WO2009145966A1

WO2009145966A1 - Multiplate clutch having a hydraulically drivable actuating piston

Info

Publication number: WO2009145966A1
Application number: PCT/US2009/037227
Authority: WO
Inventors: Eckart Gold; Götz NICKLAS; Jens Henze; Marcus Hertel; Hans Jürgen HAUCK; Martin Gerlach; Michael Wilhelm SCHÄFER; Daniel Bader
Original assignee: Borgwarner Inc.
Priority date: 2008-03-29
Filing date: 2009-03-16
Publication date: 2009-12-03
Also published as: DE102008038100B4; DE102008038100A1

Abstract

The present invention relates to a multiplate clutch (2) having a preferably hydraulically drivable actuating piston (74), having a plate pack (30) which can be compressed by the actuating piston (74), and having at least one plate carrier (22, 38), with the actuating piston (74) being movable in the axial direction (6, 8) relative to the plate carrier (22, 38). According to the invention, the actuating piston (74) is indirectly or directly in positively locking, rotationally driving connection with the plate carrier (22, 38). Here, the indirect positively locking, rotationally driving connection between the actuating piston (74) on the one hand and the plate carrier (22, 38) on the other hand takes place preferably by means of at least one restoring spring which generates the restoring movement of the actuating piston (74) and which is particularly preferably embodied as a disk spring (98).

Description

MULT1PLATE CLUTCH HAVING A HYDRAULICALLY DRIVABLE

ACTUATING PISTON

DESCRIPTION

The present invention relates to a multiplate clutch, preferably a multiple clutch, having a hydraulically drivable actuating piston, having a plate pack which can be compressed by the actuating piston, and having at least one plate carrier, with the actuating piston being movable in the axial direction relative to the plate carrier.

The prior art discloses multiplate clutches having at least one plate pack, with a hydraulically drivable actuating piston being provided for compressing the plate pack. The actuating piston is generally assigned a pressure chamber which can be acted on with oil pressure in order to move the actuating piston in the axial direction relative to a plate carrier of the multiplate clutch and press said actuating piston against the plate pack, such that the latter is compressed and a factional connection is generated between an input side and an output side of the plate pack. In order to seal off the pressure chamber for the actuating piston and if appropriate further compensating chambers with respect to other chambers within the multiplate clutch, a plurality of seal elements are provided, via which the hydraulically drivable actuating piston is supported in the radial or axial direction against a further part of the multiplate clutch, such as for example the clutch hub or the plate carrier. Here, the actuating piston is supported on the other components of the multiplate clutch in such a way that said actuating piston can be rotated relative to the plate carrier and relative to the plate pack in the tangential direction if corresponding acceleration forces act on the actuating piston.

The known multiplate clutches having an actuating piston of said type have been proven in practice, but it has been found during the operation of the known multiplate clutch that, during the transmission of torque, a more severe torque non- uniformity occurs when the plate pack of the known multiplate clutches is compressed.

It is therefore an object of the present invention to create a multiplate clutch having a hydraulically drivable actuating piston in which a particularly high degree of torque uniformity is obtained when the plate pack is compressed. Here, the multiplate clutch according to the invention should preferably be of simple construction, in such a way that said multiplate clutch can be produced and manufactured in a particularly simple manner.

Said object is achieved by means of the features specified in patent claim 1. Advantageous embodiments of the invention are the subject matter of the subclaims.

The multiplate clutch according to the invention has a drivable actuating piston, with the multiplate clutch being embodied preferably as a multiple clutch, particularly preferably as a dual clutch. Here, the actuating piston is preferably hydraulically drivable. It is thus possible, for example, for a pressure chamber to be provided on the one side of the hydraulically drivable actuating piston, which pressure chamber can be acted on with oil pressure in order to move the actuating piston in the axial direction. It would also be possible, for example, for an oil-filled compensating chamber to be provided on the other side in order to obtain substantial centrifugal oil compensation. The actuating piston is assigned to a plate pack of the multiplate clutch in such a way that the plate pack can be compressed by the actuating piston in order to generate frictional coupling between an input side and an output side of the plate pack. The multiplate clutch also has at least one plate pack, wάth it being possible for the actuating piston, during its movement, to be moved in the axial direction relative to the plate carrier. According to the invention, the actuating piston is indirectly or directly in positively locking, rotationally driving connection with the plate carrier. The plate carrier however need not necessarily be the plate carrier which is assigned to the plate pack; the plate carrier may in fact also be a plate carrier of a further plate pack within the multiplate clutch according to the invention. In the latter case, however, the further plate carrier should preferably be a plate carrier which is rotationally fixedly connected to the plate carrier of the plate pack mentioned in the introduction. The possibility of the indirect positively locking, rotationally driving connection may for example be understood to mean that the rotationally driving connection between the actuating piston on the one hand and the plate carrier on the other hand takes place by means of an additional, or preferably already-existing, component of the multiplate clutch. If the multiplate clutch according to the invention is to be a multiple clutch, then it is preferable if the actuating piston of each plate pack is indirectly or directly in positively locking, rotationaliy driving connection with the plate carrier or one of the plate carriers, with it being possible in said case for the advantageous and preferred embodiments below to also be correspondingly realized.

Since the actuating piston is in rotational] y driving connection with the plate carrier, it is possible to attain a particularly high degree of torque uniformity during the compression of the plate pack, especially since the actuating piston can no longer be rotated, or can be rotated only to a restricted extent, relative to the plate carrier or to the associated plate pack. Furthermore, the wear at the contact point between the actuating piston and the plate pack, that is to say in particular on that end plate of the plate pack which faces toward the actuating piston, is significantly lower, as a result of which the service life of the multipiate clutch can be increased. By means of a direct rotationally driving connection between the actuating piston and the plate carrier using an already-existing component instead of an additional component, it is also possible to obtain a particularly simple and weight-saving construction of the raulriplate clutch, which also permits particularly simple production of the latter.

For the above reason, in one preferred embodiment of the multipiate clutch according to the invention, the actuating piston is indirectly in positively locking, rotationally driving connection with the plate carrier by means of an already- existing functional part of the multipiate clutch. An already-existing functional part of the multipiate clutch is to be understood to mean a functional part which, in addition to its underlying function, now also has the function of generating a positively locking, rotationally driving connection between the actuating piston and the plate carrier. The already- existing functional part should preferably be a functional part which is imperatively required for the operation of the multipiate clutch and/or which is separate from the actuating piston and the plate carrier. Here, said functional part may for example be a restoring spring of the actuating piston. In said embodiment, therefore, no further component is required for the multipiate clutch, which multipiate clutch may therefore be of particularly simple construction, have a lower weight and permit simpler production and assembly.

According to a further preferred embodiment of the multipiate clutch according to the invention, the already-existing functional part which additionally generates the positively locking, indirect rotationally driving connection between - A - the actuating piston and the plate carrier is formed by at least one restoring spring which generates the restoring movement of the actuating piston. The use of the restoring spring to generate the rotationally driving connection is advantageous since the restoring spring is supported in any case at one side on the actuating piston and at the other side on the plate carrier, such that the actuating piston and the plate carrier are already in contact with one another by means of the restoring spring. The restoring force of the restoring spring also has the effect that the actuating piston and the plate carrier are already in non-positive, rotationally driving connection to a restricted extent, such that it would be necessary then merely to generate a positively locking, rotationally driving connection by modifying the restoring spring on the one hand or the actuating piston and the plate carrier on the other hand. In this way, the stated components need only be modified slightly in order to generate the indirect positively locking, rotationally driving connection, wherein an additional component would not be strictly necessary here either.

