ratio to the outer dimension of the fluid delivery surfaces, that is to say a ratio D _a / D , 2, preferably about 1.1, or to provide a value in the range of 0.4-0.9, preferably about 0.7 as a ratio to the inner diameter of the fluid conveying surfaces, that is to say as a ratio d _i / d. Furthermore, it is advantageous if the ratio of the axial extent of the frictional elements acting in the manner of a pump, which is approximately expressed by the dimension B _P in FIG. 22, to the axial extent of the frictional elements effective in the manner of a turbine, in FIG. 22 approximately by the extension B _P expresses, in the range of 0.5-1.2, preferably about 1, is. It should be pointed out here that in FIG. 22 there is a slight inaccuracy insofar as there is a friction element 24 , which is radially internally coupled to the coupling element 26 between two friction elements 22 acting in the manner of a pump, but which does not contribute to the generation of fluid circulation. The same applies to the turbine-effective area.

Furthermore, it has proven to be advantageous, but not mandatory, if, as shown in FIG. 22, the friction linings end radially on the outside in the same area as the fluid conveying surfaces bear on the different linings.

It should be pointed out that the details described above with reference to FIGS. 19-22 are independent of the manner in which the fluid delivery surfaces generating the fluid circulation are designed, that is to say regardless of whether these are on lining carriers or on end faces or Side surfaces of coverings themselves are formed. In this respect, the statements made with reference to FIGS. 19-22 also apply to the embodiments according to FIGS. 6-11.

Another advantageous variant is indicated in FIG. 23. As already explained above with reference to FIGS . 19-21, various flows or pre-filling ensure that working fluid is present in the area of the frictionally abutting or interacting surface areas in order to flow through fluid flows and / or Dissipate fluid circulation heat. In a state in which the clutch 10 is not engaged, this function of heat dissipation is not required. Since then still existing working fluid has the build-up of drag torques, which is disadvantageous, for example, when the clutch according to the invention is effective as part of a double clutch. In this case, torque should be transmitted via only one of the clutches. According to the variant shown in FIG. 23, it is now ensured that the volume area containing the frictionally acted surface areas is filled with working fluid only when a torque is to be transmitted. This can be achieved, for example, by providing a coupling element 140 which is separate from the housing arrangement 12 and which is connected, for example, to the housing arrangement 140 in a rotationally fixed manner, for the friction elements coupled to the housing arrangement 12 in a rotationally fixed manner. This coupling element 140 has a plurality of openings 142 through which fluid can flow from radially inside to radially outside. In operation, care is taken to ensure that, when the clutch is to be brought into an engaged state, fluid is conducted into the space area 34 , for example at a delivery rate of approximately 20 l / min. This fluid will flow to the outside due to centrifugal force and, due to the throttling action of the openings 142 , will accumulate in the volume area surrounded by the coupling element 140 . There it absorbs heat from the components abutting one another in a frictional manner and then dissipates the heat after it has passed through the openings 142 and has been extracted from the area 34 . If the clutch is to be brought back into a disengaged state, the fluid supply is stopped, the fluid which is still present will pass through the openings 142 and then be withdrawn. There is then no longer any fluid-related drag effect. Such a configuration is of course also possible in the variant shown in FIG. 9, in which the friction elements 24 a connected to the output shaft are connected to the various friction elements 24 a, 22 a radially outside to give coupling element 26 a.

Here again it is irrelevant in what way the fluid is conveyed areas are provided so that this aspect of the present the invention fundamentally in all of the above described design variants can be used.

Another clutch arrangement according to the invention is shown in FIG. 24. This corresponds in particular with regard to the generation of the fluid circulation to the principles described above and, insofar as the friction elements are concerned, can be designed as described above with reference to various design variants.

