WO2019200418A1

WO2019200418A1 - Clutch disk

Info

Publication number: WO2019200418A1
Application number: PCT/AT2019/060126
Authority: WO
Inventors: Stefan Astecker; Stefan Gaigg
Original assignee: Miba Frictec Gmbh
Priority date: 2018-04-16
Filing date: 2019-04-15
Publication date: 2019-10-24
Also published as: DE112019001963A5; CN111989504B; AT521020A4; CN111989504A; AT521020B1

Abstract

The invention relates to a clutch disk (1) for a friction clutch, comprising a plurality of wing-like friction assemblies (8) distributed over the circumference, wherein: - the friction assemblies (8) each have a first friction lining (10) and a second friction lining (11); - the first friction linings (10) are arranged on first friction lining carriers (12) and the second friction linings (11) are arranged on second friction lining carriers (13); and - furthermore at least one spring element (14) is arranged between each pair of the first and second friction lining carriers (12, 13). A stop element (15) is arranged between each pair of the first and second friction lining carriers (12, 13), on which stop element the at least one spring element (14) is supported and/or in which stop element the at least one spring element is partially accommodated and to which stop element the first and second friction lining carriers (12, 13) are connected or fastened, the stop elements (15) also being connected to a carrier element (5). The first friction lining carriers (12) are connected to the stop elements (15) exclusively by means of one connecting element (23) each, and the spring elements (14) are preferably designed as Belleville springs.

Description

clutch disc

The invention relates to a clutch disc for a friction clutch, comprising a disc-shaped base body with a support member, wherein the support member has an externa ßeren circumference, distributed over the receiving areas for wing-like friction modules are arranged, wherein the friction assemblies are connected to the carrier element, wherein the Reibbaugruppen each having a first friction lining and a second friction lining, wherein the first friction linings on the first friction lining carriers and the second Reibbe läge are arranged on second Reibbelagsträgem, and wherein further depending at least one Fe derelement between the first and the second friction lining carriers is arranged.

Numerous embodiments have already been described in the prior art for clutch plates with friction linings.

Thus, e.g. DE 29 20 095 Al a friction lining, in particular for metalli cal or metal-ceramic friction linings, of motor vehicle clutch discs consisting, inter alia, held in versions friction linings, which are arranged in pairs against each other on resilient lining carriers, with two identical lining carrier mutually, with their convex convex facing each other, are arranged, and each of the friction lining is connected with its version via at least two mounting rivets with its associated lining carrier and all mounting rivets of the two gegenüberlie ing lining carrier are distributed over the existing area that against a Sym metrielinie particular the pad carrier is a symmetrical distribution, without mutual overlap. Each lining carrier has corresponding apertures in the region of the projection of the fastening rivets of the opposite lining carrier. Next, the versions of the friction linings also congruent with the Belagträgem perforations. Between the two Belagträgem on the line of symmetry at least one distance rivet for biasing the lining carrier is arranged.

The arrangement of the friction linings on resilient lining carriers takes place mainly therefore, so that the metallic or metal-ceramic friction linings when engaging no blows or _

Experience shocks, whereby these friction linings erlei premature damage erlei. Such metallic hzw. In contrast to other friction linings, for example made of resin-bonded fibers, metal-ceramic friction linings are significantly less elastic. On the other hand, these metallic or metal-ceramic friction linings offer the advantage over other friction linings that higher torques can be transmitted. But with the resilient arrangement of the friction linings can also be achieved that the metering of the clutch can be improved when Einkuppein.

From WO 2015/024039 Al a clutch disc for a friction clutch is known, comprising a disc-shaped base body with a support member, wherein the Trä gerelement has an outer circumference, distributed over the receiving areas for wing-like friction assemblies are arranged, wherein the Reibbaugruppen ment with the Trägerele are connected, wherein the friction assemblies each having a first friction lining and a second friction lining wx> are arranged on the first friction linings on first friction lining carriers, the first Reibbelagsträger are connected to a spring element and the Fe derelemente are connected to the carrier element, and wherein the second friction linings are arranged on second friction lining carriers, and wherein further the spring elements between the first and the second friction lining carriers are arranged. The second friction lining carriers are connected directly to the carrier element.

The present invention has for its object to improve a clutch disc of the type mentioned, in particular to simplify their structure.