In one particularly preferred embodiment of the multiplate clutch according to the invention, the restoring spring which generates the restoring movement of the actuating piston is embodied as a disk spring. This is associated with various advantages. Firstly, there is the general advantage of a disk spring, specifically that said disk spring has a smaller axial extent than a coil spring with the same restoring force. In this way, the axial structural length of the multiplate clutch can be kept low, which is advantageous in particular if the multiplate clutch is a multiple clutch in which the individual clutches are arranged in a nested fashion in the radial direction. Furthermore, the disk spring, which is usually of thin-walled design, may be modified in a particularly simple manner in order to obtain a positively locking, rotationally driving connection with respect to the actuating piston on the one hand and the plate carrier on the other hand. Also, in general, no end shoe is required for the disk spring, as is used for example in the case of a coil spring in order to support the coil spring at the end side against the actuating piston and the plate carrier. A further significant advantage of the disk spring is that the latter, on account of its plate-shaped design, has a greater stiffness in the tangential direction than would be the case with a plurality of axially extending coil springs. While intense rotational oscillations would occur between the actuating piston on the one hand and the plate carrier or the plate pack on the other hand when using a plurality of coil springs, which rotational oscillations would ultimately lead to a torque non-uniformity during the compression of the plate pack, this is substantially eliminated with the disk spring. In one advantageous embodiment of the multiplate clutch according to the invention, the disk spring has an outer or inner contour, but preferably an outer contour, which is in engagement in the radial direction with an inner or outer contour, but preferably an inner contour, of the actuating piston, in order to obtain a positively locking, rotationaily driving connection between the disk spring and the actuating piston. The use of an outer contour on the disk spring which is in engagement with an inner contour on the actuating piston is advantageous since the actuating piston generally has a substantially tubular, axially extending, radially outer section whose inner contour need merely be slightly modified in order to obtain rotationaily driving engagement with the outer contour of the disk spring, which generally does not extend as far outward, in the radial direction as the actuating piston. In this way. no significant modification to the basic shape of the actuating piston and of the disk spring is necessary, as a result of which the manufacturing expenditure is reduced.

In one advantageous alternative or additional embodiment to the embodiment described above, at least one axially protruding projection is provided on the disk spring or on the actuating piston of the multiplate clutch according to the invention, which axially protruding projection extends in the axial direction into a cutout or depression in the actuating piston or in the disk spring. Said embodiment of the multiplate clutch according to the invention entails a particularly low level of manufacturing expenditure, especially since the cutouts or depressions can be generated in the actuating piston or in the disk spring in a particularly simple manner, for example by virtue of corresponding bores or punched-out portions being generated in the respective component. Conversely, it is possible for an axially protruding projection to be generated on the disk spring in a particularly simple manner by bending a tongue on the disk spring in the axial direction.

In a further advantageous embodiment of the multiplate clutch according to the invention, to generate the positively locking, rotationaily driving connection between the disk spring and the plate carrier, the disk spring has an inner or outer contour, preferably an inner contour, which is in engagement in the radial direction with an outer or inner contour, preferably an outer contour, of the plate carrier. Similarly to one of the embodiments specified above, it is necessary here too merely to carry out a minor modification to the plate carrier and to the disk spring if the inner contour of the disk spring is in engagement with an outer contour of the plate carrier, especially since the plate carrier generally also has a tubular section which is situated further inward and which may be used to form the outer contour and which may provide a support surface for the disk spring which is generally situated radially further outward.

In an alternative or additional embodiment to the embodiment described above, at least one axially protruding projection is provided on the disk spring or on the plate carrier of the muitiplate clutch according to the invention, which axially protruding projection extends in the axial direction into a cutout or depression in the plate carrier or in the disk spring in order to obtain the positively locking, rotationally driving connection between the disk spring and the plate carrier. With regard to the advantages of this embodiment, reference is made at this juncture to the advantages of the axially protruding projections, cutouts and depressions of an embodiment described above. In one particularly advantageous embodiment of the muitiplate clutch according to the invention, the disk spring has radially outwardly pointing disk spring tongues and/or radially inwardly pointing disk spring tongues. It is preferable here if the disk spring has both radially outwardly pointing disk spring tongues and radially inwardly pointing disk spring tongues. Disk spring tongues of said type are assigned to the respectively adjoining component and permit particularly simple axial compression of the disk spring. Here, the disk spring tongues are spaced apart from one another in the tangential direction so as to form interposed incisions. In this respect, the disk spring may have substantially the design of a known disk spring. Here, however, it is particularly preferable if the cutouts in the disk spring, which cutouts are intended to generate the positively locking, rotationally driving connection with the actuating piston or with the plate carrier, are formed by the incisions between the disk spring tongues, and/or the outer and/or inner contour of the disk spring, which generates the positively locking, rotationally driving connection with the actuating piston and/or with the plate carrier, is defined by the disk spring tongues. Said embodiment has the advantage that no disk springs which are produced especially for the purpose of generating a positively locking, rotationally driving connection are used. In fact, it is possible to use conventional disk springs with radially outwardly pointing disk spring tongues and/or radially inwardly pointing disk spring tongues, such that merely a modification to the actuating piston and/^'or of the plate carrier is necessary to generate the positively locking, rotationally driving connection between the actuating piston and the plate carrier. The manufacturing expenditure is considerably reduced in this way.

The axially protruding projection on the disk spring could fundamentally be formed by a pin or the like which has been retroactively fastened to the disk spring. However, to permit particularly simple manufacturing of the disk spring and to simplify the assembly of the muitiplate clutch, the axially protruding projection on the disk spring is formed, in a further advantageous embodiment of the muitiplate clutch according to the invention, in one piece with the disk spring. Here, the axially pro trad ing projection is preferably formed by a tongue, which is bent in the axial direction, of the disk spring, which tongue may for example be arranged on a section of the disk spring which is formed so as to be continuous in the tangential direction. A tongue bent in such a way entails a particularly low level of manufacturing expenditure. Here, it is particularly preferable if the axially protruding projection on the disk spring is formed by a disk spring tongue which is bent in the axial direction and which serves in any case to support the disk spring against the actuating piston or the plate carrier. Since said disk spring tongues are inclined in the axial direction in the installed state in any case, no further modification to the disk spring tongues is fundamentally necessary, especially since said disk spring tongues can already engage, on account of their inclination, into the cutouts or depressions in the actuating piston or plate carrier. However, to permit particularly reliable engagement of said disk spring tongues into the associated cutouts or depressions, the free end of the disk spring tongues should additionally be bent in the axial direction. In this way, a particularly secure positively locking, rotationally driving connection with the actuating piston and/or with the plate carrier is generated. Since the actuating piston and the plate carrier are generally of thicker- walled design than the above-described disk spring, the axially protruding projections on the actuating piston and/or on the plate carrier cannot simply be produced in the primary forming process of the actuating piston or of the plate carrier, as is the case with the disk spring. For this reason, the axially protruding projection on the actuating piston and/or on the plate carrier is, in a further advantageous embodiment of the multiplate clutch according to the invention, formed by a pin wliich is retroactively attached, preferably screwed on, welded on or pressed in, to the actuating piston and/or to the plate carrier. If the axially protruding projections are retroactively attached to the actuating piston and to the plate carrier in the described way, this duly involves more expenditure, but a modification to the disk spring, as was already indicated with reference to the above-described embodiments, is no longer necessary. Accordingly, it is necessary merely to modify the actuating piston and the plate carrier, while otherwise a conventional disk spring may be used to generate the positively locking, rotationally driving connection between the actuating piston and the plate carrier.

