WO2009105388A2

WO2009105388A2 - Multiple clutch system with hydraulic fluid compensation

Info

Publication number: WO2009105388A2
Application number: PCT/US2009/034064
Authority: WO
Inventors: Hans Jürgen HAUCK
Original assignee: Borgwarner Inc.
Priority date: 2008-02-18
Filing date: 2009-02-13
Publication date: 2009-08-27
Also published as: DE102008036852A1; DE102008036852B4; WO2009105388A3

Abstract

The present invention relates to a multiple clutch system (2) having an external clutch (30) as well as an internal clutch (32), which are arranged nested in the radial direction (12, 14), and an actuating piston (70) for the actuation of the external clutch (30). Provided on one side of the actuating piston (70) is a pressure chamber (86), which can be subjected to pressure in such a way that the actuating piston (70) can be displaced in the axial direction (8), whereas a compensation chamber (92) is provided on the other side of the actuating piston (70). An axial force acting on the actuating piston (70) is generated by rotation of the multiple clutch system (2) by means of a radially oriented first hydraulic fluid column inside the pressure chamber (86), whereas an opposing axial force acting on the actuating piston (70) is generated by means of a radially oriented second hydraulic fluid column in the compensation chamber (92). An overflow channel (122) for the partial removal of the oil from the compensation chamber (92) discharges into the compensation chamber (92) in such a way that the length of the second hydraulic fluid column in the radial direction (12, 14) is shortened in such a way that the mutually opposing axiai forces acting on the actuating piston (70) are balanced out. According to the invention, the overflow channel (122) is arranged in such a way that oil discharged via the overflow channel (122) is capable of being supplied particularly rapidly and effectively to the external clutch (30).

Description

MULTIPLE CLUTCH SYSTEM WITH HYDRAULIC FLUiD COMPENSATION

DESCRIPTION

The present invention relates to a multiple clutch system having an external clutch and an internal clutch, which are arranged nested in the radial direction, and an actuating piston for the actuation of the external clutch, a pressure chamber being provided on one side of the actuating piston, which pressure chamber can be subjected to pressure in such a way that the actuating piston is displaced in the axial direction, and a compensation chamber being provided on the other side of the actuating piston, whereby an axial force acting on the actuating piston can be generated by rotation of the multiple clutch system by means of a radially oriented first hydraulic fluid column inside the pressure chamber, and an opposing axial force acting on the actuating piston can be generated by means of a radially oriented second hydraulic fluid column in the compensation chamber, whereby an overflow channel for the partial removal of the oil from the compensation chamber discharges into the compensation chamber in such a way that the length of the second hydraulic fluid column in the radial direction is shortened in such a way that the mutually opposing axial forces acting on the actuating piston are balanced out.

Previously disclosed in the prior art are multiple clutch systems, which are configured as a rule as dual clutch systems and exhibit both an external and an internal clutch, in this case, the external clutch encloses the internal clutch from the outside, so that these are arranged nested in the radial direction. As a rule, the two clutches each consist of a disk pack. Also provided for the purpose of actuating the external disk pack and the external clutch is an actuating piston, which can be displaced in the axial direction. There is thus provided on one side of the actuating piston a pressure chamber, which can be supplied with pressure in such a way that the actuating piston is displaced in the axial direction. On the other hand, a so-called compensation chamber is provided on the other side of the actuating piston. The movement of the actuating piston is thus brought about by varying the pressure inside the pressure chamber. During operation of the multiple clutch system and during its rotation, a radially oriented first hydraulic fluid column occurs inside the pressure chamber, whereas a radially oriented second hydraulic fluid column occurs inside the compensation chamber. In this way, the first hydrauiic fluid column in the pressure chamber causes an axiai force to act on the actuating piston, whereas the second hydraulic fluid column in the compensation chamber causes an opposing axiai force to act on the actuating piston. 5 Since the actuating piston is inserted as a rule into a depression in the disk carrier, the pressure chamber exhibits a smaller radial extension than the compensation chamber. The result of this in the case of conventional multiple clutch systems is that the first hydraulic fluid column is configured in the radial direction so that it is shorter than the second i o hydraulic fluid column inside the compensation chamber. The consequence of this would be that the axial force acting in the opposite direction, which is produced inside the compensation chamber by the second hydrauiic fluid column, is greater, so that the actuating piston would be forced back automaticaily into an end position if no adequate counter pressure was

15 produced inside the pressure chamber. In order to prevent this, the performance of a so-called hydraulic fluid compensation is previously disclosed. For this purpose, so-called overflow channels were developed for the partial removal of the oii from the compensation chamber. Overflow channels of this kind thus discharge into the compensation chamber in

20 such a way that the length of the second hydraulic fluid column is reduced in the radia! direction and the opposing axial forces acting on the actuating piston are compensated. The oil removed via the overflow channel is conveyed directly radiaily outwards, from where it can then be returned to the oil circuit.

25 The previously disclosed multiple clutch systems have proven to be worthwhile in the sense that a simple hydraulic fluid compensation can be achieved without a significant increase in the complexity of the design. Nevertheless, a disadvantage associated with the previously disclosed multiple dutch systems having an externa! and an interna! clutch arranged

30 nested in the radial direction is that the externa! ciutch and the disks of the externa! disk pack has or have a lower service life than the internal clutch and the disks of the interna! disk pack.

On the basis of the previously disclosed prior art, an object of the present invention is thus to propose a multiple ciutch system having an

35 external and an internal clutch, which are arranged nested in the radia! direction, the intention being to provide, on the one hand, a simpier hydraulic fluid compensation for the actuating piston and, on the other hand, an increased service life for the external clutch. This object is achieved through the characterizing features indicated in patent claim 1. Advantageous embodiments of the invention are the subject of the dependent claims.

The multiple clutch system according to the invention exhibits an 5 external clutch and an internal clutch, which are arranged nested in the radial direction. Each of the two clutches can thus be formed, for example, from one disk pack as a plurality of inner and outer disks arranged alternately one behind the other. An actuating piston is also provided for the actuation of the external clutch. Executed on one side of the actuating i o piston in relation to the axial direction is a pressure chamber, which can be supplied intentionally with pressure and/or oil pressure in such a way that the actuating piston is displaced in the axial direction. A compensation chamber is executed on the other side of the actuating piston, on the other hand, if the multiple clutch system is caused to rotate, a radially oriented

15 first hydraulic fluid column occurs inside the pressure chamber, whereas a radially oriented second hydraulic fluid column occurs inside the compensation chamber. Whereas an axial force acting on the actuating piston in one direction is produced by the first hydraulic fluid column inside the pressure chamber, the second hydraulic fluid column inside the

20 compensation chamber produces an axial force acting on the actuating piston in the opposite direction, in order to bring about hydraulic fluid compensation, an overflow channel for the partial removal of the oil from the compensation chamber discharges into the compensation chamber in such a way that the length of the second hydraulic fluid column in the radial

25 direction is shortened in such a way that the opposing axial forces acting on the actuating piston are compensated. According to the invention, it is now proposed to arrange the overflow channel in such a way that the oil that is led away from the compensation chamber and via the overflow channel is supplied to the external clutch.

