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:
PRIORITY CLAIM 
   This is a U.S. national stage of application No. PCT/EP02/00899, filed on 29 Jan. 2002. Priority is claimed on that application and on the following application(s): Country: Germany, Application No.: 101 10 097.3, Filed: 02 Mar. 2001; Country: Germany, Application No.: 101 25 628.0, Filed: 25 May 2001. 

   BACKGROUND OF THE INVENTION 
   1. Field of the Invention 
   The present invention relates to a clutch arrangement, in particular for a motor vehicle, comprising a housing arrangement which is filled or can be filled with fluid, at least one first friction element which can be rotated together with the housing arrangement, and at least one second friction element which can be rotated together with an output element and can be brought to rest against at least one first friction element in order to produce a frictional interaction. 
   2. Description of the Related Art 
   A clutch arrangement of this type, which is generally also known as a wet clutch, is disclosed, for example, in DE 199 17 893 A1, which corresponds to U.S. Pat. No. 6,394,243. This clutch arrangement comprises a plurality of friction elements, referred to in general as discs, which can be brought into frictional interaction with one another. A clutch piston can be used to press these disks against one another, with the result that a torque transmission produced by Coulomb friction can be obtained between the housing arrangement and an output shaft. In the slip mode, in particular, for example when starting up, the friction elements, which slide frictionally on one another, cause at least some of the driving torque of the drive assembly to be converted into heat. Especially during slip states which last for a prolonged period, for example when starting up on a hill, this may lead to overheating in the region of the friction elements and possibly to friction linings being damaged. In order to ensure cooling, a fluid flow arrangement is provided which can be used, for example, using a fluid-conveying pump provided in the transmission arrangement, to introduce fluid into the housing arrangement and to remove fluid from the housing arrangement. In this case, the fluid flows along the friction elements, absorbs heat and transports this heat out of the region of the clutch arrangement. The fluid which is heated up as it flows through the clutch arrangement can then be cooled again, for example in a transmission cooler. The flow of fluid which is built up in this manner is comparatively slow and results, for example, in a quantity of fluid of approximately 10 l/mm flowing around the various friction elements. At very high loads, even with this amount of circulating flow, the required dissipation of heat can often not be achieved. 
   It is the object of the present invention to provide a wet clutch arrangement, in particular for a motor vehicle, in which, even at a high load, the risk of at least local overheating can be largely eliminated. 
   SUMMARY OF THE INVENTION 
   According to the invention, at least one friction element to be designed to cause the fluid to circulate around at least some areas of the friction elements. 
   Since, in the case of the clutch arrangement according to the invention, it is therefore the friction elements themselves which induce a circulation of fluid which flows around them, with the intention not being to rule out other elements contributing to causing the fluid to circulate, the effect achieved is that the fluid which is present in the housing arrangement, before it is exchanged within the context of the flow of fluid which is generally present, flows a number of times along the friction elements and thus, owing to the existing heat storage capacity of the fluid, can use said fluid to remove significantly more heat than would be possible if it were only to flow once along the friction elements. This arrangement is advantageous particularly in the case of temporary, heavy loads which then lead to an increase in the temperature of the fluid. Within the context of the exchange of fluid which is generally present, this fluid which has been brought to significantly higher temperatures is, however, drawn off from the housing arrangement and brought back to a normal temperature in the transmission cooler or in another cooler. The circulation of fluid according to the invention, which is induced by means of the friction elements themselves, can induce flows in which the flow around the friction elements or at least some of them is at a quantity of fluid of 3000 l/min. 
   One measure which can be used to provide a very high fluid-conveying efficiency is for at least one first friction element and at least one second friction element to be designed in a manner to cause the fluid to circulate. Provision may preferably be made for at least one first friction element to have at least one fluid-conveying surface, and for at least one second friction element to have at least one fluid-conveying surface. It should be emphasized here that, within the context of the present invention, a fluid-conveying surface is a surface which acts on the fluid which is to be induced to circulate, in order to set said fluid into motion, i.e., for example, in order to give the fluid a flow velocity in the circumferential direction and therefore to ensure that centrifugal forces cause this fluid to be moved radially outward. However, a fluid-conveying surface is also a surface which ensures, for example in the manner of a turbine wheel, that the torque of a fluid induced to flow is supported, and therefore ultimately particularly also on the basis of the difference in rotational speed which is present between two fluid-conveying surfaces, contributes to the fluid being conveyed and therefore to causing the fluid to circulate, which induces the cooling effect according to the invention. A further significant aspect in the present invention is that the circulation of fluid which is built up can not only better remove heat from the region of those surface areas which are acted upon thermally, but also that by supporting the torque, this circulation of fluid also contributes in the manner of a pump/turbine arrangement to the torque transmission. This means that, in the case of wet clutches of this type, the torque transmission capacity can be increased. Furthermore, this torque transmission, which is produced by the fluid circulating, is already effective in a state in which the surface-area regions which can be brought frictionally into interaction with one another are not yet in contact. 
   In order to be able to provide fluid-conveying efficiency which is as good as possible, according to the present invention, provision may be made for the at least one fluid-conveying surface to have a component of radial extent and a component of axial extent. 
   For example, provision may be made for the at least one fluid-conveying surface to be designed at least in some regions with an essentially tangentially orientated surface perpendicular. 
   In one embodiment according to the invention which can be constructed in a particularly simple manner, the at least one fluid-conveying surface can be provided by the at least one first friction element or/and the at least one second friction element having, on at least one axial side, a friction lining arrangement which provides the at least one fluid-conveying surface. This can be realized, for example, by the at least one fluid-conveying surface comprising at least one wall which bounds a groove-like channel in the friction lining arrangement in the circumferential direction. 
   In order to be able to further increase the fluid-conveying efficiency, it is proposed that the at least one first friction element or/and the at least one second friction element has, on both axial sides, friction lining arrangements which each provide fluid-conveying surfaces. 
   In one embodiment which distributes the friction load particularly well to various friction elements, provision can be made for the at least one first friction element or/and the at least one second friction element to have, just on one axial side, a friction lining arrangement which provides at least one fluid-conveying surface, and for a friction lining arrangement of a further friction element to lie opposite the other axial side. 
   In an alternative embodiment which can provide a high fluid-conveying efficiency, provision may be made for the at least one first friction element or/and the at least one second friction element to have a friction lining carrier which, preferably on at least one axial side, carries a friction lining arrangement, and for at least one fluid-conveying surface to be provided by the friction lining carrier. This can be achieved, for example, by the friction lining carrier having lining-carrying sections which follow one another in the circumferential direction, are offset axially with respect to one another and are connected to one another by connecting sections, and for the at least one fluid-conveying surface to be provided by a connecting section. 