In a further advantageous embodiment of the multiplate clutch according to the invention, to obtain a particularly effective rotationally driving connection between the described inner contour and the outer contour which is assigned to the inner contour, both the inner contour and also the outer contour have a shape which deviates from that of a circle. Here, the inner contour and the outer contour should substantially correspond to one another in terms of their shape. For example, said contours may for example have an oval shape, a cross shape or a shape which corresponds to that of a toothing. It is however preferable if the inner contour and the outer contour which is assigned to the inner contour has the shape of a polygon, which is particularly preferably designed as a regular polygon, or a polygon which is symmetrical about an axis or a point. In the case of a regular polygon, a plurality of rotational positions of the disk spring in relation to the actuating piston and/^'or the plate carrier are possible in which the disk spring can be attached to said components, such that assembly is simplified, especially since, in the case of a disk spring, no defined rotational position or assembly position in relation to said components is generally required. In a further particularly preferred embodiment of the multiplate clutch according to the invention, to avoid a complex modification to the plate carrier in order to obtain the positively locking, rotationally driving connection, the disk spring is in rotationally driving connection with the plate carrier by means of a seal element which is rotationally fixedly connected to the plate carrier, with the axially protruding projection of the plate carrier, the cutout or depression in the plate carrier or the outer or inner contour of the plate carrier being provided on the seal element. In this w^ray, the basic shape of the plate carrier need no longer be modified in order to obtain the positively locking, rotationally driving connection between the actuating piston and the plate carrier. In fact, it is necessary merely to modify the seal element which is preferably retroactively rotationally fixedly connected to the plate carrier, the modification or production of which is significantly simpler. The axially protruding projection of the plate carrier, the cutout or depression in the plate carrier or the outer or inner contour of the plate carrier is provided here preferably on a supporting part of the seal element which is composed of an elastic sealing part and a less elastic supporting part. In this way, it is possible for rotational oscillations of the actuating piston relative to the plate carrier and therefore relative to the plate pack to be reliably prevented, such that a uniform degree of torque uniformity can be obtained during the compression of the plate pack. Here, the supporting part may for example serve for the rotationally fixed fastening of the seal element to the plate carrier, and should particularly preferably be formed as a sheet-metal part, especially since said sheet-metal part can be modified in a particularly simple manner such that the positively locking, rotationally driving connection between the disk spring and the seal element, and therefore also the plate carrier, can be obtained. In contrast, the elastic sealing part may, for example, be formed by a rubber element which is vulcanized on the supporting part.

In a further preferred embodiment of the multiplate clutch according to the invention, the actuating piston has at least one radially outwardly or radially inwardly protaiding projection which engages into an inner or outer toothing of the plate carrier for holding the plates. Since the inner or outer toothing of the plate carrier, which serves to hold the plates in a rotationally fixed yet longitudinally movable manner, must already be provided on the plate carrier in any case, a fiirther modification or processing of the basic shape of the piate carrier is not necessary, as a result of which the manufacturing expenditure is reduced. Only the actuating piston need be processed so as to form the radially outwardly or inwardly protruding projection which engages into the inner or outer toothing. For this purpose, it is also possible for a plurality of radially outwardly or inwardly protruding projections to be provided, which are arranged together in the form of an outer or inner toothing.

According to a further preferred embodiment of the multiplate clutch according to the invention, the actuating piston also comprises a plate-shaped section, which faces toward the plate pack, for forming the end piate of the plate pack, with the radially outwardly or inwardly protruding projection being provided on the plate-shaped section. It would thus be possible, both in this embodiment and also in the embodiment described above, to provide a multiplicity of radially outwardly or inwardly protruding projections, which accordingly form an outer or inner toothing. If the plate-shaped section of the actuating piston forms the end plate of the plate pack, then it is possible to dispense with an end plate, which was possibly originally provided and which is not in positively locking, rotationally driving connection with the actuating piston, of the plate pack, such that the multiplicity of parts for the multiplate clutch is reduced in this embodiment. The plate-shaped section of the actuating piston may be formed here by a separate plate-shaped section which is in positively locking, rotationally driving connection with the rest of the actuating piston, but it is preferable if the plate-shaped section of the actuating piston is formed in one piece with the actuating piston and therefore forms a section of the actuating piston within the meaning of the wording. Here, the plate-shaped section of the actuating piston is designed such that it can be pressed in the axial direction flat against the adjoining plate of the plate pack. Here, it is particularly preferable if the plate-shaped section of the actuating piston also has a friction lining which faces toward the subsequent plate.

In multiple clutches, whose clutches are arranged so as not to be nested in the radial direction, the actuating piston in many cases has an elongate tubular section which surrounds the plate-supporting section of a plate carrier in the radial direction. In a further advantageous embodiment of the multiplate clutch according to the invention, to obtain a particularly simple positively locking, rotationally driving connection between the actuating piston on the one hand and the plate carrier on the other hand in this case too, the actuating piston has a tubular section which surrounds the plate-supporting section of a plate carrier in the radial direction, with the radially inwardly protruding projection being provided on the tubular section and being in engagement with the outer toothing of the plate- supporting section. Said embodiment is advantageous since, with corresponding processing or production, the plate-supporting section always has both an inner toothing and also an outer toothing, such that in said embodiment, the outer toothing is also utilized, while the inner toothing serves to hold the inner plates. In a further advantageous embodiment of the multiplate clutch according to the invention, at least one axially protruding projection is provided on the actuating piston or on the plate carrier, which axially protruding projection extends in the axial direction into a cutout or depression in the plate carrier or in the actuating piston. Here, the axially protruding projection and/or the cutout or depression in the piate carrier is preferably provided in the support section for radially supporting the plate carrier, which support section is arranged further inward in the radial direction than a plate-supporting section of the plate carrier. The axially protruding projections, cutouts or depressions in the support section of the plate carrier have the advantage over corresponding axialiy protruding projections, cutouts or depressions on the plate-supporting section of the plate carrier that the actuating piston need not extend outward in the radial direction to such an extent in order to obtain the positively locking, rotationally driving connection. In fact, only an actuating piston which is of short construction in the radial direction is necessary, such that the material expenditure and the weight are reduced. The advantages specified with reference to the above-described embodiments of the multiplate clutch according to the invention are particularly pronounced in the case of a further preferred embodiment of the multipiate clutch according to the invention, in which the plate carrier has a support section for radially supporting the same, with the actuating piston being arranged, in relation to the axial direction, entirely on a side, which faces toward the plate pack, of the support section, preferably between the support section and the plate pack. This embodiment in particular does not encompass multipiate clutches in which the actuating piston is arranged at least partially on a side, which faces away from the plate pack, of the support section, while a further part of the actuating piston extends through windows within the support section to that side of the support section which faces toward the plate pack, especially since a positively locking, rotationally driving connection could already be generated in this way. In said embodiment, the support section serves preferably for providing radial support in the inward direction, particularly preferably on a clutch hub of the multiplate clutch.

