FR2781266A1 - Clutch friction disc for friction clutches in vehicles, with zone between hub and friction disc to allow axial movement and bending - Google Patents

Abstract

The clutch friction disc consists of a hub (12) coupled to the shaft from the gearbox, which is provided with friction pads (26) on the periphery of the friction disc (10). These pads (26) are at right angles to the plane of rotation (A) of the hub and are provided with a joining piece (18) between these pads and the hub (12) in such a way that the pads can move radially in relation to the axis of rotation (A) of the hub and also to pivot in relation to its plane. This flexible section (30) joining the hub (12) to the friction pads (26) has a section in the form of an S' so that it can deform as well as forming a drive between the two parts.

Description

The present invention relates to a clutch disc for a clutch with

  friction of a motor vehicle, comprising: - a hub capable of being integrally coupled in rotation to an input shaft of the gearbox, - friction linings arranged in an external radial zone of the clutch disc, the friction linings being at least partially substantially parallel to or in a plane substantially orthogonal to an axis of rotation of the hub, and - a connection arrangement by which the friction linings of the clutch disc are connected to the hub so that that the friction linings can make a radial movement relative to the axis of rotation of the hub and / or a movement of

pivot relative to the plane.

  In automotive construction, when the drive units are mounted transversely, there is often the problem that a gearbox input shaft is no longer mounted in a pilot bearing in the crankshaft and thus centered relative to to the crankshaft. The consequence is that small axial offsets and nutation movements may appear during operation, which are induced by the irregular rotation of the crankshaft or the flywheel

of inertia attached to it.

  When using rigid clutch discs in which the friction linings are substantially rigidly coupled to the hub of the clutch disc, there is often the problem, due to axial offset or nutation movement, of wear excessive in the area of the hub profile or the input shaft profile of the gearbox, or else there is the problem that the welding or the matting between the hub and the drive disc carrying the friction linings breaks. In addition, the bearings are more heavily loaded, for example in the two-mass flywheel and in the gearbox, and there is often a bad uncoupling of the oscillations, which

  can lead to changing states in slow motion.

  Document DE 43 22 578 Ai discloses a clutch disc in which a driving disc is received by an internal toothing on an external toothing of the hub of the clutch disc, so that a limited radial mobility or else a rotation relative limited is possible between these two parts. In addition, an elastic element is arranged on the driving disc and it pushes against a support element supported on the hub and it thus establishes a centering of the disc.

driver relative to the hub.

  Document DE 44 16 949 CI1 discloses a nutation clutch disc in which the friction linings, that is to say the springs thereof, are connected to the clutch hub via a plurality of leaf spring elements substantially tangential to the

clutch hub.

  Furthermore, document FR-A-27 24 995 discloses a clutch disc in which the lining carriers are fixed to a driving disc by means of studs which can pivot relative to the driving disc by interposition of elements. elastic,

  so that a corresponding pivoting or displacement of the holders

toppings is possible.

  The objective underlying the present invention is to develop the clutch disc of the type mentioned, so as to reliably balance or compensate for nutation movements or axial offsets which appear during operation. According to a first aspect of the present invention, this objective is achieved by the fact that in such a clutch disc, the connection arrangement comprises a driving disc which is coupled substantially integrally in rotation on the one hand to the hub and on the other hand to the friction linings and which comprises in a radial zone between the coupling to the hub or to the friction linings at least one deformation zone which

  extends in the axial direction or which is bent in the axial direction.

  By providing this deformation zone which extends in the axial direction or which is bent in the axial direction, an elasticity is integrated in the clutch disc which allows reliable and safe

  nutation movements and which compensates for axial offsets.

  This effect can be amplified in particular when the deformation zone comprises a plurality of flexion zones which define a contour which extends radially from the inside to the outside under

  form of meanders in axial direction.

  A simple adaptation of the clutch discs according to the invention to different requirements, that is to say to different elasticities, can be achieved by the fact that the driving disc has a radially inner annular zone for coupling to the hub, a radially outer annular zone for coupling to the friction linings as well as a plurality of connecting sections, and that the deformation zone is provided respectively in the region of the connecting sections. The advantage here is also that we can save weight by providing recesses in the area of the

drive disc.

  Alternatively, it is however also possible that the disc part is a substantially completely closed part produced in the manner of a membrane. In this case also, one can choose the elasticity on the one hand by a choice of the material and on the other hand by a

  special realization of the meandering structure.

  The connecting sections can extend substantially radially.

  According to another independent aspect of the invention, provision is made for the connection arrangement to comprise a disk portion having a

  radially inner annular section, a radial annular section-

  outer ment and a plurality of connecting sections, the connecting sections extending in curved form radially from the inside to the outside and in at least one peripheral direction. The curvature in the peripheral direction also allows pivoting or displacement in the radial direction without constraint, so that

  can compensate for nutation movements and axial offsets.

  Of course, a combination of this aspect with the aspects mentioned above is also possible by providing for

  connecting sections curved in space.

  Preferably, the connecting sections extend approximately in an S shape. According to another aspect of the present invention, the objective mentioned above can be achieved by the fact that the connecting device comprises a driving disc which is coupled radially to the outside with friction linings and which has radially on the inside an internal toothing which meshes with an external toothing on the hub providing a play of radial movement, and that it further comprises a centering spring arrangement by which

  the driving disc is resiliently centered relative to the hub.

  In this case, a particularly simple structure can be obtained when the centering spring arrangement comprises at least one section of centering spring produced in a square which bears against

  an outer peripheral surface of the hub.

  In this case, it is possible, for example, to provide that said at least one section of centering spring produced in a square is produced by at least one spring element produced substantially in annular shape which comprises in a inner peripheral zone a plurality of elastic tabs which are bent in the direction of the axis of rotation of the hub to bear against the outer surface of the clutch hub. In order to provide, in addition to the radial centering, also the axial locking function in a simple manner in the clutch disc, it is proposed that said at least one spring element comprises at least one axial locking projection which is supported axially against a radial projection of the hub, preferably in the area of the

external teeth.

  Preferably, a respective spring element is arranged on the two

  axial sides of the driving disc.

  We can simplify the structure and reduce the number of parts when said at least one spring element is made integrally with

  the driving disc and forms an inner radial zone thereof.

  According to an alternative embodiment, it can be provided that the centering spring arrangement, fixed to a component among the hub and the driving disc, comprises at least one spring element which engages by at least one elastic tab axially in a interval formed between the internal toothing and the external toothing and which bears under prestress against the other component. Since in this case the individual elastic tabs engage in the region of the toothing, an extremely short embodiment is produced in

axial direction.

  To distribute the forces, it is also advantageous here that on each side of said component is arranged a spring element, and that the spring elements engage alternately from the two axial sides in a respective interval between the external toothing and the

interior teeth.

  In addition, said at least one spring element may comprise at least one axial locking section which protrudes radially inwards and which bears axially against the hub, preferably against the

external toothing thereof.

  According to another independent aspect, the objective in accordance with the invention is achieved by the fact that the connection arrangement comprises: - an intermediate disc which is coupled to the hub for a common rotation and which is movable relative to the hub in a first direction of movement substantially radially to the axis of rotation of the hub, - a driving disc which is coupled on the one hand to the friction linings and on the other hand to the intermediate disc for a common rotation, and which is movable relative to the intermediate disc in a second direction of movement substantially radially with respect to the axis of rotation of the hub, the first direction of movement and the second direction of movement being different directions of movement. In this case, a Cardan coupling is provided between the friction linings and the hub, which allows a radial displacement without stress or deformation of the friction linings relative to the hub. In this case, the first direction of movement and the second direction of movement are

  preferably substantially orthogonal to each other.