   In order to be able to undertake the construction in a manner which is as simple as possible, it is proposed that the friction lining carrier is formed by deformation of an essentially ring-like sheet-metal blank. 
   It may furthermore be provided that on the lining-carrying sections, which are offset axially with respect to one another, lining segments of respective friction lining arrangements are provided on the axial sides of said lining-carrying sections, which are in each case directed away from one another. 
   A very high fluid-conveying efficiency can be obtained if a plurality of fluid-conveying surfaces, which follow one another in the circumferential direction, are provided on the at least one first friction element or/and on the at least one second friction element. 
   In the clutch arrangement according to the invention, a pressing element can be provided by means of which the first and second friction elements can be brought into frictional interaction with each other, the pressing element dividing an interior region of the housing arrangement into a first space region containing the friction elements and a second space region. 
   As already discussed, it is advantageous to ensure a virtually constant exchange of the fluid which is present in the housing arrangement in order to be able to remove the heat stored therein. It is therefore proposed that a fluid flow arrangement is provided for feeding fluid into the first space region and for removing fluid from the first space region essentially independently of the circulation of fluid. 
   In an alternative embodiment, provision may be made for the first space region to be essentially completely sealed off with respect to the exchange of fluid. 
   In order to set a torque-transmitting state, provision may be made for fluid to be able to be introduced into the second space region in order to act upon the pressing element so as to produce the frictional interaction of the friction elements. 
   In an alternative embodiment, the torque-transmitting state can be obtained by the fact that the pressing element can be acted upon by an actuating arrangement, which is provided essentially outside the housing arrangement, in order to produce the frictional interaction. 
   In order to remove heat as readily as possible from the region of the surface areas which interact frictionally with one another, a circulation of fluid which is as strong as possible is advantageous. Therefore, according to a further advantageous aspect of the present invention, provision may be made for the at least one first friction element or/and the at least one second friction element to have a friction lining carrier with a tab-like bent section which contributes to causing the fluid to circulate. 
   Furthermore, it is advantageous, in order to obtain an efficient circulation of fluid in the clutch arrangement according to the invention, that the number of fluid-conveying surfaces provided on the at least one first friction element or/and the number of fluid-conveying surfaces provided on the at least one second friction element is in the region of 6-48, preferably around 24, or/and that in the at least one first friction element or/and in the at least one second friction element:
         an internal dimension of the fluid-conveying surface to an external dimension of a fluid-conveying surface is in a ratio in the region of 0.35-0.85, preferably approximately 0.6, or/and   an external dimension of an outer fluid-deflecting space to an external dimension of a fluid-conveying surface is in a ratio in the region of 1.03-1.2, preferably approximately 1.1, or/and   an internal dimension of an inner fluid-deflecting space to an internal dimension of a fluid-conveying surface is in a ratio of 0.4-0.9, preferably approximately 0.7.       

   In a further preferred embodiment, provision may be made for an axial dimension of a region of axial extent taken up by the first friction elements contributing to the circulation of fluid to an axial dimension of a region of axial extent taken up by the second friction elements contributing to the circulation of fluid to be in a ratio in the region of 0.5-1.2, preferably approximately 1. In connection with causing the fluid to circulate, it has turned out to be advantageous if a friction lining is provided on at least one first friction element or/and on at least one second friction element, the internal dimension of which is in a ratio in the region of 0.6-0.9, preferably 0.75, to its external dimension. 
   According to a further aspect, the present invention relates to a clutch arrangement, in particular for a motor vehicle, comprising a housing arrangement which is filled or can be filled with fluid, at least one first friction element which can be rotated together with the housing arrangement, at least one second friction element which can be rotated together with an output element and can be brought to rest against at least one first friction element in order to produce a frictional interaction, and a pressing element which is arranged displaceably in the housing arrangement and by means of which the first and second friction element can be brought into mutual friction interaction. 
   According to the invention, provision is furthermore made for the pressing element to be acted upon by an actuating arrangement, which is essentially provided outside the housing arrangement, to produce the frictional interaction. 
   In an arrangement of this type, the actuation is therefore undertaken from outside the housing, for example by means of a conventional engagement or disengagement mechanism, a diaphragm-spring-like energy accumulator or the like. Fluid lines via which fluid has to be conducted into the housing arrangement in order to activate the clutch are not required. A design of this type is advantageous in particular in conjunction with the further principles of the present invention, thus in particular the causing of a circulation of fluid in the region of the surface areas acting frictionally on one another, since here an external supply of fluid in order to cool the regions which are acted upon thermally is not required. 
   For example, provision may be made for the housing arrangement to be essentially completely sealed off with respect to the exchange of fluid. 
   Furthermore, a torsional-vibration damping arrangement is preferably provided in the clutch arrangement according to the invention, which damping arrangement can be provided in the torque transmission path between a driving element, which is to be coupled to the housing arrangement, and the at least one first friction element, or/and can be provided in the torque transmission path between the at least one second friction element and the output element. 
   Furthermore, a starter-generator arrangement can be provided in the clutch arrangement according to the invention, a rotor arrangement, which preferably carries permanent magnets, of the starter-generator arrangement being coupled to the housing arrangement for rotation together. 
   The present invention furthermore 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-conveying surface is provided by the friction lining carrier. 
   In this case, provision may again be made for the friction lining carrier to have lining-carrying sections which follow one another in the circumferential direction, are offset axially with respect to one another and are connected to one another by connecting sections, and for the at least one fluid-conveying surface to be provided by a connecting section. 
   The friction lining carrier may, for example, be formed by deformation of an essentially annular sheet-metal blank. 