30 Thanks to the overflow channel, the length of the second hydraulic fluid column is reduced initially in the radial direction in such a way that a particularly easy hydraulic fluid compensation is achieved. However, the oil that is led away from the compensation chamber via the overflow channel is not easily led away to the outside in the radial direction in order to be

35 returned to the cooling-oil circuit. Rather, the overflow channel according to the invention is arranged in such a way that the oil that is led away via the overflow channel is supplied to the external clutch, so that additional cooling medium and lubricating medium are available for the external clutch and the externa! disk pack, by means of which adequate cooling and lubrication of the externa! ciutch and an associated increase in their service life are achieved. in a preferred embodiment of the multiple clutch system according to 5 the invention, the compensation chamber is delimited among other things by the actuating piston and a disk carrier, preferably an external disk carrier of the multiple ciutch system, in which case an oil guide element is attached to the disk carrier in such a way that the overflow channel is executed between the disk carrier and the oil guide element. The oil guide i o element permits a particularly simple embodiment of the disk carrier, especially as the oil guide element only needs to be attached to the completed disk carrier subsequently in order to provide the overflow channel, intricate machining of the disk carrier, in order to provide an overflow channel inside the disk carrier, is superfluous. The preferably

15 subsequently attached oil guide element also has the advantage that this can be selected, if necessary, from a multiplicity of oil guide elements, in order to achieve the desired reduction in the length of the second hydraulic fluid column in the radiai direction in a particular application. in order to be able to produce the overflow channel particularly

20 easily and accurately by the attachment of the oil guide element to the disk carrier, at least one projecting abutment is provided on the side of the oil guide element facing towards the disk carrier for the purpose of supporting the oil guide element on the disk carrier in a further preferred embodiment of the multiple clutch system according to the invention. If, for example, the

25 oil guide element in question is a sheet metal component, then these projecting abutments can be produced by embossing the oil guide element in sheet form in order to achieve a particularly low production cost. By positioning the oil guide element at a distance from the disk carrier, which is achieved by the projecting abutments, the overflow channel is created

30 between the oil guide element, the projecting abutments and the disk carrier. In addition, the projecting abutments can be provided on the oil guide element in such a way that a press fit is produced when the oil guide element is pushed into or onto the disk carrier. Here, too, the projecting abutments provided on the oil guide element are far easier to produce than

35 would be the case for projecting abutments on the disk carrier of thick- walied execution, so that the cost of production is also reduced in this way. According to a further preferred embodiment of the multiple clutch system according to the invention, the overflow channel exhibits a radially internal inlet opening and a radially externa! outlet opening, i.e. the iniet opening is arranged further inwards radialiy than the outlet opening, in 5 order to ensure the reliable and rapid removal of the oil from the compensation chamber via the overflow channel. Since the disk carrier extending in the radial direction as a rule provides axial sealing of the oil chambers inside the multiple clutch system, the radially externa! outlet opening is constituted by at least one groove in the disk carrier, in order to i o permit the intentional supply of the oil that is led away via the overflow channel to the external clutch, it is preferable, therefore, for the groove to be executed in a supporting section of the disk carrier, which serves to provide radial support for the disk carrier on a clutch hub or a clutch pipe. The groove constituting the externa! outlet opening couid thus be formed,

15 for example, in a part section of the supporting section of the disk carrier extending in the radial direction. However, in order to provide particularly rapid removai of the oil as it is led away via the overflow channel in the direction of the externa! clutch, it is particularly preferable for the groove to be executed in a tubular part section of the supporting section, in which

20 case the tubular part section constitutes a boundary of the compensation chamber and/or the overflow channel in the radial direction. The oil that is led away can thus be discharged particularly effectively via the groove associated with the overflow channel radially towards the outside before then being supplied to the external clutch.

25 in a further preferred embodiment of the multiple clutch system according to the invention, a second actuating piston for the actuation of the internal clutch is provided, in which the overflow channel discharges into a further channel between the disk carrier, preferably the supporting section of the disk carrier, and the second actuating piston. Whereas an

30 additional component part in the form of the previously mentioned oil guide element may be necessary in the overflow channel, the further channel is delimited by existing component parts of the multiple clutch system, namely on the one hand the disk carrier and on the other hand the second actuating piston. The construction is simplified in this way, since an

35 additional component part is dispensed with. In this embodiment, therefore, attention should be paid, and this is also preferable, to ensuring that the axially displaceable second actuating piston cannot be displaced into an end position to such an extent that the further channel is closed. This can be brought about, for example, by restricting the freedom of movement of the second actuating piston in the axial direction, in conjunction with which, for example, further projecting abutments could be provided for this purpose between the disk carrier on the one hand and the second 5 actuating piston on the other hand. in order to achieve particularly effective cooling and lubrication of the externa! ciutch, the further channel in a particularly preferred embodiment of the muitipie clutch system according to the invention extends in the radial direction towards the outside to such an extent that the oil that is led i o away via the further channel can be used, if necessary, for the cooling or/and lubrication of a radiaily externally located component part of the internal clutch, in an ideal case, the further channel leads outwards in the radial direction to such an extent that the oil that is led away via the further channel is conveyed past the interna! clutch in such a way that the

15 aforementioned oil provides no cooling or/and lubrication of any kind for the internal clutch. The oil that is led away via the overflow channel and the further channel is prevented in this way, with the internal ciutch open, from producing any return torque there. in the case of multiple clutch systems having clutches nesting in the

20 radial direction, the disk-carrying sections of the disk carriers regularly constitute a flow barrier, so that the externa! clutch in particular can only be provided with an adequate quantity of cooling oil with difficulty. For this reason, in an advantageous embodiment of the muitipie ciutch system according to the invention, the further channel in the radial direction

25 towards the outside leads to an internal disk-carrying section of the disk carrier for the internal clutch, oil passageways being provided to permit the passage of the oil that is led away via the overflow channel and the further channel in the internal disk-carrying section, it is particularly preferable in this case if the oil passageways in the radial direction towards the inside

30 are arranged inside the external clutch, so that a particularly direct suppiy of the oil that is led away to the externa! clutch is possible. In this and in the previously described embodiment, the further channel should also be configured in such a way that this extends exclusively or predominantly in the radia! direction, but without this also being inclined in the axial direction.