  This Cardan coupling is provided for example in a clutch disc which comprises: - at least a first drive projection which extends substantially radially on a component among the hub and the intermediate ring, and a first recess d drive associated with each first drive projection on the other component among the hub and the intermediate ring and extending substantially radially and receiving the first drive projection associated with play of radial movement, and - at least one second drive projection which extends substantially radially over one component from the intermediate disc and the drive disc, and a second drive recess associated with each second drive projection from the other component from the intermediate disc and the drive disc , extending substantially radially and receiving the second drive projection associated with

radial movement play.

  In this concrete embodiment, it is advantageous for an obstacle-free realization of the radial movement in any direction that said at least one first driving projection and said at least one second driving projection are offset by one

  relative to each other by about 90 in the peripheral direction.

  According to another independent aspect, the objective mentioned above is achieved by the fact that the connection arrangement comprises: - on the hub a hub flange protruding radially and connected in rotation with it, - a driving disc which is coupled radially outside to the friction linings and which comprises radially inside two connecting sections, a respective connecting section being provided at least locally on an axial side of the hub flange, a plurality of studs link by which the link sections are each connected to the hub flange for a common rotation, but which allow a relative radial movement and a relative peripheral movement of a predetermined value between the link sections on the one hand and the flange of hub on the other hand, - an elastically deformable arrangement, preferably a layer of elastomeric material, received under prestressing between at least one of the

  connecting sections and the hub flange.

  In this case, one can for example provide that the connecting studs are fixed relative to one of the structural groups among the connecting sections and the hub flange and movable in radial and peripheral direction relative to the other structural group. respective. The deflection movement or movement movement of the friction linings relative to the hub, allowed by the elasticity, can be further improved or simplified by the fact that there is provided an elastically deformable arrangement between the two sections of

  connection on the respectively associated axial side of the hub flange.

  According to another independent aspect of the present invention, the objective mentioned above is achieved by the fact that the connection arrangement comprises a torsional oscillation damper arranged in the torque transmission path between the hub and the friction linings , said damper having an inlet side and an outlet side, the inlet side and the outlet side being movable relative to each other in the radial and / or axial direction, and / or one at least the inlet and outlet sides being able to pivot relative to the plane and relative to the other side. In this case, the torsional oscillation damper is advantageously used on the one hand to dampen torsional oscillations which appear, for example, in the range of idle rotation speeds, and on the other hand to provide for play. io movement necessary for the movable components relative to each other during the appearance of nutation movements or axial offset. Of course, when a torsional oscillation damper is provided, the structural zones coupled by it are also movable relative to each other in the peripheral direction, in order to fulfill the function of damping the oscillations. of torsion. The relative mobility in the radial direction and / or in the axial direction then serves substantially to allow a nutation movement, this radial displacement or this axial displacement can also appear when torsional oscillations occur, the structural groups simultaneously performing a relative peripheral movement. It will be noted with regard to the input side and the output side, that one refers respectively for example to the flow of the force or the torque in the drive state of a drive unit. Of course, we can reverse the functional association of the input side and the output side to certain groups

  structural in pushing operation.

  One can realize such a construction method for example in a connection arrangement which comprises: - a driving disc received by an internal toothing with radial movement play and with peripheral movement play on an external toothing of the hub, - a hub flange of the torsional oscillation damper, coupled in rotation to the hub, - a spring arrangement comprising at least one spring which extends approximately in the peripheral direction and which bears in its end zones against edges of respective control on the one hand of the hub flange of the torsional oscillation damper and on the other hand of the driving disc, said at least one spring being movable, in the bearing zone against the respective control edge of the driving disc and / or in the bearing area against the respective control edge of the hub flange of the torsional oscillation damper, with respect to the respective control edge a u least in the direction of approximately radial extension of

the associated command edge.

  Alternatively, it is also possible that the connecting arrangement

  comprises a driving disc having a radial disc part-

  outer part and a radially inner disc part, the radially outer disc part having an internal toothing which meshes with an external toothing on the radially inner disc part, with relative play of movement in radial direction and in peripheral direction, and that the torsional oscillation damper comprises a spring arrangement having at least one spring arranged in the region of the meshing teeth, which can come to bear in its end regions on the one hand against the external teeth and on the other part against the internal teeth. In this way, a very short arrangement is again made in the axial direction which allows an enlarged structural space for other components or which results in the general reduction of the need in place for a friction clutch produced with such a disc. clutch. In this case, the torsional oscillation damper is preferably arranged

  in the radially outer zone of the driving disc.

  Radial mobility and / or mobility in nutation alone or in addition is made possible by elastic deformation of a coupling arrangement which couples the inlet side and the outlet side. In this case, it is possible, for example, to provide that the entry side comprises a driving disc with internal toothing, and in that the exit side comprises covering discs arranged on both sides of the driving disc, which are joined in rotation to the hub, the hub having an external toothing associated with the internal toothing. Here, provision is preferably made to match the internal toothing of the driving disc and the external toothing of the hub to each other, so that the driving disc and the hub are movable relative to each other. in the peripheral direction, in the direction

radial and in axial direction.

  According to another embodiment, which can however be combined without any problem with other embodiments according to the invention of a clutch disc with elastic coupling, it can be provided that the arrangement of connection includes a bellows coupling arrangement. It has been found that such bellows coupling arrangements proceed, in particular when transmitting the torque with axial offset and / or axial tilt, to compensate for these axial errors without causing wear, and that '' they also have the advantage of

extremely low mass.

  In this case, it is for example possible to provide that the bellows coupling arrangement comprises at least one coupling bellows which extends substantially in the direction of the axis of rotation of the hub and which is coupled in a first zone d end at the hub and in a second end zone at the friction linings. For example, the coupling arrangement to

  bellows may include a metallic coupling bellows.

  The present invention will be described in more detail in the following with reference to preferred embodiments illustrated in the accompanying drawings. The figures show: FIG. 1 a schematic axial partial view of a drive disc of a clutch disc according to the invention, which is connected to a hub; Figure 2 a section of the arrangement illustrated in Figure 1 along a line II-II; Figure 3 a view corresponding to that of Figure 1 of an alternative embodiment of the drive disc; Figure 4 a sectional view along a line IV-IV in Figure 3; Figure 5 an axial view of an alternative embodiment of the driving disc; Figure 6 a partial longitudinal sectional view of another clutch disc according to the invention; FIGS. 7a, b each a view in longitudinal section in peripheral zones different from the spring elements illustrated in FIG. 6; Figures 8, 9 a modification of the clutch disc illustrated in Figure 6; Figures 1 Oa, b each a view corresponding to Figures 7a and 7b; Figures 1 1 to 13 other respective modifications of the clutch disc shown in Figure 6; Figure 14 a longitudinal sectional view through a friction clutch which comprises a clutch disc according to the invention according to another embodiment; Figure 15 an axial view of the significant area of the clutch disc shown in Figure 14; Figure 16 an enlarged view corresponding to Figure 15 Figure 17 a sectional view along a line XVII-XVII of Figure 16; Figure 18 a sectional view along a line XVIII-XVIII of Figure 16; Figure 19 a sectional view along a line XIX-XIX of Figure 17; Figure 20 a modification of the clutch disc shown in Figure 16; figure 21 another modification of the clutch disc shown in figure 16; Figure 22 a longitudinal sectional view of another alternative embodiment of a clutch disc according to the invention; Figure 23 another alternative embodiment of a clutch disc according to the invention; Figure 24 a clutch which comprises another embodiment of a clutch disc according to the invention; Figure 25 a partial axial view of the clutch disc of Figure 24 in the area of the torsional oscillation damper; FIG. 26 a view in longitudinal section which shows another embodiment of a clutch disc according to the invention; Figure 26a a modification of the embodiment illustrated in Figure 26; Figure 26b an axial view of the clutch disc of Figure 26a; and Figure 27 a partial longitudinal sectional view of another embodiment of a clutch disc according to the invention comprising

a coupling bellows.