In a further particularly preferred embodiment of the multiplate clutch according to the invention, the actuating piston can be or is supported in the radial direction on the plate carrier via the protruding projections, the restoring spring and/or the seal element. By means of said embodiment, it is possible for the actuating piston to be centered with respect to the other components of the multiplate clutch, in particular with respect to the plate carrier, and vice versa even during assembly. This not only facilitates assembly; in fact, it is also possible for undesired vibrations, which are attributed for example to a tilting movement of the components, to be prevented during later operation of the multiplate clutch.

With a certain design of multiplate clutches, it is possible only with an increased amount of expenditure to provide a positively locking, rotationally driving connection between the actuating piston for compressing the plate pack and the plate carrier which is assigned to said plate pack. For this reason, in a further particularly advantageous embodiment of the multiplate clutch according to the invention, the plate carrier forms a first plate carrier to which the plate pack is assigned in the form of a first plate pack, with a second plate carrier for a second plate pack being provided and with the actuating piston being indirectly or directly in positively locking, rotationally driving connection with the second plate carrier in order to compress the first plate pack. Therefore, although the actuating piston is in positively locking, rotationaily driving connection with a plate carrier, said plate carrier is not assigned to the plate pack which can be compressed by the actuating piston. The first and second plate carriers, which are preferably designed as outer plate carriers, may nevertheless likewise be rotationally fixedly connected to one another by means of a clutch hub or the like. Said embodiment simplifies the realization of the positively locking, rotationally driving connection between the actuating piston and the plate carrier, in particular when the two plate packs are arranged in a nested fashion in the radial direction.

The invention is explained in more detail below on the basis of exemplary embodiments and with reference to the appended drawings, in which: Figure 1 shows a partial side view of an embodiment of the multiplate clutch according to the invention in a sectioned illustration,

Figure 2a shows the detail A from figure 1 in a first embodiment of the multiplate clutch according to the invention,

Figure 2b shows a view in the direction of the arrow a of figure 2a in a first alternative,

Figure 2c shows a view in the direction of the arrow a in figure 2a in a second alternative.

Figure 3 shows the detail A from figure 1 in a second embodiment of the multiplate clutch according to the invention, Figure 4 shows the detail A from figure 1 in a third embodiment of the multiplate clutch according to the invention,

Figure 5 shows the detail B from figure 1 in a fourth embodiment of the multiplate clutch according to the invention.

Figure 6 shows the detail B from figure 1 in a fifth embodiment of the multiplate clutch according to the invention,

Figure 7 shows the detail B from figure 1 in a sixth embodiment of the multiplate clutch according to the invention,

Figure 8 shows the detail B from figure 1 in a seventh embodiment of the multiplate clutch according to the invention, Figure 9 shows the detail C from figure 1 in an eighth embodiment of the multiplate clutch according to the invention,

Figure 10 shows the detail D from figure 1 in a ninth embodiment of the multiplate clutch according to the invention,

Figure 1 1 shows the detail D from figure 1 in a tenth embodiment of the multiplate clutch according to the invention, and

Figure 12 shows a partial side view of a further embodiment of the multiplate clutch according to the invention in a sectioned illustration. The basic design of an embodiment of the multiplate clutch 2 is firstly described below, which basic design applies to all of the embodiments described with reference to figures 2 to 1 1. The details A, B. C and D are thus illustrated in figure 1 as black boxes, with the different embodiments of the multiplate clutch 2 in said details or regions being described in more detail later with reference to figures 2 to 11.

The multiplate clutch 2 is designed as a multiple clutch, in the present example as a dual clutch, with it being possible for the rotatable components of the multiplate clutch 2 to be rotated about a common rotational axis 4. The rotational axis 4 extends in the two opposite axial directions 6 and 8 of the multiplate clutch 2, which axial directions 6 and 8 are illustrated in figure 1 by means of corresponding arrows. Furthermore, the outwardly directed radial direction 10 and the inwardly directed radial direction 12 are indicated by means of arrows. The mutually opposite tangential directions are also depicted by means of the arrows 14 and 16.

The multiplate clutch 2 firstly has an input hub 18 w^rhich can be rotationally fixedly connected to a drive unit. The input hub 18 is rotationally fixedly connected, by means of its end which points in the axial direction 8. to a driver disk 20 which extends outward in the radial direction 10 from the input hub 18. That edge of the driver disk 20 which points outward in the radial direction 10 is in rotationally driving connection with a first plate carrier 22 which is designed as an outer plate carrier. The fust plate carrier 22 comprises a tubular plate- supporting section 24 which extends in the axial direction 8 from the driver disk 20. The plate-supporting section 24 has an inner toothing 26 which serves for the rotationally fixed connection to outer plates 28 of an outer first plate pack 30, with the outer plates 28 being in rotationally driving connection with the plate- supporting section 24 in such a way that said outer plates 28 can be moved in the axial direction 6 or 8. The first plate carrier 22 also comprises a support section 32 which extends inward substantially in the radial direction 12 from that end of the plate-supporting section 24 which points in the axial direction 8. The first plate carrier 22, which is designed as an outer plate carrier, is therefore of substantially shell-shaped design. The support section 32, which extends in the radial direction 12, serves for radially supporting the first plate carrier 22 inward in the radial direction 12 against a substantially tubular clutch hub 34 which surrounds a transmission-side supporting tube 36 and transmission input shafts (not illustrated in any more detail) at the outside in the radial direction 10.

The clutch hub 34, which is rotationally fixedly connected to the support section 32 of the first plate carrier 22, extends from the support section 32 in the axial direction 6 and is rotationally fixedly connected there to a second plate carrier 38 which is likewise designed as an outer plate carrier. The fust plate carrier 22 and the second plate carrier 38 are therefore rotationally fixedly connected to one another by means of the clutch hub 34. The second plate carrier 38 firstly has a support section 40 which extends outward substantially in the radial direction 10 from the clutch hub 34. The support section 40 is adjoined outward in the radial direction 10 by a tubular plate-supporting section 42, with the plate- supporting section 42 extending from the support section 40 in the axial direction 6. The second plate carrier 38 therefore also has a substantially shell-shaped design. The plate-supporting section 42 of the second plate carrier 38 likewise has an inner toothing 44 which serves for the rotationally fixed connection to the outer plates 46 of a second plate pack 48, with the outer plates 46 being in engagement with the inner toothing 44 of the second plate carrier 38, in such a way that said outer plates 46 may also be moved in the axial direction 6 or 8. The multiplate clutch 2 also has a first inner plate carrier 50 which is assigned to the first plate pack 30. The first inner plate carrier 50 therefore comprises a tubular plate-supporting section 52 with an outer toothing 54 which is in rotationaily driving connection with the inner plates 56 of the first plate pack 30. The outer plates 28, which are arranged in an alternating fashion with the inner plates 56 in the axial direction 6, 8, therefore form, together with the inner plates 56, the first plate pack 30 which may also be referred to as the outer clutch of the multiplate clutch 2. The plate-supporting section 52 is adjoined in the axial direction 6 by a support section 58 of the first inner plate carrier 50, with the support section 58 extending inward substantially in the radial direction 12 up to a first output hub 60, to which the support section 58 is rotationally fixedly connected. The first inner plate carrier 50 can therefore be rotationally fixedly connected by means of the first output hub 60 to a first transmission input shaft (not illustrated in any more detail). The second plate pack 48 is also assigned a second inner plate carrier 62. The second inner plate carrier 62 also lias a tubular plate-supporting section 64 which is provided with an outer toothing 66. The outer toothing 66 is in rotationally driving engagement with inner plates 68 of the second plate pack 48, with the inner plates 68 forming, together with the outer plates 46, the second plate pack 48 which may also be referred to as the inner clutch of the multiplate clutch 2. The inner plates 68 are also arranged in an alternating fashion with the outer plates 46 in the axial direction 6 or 8. The tubular plate-supporting section 64 extends in the axial direction 6, with the plate-supporting section 64 being adjoined here by a support section 70. The support section 70 extends inward in the radial direction 12 from the plate-supporting section 64, in order to be rotationally fixedly connected there to a second output hub 72 which may be rotationally fixedly connected to a second transmission input shaft (not illustrated).