35 it is also preferable if the outlet opening of the further channel in the radial direction is in aiignment with the oil passageways. In order to achieve a direct supply of the oil that is ied away via the overflow channei and the further channel to the external clutch, the oil passageways in the internal disk-carrying section in a particularly advantageous embodiment of the multiple clutch system according to the 5 invention are arranged in the radial direction towards the outside at least partially in alignment with oil passageways in a disk-carrying section of an internal disk carrier of the external clutch. The oil passageways in the radial direction should thus overlap at least partially, in order for them to be able to convey the oil that has been led away directly onwards to the external i o clutch. The oil passageways in the disk-carrying section of the internal disk carrier of the external clutch should be arranged radially inside the external clutch in the disk-carrying section of the internal disk carrier, in order to permit a direct supply. in a further advantageous embodiment of the multiple clutch system

15 according to the invention, a spring device, preferably a disk spring, for pre- tensioning of the actuating piston is arranged in an initial position between the actuating piston and the disk carrier. The spring device can thus be utilized for returning the actuating piston to the initial position relative to the disk carrier. On the basis of the hydraulic fiuid compensation acting through

20 the overflow channel, however, the spring device only has to apply a small force in order to force the actuating piston back into the initial position, so that a particularly light and space-saving spring device can be selected. in a further preferred embodiment of the multiple clutch system according to the invention, the aforementioned spring device, in this case

25 preferably a disk spring, is capable of being supported or is supported on the disk carrier with the interposition of the oil guide element. Two important advantages are associated with this. The spring device, which as a rule consists of a harder material than the disk carrier, is prevented on the one hand from causing wear in the support area. It is thus possible in

30 particular to prevent the support fingers of a disk spring from digging into the material of the disk carrier, which can lead to the formation of abrasion particles in the oil and finally to a reduction in the spring force. By supporting the spring device on the oil guide element, on the other hand, the oil guide element can be retained securely in its position on the disk

35 carrier. When assembling the oil guide element on the disk carrier, this also leads to the oil guide element being forced into its fastening position from the outset by the spring device. According to a further advantageous embodiment of the multiple clutch system according to the invention, the oil guide element is capable of assembly by being pushed together, or is assembled by being pushed together, with the disk carrier, preferably in the axia! direction, and 5 particularly preferably it is capable of assembly by being pressed together, or is pressed together, so that simple assembly of the oil guide element on the disk carrier is possible. As already mentioned above, the press fit in this case could be produced by the projecting abutments on the oil guide element. i o According to a further advantageous embodiment of the multiple clutch system according to the invention, the oil guide element is capable of being introduced or is introduced into a depression in the disk carrier. Such a depression, which can be produced by repositioning the supporting section of the disk carrier rearwards in an internally located area in the axial

15 direction, for example, thereby creates a space, in which the compensation chamber can be executed and into which the oil guide element can be introduced particularly easily. The oil guide element in this case is preferably configured as a bowl-shaped annular component, that is to say the oil guide element is of bowl-shaped configuration, although it exhibits a

20 central opening in its base, through which a clutch hub or similar can extend. An annular inlet opening for the overflow channel can aiso be created in this way. in a further preferred embodiment of the multiple clutch system according to the invention, the oil guide element exhibits an external collar,

25 which is capable of being supported or is supported in the axial direction on the disk carrier. In this case, the external collar is preferably supported outside the depression on the disk carrier. The externa! collar can also be supported directly or indirectly on the disk carrier and thus serves, among other things, to establish the attachment position for the oil guide elements

30 on the disk carrier during assembly.

According to a further preferred embodiment of the multiple clutch system according to the invention, the external collar of the oil guide element serves not only as an abutment or, as described below, as a seal, but rather the external collar is configured in such a way that the spring

35 device is capable, with the interposition of the external collar, of being supported or is supported on the disk carrier. As already mentioned above, it is possible by this means to ensure that the oil guide element is already retained in its attachment position by the spring device via the external collar. In addition, the external collar prevents damage to the disk carrier in the support area of the spring device. in order to achieve a particularly specific and loss-free supply of the oil that is led away via the overflow channei to the external clutch, a seai for 5 sealing the overflow channei in relation to a space other than the compensation chamber is provided on the oil guide element in a further preferred embodiment of the multiple clutch system according to the invention. The seal is thus intended in particular to provide sealing of the overflow channel in relation to a further space, which is formed between the i o actuating piston and the disk carrier, but is arranged further towards the outside in the radial direction than the compensation chamber, especially as the greatest oil loss takes place as a rule via this further space, but without the possibility of making the discharged oil available to one of the two dutches for further cooling, in the embodiment described here, it is

15 particularly preferable for the sea! to be arranged on the external collar of the oil guide element for the purpose of sealing the overflow channel. Thus, the seal could preferably be configured and arranged in such a way that the overflow channei is sealed by the compression of the externa! collar of the oil guide element against the disk carrier.

20 in a further preferred embodiment of the multiple clutch system according to the invention, assembly openings are provided in the actuating piston to permit the passage of an assembly tool, for example the die of a press tool, which in the axial direction are arranged at least partially in alignment with the external collar of the oil guide element. !n this way, the

25 oil guide element can initially be assembled or pushed together with the actuating piston to form a module, and this module can then be incorporated into the multiple clutch system. During the incorporation process, the dies of a press tool or similar can be passed through the assembly openings in the actuating piston in order to press against the

30 externa! collar of the oii guide element, in conjunction with which the oil guide element can be pushed or forced by this pressure onto or into the disk carrier. The assembly is simplified considerably in this way.