It can be seen in the embodiment variant shown in FIG. 24 that the housing section 150 b opposite the clutch piston 32 b and extending radially inward has an opening which is preferably concentric with the axis of rotation A radially on the inside. Through this, an axial, substantially cylindrical extending formed by shaping 152 b of the clutch piston 32 is performed with provision of a sealing effect of a sealing element 154 b. The entire interior of the housing 12 b, comprising the spatial areas 34 b, 36 b, is thus sealed in a fluid-tight manner and prefilled with fluid. The two spatial areas 34 b, 36 b are radially outward in direct connection, since there the coupling piston 32 b is connected by a toothing arrangement 156 b provided thereon, as well as the friction elements 22 b, to the housing arrangement 12 b in a rotationally fixed manner. For the clutch piston 32 b a generally designated 158 b actuating mechanism is provided. This can be designed, for example, in the manner of a conventional piston / cylinder actuating mechanism for actuating friction clutches, in the manner of an energy store, for example a membrane spring, or another actuator. The mechanism 158 b acts on the projecting from the housing arrangement 12 b area 152 b of the hitch be piston 32 b and thus presses this to produce the Einkuppelzu state against the various friction elements 22 b, 24 b. There are therefore no fluid lines required to produce the engagement state, which simplifies the structure, particularly in terms of fluid management. In order to move the clutch piston in a defined manner during the transition to the disengagement state away from the friction elements, it could be considered to provide either an axially preloading spring element within the housing arrangement 12 b or outside the same, which only have a comparatively low spring force got to.

The embodiment variant shown in FIG. 24 combines the principle of a wet-running clutch, that is to say cooled by fluid flow, with the actuation of a conventional dry friction clutch. Such a clutch arrangement can therefore be used, for example, where a conventional actuation, that is to say actuation of a conventional dry friction clutch, is to be provided, but due to the specific application, the load that would occur in particular in slip operation would be too great for a dry friction clutch. It should also be pointed out that all the measures described above can of course be provided in the embodiment according to FIG. 24 with regard to the structure and the effect of the friction elements.

A development of the clutch arrangement according to the invention is shown in FIG. 25. It can be seen here that the housing arrangement 12 of the coupling arrangement 10 can be coupled to a drive shaft or another drive element via a rotary vibration damper, generally designated 200 , for common rotation. For this purpose, the housing arrangement 12 has an area 202 which is extended radially outward in a flange-like manner and forms the secondary side of the torsional vibration damper 200 . Cover elements 204 , 206 essentially forming the primary side are provided on both axial sides of the region 200 which is elongated in the manner of a flange. In a manner known per se, a plurality of damper springs 208 act between the cover elements 204 , 206 and the flange-like region which is extended radially outwards, so that the housing arrangement 12 can rotate against the cover elements 204 , 206 which essentially form the primary side in a limited range of rotation angles. This primary side can then be connected to the drive shaft via a flexible plate or the like.

In the embodiment variant shown in FIG. 26, the torsional vibration damper 200 is provided on the output side and lies in the torque transmission path between the coupling element 26 and the schematically illustrated output shaft 18 . In this case, the Ge housing arrangement 12 is connected directly to the drive shaft, for example via a flex plate. The torsional vibration damper 200 is in turn constructed in accordance with a conventional design and has, for example in connection with the coupling element 26, a flange-like central disk element in the manner of the region 202 recognizable in FIG. 25 and two cover disk elements 204 , 206 lying on both axial sides thereof, which of course also can be integrally formed with each other.

In the embodiment shown in FIG. 27, the torsional vibration damper 200 is present in the interior of the housing arrangement 12 , ie in the area filled with working fluid. A generally designated 210 support member carries both the friction members 22 and the clutch piston 32 rotatably. In its radially outer region, this carrier element 210 then forms the central element 200 , on the two sides of which cover elements 204 , 206 integrally formed with the housing arrangement 12 are provided for interaction with the damper springs 208 . Here, too, the torsional vibration damper 200 is provided on the drive side, that is to say in the torque transmission path between the drive shaft and the friction elements 22 . In the embodiment variant shown in FIG. 28, the torsional vibration damper 200 is again arranged inside the housing arrangement 12 , but now on the output side between the coupling element 26 and a further coupling element 212 which is coupled in a rotationally fixed manner to the output shaft.