As can be seen from the above description, the first plate pack 30, which forms the outer clutch, is arranged in the radial direction 10 outside the second plate pack 48. which forms the inner clutch of the multiplate clutch 2. The first plate pack therefore surrounds the second plate pack 48, such that the two plate packs 30, 48 are arranged in a nested fashion in the radial direction 10, 12. In this way, it is possible to obtain a particularly short axial structural length of the multiplate clutch 2.

To be able to compress the first plate pack 30 and therefore close the outer clutch of the multiplate clutch 2, the multiplate clutch 2 also has a hydraulically drivabie actuating piston 74. The actuating piston 74 extends substantially in the radial direction 10. 12 and comprises a radially inner piston section 76 and a radially outer force-transmission section 78. Both the force-transmission section 78 and also the piston section 76 are arranged on a side 80. which faces toward the first plate pack 30 and which points in the axial direction 6, of the support section 32 of the first plate carrier 22. The actuating piston 74 is therefore arranged entirely on that side 80 of the support section 32 which faces toward the plate pack 30. such that no actuating fingers are required on the actuating piston 74, which actuating fingers would have to extend in the axial direction 6 through windows in the support section 32 of the plate carrier 22 in order to arrive at the first plate pack 30. It may also be said that the actuating piston 74 is arranged entirely within the shell-shaped first plate carrier 2. Here, at least the force-transmission section 78 of the actuating piston 74 preferably extends between the support section 32 and the plate pack 30.

The actuating piston 74 can be moved in the axial direction 6 or 8 relative to the first plate carrier 22 and the second plate carrier 38 in order to respectively close or open the outer clutch, in the form of the plate pack 30, by means of the force-transmission section 78. For tliis purpose, a pressure chamber 82 is assigned to the actuating piston 74, which pressure chamber 82 can be fed with pressurized oil via at least one bore 84 in the clutch hub 34. The pressure chamber 82 is arranged in the axial direction 8 behind the piston section 76 of the actuating piston 74 and is delimited by the support section 32, the piston section 76 and the clutch hub 34. To seal off the pressure chamber 82, encircling seals 86 are provided on the piston section 76. Here, the seals 86 do not provide any rotationally driving connection between the actuating piston 74 on the one hand and the support section 32 or the clutch hub 34 on the other hand.

The pressure chamber 82 is also assigned a compensating chamber 88 which can be fed with compensating oil via at least one further bore 90 in the clutch hub 34. The compensating chamber 88 is arranged in the axial direction 6 behind the actuating piston 74 and is delimited by the piston section 76. the support section 40 and the clutch hub 34. To seal off the compensating chamber 88 outward in the radial direction 10, an encircling seal element 92 is also provided. The seal element 92 comprises a supporting part 94 composed of sheet metal and a sealing part 96 which is vulcanized onto the supporting part 94 and which may for example be designed as a rubber element. The supporting part 94, which is designed to be less elastic than the sealing part 96, is rotationally fixedly connected to the support section 40 of the second plate carrier 38, by virtue, for example, of said supporting part 94 being pressed onto the partially tubular support section 40 of the second plate carrier 38. However, any other embodiment is also conceivable here in which a rotationally fixed connection can be generated between the seal element 92 and the second plate carrier 38. The sealing part 96 is supported in the radial direction 10 against the piston section 76 of the actuating piston 74 and thereby provides sealing of an annular gap between the actuating piston 74 on the one hand and the support section 40 of the second plate carrier 38 on the other hand.

If the pressure within the pressure chamber 82 is increased in such a way that the axiai force which acts in the axial direction 6 on the piston section 76 of the actuating piston 74 is greater than an opposing axial force which results from the pressure within the compensating chamber 88 and the restoring force of the disk spring 98. then the actuating piston 74 is moved in the axial direction 6 in order to compress the first plate pack 30 and thereby close the outer clutch. If the outer clutch is to be opened again, then it is necessary merely for the pressure within the pressure chamber 82 to be reduced again, with a restoring spring in the form of a disk spring 98, which brings about the restoring movement of the actuating piston 74, then generating an axial movement of the actuating piston 74 in the axial direction 8. The disk spring 98 is supported at one side in the axial direction 8 on the force-transmission section 78 of the actuating piston 74 and at the other side in the axial direction 6 on the support section 40 of the second plate carrier 38, and thereby brings about a restoring movement of the actuating piston 74 into its starting position shown in figure 1.

Alternatives regarding the further design of the multiplate clutch 2 of figure 1 are described below with reference to figures 2a to 8. The embodiments according to figures 2a to 8 have in common the fact that the actuating piston 74 is indirectly in positively locking, rotationally driving connection with the second plate carrier 38. The indirect positively locking, rotationally driving connection between the actuating piston 74 on the one hand and the second plate carrier 38 on the other hand is obtained here by means of an already-existing functional part of the multiplate clutch 2. An already-existing functional part is to be understood in this connection to mean a functional part of the multiplate clutch 2 which has some function other than generating a rotationally driving connection, with said already- existing functional part now also assuming the function of generating an indirect positively locking, rotationally driving connection between the actuating piston 74 and the second plate carrier 38. In the embodiments according to figures 2a to 8, said already-existing functional part is formed by the above-mentioned disk spring 98. Figure 2a thus shows the detail A from figure 1 in a first embodiment. The actuating piston 74 has, at its outer edge of the force-transmission section 78 in the radial direction 10, a tubular section 100 which adjoins the force-transmission section 78 and which extends in the axial direction 6 from the force-transmission section 78 to the first plate pack 30. The tubular section 100 of the actuating piston 74 has an inner contour 102 which has a shape which deviates from that of a circle. In contrast, the disk spring 98, which is supported in the axial direction 8 on the actuating piston 74, has an outer contour 104 which likewise has a shape which deviates from that of a circle, with the shape of the outer contour 104 of the disk spring 98 corresponding substantially to the shape of the inner contour 102 of the tubular section 100 of the actuating piston 74. The positively locking, rotationally driving connection between the actuating piston 74 on the one hand and the disk spring 98 on the other hand is therefore obtained in that the outer contour 104 engages in the radial direction 10 into the inner contour 102 of the actuating piston 74. It is therefore necessary merely to modify the inner and outer contours 102, 104 in order to generate a positively locking, rotationally driving connection between the actuating piston 74 and the disk spring 98, and additional components are not necessary here.