  Figures 1 and 2 show a first embodiment of a disc

  clutch according to the invention. This clutch disc 10

  carries a hub 12 which can be coupled via an internal toothing 14 to an external toothing on an input shaft not illustrated of a gearbox for common rotation. The clutch disc further comprises a driving disc 18 which comprises in the illustrated embodiment an inner annular section 20, an outer annular section 22 and a plurality of connecting sections 24 which connect these annular sections 20, 22. The section outer ring 22 is coupled to friction linings 26 (suggested

  only schematically) of the clutch disc, and this is direct

  either with interposition of packing springs or the like.

  As can be seen in particular in FIG. 2, the driving disc 18 has been produced in the region of the interior annular section 20 comprising a cylindrical section 28 which surrounds a surface

  outer peripheral of the hub 12 and which is firmly connected to it

  ci for example by forming a longitudinal clamping joint, by welding, by riveting or by other suitable connection methods. A deformation zone 30 is formed in each connecting section 24 in a central region, which has a plurality of curvatures 32, so that the meandering profile illustrated in FIG. 2 is formed with sections bent or extending in the direction axial. By providing these deformation zones, the driving disc 18 can be elastically deformed, so that a relative movement between the radially inner zone o of the driving disc 18, that is to say the inner annular zone 20 firmly connected to the hub 12, and the radially outer zone thereof, that is to say the outer annular section 22 firmly connected to the friction linings 26, can appear both in the radial direction and in the direction of the pivoting or nutation movements . Thus, it is possible to compensate for small axial offsets which exist between a crankshaft of an internal combustion engine not illustrated and an input shaft of the gearbox during operation thanks to the elastic mobility of the radially inner zone with respect to the radially outer zone of the clutch disc; similarly, thanks to the elastic deformation, it is possible to compensate for nutation movements which appear during operation and which are induced by an irregular rotation of the crankshaft and / or of the input shaft of the gearbox.

of speeds.

  In this case, the elasticity can be adjusted by the width of the individual connecting sections 24 as well as by the number and the layout of the sections bent or extending in the axial direction. The openings 34 visible in Figure 1 between the individual connecting sections 24 allow the approximation of a tool by which one can screw a modular structure coupling on a flange of the crankshaft. It is however also possible to produce the driving disc 18 in the manner

  of a continuous membrane in the peripheral direction.

  The driving disc 18 is preferably punched from a sheet metal part and it is bent by suitable tools to take the

necessary form.

  In addition, it is possible that the connecting sections 24 illustrated in axial extension in FIG. 1 include a peripheral extension component, so that one integrates here in addition

  elasticities in the driving disc 18.

  Figures 3 and 4 show a modification of the embodiment illustrated in Figure 1, in which there are again provided an inner annular section 20a, an outer annular section 22a and a plurality of connecting sections 24a to form a driving disc 1 8a. As can be seen in FIG. 4, the driving disc i 8a is located approximately in a plane E orthogonal to the axis of rotation A of the clutch disc 10, and it does not have the sections protruding in the axial direction out of the plane E, as is the case in the embodiment according to FIGS. 1 and 2. In place of these, the individual connecting sections 24a extend in peripheral direction radially from the inside to the outside, so that a pivoting of the outer annular section 22a relative to the inner annular section 20a, that is to say for example outside of the plane E, is also possible here by elastic deformation of the connecting sections 24a. Thanks to the S-shaped meandering layout, this

  elasticity is further improved.

  It can be seen in Figure 4 that an embodiment has been chosen in which the driving disc 1 8a is welded to the hub 12a. In addition, we again see the openings 34a through which we can have access to screws 16a illustrated diagrammatically by which

  screw a flywheel to a crankshaft.

  It will be noted that the connecting sections 24a can have different layouts; thus, one can for example also provide a mode of

  realization in which these present a path in the form of mean-

  dres or S-shaped radially from the inside to the outside, as illustrated in Figure 2, however with meandering or S-shaped profile in the peripheral direction, but not in the axial direction. Thanks to this, we also provide elasticity to compensate for an offset

  axial, that an elasticity to allow the movement of nutation.

  FIG. 5 shows another modification of the elastically deformable driving disc 18b which also includes an inner annular section 20b, an outer annular section 22b as well as a plurality of connecting sections 24b which connect them and which again extend radially , in the illustrated embodiment. To the outer annular section 22b are connected a plurality of T-shaped packing spring supports 38b which are each connected in their free T-shaped end zones 40b to packing springs or packing holders 36b. Seen radially from the inside to the outside, we also see here a profile which has an extension component in the form of a connecting bar in the peripheral direction, for example at the transition of a connecting bar 24b towards the outer annular section 22b and further towards a T-shaped packing spring support 38b. In order to further improve the elasticity, it is possible to open the outer annular section 22b in the respective peripheral zone between the individual connecting sections 24b, so that an outer annular section which does not extend here is produced not continuously; this is also possible in the embodiments according to FIGS. 1 to 4. The visible recesses 34b can also be circular recesses which leave only very thin thicknesses of residual material in the form of bars, thanks to which manufacturing with tools of

punching is simplified.

  It will be noted that it is also possible to produce the driving disc in combination with one of the principles mentioned above. This means that this driving disc can comprise connecting bars having bending zones extending in the axial direction and also bending zones extending in the peripheral direction, and it is then possible to arrange, if necessary, on the radially external zone, that is to say on the outer annular section 22, the plurality of lining spring supports 38b visible in FIG. 5, on which the linings can also be arranged directly

  friction by omitting the packing springs 36b.

  The embodiment illustrated in FIGS. 1 to 5 of a clutch disc or of a driving disc has the advantage of being able to integrate in an extremely simple and economical manner the possibility of nutation movement and of radial movement in a disc. clutch using low cost materials. Since no friction parts have been provided for each other during operation, the occurrence of friction wear is excluded. In addition, an achievement is obtained which requires very little space thanks to the

simple structure.

  Figures 6 and 7 show another embodiment of a clutch disc according to the invention 10c. The clutch disc 10c

  in turn comprises the hub 12c having the internal toothing 14c.

  On its outer surface 42c, the hub has an external toothing 44c. The driving disc 18c is produced as a solid piece which carries the friction linings 26c radially to the outside by means of the lining springs or other lining carriers 36c. The driving disc 18c has an internal toothing 46c which meshes with the external toothing 44c, so that there is a radial gap 48c allowing a slight relative radial movement.

  between the driving disc 18c and the hub 12c.

  There are provided on the driving disc 18c on both sides, spring elements 50c which have a continuous radially outer annular zone 52c by which the spring elements 50c are

  fixed by fixing studs 54c on the driving disc 18c.

  In their radially inner zones, the spring elements 50c have a plurality of legs 56c or 58c separated by radial slots, the legs 56c and 58c being provided alternately in the peripheral direction. The tabs 56c are longer and they are bent in the axial direction so as to bear under prestress on the outer surface 42c of the hub 12c. The tabs 58c are shorter and they extend only radially as far inward as they do not go to the outer surface 42c of the hub 12c, but they only clamp the outer teeth 44c of the hub together. 12c. Thus, on the one hand, radial centering is ensured between the hub 12c and the driving disc 18c by means of the tabs 56c which bear, with distribution in the peripheral direction, against the external surface 42c of the hub 12c, and on the other hand a centering or axial retention of the driving disc 18c on the hub 12c by means of the tabs 58c. When nutation movements appear or else if there is an axial offset, the driving disc 18c can move relative to the hub 12c thanks to the interval 48c between the teeth 44c, 46c, or it can also pivot out of the plan E. For this purpose,

  the individual teeth can be produced in a domed fashion.