According to a further advantageous embodiment of the multiple clutch system according to the invention, the actuating piston can be

35 introduced into the oii guide eiement in the axial direction. The actuating piston, for example, can thus exhibit a bulbous section projecting in the axial direction, which is introduced into the aforementioned depression and into the oil guide element, which, for example, is configured as a bowi- shaped annular component, in order to seal the annular gap between the actuating piston and the oil guide element, a sealing lip is provided on the actuating piston. A sealing lip of this kind should be of circumferential configuration and should preferably extend in the radial and axial direction 5 in order to achieve the highest possible sealing effect. At least one projecting abutment is provided on the side of the oil guide element facing towards the actuating piston. This projecting abutment can be configured similarly to the aforementioned projecting abutments, for example. However, the projecting abutment is provided on the oil guide element in i o such a way that the actuating piston in an end position is supported on the projecting abutment in the axial direction, in which case the sealing Sip is positioned at a distance from the oil guide element in the end position of the actuating piston in the axial direction. Supporting of the actuating piston on the projecting abutment can take place indirectly or directly in this case.

15 In any case, the projecting abutment prevents the sealing lip from being pressed against the oil guide element in the axial direction and thus from being deformed in the axial direction when the actuating piston is in the end position. The durability of the sealing lip, and thus its tightness, are significantly increased in this way. in addition, the one or more projecting

20 abutments are particularly easy to manufacture, as previously mentioned with reference to another embodiment. in a further advantageous embodiment of the multiple clutch system according to the invention, the sealing lip is arranged or configured on a sealing element and/or as part of a sealing element, in which case the

25 sealing element can be combined with the actuating piston. It is preferable in this case for the sealing element to be capable of being pushed together or to be pushed together with the actuating piston, it is particularly preferable for the sealing element to be capable of being pressed together or to be pressed together with the actuating piston, especially as the

30 connection between the sealing element and the actuating piston is then particularly easy to produce. in a further particularly preferred embodiment of the multiple clutch system according to the invention, the actuating piston, the sealing element and the oil guide element can first be assembled to produce a module, in

35 which case this module can then be incorporated into the multiple clutch system. This embodiment is advantageous in the sense that the initially separate oil guide element, by causing the same to rotate about its axis of rotation, can be pushed onto the sealing element on the actuating piston, in conjunction with which the rotation prevents the sealing lip from being folded or bent on the sealing element in the direction of attachment, as a result of which the sealing effect would be lost. Such a relative rotational movement between the actuating piston on the one hand and the oii guide 5 element on the other hand is not possible in the prior art, since the actuating piston together with the sealing element in this case is not introduced into the oil guide element until after the oil guide elements have been positioned on the disk carrier, in conjunction with which the rotation is prevented by actuating fingers which extend through windows in the disk i o carrier. Thanks to the ability of the actuating piston, the sealing element and the oil guide element to be composed into a common module, a particularly simple assembly of this module and a simple attachment of the same in the multiple clutch system is possible, including when the actuating piston exhibits the aforementioned actuating fingers, which extend through

15 windows in the disk carrier. The module consisting of the actuating piston, the sealing element and the oil guide element thus only requires to be pushed onto the disk carrier in the axiai direction without the need for any rotation, which would be prevented by the actuating fingers. As already explained, the assembly openings in the actuating piston can be of benefit

20 in this case in order to permit the use of a corresponding press tool, which is capable of being pressed against the external collar of the oil guide element. Mention should also be made in this context of the fact that the aforementioned spring device can already be integrated into the module, provided that the spring device is supported on the one hand on the

25 actuating piston and on the other hand on the oil guide element.

As already explained above, only a limited possibility exists, with the actuating piston in its installed state, to rotate the actuating piston relative to the disk carrier if the actuating piston exhibits actuating fingers for the actuation of the external clutch, which fingers extend through windows in

30 the disk carrier. Thanks to the separate oil guide element, which can be arranged on the sealing element and/or the sealing lip of the actuating piston even before its attachment to the disk carrier, such a rotating movement is no longer necessary, however. Accordingly, in a further preferred embodiment of the multiple clutch system according to the

35 invention, actuating fingers for the actuation of the external clutch are provided on the actuating piston, which fingers extend through windows in the disk carrier, preferably in the supporting section of the disk carrier to the external clutch. - 1 9 -

The invention is explained below in more detail on the basis of an illustrative embodiment with reference to the accompanying drawings. In the drawings:

Fig. 1 depicts a partial side view of an embodiment of the multiple 5 clutch system according to the invention in a sectioned representation, and Fig. 2 depicts the detail A in Fig. 1 as an enlarged representation. Fig. 1 depicts an embodiment of the multiple clutch system 2 according to the invention, in which the multiple clutch system 2 in this example is configured as a dual clutch system and a disk clutch device, in i o addition, the multiple clutch system 2 together with a torsional vibration damper 4 forms a clutch/damper unit. The multiple clutch system 2 and the torsional vibration damper 4 exhibit a common axis of rotation 6, which extends in the mutually opposing axial directions 8, 10. in addition, the outwardly oriented radial direction is indicated by the arrow 12, whereas the

15 inwardly oriented radial direction is indicated by the arrow 14.

The clutch/damper unit initially exhibits an input hub 16, which is capable of being attached rigidly to an engine output shaft 18 that is only suggested here. The input hub 16 is rigidly attached to a primary element 20 of the torsional vibration damper 4. The primary element 20 is attached

20 to a secondary element 24 of the torsional vibration damper 4 in a torsionally elastic manner at its external periphery via spring devices 22 extending in the circumferential direction.

The multiple clutch system 2 exhibits a disk carrier 26, which is drivingly connected to the secondary element 24 via a driver device 28,

25 which is configured as a driving plate. The disk carrier 26 is configured as an external disk carrier for an external clutch 30 and an internal clutch 32, in conjunction with which it is also possible to speak of an external disk pack in the case of the external clutch 30, and an internal disk pack in the case of the internal clutch 32. The external clutch 30 encloses the internal

30 clutch 32 from the outside, that is to say the external and internal clutch 30, 32 are arranged nested in the radial direction 12, 14. The disk carrier 26 exhibits a tubular external disk-carrying section 34 intended to receive the external disks of the external clutch 30 and a tubular internal disk-carrying section 36 intended to receive the external disks of the internal clutch 32.

35 The two disk-carrying sections 34, 36 are supported by means of a common supporting section 38 in the radial direction 14 towards the inside on a tubular clutch hub 40. Also assigned to the externa! clutch 30 is an external internal disk carrier 42, which exhibits a disk-carrying section 44 intended to receive the internal disks of the external clutch 30, in conjunction with which the disk- carrying section 44 is connected to an output hub 48 via a supporting 5 section 46, which is capable of being rigidly connected to a first gearbox input shaft 50. in a corresponding manner, there is assigned to the interna! clutch 32 an internal disk carrier 52, which exhibits a tubular disk-carrying section 54 intended to receive the interna! disks of the internal clutch 32, in conjunction with which the disk-carrying section 54 is supported by means i o of a supporting section 56 on a further output hub 58, which can be connected in turn to a second gearbox input shaft 60 configured as a hollow shaft, as illustrated in Fig. 1.