With regard to the design of the inner and outer contours 102, ] 04, certain shapes have proven to be particularly advantageous. Figure 2b thus shows a first design variant. Both the inner contour 102 of the tubular section 100 of the actuating piston 74 and also the outer contour 104 of the disk spring 98 are formed here in the shape of a polygon if said contours 102, 104 are viewed in the axial direction 8. In a further particularly advantageous design variant, which is illustrated in figure 2c, the inner contour 102 of the tubular section 100 of the actuating piston 74 is formed substantially by an inner toothing. The disk spring 98, in contrast, has disk spring tongues 106 which point outward in the radial direction 10 and which are spaced apart from one another in the tangential direction 14, 16 so as to form interposed incisions 108. The disk spring tongues 106 therefore form, together with the interposed incisions 108, an outer-toothing- like outer contour 104 of the disk spring 98, which outer contour 104 engages in the radial direction 10 into the inner- toothing- like inner contour 102 of the actuating piston 74. Figure 3 shows the detail A from figure 1 in an alternative embodiment to figures 2a to 2c, with the intention being for only the differences to be explained below; the same reference symbols are used for identical or similar parts, and the above description applies correspondingly with regard to said parts. In the embodiment according to figure 3, the positively locking, rotationally driving connection is not obtained by means of the inner contour 102 of the actuating piston 74. In fact, a projection HO which protrudes in the axial direction 8 is provided on the disk spring 98. The axially protruding projection 1 J O is formed in one piece with the disk spring 98. with said axially protruding projection 110 being formed by a disk spring tongue 106, which is bent in the axial direction 8, of the disk spring 98. The axially protruding projection 1 10 in the form of the disk spring tongue 106 which is bent in the axial direction 8 extends in the axial direction 8 into a cutout 112 which is provided in the force-transmission section 78 of the actuating piston 74. Alternatively, said cutout 1 12 may also be formed by a depression in the force-transmission section 78, with a cutout 112 being preferable in order to be able to obtain better tolerance compensation. The protruding projection 110, which abuts against those flanks of the cutout 1 12 which are arranged in the tangential direction 14, 16, therefore generates a positively locking, rotationally driving connection between the disk spring 98 on the one hand and the actuating piston 74 on the other hand.

A further alternative to the embodiment according to figure 3 is illustrated in figure 4, with the intention here also being to describe merely the differences; the same reference symbols are used for identical or similar parts, and the above description applies correspondingly with regard to said parts. In the embodiment according to figure 4, the axially protruding projection 110 is arranged on the force-transmission section 78 of the actuating piston 74, whereas the cutouts 1 12 are provided in the disk spring 98. The axiaily protruding projection 1 30 is formed here by a pin 114 which is screwed on, welded on or pressed in and which, after being fastened to the actuating piston 74, extends in the axial direction 6 through or into the cutouts 1 12 in the disk spring 98. Since the attachment of a protruding projection 1 10 of said type has proven to be particularly complex within the context of the primary forming process for the actuating piston 74, the pin 1 14 has been retroactively attached to the actuating piston 74 in order to reduce the production expenditure. As already explained with reference to figure 2c, the disk spring 98 has, in one particularly preferred embodiment, radially outwardly pointing disk spring tongues 106, between which in the tangential direction 14, 16 are formed the incisions 108. To keep the production expenditure for the disk spring 98 particularly low, the interposed incisions 108 in the disk spring 98 in said embodiment serve not only to space the disk spring tongues 106 apart in the tangential direction 14, 16, but rather also as cutouts 112 into which the axially protruding projections 110 extend in the axial direction 6.

With the embodiments according to figures 2a to 4, a positively locking, rotationally driving connection has hitherto been generated only between the actuating piston 74 on the one hand and the disk spring 98 on the other hand. To obtain an indirect positively locking, rotationally driving connection between the actuating piston 74 on the one hand and the second plate carrier 38 on the other hand, it is now necessary for the region which forms the detail B from figure 1 to also be specially modified as shown in the different alternatives according to figures 5 to 8.

Figure 5 thus shows the detail B from figure 1 in a first alternative. Here, the disk spring 98 has an inner contour 1 16 which points inward in the radial direction 12. Opposite said inner contour 1 16, an encircling projection 118 is provided on the support section 40 of the second plate carrier 38, which projection 118 extends in the axial direction 8 and on that side of which projection 1 18 which points outward in the radial direction 10 is provided an outer contour 120. The inner contour 1 16 may thus again have a shape which deviates from that of a circle, preferably the shape of a polygon, while the inner contour 116 has a corresponding shape. Furthermore, the inner contour 116 may - similarly to the inner contour 102 according to figure 2c - have an outer-toothing-like outer contour 120, while the inner contour 116 of the disk spring 98 is formed by radially inwardly pointing disk spring tongues 122 and the interposed incisions 124. With regard to the advantages and the further design, it is possible here to make reference to the description with regard to figures 2a to 2c, which applies analogously. Regardless of the respective design variant, the inner contour 116 of the disk spring 98 engages in the radial direction 12 into the outer contour 120 on the second plate carrier 38, such that a positively locking, rotationally driving connection is also generated between the disk spring 98 on the one hand and the second plate carrier 38 on the other hand.

A similar embodiment to the embodiment according to figure 5 is described beiow with reference to figure 6, with only the differences being discussed; the same reference symbols are used for identical or similar parts and the above description applies correspondingly with regard to said parts. In contrast to the embodiment according to figure 5, in the embodiment according to figure 6, the positively locking, rotationally driving connection between the disk spring 98 and the second plate carrier 38 is generated indirectly by means of the seal element 92. The supporting part 94 of the seal element 92, which supporting element 94 is already rotationally fixedly connected to the support section 40 of the second plate carrier 38, is thus extended outward in the radial direction 10. The above-described outer contour 120 of the plate carrier 38 is provided on the radially outer section which is thereby generated. Since the supporting part 94 of the seal element 92 is designed to be less elastic than the sealing part 96 of the seal element 92, the torque of the second plate carrier 38 can be transmitted substantially without hysteresis to the disk spring 98. A corresponding modification to existing seal elements 92 is also considerably simpler than an adaptation of the basic shape of the second plate carrier 38 to its new task. Figure 7 shows an alternative embodiment for generating a positively locking, rotationally driving connection between the disk spring 98 on the one hand and the second plate carrier 38 on the other hand. Similarly to the connection of the disk spring 98 to the actuating piston 74 according to figure 3, use is made here of an axially protruding projection 128. The axially protruding projection 128 is formed in one piece with the disk spring 98. The axially protruding projection 128 is thus formed by a radially inwardly pointing disk spring tongue 122 which is bent in the axial direction 6. The axially protruding projection 128 extends here into a cutout 130 in the support section 40 of the second plate carrier 38 and thereby generates a positively locking, rotationally driving connection in the tangential direction 14, 16. With regard to the advantages of such an embodiment, reference is made here to the advantages, described with reference to figure 3. of the connection of the disk spring 98 to the actuating piston 74. Said statements apply analogously. Figure 8 shows a further alternative to the embodiments according to figures 5 to 7. Below, only the differences with respect to the embodiment according to figure 7 are explained, and the same reference symbols are used for identical or similar parts, and the above description applies correspondingly with regard to said parts. The axially protruding projection 128 in the embodiment according to figure 8 is thus provided not on the disk spring 98 but rather on the support section 40 of the second plate carrier 38. The protrading projection 128 is again formed by a pin which is retroactively fastened to the support section 40 of the plate carrier 38, with reference being made in this regard to the preceding description of figure 4, which applies correspondingly in this regard. The pin or the axially protrading projection 128 extends in the axial direction 8 into cutouts 132 which are formed by the incisions 124, which are arranged between the radially inwardly pointing disk spring tongues 112, of the disk spring 98.