The object of the invention is ge in the above-mentioned clutch disc triggers that is arranged between the first and second friction lining carriers depending on a stop element, on which the spring elements are supported and / or in which the spring elements are partially received, and with the are connected to the first and second friction lining carrier or connected thereto, and further connected to the carrier element, further that the first friction lining are exclusively connected via a respective connecting element with the stop elements and that the spring elements are preferably formed as a plate springs. The advantage here is that so that the structure of the friction assemblies can be structurally simplified. Along with this, the mass of the friction assemblies and thus the overall weight of the clutch disc can be reduced. In addition, the reduction of the different individual parts of the friction assemblies can reduce the sources of error in the production process of the coupling slide. Compared to versions of clutch plates with two spring plates on which the friction lining carriers are mounted, Kings the attacks can be designed as a simple standard sheet metal elements. By avoiding spring plates, and the preferred use of disc springs, the support of the first friction linings in the compressed state, ie in the coupled state of the clutch disc, can be improved. Thus, in turn, the usable friction volume of the friction linings can be increased, since a more uniform wear of the first friction linings is made possible by the improved contact of the first friction linings in the sprung state. In addition, with the embodiment of the spring elements as plate springs, the desired spring force can be more easily adapted to the respective application in comparison to spring plates.

To further improve the above effects and advantages of the clutch disc can be provided for variants of the clutch disc that the second friction pad are connected exclusively via a respective connecting element with the Anschlagele element and / or that between the second friction lining and the stop elements also spring elements, in particular plate springs , are arranged.

A simpler assembly and disassembly of the friction linings can be achieved if, according to a further embodiment of the clutch disc, the first and the second Reibbe- lagsträger verbun via a common connecting element with the stop elements are the.

According to a preferred embodiment of the clutch disc can be provided to who, that the connecting elements with which the first friction lining with the stop elements are connected to each extending through an opening in the spring elements, in particular cup springs, extend therethrough. It is thus a flexible, pivotable position tion and suspension of the first friction linings with the first friction lining on the Anschla gelementen reachable. Thus, the compression can be improved when closing the clutch be, since a more even investment of the entire friction surface of the first friction linings can be achieved at the respective friction partners.

To further improve this effect of the flexible mounting of the friction linings of the hitch be disc can be provided disc according to a further preferred embodiment of the clutch, that also the connecting elements, with which the second friction lining carrier are connected to the stop elements, in each case by a breakthrough in the Spring elements, in particular disc springs, extend therethrough.

According to another embodiment of the clutch disc can be provided that the spring elements, in particular disc springs, which are arranged between the first Reibbelagsträgem and the stop elements, have a larger diameter than the Fe derelemente, in particular disc springs arranged between the second friction lining carriers and the stop elements are. It can thus be achieved that the spring elements, in particular disc springs, are supported in different areas of the stop elements, whereby the drag losses of the clutch equipped with the clutch disc can be reduced. It can thus be the adhesion of the friction linings to fixed hitch be halves avoided with the clutch open.

According to a further embodiment of the clutch disc can be provided that the second friction pad are rigidly connected to the stop elements, so that therefore only the first friction linings are spring-mounted. It is in this way easily possible to provide a clutch disc with a resilient and a rigid side.

To further increase the consumable wear volume may be provided according to a Ausfüh tion variant of the clutch disc, that the first and the second Reibbe bearing carrier in the region of the connecting elements for the connection of the first and the two th friction lining with the stop elements have a recess for receiving the connecting elements.

In order to reduce the flexible mounting of the friction linings to below a predeterminable extent or even in the case of the friction linings without spring elements, it is possible to avoid the friction lining. _ s _

Chen during engagement and thus a better investment to the friction partners ermögli chen can be provided according to a variant that the attacks each have a he-raised area extending in the direction of the second friction lining or in the direction of the first friction lining.

Zürn better understanding of the invention, this will be explained in more detail with reference to the following figures.

Each shows in a simplified, schematic representation:

Figure 1 is a clutch disc in a view in an oblique view from the front.

FIG. 2 shows a friction assembly of the clutch disk according to FIG. 1 in an exploded view and an oblique view; FIG.

3 shows a cross section through a wing-like friction assembly of the clutch disc of FIG. 1.

4 shows a detail of a variant of a clutch disc in Be tenansicht cut;

Fig. 5 cut a section of another embodiment of a clutch disc in side view

6 shows a variant of a clutch disc in an oblique view from the front.