   It is furthermore advantageous if on the lining-carrying sections, which are offset axially with respect to one another, lining segments of respective friction lining arrangements of the friction element are provided on the axial sides of said lining-carrying sections, which sides are in each case directed away from one another. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
       FIG. 1  shows a view of a partial longitudinal section of a clutch arrangement according to the invention; 
       FIG. 2  shows a partial axial view of a friction element used in the clutch arrangement in  FIG. 1 ; 
       FIG. 3  shows a view of the friction element illustrated in  FIG. 2  radially from the outside; 
       FIG. 4  shows a partial axial view of a friction element designed in an alternative manner; 
       FIG. 5  shows a modification of the friction element illustrated in  FIG. 4 ; 
       FIG. 6  shows an alternative embodiment of the clutch arrangement according to the invention; 
       FIG. 7  shows a partial axial view of a friction element used in the clutch arrangement in  FIG. 6 ; 
       FIG. 8  shows a view corresponding to  FIG. 6  of a further alternative embodiment of the clutch arrangement according to the invention; 
       FIG. 9  shows a further illustration of an alternative embodiment of the clutch arrangement according to the invention; 
       FIG. 10  shows a partial axial view of a friction element used in the embodiment according to  FIG. 9 ; 
       FIG. 11  shows a partial axial view of a further friction element used in the embodiment according to  FIG. 9 ; 
       FIGS. 12-15  show various embodiments of friction lining carriers for outer and inner disks; 
       FIG. 16  shows a partial sectional view of an alternative type of embodiment of a clutch arrangement 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  shows a sectional view of a friction element; 
       FIGS. 19-21  show views of partial longitudinal sections of clutch arrangements according to the invention which illustrate the various possibilities for the flow of fluid; 
       FIG. 22  shows a view of a partial longitudinal section of a clutch arrangement according to the invention used to illustrate various dimensions; 
       FIG. 23  shows a view of a partial longitudinal section of an outer disk carrier; 
       FIG. 24  shows a view of a partial longitudinal section of a clutch arrangement according to the invention according to an alternative embodiment; 
       FIGS. 25-30  show further embodiments of the clutch arrangement according to the invention in conjunction with a torsional-vibration damper or a starter-generator arrangement. 
   

   DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
   In  FIG. 1 , wet clutch arrangement  10  comprises a housing arrangement  12  which can be coupled via a plurality of fastening elements and a coupling element (not illustrated), such as, for example, a flexiplate, to a drive shaft, for example a crankshaft of an internal combustion engine, for rotation together. On the axial side which is situated at a distance from the coupling to the drive shaft, the housing arrangement  12  has a housing hub  16  which engages, for example, in a transmission arrangement (not illustrated) where it drives a fluid-conveying pump such that it rotates. An output shaft  18  which protrudes with its free end into the interior  20  of the housing arrangement  12  is arranged concentrically to the housing hub  16 . This output shaft  18  may, for example, be a transmission input shaft. 
   A plurality of first friction elements  22  which are coupled to the housing arrangement  12  for rotation together is provided in the housing arrangement  12 . Furthermore, a plurality of second friction elements  24  is provided, the second friction elements  24  being coupled via a coupling element  26  and an output hub  28  to the output shaft  18  for rotation together. An abutment element  30  is provided in a rotationally fixed manner on the coupling element  26  and in a manner such that it is fixed at least in an axial direction by a securing ring  31 . The first friction elements  22  and second friction elements  24  are situated between this abutment element  30  and a clutch piston  32 . The clutch piston  32  divides the interior  20  of the housing arrangement  12  into a first space region  34 , which contains the friction elements  22 ,  24 , and a second space region  36 . Fluid can be introduced into the second space region  36  via a central opening  38 , which is provided in the output shaft  18 . In order to seal off this second space region  36  with respect to the first space region  34 , the clutch piston  32 , which is of essentially ring-like design, is held in a fluid-tight, but axially displaceable manner radially on the outside and radially on the inside on respective mounting elements  40 ,  42  with the interposition of sealing elements. A plurality of fluid-flow ducts  44  which permit fluid to be supplied into the space region  36  are provided in the radially inner mounting element  42 . 
   Fluid can also be introduced into the first space region  34  or fluid can be conducted out of the latter. 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 , said separating element forming a flow space  48  between the housing hub  16  and itself and furthermore forming a flow space region  50  between the output shaft  18  and itself. Working fluid can be introduced through the flow space region  48  into the space region  34 , for example by the fluid-conveying pump which is provided in the transmission arrangement, so that said working fluid flows radially to the outside at the right-hand end of the housing arrangement  12 . The fluid then flows around the friction elements  22 ,  24 , passes radially inward and is drawn off again via the flow space region  50 . This enables the fluid which has been heated in the housing arrangement  12 , as will be described below, to be continuously exchanged and replaced by cooler fluid. 
   At least some of the first friction elements  22  and some of the second friction elements  24  carry respective friction lining arrangements  52 ,  54  on their two axial sides. A further friction element is then in each case situated axially opposite said friction lining arrangements  52  and  54  for the purpose of frictional interaction. The various friction elements  22 ,  24  are supported on the housing arrangement  12  and on the coupling element  26  in a rotationally fixed manner by an engagement in the manner of an axial toothing, and in a manner such that they can be displaced axially in the direction of the axis of rotation A. The construction of a friction element of this type, which is provided with friction lining elements  52 ,  54 , will be described below in respect of a first friction element  22  with reference to  FIGS. 2 and 3 . It should be pointed out that the basic construction is equally applicable to the second friction elements  24 , which are provided with friction lining arrangements  52 ,  54 . 
   It can be seen in  FIG. 2  that this first friction element  22  has a friction lining carrier  56  having an essentially ring-like contour. When viewed radially from the outside, it can be seen that the friction lining carrier  56  is designed with an undulated structure and has lining-carrying sections  58 ,  60  which are offset with respect to one another in the direction of the axis of rotation A. On their sides facing axially away from one another, the lining-carrying sections  58 ,  60  carry respective lining segments  62  and  64  of the friction lining arrangements  52 ,  54 . In the region of each of the friction-carrying sections  58 ,  60 , a coupling projection  66  and  68 , respectively, is provided radially on the outside and is used to bring about the rotationally fixed coupling to corresponding coupling projections  70  of the housing arrangement  12 . 