  1 5 When the interval between the teeth 44c, 46c in the peripheral direction is canceled, a torque transmission link of

  rotation between these components is established.

  In order to avoid foreign friction and pivoting influences, the driving disc 18c is preferably arranged in the middle above

  the profile of the input shaft of the gearbox, i.e.

  above the internal toothing 14c, and the spring elements 50c are preferably produced equally to the left and to the right with respect to their radial centering forces. For example, these spring elements 50c can be made of spring steel. Centering can be direct or indirect, that is to say that the spring elements 50c can push directly against the external surface 42c of the hub 12c, or else a mounting element can be arranged between the two made for example from a material with a low coefficient of friction, for example plastic. It is also possible to provide the individual spring elements 50c and / or the hub 12c with a coating entirely or only in their region in mutual support, so that there is a desired coefficient of friction between these elements, which ensures d on the one hand a possible reduction in wear and which on the other hand ensures constant maintenance of the friction states over the life of the clutch disc 10c. The advantage is that the centering in the radial direction and the centering in the axial direction are ensured by the same components, that is to say by the spring elements 50c, of

  so no additional components are needed.

  Figures 8 to 10 show a modification of this embodiment. In this embodiment, the tabs 56d of the spring elements 50d are bent in an axial direction towards the driving disc 18d and they thus engage in the interval 48d between the teeth of the external toothing 44d and of the internal toothing 46d. In each of the spring elements 50d are provided the curved legs

  56d and the rectilinear legs 58d which alternate in the peripheral direction.

  For example, Figure 8 shows a section in a plane in which we see the tab 56d which enters the interval 48d, and a tab 58d disposed behind it in a peripheral direction which extends radially in the area of the internal toothing 44d. In the region of the tab 56d of the spring element 50d on the right in FIG. 8, the spring element 50d on the left in FIG. 8 does not include a tab, in order to allow the passage of the tab 56d from the spring element on the right. A lug 56d of the spring element 50d on the left then engages with peripheral offset (illustrated in FIG. 9) in the interval 48d, and a lug 58d of the same spring element 50d

  penetrates radially inwards into the region of the teeth 44d.

  Thanks to this, an alternating engagement is distributed distributed in the peripheral direction from the two axial sides in the intervals 48d. For example, one can also imagine that at the location where a lug 56d of one of the spring elements 50d engages in the interval 48d, a lug 58d of the other spring element 50d engages radially

  inward on the other axial side.

  Thanks to their elasticity, the individual tabs 56d bear under prestress against the internal toothing 44d, so that due to the regular distribution in the peripheral direction, a centering force is again generated for the driving disc 18d relative to the 12d hub. Since the teeth 44d and 46d are produced in convex form, as illustrated, a pivoting movement of the driving disc 18d and / or of the hub 12d out of the position oriented towards the plane E is possible, in addition to the relative oriented movement

only in radial direction.

  Since in this embodiment, the individual elastic tabs 56d are very tight, a very centering force

progressive is generated here.

  Figures 11 and 12 show another modification of the clutch disc 10 Oe according to the invention. It can be seen in FIG. 11 that the driving disc 18e comprises alternately curved legs 62e, 64e in its radially inner zone e which, seen in peripheral direction, have a mutual distance which corresponds to the width of the external toothing 44e on the hub 12th. Thus, the legs 62e, 64e alternately curved form the toothing themselves. The bending and the elasticity respectively of the driving disc 18e in this radially inner zone 60e can be produced for example by slits or by another geometric weakening of the sheet metal part which forms the driving disc 18e. In the axial direction, the legs 62e and 64e bear against respective locking rings 66e which are fixed in grooves on the hub 12e. Because of the axial support and the tightening thus produced of the legs 62e, 64e, the centering effect produced by the support of the latter against the external surface 42e of the

12th hub is further amplified.

  Due to the regular distribution of forces, the legs 62e, 64e are preferably made symmetrically and an equal number of legs are provided on each axial side, so as to obtain a symmetrical embodiment. Here, it is also advantageous that the driving disc 18e is again in the middle above the teeth 14e of the hub 12e and that the lugs 62e and 64e are also produced.

  identical in terms of their centering force.

  In FIG. 12, the toothing 44e on the external surface 42e of the hub 12e is produced by axially limited and successive recesses in the peripheral direction, so that wall elements 66e are formed in the two axial end zones of these recesses between the respective teeth of the teeth 44e, elements against which the legs 62e or 64e can bear in axial direction which engage between the individual teeth of the

s teeth 44th.

  On the height of the teeth 44e, that is to say on the radial extension of the teeth thereof, one can adjust to a desired value the surface pressing formed between the teeth 44e and the teeth 46e by the legs 64th

and 62nd.

  In the embodiment illustrated in FIGS. 11 and 12, the centering function both in the radial direction and in the axial direction and also the elasticity to allow nutation movements or to compensate for an axial offset are integrated in the driving disc. 18th which simultaneously ensures the coupling of the torque to the hub 12e. Thanks to this, we can still

save components.

  Figure 13 shows another modification of the clutch disc 10f in which are provided only legs 64f bent axially to one side, which rest against the outer surface 42f of the hub 12f and which are supported axially on a locking element or a projection 66f. Between the individual legs 64f which are not part of the toothing 46f here are provided individual projections 68f which extend radially and which alternate with the projections 64f in peripheral direction and thus form the teeth for the toothing 46f which mesh with the teeth. teeth 44f. In addition, the teeth 68f bear against a radial projection 70f on the teeth 44f in the other axial direction. It will be noted that another embodiment is here also possible in which the legs 64f form the teeth of the toothing 46f which then engage between the teeth of the toothing 44f and in which the legs 68f serve only for axial fixing by pressing against

projection 70f.

  Figures 14 to 21 show another embodiment of a clutch disc 10g according to the invention in which the relative mobility between the clutch hub 12g and the friction linings

  26g is provided by a Cardan link.

  In FIG. 14, the clutch disc 10g is illustrated in an integrated manner in a friction clutch 72g, the friction clutch 72g having a usual structure, which is why we forgo a

  more detailed description. Figure 15 shows the axial view of the area

  of the clutch disc 10g, in which a connection can be established between the hub 12g and the driving disc 18g located radially outside. It can be seen that the hub 12g has two drive projections 74g arranged at an angular distance of 180 and projecting radially outward. An intermediate disc 76g has been provided which surrounds the hub 12g and which has a central opening 78g greater than the outside diameter of the hub 12g substantially circular, so as to form a play of movement for the intermediate ring 76g. In addition, the intermediate ring 76g has two driving recesses 80g which are also arranged at an angular distance of 180 and in which the driving projections 74g respectively engage, so that the intermediate disc 76g is movable towards the up and down from the

  12g hub in the illustration in Figure 15.

  The intermediate disc 76g has on its outer surface two other driving recesses 82g offset by 90 relative to the driving recesses 80g, in which engage driving projections 84g of the driving disc 18g, so that the disc 18g coach is movable relative to the intermediate disc 76g in the direction from right to left or vice versa. This is also possible because the driving disc 18g has an inside diameter greater than the outside diameter of the intermediate disc 76g. Thanks to the overlap of these two movement movements, any radial movement of the friction linings 26g, which are in turn coupled to the driving disc 18g,

  is possible compared to the 12g hub.

  It can be seen that the connection zone between the driving disc 18g and the hub 12g is radially very far inside, so that the available structural space can be optimally exploited. It should be noted, however, that the surface pressures which occur due to small action radii in the area of the driving projections in engagement with the driving recesses become very large. For axial fixing, it is possible, for example, to vulcanize an elastomeric material which keeps the moving parts in axial direction with respect to each other and which simultaneously ensures a

  recall effect in a centering position.