The supporting section 38 of the disk carrier 26 comprises an externa! part section 62, which extends in the radial direction 12, 14, a

15 tubular part section 64, which extends in the axia! direction 8 starting from the external part section 62, and an internal part section 66, in conjunction with which the latter extends in the radia! direction 14 inwards as far as the clutch hub 40, starting from the end of the tubular part section 64 facing in the axial direction 8. it could also be said that the interna! part section 66 is

20 repositioned rearwards in the axial direction 8 in relation to the externa! part section 62 to form a depression 68 in the supporting section 26, in conjunction with which the depression 68 is open in the axial direction 10.

The multiple clutch system 2 also exhibits an actuating piston 70, which is so arranged as to be capable of being displaced on the clutch hub

25 40 in the axial direction 10 behind the supporting section 38 of the disk carrier 26 in the axial direction 8, 10, in conjunction with which the actuating piston 70 serves for the actuation and the compression of the externa! clutch 30. The actuating piston 70 in turn comprises an external part section 72, which extends in the radial direction 12, 14, and attached

30 thereto in the radial direction 14 a tubular part section 74, which extends in the axiai direction 8, and an interna! part section 76, in conjunction with which the internal part section 76 extends in the radial direction 14 towards the inside as far as the clutch hub 40, starting from the end of the tubular part section 74 facing in the axial direction 8. By analogy with the

35 supporting section 38 of the disk carrier 26, it is also possible here to mention the fact that the internal part section 76 is arranged offset in the axial direction 8 in relation to the externa! part section 72. In order to be able to compress the disk pack of the external clutch 30 with the help of the actuating piston 70, the externa! part section 72 exhibits actuating fingers 78 at its external end projecting in the axial direction 8, which fingers extend through windows 80 in the external part section 62 of the supporting section 38 of the disk carrier 26.

5 An actuating piston 82 is also provided for the internal clutch 32. The actuating piston 82 is supported in the radial direction 14 from the outside on the tubular part section 64 of the supporting section 38 of the disk carrier 26. in addition, the actuating piston 82, which is also capable of displacement in the axial direction 8, 10, exhibits an externa! part section i o 84, which, irrespective of the displacement position of the actuating piston 82 in the axial direction 8, is located at a distance from the external part section 62 of the supporting section 38 of the disk carrier 26, in conjunction with which the external part section 84 of the actuating piston 82 extends in the radial direction 12.

15 Further aspects of the design of the multiple clutch system 2 are explained below with reference to Fig. 2, which depicts the detail A in Fig. 1 as an enlarged representation.

A pressure chamber 86 is executed on the side of the actuating piston 70 facing in the axial direction 10. The pressure chamber 86 can be

20 subjected to pressure via a bore 88 in the hub part 40, by introducing hydraulic oil via the bore 88. This causes an axial displacement of the actuating piston 70 in the axial direction 8 and thus a compression of the externa! clutch 30 via the actuating fingers 78 of the actuating piston 70. The pressure chamber 86 is delimited in the axial direction 8 by the internal

25 part section 76, in the axial direction 10 by a partition wall 90 on the clutch hub 40, and in the radial direction 12 by the tubular part section 74 of the actuating piston 70. The delimitation in the radial direction 14 towards the inside is provided by the clutch hub 40, in so far as the aforementioned bore 88 is not present. The pressure chamber 86 is sealed in this case by

30 means of seals (no reference designations) on the partition wall 90, the actuating piston 70 or/and the clutch hub 40.

A compensation chamber 92 is provided on the other side of the actuating piston 70 or, to put it more accurately, in the axiai direction 8 behind the actuating piston 70. The compensation chamber 92 in this case

35 essentially comprises the space enclosed by the depression 68 in the supporting section 38 of the disk carrier 26. The compensation chamber 92 is essentially delimited in the axial direction 8 by the internal part section 66 of the supporting section 38 of the disk carrier 26, in the axiai direction 10 by the internal part section 76 of the actuating piston 70 and in the radial direction 12 by the tubular part section 64 of the supporting section 38 of the disk carrier 26. The compensation chamber 92 is delimited towards the inside by the clutch hub 40, and here too one or a plurality of bores 94 5 is/are provided in the clutch hub 40 for the introduction of oil into the compensation chamber 92 in the radial direction 12.

An oii guide element 96 is also positioned on the supporting section 38 of the disk carrier 26. The oil guide element 96 is preferably configured as a sheet metal component and is comprised essentially of a bowl-shaped i o annular component. The oil guide element 96 in this case is inserted or pressed into the depression 68 in the supporting section 38 of the disk carrier 26. The oil guide element 96 is comprised essentiaiiy of an interna! part section 98, which is separated by the clutch hub 40 in the radial direction 12 and extends outwards in the radiai direction 12, of a tubular

15 part section 100, which adjoins the internal part section 98 in the radial direction 12 and extends in the axiai direction 10, and of an external collar 102 adjoining the tubular part section 100 in the axiai direction 10, which in turn extends outwards in the radial direction 12.

Provided on the side of the internal part section 98 of the oil guide

20 element 96 facing towards the internal part section 66 are a plurality of projecting abutments 104, which make possible a support for the internal part section 98 of the oil guide element 96 on the internal part section 66 of the supporting section 38 in the axiai direction 8. Executed in addition on the side of the internal part section 98 of the oil guide element 96 facing

25 towards the actuating piston 70 are a plurality of projecting abutments 106, which as a result extend in the axiai direction 10, starting from the internal part section 98. The importance of the projecting abutments 106 is discussed below in greater detail. Executed furthermore on the side of the tubular part section 100 of the oil guide element 96 facing towards the

30 tubular part section 64 of the supporting section 38 are additional projecting abutments 108, which consequently project in the radial direction 12 and provide a support for the oii guide element 96 in the radial direction 12 on the tubular part section 64 of the supporting section 38. The externa! collar 102 of the oil guide element 96, with the oil guide element 96 in its installed

35 state, is supported indirectly or directly in the axiai direction 8 on the externa! part section 62 of the supporting section 38 of the disk carrier 26. The indirect support of the external collar 102 on the external part section 62 is provided here, preferably via a seal 110 on the external collar 102 of the oil guide element 96.