   It can furthermore be seen in  FIG. 3  that the lining-carrying sections  58 ,  60 , which are offset axially with respect to one another, are connected to one another by connecting sections  72 . These connecting sections  72  extend, as can also be seen in  FIG. 2 , approximately from radially on the inside to radially on the outside and lie essentially in a plane containing the axis of rotation A. For example, the respective connecting sections can be formed with surface perpendiculars standing tangentially to a circumferential circular line. On their surface-area regions which point in the circumferential direction, these connecting sections  72  form fluid-conveying surfaces  74 ,  76 . In this case, the fluid-conveying surfaces  74 ,  76  of the first friction elements  22  which are coupled to the housing arrangement  12  for rotation together, act, for example in a coupling process in which the first friction elements  22  have a significantly higher speed of rotation than the second friction elements  24 , as pump blade surfaces and ensure that a flow of fluid which is guided radially outward is produced in their vicinity. In the same manner, the fluid-conveying surfaces which are provided in a corresponding manner on the second friction elements  24  act as turbine blade surfaces which, owing to the difference in rotational speed between the first friction elements  22  and the second friction elements  24 , are used for the fluid, which is set in motion by the fluid-conveying surfaces  74 ,  76  of the first friction elements  22 , for the purpose of supporting the torque and in the process conduct this fluid radially inward, or are used for conveying the fluid radially inward. This fluid, which is conducted or conveyed radially inward by means of the fluid-conveying surfaces of the second friction elements  24 , therefore replaces the fluid which is conveyed from radially on the inside to radially on the outside by the fluid-conveying surfaces  74 ,  76  of the first friction elements  22 . A circulation of fluid is therefore built up, as shown by dashed-line arrows in  FIG. 1 , which ultimately corresponds to the circulation of fluid in the manner produced by an impeller and a turbine wheel of a hydrodynamic torque converter or a fluid clutch. The circulation of fluid produced in the clutch arrangement  10  according to the invention has the effect of inducing a continuous fluid circulation and flow around the friction elements  22 ,  24  independently of the discussed exchange of the fluid present in the housing arrangement  12 , which exchange of fluid can take place, for example, at a rate of 10 l/mm, said circulation of fluid making it possible, for example, to produce a flow around the friction elements  22 ,  24  with a quantity of liquid of 3000 l/min. This enables the frictional heat which is produced in the various friction elements  22 ,  24  in the friction or slip mode, especially in starting-up processes which greatly stress these friction elements, to be significantly better absorbed in the fluid. The circulation of fluid which is built up in accordance with the invention is combined with the comparatively slow exchange of fluid, with the result that some of the fluid which has been brought to a comparatively high temperature by the circulation is continuously drawn off and replaced by cooler fluid. 
   It should be emphasized here that the principle which is illustrated in  FIG. 1  of causing the fluid to circulate may, of course, be provided independently of the number of first friction elements or second friction elements. The positioning which is illustrated in FIG.  1  and in which the first friction elements  22 , which are designed to convey fluid, are first of all arranged following one another, in which case a respective second friction element  24 , which is of essentially plate-like design, is situated between them and then, after a transitional friction element  22  which does not carry any friction linings, are followed by the second friction elements  24  which are designed to convey fluid and between which a first friction element, which is essentially of plate-like design and is not provided with friction linings, is situated, the fluid is caused to circulate all the way around the friction elements  22 ,  24 . A staggered arrangement of first friction elements  22  contributing to producing the fluid flow and of second friction elements  24  contributing to producing the fluid flow enables a plurality of local regions of fluid circulation to be produced 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 , which are designed to produce the fluid. For example, first friction elements  22  which act more as impellers or pump blades may be provided. 
   It can furthermore be seen that in the axially central region two first friction elements  22  follow each other, thus providing a non-effective pairing of friction surfaces. This can be avoided, for example, by ultimately no friction linings being provided on the friction lining carriers of the first friction elements  22 , but on all second friction elements  24 , in particular also on the plate-like, second friction element  24  which can be seen on the right in  FIG. 1 , friction linings being provided on both sides. In the context of the present invention, a friction surface carrier of this type which does not carry any friction linings can nevertheless be viewed as a friction lining carrier particularly in respect of the construction which is relevant to conveying fluid. 
     FIG. 4  illustrates a modified embodiment of a first friction element  22 . It can be seen in comparison to the embodiment according to  FIG. 2  that the projections  66 ,  68 , which are used for the rotational coupling and are offset with respect to one another, are shifted radially further outward and that fluid passage openings  78  are provided between the individual friction lining segments of the friction lining arrangements, in each case in the transition region situated in the circumferential direction between the lining-carrying sections  58 ,  60 . These fluid passage openings  78  permit the fluid to circulate essentially unhindered. In the embodiment according to  FIG. 5 , these fluid passage openings  78  are open radially outward, so that comparatively long stretched-out projections  66 ,  68  are provided here in each case in the radial direction for coupling to the corresponding formation  70  of the housing arrangement  12 . The various connecting sections  72  are in each case also provided here to provide the fluid-conveying surfaces, which can be seen in FIG.  3 . 
   It should be emphasized that the embodiments according to  FIGS. 4 and 5  may also be used with the second friction elements  24 , which are coupled to the output shaft  18 , in which case the various openings and coupling projections then extend radially inward with respect to the region which carries the friction lining segments. 
     FIGS. 12-15  illustrate various design variants of friction lining carriers  56  both for the second friction elements  24 , which are to be coupled to the output shaft  18 , and for the first friction elements  22 , which are to be coupled to the housing arrangement  12 . A friction lining carrier  56  for a friction element  24 , which is to be coupled to the output shaft  18 , can be seen in FIG.  12 . Said friction lining carrier has, as already previously described, the various lining-carrying sections  58 ,  60  which are offset axially with respect to one another and are coupled to one another by the connecting sections  72 . The connecting sections  72  again form the fluid-conveying surfaces  74 ,  76  on the surface areas which are orientated in the circumferential direction. A web section  100 ,  102  extends radially inward from each of the lining-carrying sections  58 ,  60 . Said web sections lead into a radially inner, ring-like section  104  which has, on its inner circumferential side, a toothing (not illustrated) for the rotationally fixed coupling to the coupling element  26 . Since the lining-carrying sections  58 ,  60  are offset axially with respect to one another, the web sections  100 ,  102 , which in each case extend from them, run in the pattern which is illustrated in  FIG. 12  at an inclination with respect to the axis of rotation A or a plane which is orthogonal thereto. Passage openings  106  are formed in each case between the individual web sections  100 ,  102  and the fluid which has been induced to circulate can pass through them in the axial direction. 
   In the design variant which is illustrated in  FIG. 13 , web sections  100  extend just from one set of lining-carrying sections  58 ,  60 , namely from the lining-carrying section  60 . The lining-carrying sections  58  are not attached directly to the ring section  104  in their radially inner region. This produces a configuration in which the web sections  100  can lie in the same plane as the lining-carrying sections  60  and in which furthermore, owing to the halved number of web sections, which can then be somewhat wider, the openings  106  formed between the individual web sections  100  are in principle larger. 
     FIG. 14  illustrates a friction lining carrier  56  for a friction element which is to be coupled radially on the outside, i.e. for example, a friction element  22  which is to be coupled to the housing arrangement  12 . The lining-carrying sections  58 ,  60 , which are offset axially with respect to one another, and the connecting sections  72  connecting them, with the fluid-conveying surfaces  74 ,  76  provided on them, can also be seen again here. Web sections  108  which lead into an outer ring section  110  adjoin the lining-carrying sections  60  axially on the outside. Said ring section has an external toothing  112  for the 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  and the fluid can pass through them in the axial direction. It should be emphasized here that web sections may, of course, also or additionally emerge radially outward from the lining-carrying sections  58 , thus again resulting in the provision of the inclined orientation of the various web sections, which can be seen in the example of FIG.  12 . 