  In the embodiment according to FIGS. 16 and 17, the connection is offset slightly radially outwards, so that the surface pressure which occurs can be reduced in the region of the projections in engagement in the recesses. The axial fixing is carried out here by elements of leaf spring 86g which are riveted on the intermediate disc 76g, as seen in Figure 18, and which are supported by free end zones respectively against the driving disc 1 8g and against the hub disc 1 2g. Preferably, such leaf spring elements are provided on the two axial sides, so as to obtain axial retention and centering in the two directions. In addition, these springs 86g provide a return torque when nutation movements appear. To facilitate these nutation movements, each of the projections 74g and 84g has a curved structure or surface to allow the individual components to pivot relative to each other, as is

see in Figure 19.

  It can also be seen in FIG. 16 that several through openings 88g are provided in the hub 12g which allow the respective passage of screws and tools. Thanks to this, the mounting of the structural unit formed by the two-mass flywheel is simplified, by the

  pressure plate and by the clutch disc.

  FIG. 20 shows an embodiment corresponding to the embodiments described above, in which it is not individual projections and recesses which provide the peripheral drive and the radial mobility respectively, but 90h and 92h engagement arrangements produced in the form teeth and additionally provided on both sides of individual projections 74h, 84h or recesses 80h, 82, thanks to which the surface pressure can be further reduced. What is important is that the toothing arrangements 90h and 92h are oriented respectively so that they do not hinder free mobility in the direction of the arrows P1 and P2. Due to the eccentric arrangement of the additional teeth, a radial force component is produced from the peripheral force of the torque. This force must be compensated for by the strength of the individual components, because otherwise deformation can

  occur and the 76h intermediate disc may be stuck.

  The teeth 90h, 92h can also be provided without the projections

74h and 84h.

  Another modification is shown in FIG. 21 in which not only respective individual projections 74i and 84i and associated recesses 80i and 82i are provided, but several such respective projections 74i and 84i. Correspondingly, the number of recesses 82i and 80i is also increased. In this way, we can reduce the

surface pressure.

  It will be noted that the illustrated positioning position of the projections and recesses is done as desired. Thus, it is possible for example to form on the intermediate ring respective projections and on the other components of the respective recesses, or else it is possible to provide on the intermediate ring projections radially inside and recesses radially outside and Conversely; we see this in

  the embodiment according to FIG. 21.

  Figure 22 shows another embodiment of a clutch disc 10k according to the invention. In the clutch disc k, the driving disc 18k is divided into two, that is to say that it comprises two disc parts 94k and 96k which are connected to each other in their radially outer zones by 98k studs with interposition of packing springs or a 36k packing holder. Radially inside, the two disk parts 94k, 96k are at an axial distance and they receive between them a hub flange 98k which is integrally connected in rotation to the hub 12k, for example welded thereon. The hub flange 98k has several lO openings 100k distributed in the peripheral direction which are crossed by the studs 102k firmly connecting the two disk parts 96k, 94k radially inside. In particular, the diameter of the openings k is greater than the outside diameter of the studs 102k in the area located in the openings 100k. In addition, a layer of elastomeric material 104k has been arranged between the hub flange 98k and the disk portion 94k which is held under prestress by the studs 102k. When nutation movements or an axial offset of low value appear, the driving disc 18k can move by a small value compared to the hub 12k by elastic deformation of the elastomer layer 104k, thanks to the mobility of the studs 102k in the openings 100k. When these movements become stronger, the state of friction adhesion is overcome and the driving disc 18k can move more with a sliding movement of the elastomer layer 104k from the hub flange 100k. During the transmission of very strong torques, the studs 102k come to bear against the peripheral wall of the openings 104k, so that in this state, a direct transmission of the torque is ensured by omitting the elastomeric material and can avoid excessive loading in this area. Since there is no movement play in this region, but a prestress is always generated due to the 104k elastomeric material, we avoid

clicking noises.

  Although this is not illustrated in FIG. 22, it is of course also possible to arrange an elastomer layer on both sides, that is to say also between the disc portion 96k and the hub flange 98k. In addition, it is possible to make the 12k hub in one

  single piece with 98k hub flange.

  Due to the articulation point located very far inside, a low stiffness 10k clutch disc can be produced here, and the stiffness can be influenced by the thickness and the shape of the individual disc parts. or by the choice of the elastomeric material. In addition, a practically symmetrical structure has been produced in the axial direction, which results in a regular load of the different

components.

  FIG. 23 shows another embodiment of the clutch disc 101 according to the invention which is illustrated here in association with a two-mass flywheel 1061 of known structure. The clutch disc 101 shown here also in connection with the input shaft 1081 of the gearbox in turn comprises a driving disc 181 which has on an cylindrical section located radially inside an internal toothing 461 in mesh with the external toothing 441 of the hub 121 by providing a play of radial and peripheral movement 481. There is also provided a torsional oscillation damper 1 101. This comprises a flange 1 121 which is firmly connected to the hub 121 and which is surrounded on its axial sides on the one hand by the driving disc 181 and on the other hand by a cover disc part 1141 secured thereto. There are provided in the flange 1 1 21, in the driving disc 181, and in the cover disc part 1141 of the respective spring windows having control edges 1 161, 1 181, 1201 for the springs 1221 of an arrangement with damping spring, the springs 1221 extending in a manner known per se approximately in the peripheral direction. The torsional oscillation damper 1 101 can be an idle damper which allows, when applying low torques, relative mobility between the driving disc 181 and the hub 121 of a predetermined value by compressing the springs 1221. To also allow the radial mobility or the pivoting of the driving disc 181 relative to the hub 121, the following measures can be taken: 1. The control edges 1161, 1201 of the driving disc 181 or of the disc part of cover 1 141 have, in their direction of approximately radial extension, a length such that the springs 1221 can move along these control edges 1 161 or 1201, when a relative movement between the driving disc 181 and the hub 121 appears, and they are fixed for example on the edge

1181.

  2. The control edge 1181 has in the direction of its approximately radial extension a length such that the springs 1221 can move along this control edge

  1,181 when the relative movement mentioned appears.

  3. Both the control edges 1 161 and the control edges 1201 have a length in their direction of extension such that the springs 1221 can move along the latter in the radial direction or approximately in the radial direction, when the drive disc 1 181 moves in the radial direction or in the direction

  a pivoting movement relative to the hub 121.

  We see that it is not necessary to provide other additional components to allow this radial displacement or the nutation movement. This is made possible by the mere production of the respective control edges of the oscillation damper of

twist 1101.

  The illustrated embodiment is advantageous in particular because thanks to it, the relative movements mentioned may appear or are possible in the range of small loads or low torques. Particularly in this range of low torques, such movements are to be expected. For higher torques, the clutch disc generally centers itself, or the friction forces which appear

  are so high that a relative movement cannot appear.

  Consequently, in particular in this critical range of low torques, it is possible to exclude or at least significantly reduce the appearance of wear on the various components. Similarly, thanks to an appropriate design of the characteristic curve of the shock absorber, it is possible to avoid or at least significantly reduce a

  clicking of the gearbox at idle.

  Figures 24 and 25 show a modification in which the torsional oscillation damper 110 Om is no longer in the radially inner zone, but in the radially outer zone and in which it is further integrated directly in the axial zone of the 18m drive disc or 112m hub flange. The hub flange 112m has an external toothing 124m with which an internal toothing of the driving disc 18m meshes, so that a play of movement is possible both in the radial direction and in the peripheral direction. We can see this in particular in the illustration of figure 25. In this case, we can say that the parts

  18m and 112m form a driving disc divided in two.