As already mentioned in the introduction, the indirect positively locking, rotationally driving connection between the actuating piston 74 on the one hand and the second plate carrier 38 on the other hand is generated by means of a positively locking, rotationally driving connection between the actuating piston 74 and the disk spring 98 and a positively locking, rotationally driving connection between the disk spring 98 and the second plate carrier 38. Here, an already- existing functional part, specifically the disk spring 98, is resorted to, such that no additional functional part is required. In fact, it is necessary merely to slightly modify the disk spring 98 or the components which adjoin the latter. The use of a restoring spring in the form of the disk spring 98 is particularly advantageous here since the disk spring 98, in contrast to a coil spring, can firstly be modified in a particularly simple manner and secondly permits only small rotational fluctuations of the actuating piston 74 with respect to the second plate carrier 38, with the latter being attributable to the plate shape of the disk spring 98.

Further embodiments of the multiplate clutch 2 of figure 1 are described below with reference to figures 9 to 11. In said embodiments, the actuating piston 74 is not indirectly rotationally fixedly connected to one of the plate carriers 22, 38 in a positively locking manner by means of an already-existing functional part of the multiplate clutch 2; in fact, the actuating piston 74 is directly in positively locking, rotationally driving connection with the first plate carrier 22. Figure 9 thus shows an embodiment of the multiplate clutch 2 in the region of the detail C from figure 1. The substantially tubular section 100 of the actuating piston 74 is, at its end which points in the axial direction 6 and which faces toward the first piate pack 30, provided with or in rotationally driving connection with a plate-shaped section 134. For this purpose, the plate-shaped section 134 of the actuating piston 74 may for example be formed in one piece with or cohesively connected to the actuating piston 74. It is however likewise possible for the rotationally driving connection between the tubular section 100 and the plate- shaped section 134 to be generated in some other way, even though a cohesive connection is preferable here. The plate-shaped section 134 therefore forms the end plate of the first plate pack 30, such that it is possible here to dispense with a separate end plate which was originally provided. The number of individual parts to be used during assembly is reduced in this way.

The plate-shaped section 134 is preferably composed of an inner partial section 136, which extends inward in the radial direction 12 from the tubular section 100, and an outer partial section 138 which extends outward in the radial direction 10 from the tubular section 100 of the actuating piston 74. On account of said design, particularly uniform pressing of the plate-shaped section 134 of the actuating piston 74 against the first plate pack 30 in the axial direction 6 is possible. A projection 140 which protrudes outward in the radial direction 10 is provided at the outer edge of the outer partial section 138 of the plate-shaped section 134, which projection 140 engages into the inner toothing 126 of the plate- supporting section 24 of the first plate carrier 22 in order to obtain a direct positively locking, rotationally driving connection between the actuating piston 74 on the one hand and the first plate carrier 22 on the other hand.

The embodiment described with reference to figure 9 has proven to be advantageous, but said embodiment requires that the actuating piston 74 or the plate-shaped section 134 thereof must be pulled outward to a particularly great extent in the radial direction 10 in order to place the radially protruding projection 140. which may for example be one of a multiplicity of radially protruding projections 140 which, together, form an outer toothing, into engagement with the inner toothing 26 of the plate-supporting section 24. The latter situation may under some circumstances be undesirable. Figures 10 and I i thus show alternative embodiments to the embodiment according to figure 9.

In figure 10, which shows the embodiment of the multiplate clutch 2 from figure 1 in the detail D, a projection 142 which protrudes in the axial direction 6 is provided on the support section 32 of the first plate carrier 22. Similarly to that already described with reference to figures 4 and 8, the protruding projection 142 is formed by a pin which is retroactively fastened to the support section 32. The protruding projection 142 extends in the axial direction 6 into a cutout 144 in the force-transmission section 78 of the actuating piston 74. It is however likewise possible to provide the protruding projection 142 on the force-transmission section 78 of the actuating piston 74, with said protruding projection 142 then extending in the axial direction 8 into the cutout 144 in the support section 32 of the first plate carrier 22. as shown in figure 11. In both cases, the actuating piston 74 need not extend outward in the radial direction 10 to such an extent as to generate a positively locking, rotationally driving connection between the plate carrier 22 and the actuating piston 74. Said direct positively locking, rotationally driving connection is in fact already generated in the region of the support section 32 of the first plate carrier 22 and in the force-transmission section 78 of the actuating piston 74. Finally, a further embodiment of the multiplate clutch 2 according to the invention is described with reference to figure 12, which is duly also embodied as a dual clutch, but in which the plate packs 30, 48 are not arranged in a nested fashion in the radial direction 10. 12. The actuating piston 74 thus has, to actuate the plate pack 30, a substantially tubular section 146 which surrounds a plate- supporting section 148 of an outer plate carrier 150 in the radial direction 10. Projections 152 which protrude inward in the radial direction 32 are provided on the tubular section 146 of the actuating piston 74, which projections 152 are in engagement with an outer toothing of the plate-supporting section 148 in order to generate a direct positively locking, rotationally driving connection between the actuating piston 74 on the one hand and the outer plate carrier 150 on the other hand.

Both the embodiment according to figure 9 and also the embodiment according to figure 12 have the decisive advantage that the direct positively locking, rotationally driving connection between the actuating piston 74 and the respective plate carrier is generated using a toothing which is provided on the corresponding plate-supporting section in any case, such that no special adaptation of the plate carrier or of the plate-supporting section is necessary. The embodiments according to figures 9 and 12 are particularly recommended if the actuating piston 74 is, on account of the given circumstances, arranged in any case particularly far outward in the radial direction 10. The embodiment according to one of figures 10 or 11 is recommended otherwise, especially since the direct positively locking, rotationally driving connection between the plate carrier 22 and the actuating piston 74 can be generated here already in the region of the support section 32 of the plate carrier 22.

In all of the above-described embodiments, the positively locking, rotationally driving connection between the actuating piston 74 on the one hand and the plate carrier 22, 38, 150 on the other hand is generated in such a way that the actuating piston 74 can be or is supported in the radial direction 10 or 12 on the plate carrier 22. 38. 150 via the protruding projections 1 10, 128, 140, 142, 152. the restoring spring in the form of the disk spring 98 and/or the seal element 92, such that the generation of the positively locking, rotationally driving connection is also associated with a centering or alignment of the actuating piston 74 relative to the plate carrier 22, 38, 150. Furthermore, any tilting movement of the actuating piston

74 relative to the rotational axis 4 is effectively restricted in this way, with said advantage coming to bear in particular in the embodiment according to figure 12, in which use is made of an actuating piston 74 with a particularly large structural length. Also, the encircling seals 86 and the seal element 92 are relieved of load, such that said seals 86 and seal element 92 may be designed to a great extent for the function for which they were intended, specifically for the sealing of annular gaps. List of reference symbols