Fig. 7, the support member of the clutch disc of FIG. 6 in an oblique view from the front

8 shows a friction lining carrier for the clutch disk according to FIG. 6 and the carrier element according to FIG. 7 in an oblique view from the rear. Introductoryly it should be noted that in the differently described embodiments, the same parts provided with the same reference numerals or the same component names who the, with the disclosures contained in the entire description mutatis mutandis to sliding surfaces with the same reference numerals or. transferred the same component names who can. Also, the position information selected in the description, such as above, un th, laterally, etc. related to the immediately described and illustrated figure and these position information in a change in position mutatis mutandis to transfer to the new location.

In Fig. 1, a first embodiment of a clutch plate 1 is shown for a known from the prior art friction clutch.

The clutch disc 1 substantially corresponds to those known in the art. Essentially, it is meant that - as will be explained in more detail below - differences in terms of the structure in relation to the frictional linings comprising Reibbaugruppen exist.

Accordingly, the clutch disc 1 a, in particular disk-shaped Grundkör by 2. On or in the main body 2 a plurality of torsion springs 3 are arranged. In addition, a recess 4 is centrally formed for receiving a shaft, not shown. Since this is known in principle from the prior art, reference is made to the relevant literature for details.

The base body 2 comprises a carrier element 5. The carrier element 5 is arranged at least in the region of an outer circumference 6 of the base body 2. Preferably, the carrier element 5 extends over the entire base body 2, that is, from the recess 4 to the outer circumference 6. The recess 4 is thus preferably (also) formed in the carrier element 5 from. Furthermore, the torsion springs 3 are preferably arranged in corresponding receptacles in the carrier element 5. However, the carrier element 5 can also be formed only ring element which is connected to the base body 2. On the other hand, the carrier element 5 may also be formed integrally with the base body 2.

There is also the possibility that on the carrier element 5 on both sides, in particular failed benförmige, cover (not shown) at least z ^. are arranged. Preferably, the carrier element 5 is made of a metal sheet, in particular a steel sheet.

It is further preferred if the carrier element 5 is formed in one piece, that is not composed of several parts.

On the outer circumference 6 of the carrier element 5 are distributed, in particular regularly distributed, a plurality of receiving areas 7 arranged to receive wing-like friction assemblies 8 or formed. In concrete in Fig. 1 shown example of the clutch disc 1 six receiving areas 7 and accordingly six friction assemblies 8 are present. However, this number should not be understood as limiting the invention. Rather, more or fewer receiving areas 7 and friction assemblies 8 may be present.

The friction assemblies 8 are verbun in the receiving areas 7 with the carrier element 5 to. For this purpose, 8 holes are preferably provided both in the receiving areas 7 and the Reibbaugrup pen, so that each of the friction assemblies 8 surfaces with the Aufnahmeberei 7 via a plurality of rivets 9, which extend through these holes are connected.

Instead of or in addition to the rivets 9, the fixation, i. the connection of the friction assemblies 8 with the receiving areas 7 of the carrier element 5 also takes place positively, for example by the receiving portion 7 facing end portion of the friction assembly 8, in particular a friction lining carrier, at least approximately 90 ° bent and inserted into a corresponding slot-shaped receptacle of the receiving area 7 is. However, the positive connection can also be formed, for example, by a dovetail-shaped design of the end region of the friction assemblies 8, which engage in correspondingly shaped recesses in the receiving regions 7.

In principle, other methods for connecting the friction assemblies 8 with the Trä gerelement 5 are possible, such as glands, welds, etc. Each of the friction assemblies 8 of the clutch disc 1 forms its own assembly. The friction assemblies 8 include or consist of, as is apparent from the exploded view in Fig. 2 and the cross section in Fig. 3, from a first friction lining 10, a second friction lining 11, a first friction lining support 12, a second friction lining support 13 and In the embodiment of the clutch disc 1 shown in FIGS. 1 to 3, two spring elements 14 are arranged, wherein a spring element 14 is assigned to the first Reibbelagsträger 12 and the second spring element 14 the second Reibbelagsträ ger 13.

Each friction assembly 8 has only one first friction lining 10 and only one second friction lining 11.

Preferably, all friction assemblies 8 of the clutch disc 1 are identical. The comments on the friction assembly 8 can therefore be transferred to all friction assemblies 8 of the clutch disc 1.

The first friction lining 10 is connected to the first friction lining carrier 12, preferably sintered on the sen. However, other connection methods can also be used. By way of example, the first friction lining 10 can be glued to the first friction lining carrier 12 or can be adhesively bonded thereto, for example soldered. In addition, there is also the possibility of riveting (or possibly screwing) of the first friction lining 10 with the first friction lining carrier 12. The same with regard to the connection methods applies to the second friction lining 11 and the second friction lining carrier 13 too.