  The springs 122m of the torsional oscillation damper 110m are arranged in the peripheral direction between two respective teeth 128m of the teeth 126m or else they are clamped between these teeth. In this region, no teeth of the external teeth have been provided on the hub or on the 112m hub flange. For the support against the teeth 130m of the external toothing 124m, there is provided a driving element 132m which has a symmetrical structure in the axial direction, FIG. 25 showing only the elements located on an axial side. The drive element 132m comprises, on the two sides of the springs 122m, drive lugs 134m in the form of a funnel which bear against the springs 122m on both sides of the drive disc 18m and which are further supported by lugs axially curved (not shown) against the teeth 130m of the external teeth 124m. The drive lugs 134m are connected by a connecting bar 136m which extends radially inside the springs 122. When a relative rotation occurs between the hub flange 11 2m and the drive disc 18m, the springs 122m come lean by one of their end zones directly against a tooth 128m of the internal toothing 126m and by their other end zone against a tooth 130m of the external toothing 124m via the drive lugs

  associated 134m from the driving element 132m.

  Thanks to this embodiment, it also ensures relative mobility in the radial direction and a nutation movement, and to facilitate this movement the individual teeth can be produced with a

  domed shape of the teeth 128m or 130m.

  In addition, centering springs 140m, 142m are provided on the 18m discs, which center these axially with respect to the hub flange 112m. The embodiment shown in FIGS. 24 and 25 is advantageous in particular when there is only a small structural space, in particular when it is necessary to provide through openings in the interior area of the clutch disc, with through which we must thread the 138m screws visible in figure 24 by which we screw

  a flywheel on a crankshaft.

  Figure 26 shows another embodiment of a clutch disc 1 On according to the invention. The driving disc 18n and the hub 12n are in engagement via respective teeth 46n and 44n, a play of peripheral movement and a play of radial movement being provided between these teeth, as described above. The cover discs 150n, 152n are firmly connected to the hub 12n and they have respective windows comprising control edges or support zones 154n, 156n. In association with these openings, the driving disc 18n has an opening 162n which also respectively forms control edges 116n and support zones. A respective elastic element 158n is associated with each group of control edges or support zones 154n, 158n 116n, that is to say the openings forming these zones, which allows, thanks to its elastic deformation, a movement relative device between the driving disc 18n and the cover discs 150On, 152n and thus the hub 12n, and thanks to its elasticity, it allows radial mobility of the driving disc 18n relative to the hub 12n or else a

  pivoting in the direction of a nutation movement.

  The elastic elements 158n can be formed for example by springs which extend approximately in the peripheral direction, and provision can be made, as mentioned above, for a certain mobility in the radial direction in the region of the respective control edges 154n, 156n, 116n, or else the elastic elements 158n may be bodies, for example massive bodies made of rubber or another elastically deformable material. It is, for example, possible to produce the elastic elements 158n in spherical form and to produce in correspondence the bearing zones 154n, 156n by spherical or cap-shaped surfaces, on which the respective spherical elements 158n are held as well. in peripheral direction than in radial direction. As illustrated in FIG. 26, relative mobility can also be facilitated here by providing a certain interval between the elements elastically.

  deformable 158n and support areas.

  The illustrated embodiment acts as a damper for torsional oscillations, in particular in a load range up to approximately Nm in the peripheral direction, which can compensate for axial offsets and which also allows nutation movements. This is a load range that appears in idle operation and also in partial load operation. For higher rotational torques, a rotary coupling in cooperation of shapes takes place in the peripheral direction through the teeth 44n, 46n. The relative mobility between the teeth 44n, 46n in the axial direction and in the radial direction remains maintained due to the play of movement always provided in these directions. This ultimately means that even when the torsional oscillation damper 1 1 On is covered by the teeth 44n, 46n in mutual support, compensation for the axial offset by nutation movements is still possible. Since the teeth 44n, 46n in mutual support are in this case highly loaded, it is advantageous to inductively harden at least the teeth 44n on the hub or to treat it in another way to protect it against wear, coat it

  for example a layer of material promoting sliding.

  It can also be seen in FIG. 26 that a friction device 160n is provided, comprising respective friction elements on the two sides of the driving disc 18n and a prestressing spring; when

  this 160n friction device is provided, it must be ensured that it

  it does not hamper radial mobility or nutation movements. Thanks to an appropriate choice of several elastically deformable elements which are arranged in successive distribution in the peripheral direction, it is possible to provide a characteristic curve with several stages of this torsional oscillation damper 1 10 On, said curve also containing a range of Idle damping. However, it is also possible to configure the elastically deformable elements of

  so as to provide only an idle damping function.

  Instead of the spherical shape mentioned, it is also possible to provide cylindrical shapes for the individual elastic bodies or to produce several elastic bodies with

  different shapes arranged in distribution in the peripheral direction.

  It will be noted that the embodiment illustrated in FIG. 26 can be achieved by a corresponding choice of the elasticity of the elements 158n substantially for the sole function allowing nutation movements or compensation for an axial offset, without providing for

  supplement a damping function for torsional oscillations.

  It will be noted that in the torsional oscillation dampers illustrated, it is possible to use different types of springs, so as to obtain a damping function in steps. In addition, a friction device can be provided which assists the damping during the appearance

  of a relative movement, in particular of a relative rotation.

  Figures 26a and 26b show a modification of the embodiment illustrated in Figure 26. While in the embodiment according to Figure 26, the two cover discs 150n and 152n are firmly connected to the hub 12n for example by matting, we provides in the embodiment according to Figures 26a and 26b that the two cover discs 150n, 152n have in their radially inner zone a respective toothed configuration 190n, 192n which is complementary to the teeth 44n of the hub 12n. This means that the teeth 190n, 192n mesh with the teeth 44n substantially without play both in the radial direction and in the peripheral direction. In the region of the teeth 44n is provided on the hub 12n a radial step or a radially projecting area 194n against which the two cover discs 150n, 152n abut at their teeth 190n, 192n. This means that the projecting area 194n is held axially between the two cover discs 150n, 152n. In the radially outer zone, the cover discs n, 152n are firmly connected to each other by riveting studs 102n or the like which pass through corresponding openings 196n in the drive disc 18n. It is therefore here that the force cooperation of the two cover discs i150n, 152n takes place, maintaining between them the projecting area 194n, and thus the axial fixing relative to the hub 12n of the structural group formed by the cover discs. 150n, 152n. This type of axial fixing of the cover discs 150n, 152n on the hub 12n has a less loaded construction compared to the embodiment according to FIG. 26 which represents a low-cost solution, in particular when nutation movements appear, because the force cooperation between the two cover discs 150n, 152n takes place in their radially outer zone, as described

  before. This is very advantageous for the solidity of such a connection.

  In addition, FIG. 26a shows the friction device 160n with the two friction rings 198n, 200n which bear against the driving disc 18n, a prestressing element, for example in the form of a spring washer 202n, acting between the cover disc n and the friction ring 198. It will again be noted that any kind of friction device can be used here. In the radially outer zone, the friction linings 26n are supported by riveting again on the lining carriers, such as for example lining springs 36n. These lining carriers or lining springs 36n are firmly connected to the driving disc 18n by a

plurality of studs 204n.