   In the design variant which is illustrated in  FIG. 15 , projections  116  which protrude radially outward are formed in the transition region between the lining-carrying sections  60 ,  58 . Since these projections  116  extend over the connecting sections  72  and the lining-carrying sections  58  from the lining-carrying sections  60 , 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 illustrated above can be seen in  FIGS. 16-18 . In this embodiment, the various friction elements are constructed in each case from at least one annular-disk-like sheet-metal element. The first and second friction elements  22 ,  24  which contribute to the circulation of fluid each comprise two such sheet-metal elements  118 ,  120 ,  122 ,  124  formed in the manner of conventional disks. Whereas the sheet-metal elements  118 ,  120  have the openings  114  radially on the outside again for the axial passage of fluid, the sheet-metal elements  122 ,  124  have the openings  106  radially on the inside for the passage of fluid. An arrangement which provides the fluid-conveying surfaces is inserted between two of these sheet-metal elements  118 ,  120 ,  122 ,  124  in each case. Said arrangement may comprise, for example, the conveying-surface element  126  which can be seen in FIG.  17 . Said element again has sections  58 ,  60  which are offset axially with respect to one another, correspond to the lining-carrying sections in the variants described previously and are connected to one another by connecting sections  72 . Each of these connecting sections  72  again provides the fluid-conveying surfaces  74 ,  76  on both of its circumferential sides. The conveying-surface element  126  can be connected fixedly, for example by soldering, bonding or the like, to the associated sheet-metal elements  118 ,  120  and  122 ,  124 , which are produced, for example, by punching. It should be emphasized that, of course, conveying-surface arrangements constructed in another manner, for example from a plurality of parts, may also be provided here. The friction elements  22 ′,  24 ′, which do not directly contribute to the circulation of fluid, are designed in the manner of conventional disks, i.e. likewise comprise annular-disk-like sheet-metal elements or the like which carry friction linings on both of their axial sides. It should be emphasized that, of course, friction linings can also be provided on the friction elements  22 ,  24  which produce the circulation of fluid. Friction linings with duct-like hollows provided on their surface areas may especially be used here, with the result that fluid can also flow in these surface-area regions to improve the removal of heat. It is furthermore also emphasized that, in the clutch arrangement according to the invention, those friction elements which contribute, owing to an appropriate geometry, to causing the fluid to circulate, do not necessarily also have to carry the friction linings. For example, the conveying-surface element which is illustrated in  FIG. 17  can be integrated in a clutch arrangement without friction linings provided on it, and mating friction elements, which are, for example, of annular disk-like design and bear friction linings which, for example, are continuous in the circumferential direction, can be provided on both sides of said conveying-surface element. It is also, of course, possible, in an arrangement as will be described below with reference to  FIGS. 6-11 , to provide surface-area ducts in friction elements, which are constructed, for example, from sheet metal, and then on corresponding mating friction elements to provide, in the circumferential direction, either continuous friction linings or friction linings, for example, likewise having surface-area ducts. 
   The design which can be seen in  FIGS. 16 and 17  can be produced in a simple manner owing to the use of standard components and is therefore also cost-effective. In order, in a clutch arrangement according to the invention, to intensify the circulation of fluid even further, it may be provided that, on the various components formed from sheet metal, for example the lining carriers  56  described above, not only are the openings permitting the passage of fluid or recesses provided radially outside or radially within the friction linings, but also additional conveying or blade surfaces are provided. As can be seen in the example of  FIG. 18 , this can be undertaken, for example, by the fact that when an opening  114  situated radially on the outside is formed, the sheet-metal part is not punched completely, but rather a U-shaped punched section is formed and in this manner a tab  127  which is bent laterally or obliquely is then produced. A plurality of such tabs which follow one another in the circumferential direction act in the manner of conveying blades and intensify the circulation, which has in any case already been provided by the measures according to the invention which have been described above. The angle at which these tabs  127  are bent with regard to a plane which is essentially orthogonal to the axis of rotation A is preferably in the region of approximately 90°, but may also be in the angular range of 15-165°. 
   A modified embodiment of the clutch arrangement according to the invention is illustrated in FIG.  6 . Components which correspond to previously described components are referred to with the same reference numbers with the addition of an “a”. Only the substantial structural and functional differences will be discussed below. 
   In the embodiment according to  FIG. 6 , friction lining arrangements  52   a ,  54   a , in the form of friction linings designed, for example, in a ring-like manner are again provided on both sides of the first and second friction elements  22   a ,  24   a , which induce the fluid to circulate. As can be seen, for example in  FIG. 7  with reference to a first friction element  22   a  and the friction lining  52   a  provided on it, the latter has made on it, for example by punching or embossing, a plurality of fluid flow ducts  80   a  which preferably extend essentially radially. Each of these fluid flow ducts  80   a  is bounded in the circumferential direction by walls which now provide the fluid-conveying surfaces  74   a ,  76   a . In this case, those fluid-conveying surfaces  74   a ,  76   a  which are provided on the first friction elements  22   a  which can be rotated with the housing arrangement  12   a  again, in the slip mode, take on the function of the pump blade surfaces while the corresponding fluid-conveying surfaces on the second friction elements  24   a  again provide the function of the turbine blade surfaces. In this embodiment, the friction lining carriers  56   a  are provided as sheet-metal parts which are of essentially planar design. It can also be seen here that a second friction element or first friction element, on which no friction linings are provided, is in each case again situated between two first friction elements  22   a  or second friction elements  24   a , which induce the fluid to circulate. 