As can also be appreciated from Fig. 2, a sealing element 1 12 is arranged in addition on the actuating piston 70. The sealing element 112 comprises a carrying component 114 having an L-shaped cross section, 5 which is pushed or pressed in the axial direction 10 onto the actuating piston 70 and/or onto the bulging part in the form of the internal part section 76 and the tubular part section 74. Also provided on the carrying component 114 is a sealing lip 116, which, for example, can be molded onto the carrying component by vulcanization. Since the actuating piston i o 70 can be introduced in the axiai direction 8 into the depression 68 and/or the oil guide element 96, the sealing tip 116 provides sealing of the resulting annular gap between the actuating piston 70 and the oi! guide element 96. The sealing lip 116 extends in the radial direction 12 outwards in order to adjoin the tubular part section 100 of the oil guide element 96, in

15 addition to which it is inclined in the axial direction 8, so that the sealing iip 1 16 projects in the axial direction 8 above the carrying component 1 14 of the sealing element 112. Thanks to the circumferential sealing lip 116, the compensation chamber 92 is thus sealed in relation to a further space 118, which is executed between the actuating piston 70 and the supporting

20 section 38 of the disk carrier 26, but is arranged further to the outside in the radial direction 12 than the compensation chamber 92.

Also arranged in the aforementioned further space 1 18 is a spring device 120 in the form of a disk spring, which is caused to move by the pre- tensioning of the actuating piston 70 in the axial direction 10 into an initial

25 position relative to the disk carrier 26. The spring device 120 in this case is supported on the one hand on the actuating piston 70, and on the other hand indirectly on the supporting section 38, or, to put it more accurately, the external part section 62 of the supporting section 38 of the disk carrier 26. The expression indirectly is used here to denote that the spring device

30 120, with the interposition of the externa! collar 102 of the oil guide element 96, is supported on the disk carrier 26. in this way, the oil guide element 96 can be held particularly securely in its attachment position illustrated in Fig. 2, while the seal 110 seals particularly securely against the external collar 102 of oil guide element 96. Mention should be made at this point,

35 however, of the fact that the spring device 120 can also be supported directly on the supporting section 38 of the disk carrier 26, in conjunction with which the external collar 102 could exhibit a short length 12 in the radial direction for this purpose. Thanks to the projecting abutments 104 and 108 on the oil guide element 96, the oil guide element 96 in the installed state is separated from the supporting section 38 of the disk carrier 26 to such an extent that an overflow channel 122 is executed between the oil guide element 96 on the 5 one hand and the supporting section 38 of the disk carrier 26 on the other hand. The overflow channel 122 in this case consists of a first part section 124, which is executed between the internal part section 98 of the oil guide element 96 and the internal part section 66 of the supporting section 38 and extends towards the outside in the radial direction 12, starting from a i o radially internal inlet opening 126, and a second part section 128, which in the radial direction 12 is executed between the tubular part section 100 of the oil guide element 96 and the tubular part section 64 of the supporting section 38 and extends in the axial direction 10. The seal 1 10 on the external collar 102 of the oil guide element 96 in this case produces sealing

15 of the overflow channel 122 in relation to the further space 118. The second part section 128 of the overflow channel 122 leads to an externally situated outlet opening 130 of the overflow channel 122, in conjunction with which the outlet opening 130 is formed by at least one groove 132 in the tubular part section 64 of the supporting section 38 of the disk carrier 26.

20 The overflow channel 122 discharges via its inlet opening 126 into the compensation chamber 92 in such a way that the effective hydraulic fluid column inside the compensation chamber 92 is shortened in the radial direction 12 in such a way that the axial force resulting from the hydraulic fluid column acting on the actuating piston 70 in the axial direction 10

25 corresponds to some extent to the axial force acting in the axial direction 8, which is produced by the hydraulic fluid column in the pressure chamber 86. The mutually opposing axiai forces thus cancel one another out, so that a simple hydraulic fluid compensation is effected and the spring device 120 needs to apply only a low spring force and/or return force in order to cause

30 the actuating piston 70 to return to its initial position. it will be appreciated from the preceding description that the oil inside the compensation chamber 92 is discharged partially from the compensation chamber 92 at the level of the inlet opening 126, in order to reduce the effective hydraulic fluid column inside the compensation

35 chamber 92 and, by so doing, to effect a hydraulic fluid compensation. This discharged oil now flows via the first part section 124 of the overflow channel 122 in the radial direction 12 outwards, in order to make its way in the axial direction 10 through the second part section 128 of the overflow - 13 - channel 122 as far as the outlet opening 130 in the form of the groove 132. The discharged oii now makes its way through the outlet opening 130 from one side of the supporting section 38 to the other side of the supporting section 38, where it passes into a further channel 134.

5 The further channel 134 extends in a linear fashion in the radial direction 12, in conjunction with which the further channel 134 is delimited in the axial direction 10 by the externa! part section 62 of the supporting section 38 of the disk carrier 26, and in the axiai direction 8 by the external part section 84 of the second actuating piston 82. As can be appreciated i o from Fig. 1 , the externa! part section 84 of the second actuating piston 82 extends outwards in the radial direction 12 to such an extent that the discharged oil, which exits from the further channel 134 in the radial direction 12, can be used if necessary for the cooling or/and lubrication of a radially external part of the internal clutch 32. The oii exiting from the

15 further channel 134 is thus used only partially, and preferably not at ail, for cooling of the internal clutch 32.

The further channel 134 carries the discharged oii in the radial direction 12 outwards to the internal disk-carrying section 36 of the disk carrier 26. in order generally to prevent the discharged oil from being

20 supplied to the internal clutch 32, oil passageways 136 are provided in the internal disk-carrying section 36, via which the discharged oii can pass in the radial direction 12 in order to find its way to the disk-carrying section 44 of the external interna! disk carrier 42. Oil passageways 138 are also provided in the disk-carrying section 44 of the externa! internal disk carrier

25 42. In this case, the oil passageways 136 are at least partially in alignment in the radia! direction 12 outwards with the oii passageways 138 in the disk- carrying section 44 of the external interna! disk carrier 42. it is apparent from the above description that the overflow channei 122 is arranged in such a way that the oil discharged via the overflow

30 channel 122 can be suppiied to the external clutch 30, in order to ensure particularly effective cooling of the particularly highly thermally ioaded externa! clutch 30. The oil discharged from the compensation chamber 92 via the overflow channei 122 is thus not spent without being utilized, but serves for the cooling and lubrication of the external clutch 30. Thanks to

35 the described embodiment of the further channels 134 and the oii passageways 136 and 138, it is also possible to ensure that the oil discharged from the compensation chamber 92 can be supplied particularly rapidly to the externa! ciutch 30, without being heated too strongly by other component parts of the multiple clutch system 2, for example the internal clutch 32.