In Fig. 29 a coupling arrangement 10 according to the invention is shown dung in Verbin voltage having a generally designated 220 starter-generator Anord. On the side facing an engine block 222 , the housing arrangement carries a rotor arrangement 224 of the starter-generator arrangement, which can also be coupled to the housing arrangement 12 for common rotation via the torsional vibration damper 200 , for example. Either radially inside or, as in the example shown, radially outside the rotor arrangement 24 , the line coils face the stator arrangement 226 of the starter-generator arrangement 220 . The stator assembly 226 is, for example, held on the engine block 222 in a rotationally fixed manner.

In the embodiment variant shown in FIG. 30, the rotor arrangement 224 is arranged on the output side of the housing arrangement 12 . The stator arrangement 226 is carried, for example, on the inside of a transmission bell 228 .

It should be noted that in the embodiments described with reference to FIGS. 25-30, the internal structure of the clutch arrangements, in particular insofar as the various friction elements are concerned, as described above with reference to FIGS . 1-24 can be. Here too, as indicated by circulation circles, the fluid circulation flowing around the friction elements is provided. It is a matter of course to provide both the torsional vibration damper 200 and the starter-generator arrangement 220 in a clutch arrangement 10 according to the invention. For example, it is possible to couple a drive shaft via a flexible plate or the like to the rotor arrangement of the starter-generator arrangement, to couple the rotor arrangement to the input side or primary side of the torsional vibration damper and then to output the output side of the torsional vibration damper to the housing arrangement of the clutch arrangement according to the invention to couple.

It should also be noted that the principle of the invention Generation of fluid circulation in the area of rubbing each other in Interacting friction elements of course also apply can be found in double wet clutch arrangements, in which two different output shafts through two sets of friction elements optional engagement of one of the two wet-running clutches in rotation Torque transmission connection are brought with a drive shaft can.

Claims (32)