   In order to avoid the blind frictional surface, which can also be seen in  FIG. 6 , between two directly adjacent, first friction elements  22   a , an arrangement as is shown in  FIG. 8  can be provided. It can be seen here that a friction lining  52   a  (in the case of the first friction elements  22   a ) and  54   a  (in the case of the second friction elements  24   a ) is provided in each case on just one axial side of the first friction elements  22   a  and of the second friction elements  24   a . Each of these friction linings  52   a ,  54   a  again has the discussed ducts  80   a . The abutment element  30   a  can also carry a friction lining  54   a  of this type having ducts  80   a . In this embodiment, the local circulations which have already been discussed previously are then produced. Whereas the embodiment which is illustrated in  FIG. 8  has an improved torque transmission capacity with the same number of friction elements owing to the avoidance of a non-effective blind frictional surface, the plurality of local circulations has the effect of achieving a slightly reduced flow volume in comparison to the global circulation flow of FIG.  6 . Also, an axially very compact embodiment is obtained. Both the embodiment illustrated in FIG.  6  and the embodiment illustrated in  FIG. 8  has the advantage of having a structural design which is extremely simple to produce. It can be seen especially that a significantly smaller axial overall size is achieved owing to the omission of the connecting sections of the embodiment according to  FIG. 1 , although overall the fluid-conveying surfaces provided in the region of the friction lining arrangements provide a smaller overall surface area and there is thus also a reduced conveying efficiency. In order to counteract this, the axial constructional space which is available should be utilized to make the thickness of the various friction linings and the depth of the grooves made in them to be as great as possible. 
   A further modification of the fluid-conveying surfaces in the area of the principle of the invention which uses friction linings is illustrated in  FIG. 9. A  plurality of first friction elements  22   a  and at least one second friction element  24   a  in an axially staggered arrangement are also provided here. 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 illustrated previously, the second friction elements  24   a , which are coupled via the coupling element  26   a  to the output shaft, are now designed as “external disks”, i.e. their rotational locking projections reach radially outward. The first friction elements  22   a  are designed as “internal disks” and have inner rotational coupling projections for engagement with corresponding formations  70   a  on the housing arrangement  12   a . A system of the dual-line principle is also illustrated here, in which, in order to produce the engaged state, the fluid pressure in the first space region  34   a  is increased by increased supply of fluid over the fluid pressure in the second space region  36   a . The clutch piston  32   a  is therefore pressed axially against the friction elements  22   a  and  24   a . At least one passage opening  90   a  which enables an exchange of fluid even when the clutch arrangement  10   a  is engaged is provided in the clutch piston  32   a . The clutch piston  32   a  is coupled in a rotationally fixed manner via a rotational coupling arrangement  91   a  to the housing arrangement  12   a , but can be moved axially with respect to the latter. In this case, the clutch piston  32   a  is therefore also to be considered as the first friction element which can be rotated with the housing arrangement  12   a  and which ultimately also carries a friction lining  52   a.    
   In  FIG. 10 , a partial axial view of a second friction element  24   a  can be seen. It can be seen that the friction lining  54   a  provided on it has grooves or ducts  80   a  which are sealed off radially toward the inside. A radially inner, ring-like section  82   a  remains. In the radially inner end region of the ducts  80   a , passage openings  84   a  are provided in the friction lining carrier  56   a . The friction linings  52   a  of the first frictional elements  22   a , which can be seen in  FIG. 11 , likewise have a plurality of ducts  80   a  which are restricted radially to the inside and in their radially inner end region lead into a ring-like duct region  86   a . This ring-like duct region  86   a  lies opposite the passage openings  84   a . In the same manner as in the embodiments described previously, the side walls which bound the ducts  80   a  form respective fluid-conveying surfaces  74   a ,  76   a . In the case of the first friction elements  22   a , which can be rotated together with the housing arrangement  12   a , these fluid-conveying surfaces  74   a ,  76   a  again act as blade surfaces which convey the fluid radially outward, while the fluid-conveying surfaces  74   a ,  76   a , which are provided on the second friction elements  24 , assist the flow of fluid radially inward and are used to support the torque. In the design variants which are illustrated in  FIG. 9 , local circulations are again produced, said circulations extending in each case over a lining carrier of a second friction element  24   a , a friction lining  54   a  of a second friction element  24   a  and a friction lining  52   a  of a first friction element  22   a . It should be emphasized that, in this embodiment, the coupling element  26   a , which lies radially outside the various friction linings  52   a ,  54   a , takes on a function for assisting the deflection of the circulation of fluid in the radially outer region whereas, in the previously described embodiments, this coupling element has provided a corresponding deflection of the circulation of fluid in the radially inner region. The deflection in the radially outer region takes place there by means of those sections of the housing arrangement which are situated radially on the outside. In particular with regard to the embodiments illustrated in  FIGS. 6-11 , it should be emphasized that friction elements of this type do not, of course, necessarily have to comprise a separate carrier element and separate friction linings attached thereto, for example by bonding. On the contrary, friction elements which are constructed as a single part, for example from fiber composite material, for example carbon fiber composite, may also be provided here, it being possible for said friction elements to then be configured as desired in terms of their geometry, but it also being possible for them to be designed, for example, like the friction elements which can be seen in FIG.  8 . Within the context of the present invention, these friction elements then have, on their axial sides, friction linings or friction lining sections which are designed as a single piece with a body region which is designed for attachment to the housing arrangement or to the output shaft. 
   Of course, in friction elements of this type, in which the friction linings or friction lining sections are thus formed integrally from the same material as the body regions designed for attachment to other components, it is also possible to provide a meandering structure, as can be seen, for example, in FIG.  17 . 
   The embodiments which have been previously described and also those which have yet to be described below, in particular the embodiment illustrated in  FIG. 9 , are also suitable as a clutch arrangement in a hydrodynamic torque converter or a fluid clutch, i.e. as a “torque converter lockup clutch arrangement”. In this case too, when the torque conversion state is brought about, a considerable part of the torque which is introduced is converted into frictional heat which can then be rapidly removed by the circulation induced in accordance with the invention. It is of substantial advantage in all of the embodiments according to the invention that the quantity of fluid which is conveyed during the circulation of fluid increases with increasing difference in rotational speed between the various friction elements which bear frictionally against one another and are effective as pumps or turbines. That is to say, in particular if there is a heavy friction loading, i.e. if there is a large slip, a large quantity of fluid is circulated by the circulation of fluid, with the effect of a significantly improved removal of the heat produced by friction. The circulation of fluid, which is produced in the region of the various surface-area regions themselves which become frictionally effective, ensures that ultimately fluid can be conveyed very rapidly to all of the surface-area regions which are acted upon thermally and heat can be removed from there. 