The embodiment of the multiple clutch system 2 described here offers further advantages in addition to the advantageous cooling of the 5 externa! clutch 30. If, for example, the actuating piston 70 were to be displaced in the axial direction 8 as far as an end position, the actuating piston 70 or its internal part section 76, where appropriate with the interposition of the carrying component 114 of the sealing element 112, will come up against the abutment 106 of the internal part section 98 of the oil i o guide element 96 projecting in the axial direction 10. In this case, the height of the projecting abutment 106 in the axial direction 10 is selected in such a way that the sealing iip 116 of the sealing element 112 bears against tubular part section 100 of the oil guide element 96, and, to be precise, continuing in the radial direction 12, although the sealing lip remains

15 separated in the axial direction 8 from the internal part section 98 of the oil guide element 96. in the described end position, the sealing lip 116 is thus not deformed in the axial direction 10 by the internal part section 98 of the oil guide element 96, which could lead to the folding down of the sealing lip 116 and consequently to a loss of the sealing effect. This problem is

20 solved, both in the assembly of the multiple clutch system 2 and in the subsequent operation of the multiple clutch system 2, by the projecting abutments 106. The projecting abutments 106 should also project to a sufficient extent in the axial direction 10 to ensure that the sealing lip 116 in the end position does not extend as far as the height of the projecting

25 abutment 108, provided that the projecting abutments 108 are produced by the partial deformation of the tubular part section 100, in order to ensure the tightness of the compensation chamber 92 in this area. This is not required, however, if the projecting abutments 108 are not produced by deformation of the tubular part section 100, but, for example, have been

30 applied subsequently from the outside, since the supporting surface facing towards the sealing lip 116 then exhibits no interruption or depression of any kind. it is also apparent from the above description that the multiple clutch system 2 can be installed particularly easily. The actuating piston 70, the

35 sealing element 1 12 and the oil guide element 96 can thus be combined initially into a common module, in conjunction with which this coherent module is only incorporated into the multiple clutch system 2 subsequently. The following procedure is adopted in this case: the sealing element 112 is first pushed or pressed onto the actuating piston 70 in the axial direction 10. Furthermore, depending on the embodiment of the selected oil guide element 96, the spring device 120 can already be brought into a position on the module, in which the spring device 120 is supported on the side of the 5 actuating piston 70 facing in the axial direction 8.

The oil guide element 96 is then pushed onto the sealing element 112 in the axial direction 10 in such a way that the sealing element 112 and/or the tubular part section 74 of the actuating piston 70 reaches the tubular part section 100 of the oil guide element 96. At the start of this o pushing-on process, the oil guide element 96 must be rotated relative to the sealing element 1 12 about the axis of rotation 6, in order to prevent the sealing lip 1 16 of the sealing element 1 12 that is inclined in the axiai direction 8 from being folded down or folded down in the axial direction 10, which would inevitably lead to the loss of the sealing effect of the sealing lip5 116. The particular advantage of the modular configuration is evident here. If, in fact, the oil guide element 96 were already to be securely attached to the supporting section 38 of the disk carrier 26, before subsequently introducing the sealing element 1 12 together with the actuating piston 70, the actuating fingers 78 of the actuating piston 70 projecting through the 0 windows 80 in the supporting section 38 would lead to a restricted relative ability of the sealing element 1 12 to rotate in relation to the oil guide element 96. It would then not be possible to ensure that the sealing lip 116 at the time of assembly retains its sealing effect for the compensation chamber 92. 5 As already indicated, the module consisting of the actuating piston

70, the sealing element 112, the oil guide element 96 and the spring device 120 is only connected to the supporting section 38 of the disk carrier 26 subsequently in the axial direction 8. For this purpose, assembly openings 140 are provided in the external part section 72 of the actuating piston 70,0 and these are arranged in the axial direction 8 at least partially in alignment with the external collar 102 of the oil guide element 96. As can be appreciated from Fig. 2, a die 142 of an assembly too! in the form of a press tool can thus be passed in the axial direction 8 through the assembly openings 140, in order to press in the axial direction 8 against the external5 collar 102 and to cause the oil guide element 96 to be pressed into the depression 68 inside the supporting section 38 of the disk carrier 26. The process of pressing in the oil guide element 96 could also be effected by the actuating piston 70 acting on the oil guide element 96 in the axial direction 8 under compression of the spring device 120, although under certain circumstances this can lead to excessively strong loading of the spring device 120, of the interjacent sealing element 112 or of the internal part section 98 of the oil guide element 96, so that the aforementioned procedure is preferable.

List of reference designations

2 multiple clutch system

4 torsional vibration damper 6 axis of rotation

8 axial direction

10 axiai direction

12 radial direction

14 radial direction 16 input hub

18 engine output shaft

20 primary element

22 spring device

24 secondary element 26 disk carrier

28 driver device

30 external clutch

32 internal clutch

34 external disk-carrying section 36 internal disk-carrying section

38 supporting section

40 clutch hub

42 outer internal disk carrier

44 disk carrier section 46 supporting section

48 output hub

50 gearbox input shaft

52 inner internal disk carrier

54 disk carrier section 56 supporting section

58 output hub

60 gearbox input shaft

62 external part section

64 tubular part section 66 interna! part section

68 depression

70 actuating piston

72 external part section 74 tubular part section

76 internal part section

78 actuating finger

80 window

82 actuating piston

84 external part section

86 pressure chamber

88 bore

90 partition wali

92 balance chamber

94 bore

96 oil guide element

98 internal part section

100 tubular part section

102 external collar

104 projecting abutments

106 projecting abutments

108 projecting abutments

1 10 seal

112 sealing element

114 carrying component

116 sealing iip

118 further space

120 spring device

122 overflow channel

124 first part section

126 inlet opening

128 second part section

130 outlet opening

132 groove

134 further channel

136 oil passageways

138 oil passageways

140 assembly openings

142 die

Claims

1. A multiple clutch system (2) having an external clutch (30) and an internal clutch (32), which are arranged nested in the radial 5 direction (12, 14), and an actuating piston (70) for the actuation of the external clutch (30), a pressure chamber (86) being provided on one side of the actuating piston (70), which pressure chamber is subjected to pressure in such a way that the actuating piston (70) is capable of displacement in the axiai direction (8), and a compensation chamber (92) being provided on o the other side of the actuating piston (70), whereby an axial force acting on the actuating piston (70) can be generated by rotation of the multiple clutch system (2) by means of a radially oriented first hydraulic fluid column inside the pressure chamber (86) and an opposing axial force acting on the actuating piston (70) can be generated by means of a radially oriented5 second hydraulic fluid column in the compensation chamber (92), whereby an overflow channel (122) for the partial removal of the oil from the compensation chamber (92) discharges into the compensation chamber (92) in such a way that the length of the second hydraulic fluid column in the radial direction (12, 14) is shortened in such a way that the mutually 0 opposing axiai forces acting on the actuating piston (70) are balanced out, wherein the overflow channel (122) is arranged in such a way that the oil discharged via the overflow channel (122) is capable of being supplied to the external clutch (30). 5