1. Coupling arrangement, in particular for a motor vehicle, comprising:
a housing arrangement ( 12 ; 12 a) filled or fillable with fluid,
at least one first friction member ( 22 ; 22 a) rotatable together with the housing arrangement ( 12 ; 12 a),
at least one second friction element ( 24 ; 24 a) which can be rotated together with an output element ( 18 ) and which can be brought into contact with at least one first friction element ( 22 ; 22 a) for producing a friction interaction,
characterized in that at least one friction member ( 22 , 24 ; 22 a, 24 a) is designed to generate a fluid circulation flowing around the friction members ( 22 , 24 ; 22 a, 24 a) at least in regions. 2. Coupling arrangement according to claim 1, characterized in that at least a first friction member ( 22 ; 22 a) and at least a second friction member ( 24 ; 24 a) are designed to generate the fluid circulation. 3. Coupling arrangement according to claim 2, characterized in that at least one first friction member ( 22 ; 22 a) has at least one fluid delivery surface ( 74 , 76 ; 74 a, 76 a) and that at least one second friction member ( 24 ; 24 a) has at least one Has fluid delivery surface. 4. Coupling arrangement according to claim 3, characterized in that the at least one fluid delivery surface ( 74 , 76 ; 74 a, 76 a) has a radial extension component and an axial extension component. 5. Coupling arrangement according to claim 3 or 4, characterized in that the at least one fluid delivery surface ( 74 , 76 ; 74 a, 76 a) is at least partially formed with a substantially tangentially oriented surface normal. 6. Coupling arrangement according to one of claims 3 to 5, characterized in that the at least one first friction member ( 22 a) and / and the at least one second friction member ( 24 a) on at least one axial side of the at least one fluid delivery surface ( 74 a , 76 a) providing friction lining arrangement ( 52 a, 54 a). 7. Coupling arrangement according to claim 6, characterized in that the at least one fluid delivery surface ( 74 a, 76 a) comprises at least one wall defining a groove-like channel ( 80 a) in the friction lining arrangement ( 52 a, 54 a) in the circumferential direction. 8. Coupling arrangement according to claim 6 or 7, characterized in that the at least one first friction member ( 22 a) and / and the at least one second friction member ( 24 a) on both axial sides each have fluid delivery surfaces ( 74 a, 76 a) providing friction lining arrangements ( 52 a, 54 a). 9. Coupling arrangement according to claim 6 or 7, characterized in that the at least one first friction member ( 22 a) and / and the at least one second friction member ( 24 a) has at least one fluid delivery surface ( 74 a, 76 a) only on one axial side. providing friction lining arrangement ( 52 a, 54 a) and that the other axial side is opposite a friction lining arrangement ( 52 a, 54 a) of a further friction member ( 22 a, 24 a). 10. Clutch arrangement according to one of claims 3 to 9, characterized in that the at least one first friction member ( 22 ) and / and the at least one second friction member ( 24 ) has a friction lining carrier ( 56 ), which preferably has a friction lining arrangement on at least one axial side ( 52 , 54 ) carries, and that at least one fluid delivery surface ( 74 , 76 ) is provided by the friction lining carrier ( 56 ). 11. Clutch arrangement according to claim 10, characterized in that the friction lining carrier ( 56 ) in the circumferential direction of successive, axially offset Belagtra sections ( 58 , 60 ), which are connected by Verbindungsab sections ( 72 ), and that the at least one Fluid delivery surface ( 74 , 76 ) is provided by a connecting section ( 72 ). 12. Clutch arrangement according to claim 11, characterized in that the friction lining carrier ( 56 ) is formed by forming an essentially ring-like sheet metal blank. 13. Coupling arrangement according to claim 11 or 12, characterized in that on the mutually axially offset lining support sections ( 58 , 60 ) on their axially facing away from each other lining segments ( 62 , 64 ) respective Reibbe laganrangungen ( 52 , 54 ) are provided. 14. Coupling arrangement according to one of claims 3 to 13, characterized by a plurality of in the circumferential direction one after the other fluid conveying surfaces ( 74 , 76 ; 74 a, 76 a) on the we at least a first friction member ( 22 ; 22 a) or / and at least a second friction element ( 24 ; 24 a). 15. Coupling arrangement according to one of claims 1 to 14, characterized by a pressing element ( 32 ; 32 a), through which the first and second friction members ( 22 , 24 ; 22 a, 24 a) can be brought together in Reibwech interaction, whereby by the Pressing element ( 32 ; 32 a) an interior area of the housing arrangement ( 12 ; 12 a) into a first space area ( 34 ; 34 a) containing the friction elements ( 22 , 24 ; 22 a, 24 a) and a second space area ( 36 ; 36 a) is divided. 16. Coupling arrangement according to one of claims 1 to 15, characterized in that a fluid flow arrangement is seen before for the supply of fluid in the first spatial region ( 34 ; 34 a) and for the removal of fluid from the first spatial region ( 34 ; 34 a) in Essentially independent of the fluid circulation. 17. Coupling arrangement according to claim 15, characterized in that the first space region ( 34 ; 34 a) is essentially closed against fluid exchange. 18. Coupling arrangement according to one of claims 15 to 17, characterized in that in the second space ( 36 ; 36 a) fluid for acting on the pressing element ( 32 ; 32 a) for generating the frictional interaction of the friction members ( 22 , 24 ; 22 a , 24 a) can be initiated. 