  Furthermore, it can be seen in FIGS. 26a and 26b that springs 158n are used here as elastic elements which bear in peripheral direction against the respective control edges 154n, 156n, 116n of the cover discs 150n, 152n or of the 18n drive disc. It will be noted that a multi-stage damper can also be produced here by associating with each group of control edges 154n, 116, 156n several successive springs 158n in the peripheral direction which can then have different elastic characteristics, so that this first of all are the softer springs which are compressed for example to form an idling damping function, and then, when these are compressed entirely or practically entirely, it is the harder springs which start to act. For this purpose, it is possible to provide, between the successive springs in the peripheral direction, a respective support or sliding element which can slide, for example, from an inner peripheral surface of the driving disc 18n in the peripheral direction. The control edges 154n, 156n, 116n are produced so as to allow at least a slight radial and / or axial movement of the elastic elements 158n along these control edges when nutation movements appear. Since the teeth 44n, 46n bear against each other from a load of about 50 Nm in this embodiment also, and that the compensation of nutation movements, thanks to sliding surfaces the teeth 46n, 44n on each other is always possible in axial and radial direction, it is also advantageous here to harden at least the hub 12n in the region of its teeth 44n, for example by inductive hardening, or else put it on

  protection against wear, for example a sliding layer.

  Another embodiment of the clutch disc 10o in accordance with the invention is illustrated in FIG. 27. In this clutch disc also, the friction linings 260 are connected integrally in rotation to a driving disc 18o radially to the outside by means of a lining holder 360, if necessary with interposition of a lining suspension or with lining springs. The transmission of the torque between the driving disc 180 and the hub 12o of the clutch disc 10Oo is ensured here by a coupling bellows 170o. The coupling bellows 1700 surrounds the axis of rotation A approximately concentrically and it is firmly connected to the hub 12o in a first end region 172o for example in an area of a radial shoulder 174o of the hub 12o, for example by welding or similar. In its second axial end zone 1760, the coupling bellows 1700 is firmly connected to the driving disc 18o by welding. In this case, the coupling bellows 1700 forms in its two axial end zones 1720, 1760 respective cylindrical end sections, the cylindrical end section provided in the first axial end zone 172o being adjusted on a outer peripheral surface of the hub 12o, and the cylindrical end section of the coupling bellows 170o, which is provided in the second axial end zone 176o, engages in a central opening of the driving disc 180, so that the driving disc 180 rests by its inner peripheral surface on this end zone of the bellows

coupling 1700.

  Thanks to the coupling bellows 170o which has two folds 178o in the illustrated embodiment, an axial offset for example between an input shaft of the gearbox and a drive shaft of an engine is easy to compensate without that any stresses occur, when the clutch is engaged, that is to say when the friction linings 26o are wedged between a flywheel and a pressing plate. In particular when the coupling bellows o is produced in the form of a metal bellows, in addition to the high capacity with respect to the transmission of the torque, a low self-weight is ensured in the region of this bellows d 170o coupling, an elastic coupling in radial and axial direction practically

* without fatigue of the friction linings 260 on the hub 120.

  Of course, the coupling of the coupling bellows 170o with the hub 120 and / or with the driving disc 180 can be done in another way than by welding. For example, one could imagine providing the coupling bellows 170o and correspondingly the components 12o and 180 to be coupled thereto with a respective section without symmetry of revolution in the respective end zones 172o, 176o, so to establish an attack by cooperation of forces in the peripheral direction of the different components. Of course, the coupling bellows can comprise more than two folds which are illustrated or, where appropriate, also a single fold 1780. The coupling bellows 1700 and the hub 12o can be coupled with the interposition of a driving element. , just like the coupling of the bellows 1700 with the friction linings 760. It can be seen that it is possible to combine the use of a coupling bellows, as illustrated in FIG. 27, with other embodiments described. previously which provide elastic coupling in axial and radial direction

  friction linings at the hub.

  It is also possible to establish the connection between the friction linings 260 and the hub 12o by several bellows 170o arranged staggered, which are coupled to each other for example in their end zones, if necessary with interposition of elements connecting, and which may have, where appropriate, different dimensions in the radial direction and in the axial direction or also different bellows configurations. In this case, one end of each bellows is always provided for coupling to the hub, if necessary with the interposition of at least one other bellows, and another end of the bellows is provided for coupling to the linings of

  friction, if necessary with the interposition of at least one other bellows.

  In the foregoing, embodiments of clutch discs have been described which can compensate for axial offsets possibly present during the operation of a drive system between the input shaft of the gearbox and the crankshaft. , and which allow nutation movements generated because of an irregular rotation of at least one of these trees or because of an orientation of these trees which is not exactly parallel. We have shown different concepts which include on the one hand the elastic deformability of different components and on the other hand the relative mobility of individual components compared to others, being able to choose the respective concept in adaptation to loads and

  requirements that arise during operation.

  It should also be noted that the measures indicated to compensate for an axial offset or to allow the nutation movement can

  also be applied to a two mass flywheel.

Claims (32)