2. The multiple clutch system (2) as claimed in claim 1 , wherein the compensation chamber (92) is delimited by the actuating piston (70) and a disk carrier (26), preferably an externa! disk carrier, and particularly preferably an external disk carrier of the external clutch (30), of the multiple clutch system (2), an oil guide element (96) being attached to the disk0 carrier (26) in such a way that the overflow channel (122) is executed between the disk carrier (26) and the oil guide element (96), preferably projecting abutments (104, 108) being provided on the side of the oil guide element (96) facing towards the disk carrier (26) for support on the disk carrier (26). 5

3. The multiple clutch system (2) as claimed in one of claims 1 or 2, wherein the overflow channel (122) exhibits a radially internal iniet opening (126) and a radially external outlet opening (130), the radially externa! outlet opening (130) being formed by at ieast one groove (132) in

5 the disk carrier (26), preferably by at least one groove (132) in a supporting section (38) of the disk carrier (26) for the radial supporting of the same, and particularly preferably by at ieast one groove (132) in a tubular part section (64) of the supporting section (38), the tubular part section (64) constituting a boundary of the compensation chamber (92) in the radial i o direction (12).

4. The multiple clutch system (2) as claimed in one of the preceding claims, wherein a second actuating piston (82) is provided for the actuation of the internal clutch (32), the overflow channel (122)

15 discharging into a further channel (134) between the disk carrier (26), preferably the supporting section (38) of the disk carrier (26), and the second actuating piston (82), the further channel (134) particularly preferably extending in the radial direction (12) outwards to such an extent that the discharged oil can be used, if necessary, for the cooling or/and

2 o lubrication of a radially external part of the interna! clutch (32).

5. The multiple clutch system (2) as claimed in claim 4, wherein the further channel (134) leads outwards in the radial direction (12) to an internal disk-carrying section (36) of the disk carrier (26) for the internal

25 clutch (32), oil passageways (136) being provided in the internal disk- carrying section (36) to permit the passage of the oil discharged via the overflow channel (122) and the further channel (134).

6. The multiple clutch system (2) as claimed in claim 5, wherein 30 the oil passageways (136) are arranged in the interna! disk-carrying section

(36) in the radial direction (12) outwards, at ieast partially in alignment with oil passageways (138) in a disk-carrying section (44) of an interna! disk carrier (42) of the external clutch (30).

35

7. The multiple clutch system (2) as claimed in one of the preceding claims, wherein a spring device (120), preferably a disk spring, for pre-tensioning of the actuating piston (70) is arranged in an initial position between the actuating piston (70) and the disk carrier (26), the

5 spring device (120) preferably being capable of being supported or being supported on the disk carrier (26) with the interposition of the oil guide element (96).

8. The multiple clutch system (2) as claimed in one of claims 2 i o to 7, wherein the oil guide element (96) with the disk carrier (26), preferably in the axial direction (8, 10), is capable of being pushed together or is pushed together, and particularly preferably is capable of being pressed together or is pressed together.

15 9. The multiple clutch system (2) as claimed in one of claims 2 to 8, wherein the oil guide element (96), which is configured preferably as a bowl-shaped annular component, is capable of being introduced or is introduced into a depression (68) in the disk carrier (26), the oil guide element (96) preferably exhibiting an external collar (102), which is capable

20 of being supported or is supported in the axiai direction (8) on the disk carrier (26), and the spring device (120) is particularly preferably capable of being supported or is supported on the disk carrier (26) with the interposition of the external coliars (102).

25 10. The multiple clutch system (2) as claimed in one of claims 2 to 9, wherein a seal (110) for sealing of the overflow channel (122) in relation to a space (118) other than the compensation chamber (92) is provided on the oil guide element (96), in particular in relation to a further space (118), which is formed between the actuating piston (70) and the

30 disk carrier (26), but is arranged further to the outside in the radial direction (12) than the compensation chamber (92), the seal (110) preferably being arranged on the external collar (102) of the oil guide element (96).

11. The multiple clutch system (2) as claimed in one of claims 2

35 to 10, wherein assembly openings (140) to permit the passage of an assembly tool are provided in the actuating piston (70), which assembly openings in the axial direction (8) are arranged at least partially in alignment with the external collar (102) of the oil guide element (96).

12. The multiple clutch system (2) as claimed in one of claims 2 to 1 1 , wherein the actuating piston (70) is capable of being introduced in the axial direction (8) into the oil guide element (96) and a sealing Sip (116)

5 for the sealing of an annular gap between the actuating piston (70) and the oil guide element (96) is provided on the actuating piston (70), at least one projecting abutment (106) being provided on the side of the oil guide element (96) facing towards the actuating piston (70), on which the actuating piston (70) is capable of being supported in the axial direction (8) i o in an end position, in which the sealing lip (116) in the axial direction (8) is separated from the oil guide element (96).

13. The multiple clutch system (2) as claimed in claim 12, wherein the sealing lip (116) is arranged on a sealing element (1 12), which

15 is capable of connection to the actuating piston (70), the sealing element (1 12) preferably being capable of being pushed together or is pushed together with the actuating piston (70), and is particularly preferably capable of being pressed together or is pressed together.

20 14. The multiple clutch system (2) as claimed in claim 13, wherein the actuating piston (70), the sealing element (1 12) and the oil guide element (96) can be assembled into a module, the module then being capable of incorporation into the multiple clutch system (2).

25 15. The multiple clutch system (2) as claimed in one of the preceding claims, wherein actuating fingers (78) for the actuation of the external clutch (30) are provided on the actuating piston (70), which fingers extend through windows (80) in the disk carrier (26), preferably in the supporting section (38) of the disk carriers (26) for the external clutch (30).

30