19. Coupling arrangement according to one of claims 15 to 17, characterized in that the pressing element ( 32 b) for generating the frictional interaction can be acted upon by an actuating arrangement ( 158 b) provided essentially outside the housing arrangement ( 12 b). 20. Clutch arrangement according to one of claims 1 to 19, characterized in that the at least one first friction element ( 22 ) and / and the at least one second friction element ( 24 ) has a friction lining carrier with a flap-like bend ( 127 ) which contributes to the generation of the fluid circulation , 21. Coupling arrangement according to claim 3 or one of claims 4 to 20, if dependent on claim 3, characterized in that the number of the at least one first friction member ( 22 ; 22 a) provided fluid delivery surfaces and / or the number of at least a second friction member ( 24 ; 24 a) provided fluid delivery surfaces in the range of 6-48, preferably 24. 22. Coupling arrangement according to claim 3, or one of claims 4 to 21, if referenced to claim 3, characterized in that in the at least one first friction element ( 22 ; 22 a) and / or in the at least one second friction element ( 24 ; 24 a):
a fluid conveying surface inside dimension (d) to a fluid conveying surface outside dimension (D) has a ratio (d / D) in the range of 0.35-0.85, preferably about 0.6, or / and
an outer dimension (D _a ) of an outer fluid deflection space to a fluid delivery surface outer dimension (D) has a ratio (D _a / D) in the range of 1.03-1.2, preferably about 1.1, or / and
an inner dimension (d _i ) of an inner fluid deflection space to a fluid conveying surface inner dimension (d) has a ratio (d _i / d) of 0.4-0.9, preferably about 0.7. 23. Coupling arrangement according to claim 2 or one of claims 3 to 22, insofar as referred to claim 2, characterized in that an axial dimension of an axial extension area taken up by the first friction elements ( 22 ; 22 a) contributing to the fluid circulation to an axial dimension of one by the Fluid distribution contributing second friction elements ( 24 ; 24 a) occupied axial extent has a ratio in the range of 0.5-1.2, preferably about 1. 24. Clutch arrangement according to one of claims 1 to 23, characterized in that on at least a first Reibor gan ( 22 ; 22 a) and / and on at least a second friction member ( 24 ; 24 a) a friction lining is provided, the inner dimension (d _B ) to its external dimension (D _B ) has a ratio in the range of 0.6-0.9, preferably 0.75. 25. Coupling arrangement, in particular for a motor vehicle, comprising:
a housing arrangement ( 12 b) filled or fillable with fluid, at least one first friction member ( 22 b) rotatable together with the housing arrangement ( 12 b),
at least one second friction element ( 24 b) which can be rotated jointly with an output element and which can be brought into contact with at least one first friction element ( 22 b) in order to produce a friction interaction,
a pressure element ( 32 b) which is displaceably arranged in the housing arrangement ( 12 b) and by means of which the first and second friction elements ( 22 b, 24 b) can be brought into mutual frictional interaction, optionally in conjunction with one or more of the features of the preceding claims,
characterized in that the pressing element ( 32 b) can be acted upon by an essentially outside the housing arrangement ( 12 b) provided actuating arrangement ( 158 b) for generating the friction change. 26. Coupling arrangement according to claim 25, characterized in that the housing arrangement ( 12 b) is substantially completely sealed against fluid exchange. 27. Coupling arrangement according to one of claims 1 to 26, characterized by a torsional vibration damper arrangement ( 200 ) in the torque transmission path between a drive element to be coupled to the housing arrangement ( 12 ) and the at least one first friction element ( 22 ) and / or in the torque transmission path between the at least one second friction member ( 24 ) and the driven member ( 18 ). 28. Coupling arrangement according to one of claims 1 to 27, characterized by a starter-generator arrangement ( 220 ), wherein a preferably permanent magnet-bearing rotor arrangement ( 224 ) of the starter-generator arrangement is coupled to the housing arrangement ( 12 ) for common rotation is. 29. Friction member for a clutch arrangement, in particular according to one of the preceding claims, comprising a friction lining carrier ( 56 ) which carries a Reibbelagananung voltage ( 52 , 54 ) on at least one axial side, and that at least one fluid conveying surface ( 74 , 76 ) through the friction lining carrier ( 56 ) is provided. 30. Friction member for a clutch arrangement according to claim 29, characterized in that the friction lining carrier ( 56 ) in the circumferential direction of successive, axially offset Belagtra sections ( 58 , 60 ) which sections are connected by Verbindungsab ( 72 ), and that the at least one fluid delivery surface ( 74 , 76 ) is provided by a connecting section ( 72 ). 31. Friction member for a clutch arrangement according to claim 30, characterized in that the friction lining carrier ( 56 ) is formed by forming an essentially ring-like sheet metal blank. 32. Friction member for a clutch arrangement according to claim 30 or 31, characterized in that on the mutually axially offset lining support sections ( 58 , 60 ) on their respective axial sides facing away from each other lining segments ( 62 , 64 ) respective Reibbe laganrangungen ( 52 , 54 ) of Friction member ( 22 , 24 ) are provided.