Multiplate clutch

Rotational axis

Axial direction

Radial direction

Tangential direction

Input hub

Driver disk

First plate carrier

Plate-supporting section

Inner toothing

Outer plates

First plate pack

Support section

Clutch hub

Supporting tube

Second plate carrier

Support section

Plate-supporting section

Inner toothing

Outer plates

Second plate pack

First inner plate carrier

Plate-supporting section

Outer toothing

Inner plates

Support section

First output hub

Second inner plate carrier

Plate-supporting section Outer toothing

Inner plates

Support section

Second output hub

Actuating piston

Piston section

Force transmission section

Side

Pressure chamber

Bore

Encircling seals

Compensating chamber

Bore

Seal element

Supporting part

Sealing part

Disk spring

Tubular section

Inner contour

Outer contour

Disk spring tongues

Interposed incisions

Axially protaiding projection

Cutout

Inner contour

Lug

Outer contour

Disk spring tongues

Incisions

Radially outer section

Axially protruding projection

Cutout 132 Cutout

134 Plate-shaped section

136 Inner partial section

138 Outer partial section

140 Radially protruding projection

142 Axially protruding projection

144 Cutout

146 Tubular section

148 Plate-supporting section

150 Outer plate carrier

152 Radially protruding projections

Claims

1. A multiplate clutch (2) having a preferably hydraulically drivable actuating piston (74), having a plate pack (30) which can be compressed by the actuating piston (74), and having at least one plate carrier (22, 38), with the actuating piston (74) being movable in the axial direction (6, 8) relative to the plate carrier (22, 38), wherein the actuating piston (74) is indirectly or directly in positively locking, rotationally driving connection with the plate carrier (22, 38).

2. The multipiate clutch (2) as claimed in claim 1. wherein the actuating piston (74) is indirectly in positively locking, rotationally driving connection with the plate carrier (38) by means of an already-existing functional part of the multiplate clutch (2), preferably by means of at least one restoring spring which generates the restoring movement of the actuating piston (74) and which is particularly preferably embodied as a disk spring (98).

3. The multiplate clutch (2) as claimed in claim 2, wherein the disk spring (98) has an outer or inner contour (104), preferably an outer contour (104), which is in engagement in the radial direction (10) with an inner or outer contour (102), preferably an inner contour (102), of the actuating piston (74), and/or wherein at least one axially protruding projection (1 10) is provided on the disk spring (98) or on the actuating piston (74). which axially protruding projection (110) extends in the axial direction (6, 8) into a cutout (112) or depression in the actuating piston (74) or in the disk spring (98).

4. The multiplate clutch (2) as claimed in one of claims 2 or 3, wherein the disk spring (98) has an inner or outer contour (116), preferably an inner contour (116), which is in engagement in the radial direction (12) with an outer or inner contour (120), preferably an outer contour (120). of the plate carrier (38),

and/or wherein at least one axially protruding projection (128) is provided on the disk spring (98) or on the plate carrier (38), which axially protruding projection (128) extends in the axial direction (6, 8) into a cutout ( 112) or depression in the plate carrier (38) or in the disk spring (98).

5. The multiplate clutch (2) as claimed in one of claims 3 or 4, wherein the disk spring (98) has radially outwardly pointing disk spring tongues ( 106) and/or radially inwardly pointing disk spring tongues (122) which are spaced apart from one another in the tangential direction (14, 16) so as to form interposed incisions (108, 124), with the cutouts (112. 132) in the disk spring (98) preferably being formed by the incisions (108, 124) and/or with the outer and/or inner contour (104, 116) of the disk spring (98) being defined by the disk spring tongues (i O6, 122).

6. The inultiplate clutch (2) as claimed in one of claims 3 to 5, wherein the axially protruding projection (110, 128) on the disk spring (98) is formed in one piece with the disk spring (98), preferably by a tongue which is bent in the axial direction (6. 8), particularly preferably by a disk spring tongue ( 106, 122) which is bent in the axial direction (6, 8).

7. The multiplate clutch (2) as claimed in one of claims 3 to 6, wherein the axially protruding projection (1 10, 128, 142) on the actuating piston (74) and/or on the plate carrier (22, 38) is formed by a pin which is retroactively attached, preferably screwed on, welded on or pressed in, to the actuating piston

(74) and/or the plate carrier (22, 3K).

8. The multiplate clutch (2) as claimed in one of claims 3 to 7, wherein the inner contour (102, 116) and the outer contour (104, 120) which is assigned to the inner contour (102, 1 16) has a shape which deviates from that of a circle, and preferably has the shape of a polygon.

9. The multiplate clutch (2) as claimed in one of claims 3 to 8, wherein the disk spring (98) is in rotationally driving connection with the plate carrier (38) by means of a seal element (92) which is rotationally fixedly connected to the plate carrier (38). with the axially protruding projection of the plate carrier (38), the cutout or depression in the plate carrier (38) or the outer or inner contour (120) of the plate carrier (38) being provided on the seal element (92), preferably on a supporting part (94) of the seal element (92) which is composed of an elastic sealing part (96) and a less elastic supporting part (94), with the supporting part (94) particularly preferably being formed as a sheet-metal part.

10. The mυltiplate clutch (2) as claimed in claim 1 , wherein the actuating piston (74) has at least one radially outwardly or radially inwardly protruding projection (140, 152) which engages into an inner or outer toothing (26) of the plate carrier (22, 150) for holding the plates, with the actuating piston (74) preferably having a plate-shaped section (134), which faces toward the plate pack (30), for forming the end plate of the plate pack (30), and with the radially outwardly or inwardly protruding projection (140) being provided on the plate- shaped section (134).

1 1. The multiplate clutch (2) as claimed in claim 10, wherein the actuating piston (74) has a tubular section (146) which surrounds the plate- supporting section (148) of a plate carrier (150) in the radial direction (10), with the radially inwardly protruding projection (152) being provided on the tubular section (146) and being in engagement with the outer toothing of the plate- supporting section (148).

12. The multiplate clutch (2) as claimed in claim 1 , wherein at least one axially protruding projection ( 142) is provided on the actuating piston (74) or on the plate carrier (22), preferably on the support section (32) for radially supporting the plate carrier (22), which axially protruding projection (142) extends in the axial direction (6, 8) into a cutout (144) or depression in the plate carrier (22), preferably in the support section (32) for radially supporting the plate carrier (22), or in the actuating piston (74).

13. The multiplate clutch (2 ) as claimed in one of the preceding claims, wherein the plate carrier (22) has a support section (32) for radially supporting the same, preferably inward in the radial direction (12), particularly preferably against a clutch hub (34), with the actuating piston (74) being arranged, in relation to the axial direction (6, 8), entirely on a side (80), which faces toward the plate pack (30), of the support section (32), preferably between the support section (32) and the plate pack (30).

14. The multiplatε clutch (2) as claimed in one of claims 2 to 13, wherein the actuating piston (74) can be or is supported in the radial direction (10,

12) on the plate carrier (22, 38, 150) via the protruding projections (1 10, 128, 140, 152). the restoring spring and/or the seal element (92).

15. The multiplate clutch (2) as claimed in one of the preceding claims, wherein the plate carrier (22) forms a first plate carrier (22) to which the plate pack

(30) is assigned in the form of a first plate pack (30), and a second plate carrier (38) for a second plate pack (48) is provided, with the actuating piston (74) being in positively locking, rotationally driving connection with the second plate carrier (38) in order to compress the first plate pack (30), with the two plate packs (30, 32) preferably being arranged in a nested fashion in the radial direction (10, 12) and with the first and second plate carriers (22, 38) particularly preferably being designed as outer plate carriers.