Claims   1. Clutch disc for a friction clutch of a motor vehicle, comprising - a hub (12) capable of being coupled integrally in rotation to an input shaft of the gearbox,   - friction linings (26) arranged in an outer radial zone   of the clutch disc (10), the friction linings (26) being at least partially substantially parallel to or in a plane substantially orthogonal to an axis of rotation (A) of the hub (12), and - an arrangement link (18) by which the friction linings (26) of the clutch disc (10) are connected to the hub (12) so that the friction linings (26) can perform a radial movement relative to the axis of rotation (A) of the hub and / or a pivoting movement relative to the plane, characterized in that the connection arrangement comprises a driving disc (18) which is coupled substantially in rotation on the one hand to the hub ( 12) and on the other hand to the friction linings (26) and which comprises in a region radially between the coupling to the hub (12) or to the friction linings (26) at least one deformation zone (30) which   extends in the axial direction or is bent in the axial direction.   2. Clutch disc according to claim 1, characterized in the deformation zone (30) comprises a plurality of flexion zones (32) defining a contour which extends radially from the inside towards   the outside in the form of meanders in the axial direction.   3. Clutch disc according to either of claims 1 and 2,   characterized in that the driving disc (18) has a radially inner annular region (20) for coupling to the hub (12), a radially outer annular region (22) for coupling to the friction linings (26) as well as '' a plurality of connecting sections (24), and in that the deformation zone (30) is   provided respectively in the region of the connecting sections (24).   4. Clutch disc according to either of claims 1 and 2,   characterized in that the disc (18) is a piece substantially   completely closed, made like a membrane.   5. Clutch disc according to claim 3, characterized in that   the connecting sections (24) extend substantially radially.   6. Clutch disc according to the preamble of claim 1 or according to the preamble of claim 1 in association with the   Characteristics of at least one of claims 1 to 3, in which   the connection arrangement comprises a disc portion (18a; 18b) having a radially inner annular segment (20a; 20b), a radially outer annular segment (22a; 22b) and a plurality of connecting sections (24a; 24b, 40b ), the connecting sections (24a; 24b, b) extending in curved form radially from the inside   outwards and in at least one peripheral direction.   7. Clutch disc according to claim 6, characterized in that the connecting sections (24a; 24b, 40b) extend approximately in the shape of an S. 8. Clutch disc according to the preamble of claim 1, wherein the connecting device comprises a driving disc (18c) which is coupled radially outside to the friction linings (26c) and which has radially inside an internal toothing (46c) meshing with an external toothing (44c) on the hub (12c) providing for a play of radial movement, and further comprising a centering spring arrangement (50c) by which the driving disc (18c) is resiliently centered with respect to the hub (12c), characterized in that the centering spring arrangement (50c) comprises at least one section of centering spring (56c) made at an angle, which bears against an external peripheral surface (42c) of the hub (12c).   9. Clutch disc according to claim 8, characterized in that said at least one section of centering spring (56c) produced at right angles is constituted by at least one spring element (50c) produced substantially in annular shape which comprises in an inner peripheral zone a plurality of elastic tabs (56c) bent in the direction of the axis of rotation (A) of the hub to come   resting against the outer surface (42c) of the hub (12c).   10. Clutch disc according to claim 9, characterized in that said at least one spring element (50c) comprises at least one axial locking projection (58c) which bears axially against a radial projection of the hub (12c) , preferably in the area of the teeth exterior (44c).   11. Clutch disc according to either of claims 9   and 10, characterized in that a respective spring element (50c) is   arranged on the two axial sides of the driving disc (18c).   12. Clutch disc according to either of claims 9   and 10, characterized in that said at least one spring element (60e; 60f) is produced integrally with the driving disc (18e; 18f) and forms a radially inner zone (60e; 60f) thereof. 13. Clutch disc according to the preamble of claim 8, characterized in that the centering spring arrangement (50d), fixed on a component among the hub (12d) and the driving disc (18d), comprises at least a spring element (50d) which engages by at least one elastic tab (56d) axially in a gap (48d) formed between the internal toothing (46d) and the external toothing (44d) and   which is supported under pretension against the other component.   14. Clutch disc according to claim 13, characterized in that on each side of said component (18d) is arranged a spring element (50d), and in that the spring elements (50d) engage alternately from the two axial sides in a respective interval   (48d) between the outer toothing (44d) and the inner toothing (46d).   15. Clutch disc according to either of claims 13   and 14, characterized in that said at least one spring element (50d) comprises at least one axial locking section (58d) which protrudes radially inwards and which bears axially against the hub   (12d), preferably against the external toothing (44d) thereof.   16. Clutch disc according to the preamble of claim 1, characterized in that the connection arrangement comprises: - an intermediate disc (76g) which is coupled to the hub (12g) for a common rotation and which is movable relative to the hub (12g) in a first direction of movement substantially radially to the axis of rotation (A) of the hub, - a driving disc (18g) which is coupled on the one hand to the friction linings (26g) and on the other part to the intermediate disc (76g) for a common rotation, and which is movable relative to the intermediate disc (76g) in a second direction of movement substantially radially to the axis of rotation (A) of the hub, the first direction of movement and the second direction of movement being   different directions of travel.   17. Clutch disc according to claim 16, characterized in that the first direction of movement and the second direction of   displacement are substantially orthogonal to each other.   18. Clutch disc according to either of claims 16   and 17, comprising: - at least a first drive projection (74g) which extends substantially radially over a component among the hub (12g) and the intermediate ring (76g), and a first drive recess (80g ) associated with each first drive projection (74g) on the other component among the hub (12g) and the intermediate ring (76g) and extending substantially radially and receiving the first associated drive projection (74g) with radial movement play, and - at least a second drive projection (84g) which extends substantially radially over one component from the intermediate disc (76g) and the drive disc (18g), and a second drive recess (82g) associated with each second drive projection (84g) on the other component from the intermediate disc (76g) and the drive disc (18g) and extending substantially radially and receiving the second associated drive projection (84g ) with movement game t radial. 19. Clutch disc according to claim 18, characterized in that said at least one first drive projection (74g) and said at least one second drive projection (84g) are offset one   relative to each other by about 90 in the peripheral direction.   20. Clutch disc according to the preamble of claim 1, characterized in that the connection arrangement comprises: - on the hub (12k) a hub flange (98k) projecting radially and connected in rotation to the latter , - a driving disc (18k) which is coupled radially outside to the friction linings (26k) and which comprises radially inside two connecting sections (94k, 96k), a respective connecting section (94k, 96k ) being provided at least locally on an axial side of the hub flange (98k), - a plurality of connecting studs (102k) by which the connecting sections (94k, 96k) are each connected to the hub flange (98k) ) for a common rotation, but which allow a relative radial movement and a relative peripheral movement of a predetermined value between the connecting sections (94k, 96k) on the one hand and the hub flange (98k) on the other hand, and - an elastically deformable arrangement (104k), of pr ference an elastomeric material layer (104k), received under prestress between at least one of the connecting sections (94k, 96k) and the hub flange (98k). 21. Clutch disc according to claim 20, characterized in that the connecting studs (102k) are fixed relative to one of the structural groups among the connecting sections (94k, 96k) and the hub flange (98k ) and mobile in radial and peripheral direction by   compared to the other respective structural group.   22. Clutch disc according to either of claims 20   and21, characterized in that it is provided, between the two connecting sections (94k, 96k) and the respectively associated axial side of the flange   hub (98k), an elastically deformable arrangement (104k).   23. Clutch disc according to the preamble of claim 1, characterized in that the connection arrangement comprises a torsional oscillation damper (1101; 110 mm; 11 On) arranged in the torque transmission path between the hub (121; 12m; 12n) and the friction linings (261; 26n), said damper having an inlet side and an outlet side, the inlet side and the outlet side being movable relative to each other to the other in the radial and / or axial direction, and / or at least one of the inlet and outlet sides being capable of pivoting   with respect to the plane (E) and with respect to the other side.   24. Clutch disc according to claim 23, characterized in that the connection arrangement comprises: - a driving disc (181, 1141) received by an internal toothing (461) with radial movement play and with peripheral movement play on an external toothing (441) of the hub (121), - a hub flange (1121) of the torsional oscillation damper, coupled in rotation with the hub (121), - a spring arrangement comprising at least one spring (1221) which extends approximately in the peripheral direction and which bears in its end regions against respective control edges (1161, 1181, 1201) on the one hand of the hub flange (1121) of the '' torsional oscillation damper and on the other hand of the driving disc (181, 1141), said at least one spring (1221) being movable, in the support zone against the respective control edge (1161, 1201) of the driving disc (181, 1141) and / or in the support area against the control edge respective (1181) of the hub flange (1121) of the torsional oscillation damper, with respect to the respective control edge (1161, 1181, 1201) at least in the direction of approximately radial extension of the control edge associated (1161, 1181, 1201).   25. Clutch disc according to claim 23, characterized in that the connection arrangement comprises a driving disc comprising a radially outer disc part (18m) and a radially inner disc part (112m), the radially disc part outer (18m) having an inner toothing (128m) which meshes with an outer toothing (124m) on the radially inner disc part (112m) with relative movement clearance in the radial direction and in the peripheral direction, and in that the damper torsional oscillation (11 Om) comprises a spring arrangement having at least one spring (122m) arranged in the area of the meshing teeth (124m, 128m), which can come to rest in its end areas of on the one hand against the external toothing (126m) and on the other hand against the interior teeth (124m).   26. Clutch disc according to claim 25, characterized in that the torsional oscillation damper (1 1 Om) is arranged in the   radially outer zone of the driving disc.   27. Clutch disc according to any one of claims 23   to 26, characterized in that the radial mobility and / or the mobility in nutation is made possible by elastic deformation of a coupling arrangement (158n) which couples the input side and the outlet side.   28. Clutch disc according to any one of claims 23   27, characterized in that the entry side comprises a driving disc (18n) with internal teeth (46n), and in that the exit side comprises cover discs (150n, 152n) arranged on both sides of the disc drive, which are connected in rotation to the hub (12n), the hub (12n) having teeth   outer (44n) associated with the inner toothing (46n).   29. Clutch disc according to claim 28, characterized in that the internal toothing (46n) of the driving disc (18n) and the external toothing (44n) of the hub (12n) are matched to each other, of such that the driving disc (18n) and the hub (12n) are movable relative to each other in the peripheral direction, in the radial direction and in axial direction.   30. Clutch disc according to the preamble of claim 1 or   according to any one of claims 1 to 29, characterized in that   the connecting arrangement includes a coupling arrangement to bellows (1700).   31. Clutch disc according to claim 30, characterized in that the bellows coupling arrangement (1700) comprises at least one coupling bellows (170o) which extends substantially in the direction of the axis of rotation. (A) of the hub and which is coupled in a first end region (172o) to the hub (120) and in a   second end zone (1760) to the friction linings (260).   32. Clutch disc according to either of claims 30 and   31, characterized in that the bellows coupling arrangement   (1700) includes a metal coupling bellows (1700).