   In the following text, the various possibilities for the flow of fluid, which is combined or can be combined with the circulation of fluid according to the invention, are illustrated.  FIG. 19  thus shows in general a clutch arrangement  10  according to the invention in which the supply and removal of fluid takes place in the manner of a triple-line system. While fluid is introduced into the space region  36  via the central opening  38  in the output shaft  18  for the purpose of axially displacing the clutch piston  32 , or is conducted away from there again, fluid is introduced into the space region  34  via a further line which essentially encompasses the flow space region  50 . Fluid can be drawn out of the space region  34  again via a further line which encompasses the flow space region  48 . It should be emphasized that, in the illustration of  FIG. 19 , the separating element  46  is effective in the manner of a labyrinth-like seal and can comprise two sealing elements which in principle can be rotated with respect to each other. The advantage of this arrangement is that the engagement and disengagement process can be made completely independently of any states of pressure in the space region  34 . Excellent removal of heat, which can be regulated by the transmission, can therefore be obtained. Also, very precise displacement of the clutch piston  32  can be achieved. 
   The embodiment according to  FIG. 20  operates in accordance with the “dual-line principle”. The fluid is fed into the housing arrangement  12  via the central opening  38  in the output shaft  18 , specifically into the space region  36 . Fluid enters, with a constricting action being provided, into the space region  34  via one or more openings  130  in the clutch piston  32  and can flow off again via a space region  51  provided between the hub  16  and the output shaft  18 . To engage this clutch arrangement  10 , fluid is therefore fed intensely into the space region  36 . Owing to the increase in the fluid pressure in this space region  36 , the clutch piston  32  is then pressed against the friction elements. It is possible here to reverse the direction of flow of the fluid in order to obtain a more rapid disengagement process. By means of the provision of the at least one opening  130 , an exchange of fluid and a corresponding removal of heat is also continuously possible here in the engaged state. Although the desired leakage of fluid (caused by the opening or openings  130 ) has the consequence of reduced efficiency since oil has to be continuously fed back in, with a low outlay on construction a continuous exchange of fluid is possible. 
   The design variant illustrated in  FIG. 21  corresponds essentially to the design variant which is illustrated in  FIG. 20 , in which fluid is fed into the space region  36  via the central opening  38  in the output shaft  18 . 
   However, a passage opening is not provided in the clutch piston  32 . There is thus no direct connection for the exchange of fluid between the two space regions  34 ,  36 . In this variant, the space region  34  is filled with fluid in advance. The removal of heat from the regions which are acted upon frictionally takes place here merely by means of the circulation of fluid which has been built up in accordance with the invention in the region of the various friction elements. There is no exchange of fluid, by means of which fluid is removed from the space region  34 . In order to be able to compensate here for the change in volume of the space region  34 , which is induced by displacement of the clutch piston  32 , said space region  34  is not completely filled with the working fluid, i.e. an oil-like liquid or the like, with the result that a compressible volume of gas remains. 
     FIG. 22  illustrates various dimensions which are to lie within certain ranges in order to obtain an efficient circulation of fluid. It is therefore, for example, advantageous if the ratio of the internal diameter to the external diameter of the fluid-conveying surfaces ultimately causing the fluid to circulate, i.e. the ratio d/D, is in the region of 0.35-0.85, preferably around approximately 0.6. The number of effective fluid-conveying surfaces should be in the region of 6-48, preferably around approximately 24. For the friction linings, it has proven advantageous if their diameter ratio d B /D B  is in the region of 0.6-0.9, preferably around approximately 0.75. 
   The provision of the previously discussed, various openings  114 ,  106 , which are provided radially on the outside and inside, or of passage cutouts between respective coupling projections causes the formation of the radially outer and radially inner fluid flow spaces  134 ,  136 , which have already been previously discussed. These can be formed radially to the outside or radially to the inside by the various ring sections, which have previously been discussed, of the friction lining carriers  56 , but may, as can also be seen, for example, in  FIG. 1 , be bounded directly by the housing arrangement  12  or by the coupling element  26 . For these radially outer and radially inner fluid flow spaces, in which the fluid flows approximately in the axial direction, it has proven advantageous to provide a value in the region of 1.03-1.2, preferably approximately 1.1, as a ratio to the external dimension of the fluid-conveying surfaces, i.e. a ratio D a /D, or to provide a value in the region of 0.4-0.9, preferably approximately 0.7, as a ratio to the internal diameter of the fluid-conveying surfaces, i.e. as a ratio d i /d. Furthermore, it is advantageous if the ratio of the axial extent of the friction elements acting in the manner of a pump, which is expressed approximately by the dimension B P  in  FIG. 22 , to the axial extent of the friction elements which are effective in the manner of a turbine, expressed approximately by the extent B P  in  FIG. 22 , is in the region of 0.5-1.2, preferably approximately around 1. It should also be emphasized here that, in  FIG. 22 , there is a slight inaccuracy insofar as a friction element  24  which is coupled radially on the inside in a rotationally fixed manner to the coupling element  26 , but does not contribute to causing the fluid to circulate, is situated between two friction elements  22  effective in the manner of a pump. The same also applies to the region which is effective in the manner of a turbine. 
   It has furthermore turned out to be advantageous, but not compulsory, if, as illustrated in  FIG. 22 , the friction linings end radially on the outside in the same region as the fluid-conveying surfaces on the various lining carriers. 
   It should be emphasized that the details which have been described above with reference to  FIGS. 19-22  are independent of the manner in which the fluid-conveying surfaces which cause the fluid to circulate are formed, i.e. are independent of whether said fluid-conveying surfaces are formed on lining carriers or on end or side surfaces of linings themselves. In this respect, the statements which have been put forward with regard to  FIGS. 19-22  likewise apply to the embodiments according to  FIGS. 6-11 . 
   A further advantageous variant is indicated in FIG.  23 . As already explained previously with regard to  FIGS. 19-21 , it is ensured, by various flows or advance filling, that there is working fluid in the region of the surface-area regions which bear frictionally against one another or can be brought into interaction, in order to remove heat by the flow of fluid or/and circulation of fluid. However, in a state in which the clutch  10  is not engaged, this function of removal of heat is not required. Since working fluid which is still present then has the effect of building up dragging torques, which is disadvantageous, for example, if the clutch according to the invention is effective as part of a double clutch. In this case, a torque is to be transmitted via just one of the clutches in each case. According to the variant illustrated in  FIG. 23 , it is now ensured that the volume region containing the surface-area regions which are acted upon frictionally is filled with working fluid only if a torque is to be transmitted. This can be achieved, for example, by a coupling element  140 , which is formed separately from the housing arrangement  12 , being provided for the friction elements, which are coupled in a rotationally fixed manner to the housing arrangement  12 , said coupling being connected in a rotationally fixed manner to the housing arrangement  140 , for example. This coupling element  140  has a plurality of passage openings  142  through which fluid can flow radially from the inside to radially on the outside. During operation, it is ensured that if the clutch is to be brought into an engaged state, fluid is conducted into the space region  34 , specifically, for example, at a conveying rate of approximately 20 l/min. This fluid will be caused by centrifugal forces to flow radially outward and, owing to the constricting action of the openings  142 , will accumulate more intensively in the volume region surrounded by the coupling element  140 . At this point, it absorbs heat from the components bearing frictionally against one another and then removes the heat from the space region  34  after passing through the openings  142  and after the outlet. If the clutch is to be brought again into a disengaged state, the supply of fluid is stopped, the fluid which is initially still present will pass via the openings  142  and will then be removed. There is then no longer any dragging effect caused by the fluid. A design of this type is also possible, of course, in the case of the variant which is illustrated in  FIG. 9 , in which the friction elements  24   a  which are attached to the output shaft are attached to the coupling element  26   a  which surrounds the various friction elements  24   a ,  22   a  radially on the outside. 
   The manner in which the fluid-conveying surfaces are provided is also again insignificant here, and so this aspect of the present invention may in principle also be used in all of the previously described design variants. 
   A further clutch arrangement according to the invention is illustrated in FIG.  24 . This corresponds to the previously described principles, in particular in respect of causing the fluid to circulate, and can, insofar as the friction elements are concerned, be designed in the manner as described previously with respect to various design variants. 
   It can be seen in the design variant illustrated in  FIG. 24  that the housing section  150   b , which lies opposite the clutch piston  32   b  and extends radially inward, has radially on the inside, an opening which is preferably concentric with the axis of rotation A. An axial formation  152   b  of the clutch piston  32 , which formation extends essentially cylindrically and is formed by deformation, is guided through said opening with a sealing element  154   b  providing a sealing effect. The entire interior of the housing  12   b  which surrounds the space regions  34   b ,  36   b  is therefore sealed off in a fluid-tight manner and filled in advance with fluid. The two space regions  34   b ,  36   b  are directly connected radially on the outside, since the clutch piston  32   b  is, in the same manner as the friction elements  22   b , attached there in a rotationally fixed manner to the housing arrangement  12   b  by a toothing arrangement  156   b  provided on said clutch piston. An actuating mechanism referred to in general by  158   b  is provided for the clutch piston  32   b . Said actuating mechanism 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 accumulator, for example a diaphragm spring, or of another actuator. The mechanism  158   b  acts upon that region  152   b  of the clutch piston  32   b  which projects out of the housing arrangement  12   b , and therefore presses said clutch piston against the various friction elements  22   b ,  24   b  in order to produce the engaged state. Fluid lines serving to produce the engaged state are thus not required here, which substantially simplifies the design especially with regard to conducting the fluid. In order to move the clutch piston away from the friction elements in a defined manner during the transfer into the disengaged state, it could be conceivable to provide either within the housing arrangement  12   b  or outside the same a spring element which prestresses said housing arrangement axially and only has to have a comparatively small spring force. 
   The design variant illustrated in  FIG. 24  combines the principle of a wet clutch, i.e. a clutch cooled by fluid flowing around it, with the actuation of a conventional dry friction clutch. A clutch arrangement of this type can therefore be used, for example, where although a conventional actuation, i.e. actuation of a conventional dry friction clutch, is to be provided, the intended purpose of use means that the load which occurs in particular in slip mode would be too large for a dry friction clutch. It should also be emphasized that, of course, in the embodiment according to  FIG. 24 , all of the measures described previously can be provided in respect of the construction and effect of the friction elements. 
   A development of the clutch arrangement according to the invention is illustrated in FIG.  25 . It can be seen here that the housing arrangement  12  of the clutch arrangement  10  can be coupled via a torsional-vibration damper, referred to in general by 200, to a drive shaft or other driving element for rotation together. For this purpose, the housing arrangement  12  has a region  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 the two axial sides of the region  200  which is extended in a flange-like manner. 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 outward, with the result that the housing arrangement  12  can rotate within a limited angle of rotation range towards the cover elements  204 ,  206  which essentially form the primary side. This primary side can then be attached to the drive shaft via a flexiplate or the like. 
   In the design variant illustrated 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 output shaft  18  (illustrated schematically). In this case, the housing arrangement  12  is attached directly to the drive shaft, for example via a flexiplate. The torsional-vibration damper  200  is again constructed in accordance with a conventional type of construction and, for example, has connected to the coupling element  26  a flange-like central disk element in the manner of the region  202 , which can be seen in  FIG. 25 , and two covering disk elements  204 ,  206  which are situated on both axial sides thereof and may, of course, also be formed integrally with each other. 
   In the embodiment illustrated in  FIG. 27 , the torsional-vibration damper  200  is provided in the interior region of the housing arrangement  12 , i.e. in the space region which is filled with working liquid. A carrier element, which is referred to in general by  210 , carries both the friction elements  22  and the clutch piston  32  in a rotationally fixed manner. 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 , which are formed integrally with the housing arrangement  12 , are provided for interaction with the damper springs  208 . The torsional-vibration damper  200  is also provided here on the drive side, i.e. in the torque transmission path between the drive shaft and the friction elements  22 . In the design variant illustrated in  FIG. 28 , the torsional-vibration damper  200  is again arranged within the housing arrangement  12 , but now on the output side between the coupling element  26  and a further coupling element  212 , which is then coupled in a rotationally fixed manner to the output shaft. 
     FIG. 29  illustrates a clutch arrangement  10  according to the invention in conjunction with a starter-generator arrangement, which is referred to in general by  220 . 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, for example via the torsional-vibration damper  200 , to the housing arrangement  12  for rotation together. The stator arrangement  226 , which has conducting coils, of the starter-generator arrangement  220  lies either radially within or, as in the example illustrated, radially outside the rotor arrangement  24 . The stator arrangement  226  is held in a rotationally fixed manner, for example, on the engine block  222 . 
   In the design variant illustrated 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 emphasized that, in the embodiments described with reference to  FIGS. 25-30 , the inner construction of the clutch arrangements can be designed as previously described with reference to  FIGS. 1-24 , in particular as far as the various friction elements are concerned. In this case too, as indicated by circulation circles, the circulation of fluid which flows around the friction elements is provided. It is self-evident 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 flexiplate 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 couple the output side of the torsional-vibration damper to the housing arrangement of the clutch arrangement according to the invention. 
   It should furthermore be emphasized that the principle of the invention of causing fluid to circulate in the region of friction elements which can be brought frictionally into action with one another may, of course, also be used in double wet clutch arrangements, in which two sets of friction elements can be used to bring two different output shafts into a torque-transmitting connection with a drive shaft by alternate engagement of one of the two wet clutches.