Between the first friction lining support 12 and the second friction lining support 13 is a stop element 15 is arranged. The stop element 15 is in particular a sheet metal element, preferably made of a steel.

The stop element 15 has a plurality of openings 16 along an end face 16, via which the stop element 15 can be connected to the carrier element 5 in the manner described above, in particular riveted. This end face 16 is preferably concavely curved, since it preferably the partial region of the circumference 6 of the Trä gerelementes 5 nachformt, in which the stop element 15 is arranged on the carrier element 5.

Next, the stop element 15 has a spring element receptacle 17. This can be formed as a recess or as a break in the stop element 15. The Federele ment recording 17 is preferably so large that the two spring elements 14 can be partially absorbed therein and optionally on the stop element 15 from support zen. In the illustrated embodiment of the clutch disc 1, the Federele ment recording 17 has a diameter 18 which is greater than a (maximum) diameter 19 of the spring elements 14. The size of the diameter 18 he spring element receptacle 17 is because preferably in such a dimensioned that the two Spring elements 14 just fit into this through broke 16 and that they can be easily installed (inserted).

The two spring elements 14 are formed in the preferred Ausführangsvariante the clutch disc 1 as Telierfedem. They are in the passage 18 of the Anschlagele Mentes 15 gegengleich arranged such that they taper conically outwards in the direction of the first and second friction lining 12, 13, as can be seen from Fig. 2. Thus, the two disc springs in this embodiment of the clutch disc in the region of the largest diameter 18 (= outer diameter) in the spring element receptacle 17 to each other.

Instead of Telierfedem also differently shaped spring elements 14 can be used who the, for example, Evolutfedern, ring springs, etc. Preferably, spring elements 14 Kings, which are arranged around the circumference of the aperture 18 extending around Kings NEN. However, since the training as Tellerfern is the preferred, this embodiment will be described in more detail below. However, the versions can also be transferred to hitch be discs 1 with other spring elements 14.

The height of the spring elements 14 in the direction of the first friction lining support 12 and the second friction lining support 13 is preferably dimensioned so that they rest in any position on the spring elements 14, so both in the coupled and decoupled to stand. Although in Figs. 2 and 3 plate springs with circular shape (viewed in plan view) are provided, and this is also the preferred embodiment of the invention, Kings NEN also be shaped differently, such as square, etc. The Federelementauf measure 17 adapted to the specific shape of the disc springs accordingly.

In addition to the spring elements 14 designed as disc springs, the friction assembly 8 no longer has any further spring elements.

The first and the second friction lining carrier 12, 13 have at the back, ie at the Anschlage gelement 15 facing surface, at least one driver element 20 (in the figures, only arranged on the first friction lining 12 driver elements 20 are visible bar), located in Direction of the stop element 15 and in this in one of the cross-sectional shape of the driver element 20 corresponding recess 21 or breakthrough extends. Preferably, the first and the second friction lining carrier 12, 13 depending Weil two driver elements 20. These are preferably arranged diagonally offset from one another. With the help of these driver elements 20 a rotation for the ers th and the second friction lining 10, 11 is achieved. For this purpose, a height 22 of the driver 20 is dimensioned over the surface of the stop element 15 such that the Mitnehmerele elements 20 engage in any relative position of the first and second friction lining carrier 12, 13 to the stop element 15 in the corresponding recesses 21 and openings. In addition, a torque transmission can take place with the driver elements.

The driver elements 20 may be designed as bolts, which are connected to the first and the second friction lining carrier 12, 13. However, the driver elements 20 are preferably by deep drawing from the first and the second friction lining support 12, 13 Herge presents, so integrally formed with the first and the second friction lining 12, 13.

It is also possible for more than the two driver elements 20 shown to be arranged or moved. be formed, for example, three, four, etc. Also in these embodiments, a diagonal arrangement as shown in Fig. 2, are selected, in which case (each) two driver elements 20 may be arranged side by side. Further, there is the possibility that all Mitnehm he elements 20 are the same size, in particular special have an equal diameter. However, it is also different sized driver elements 20, in particular with different diameters, ver used. The smaller driver elements 20 may be radially further inside lie lowing and the larger driver elements 20 radially outward lying on the friction lining carriers 12, 13 may be arranged.

The first and the second friction lining carrier 12, 13 may each be separately connected directly to the stop element 15, for example via rivets, screws, etc. For the accessibility to these connecting elements corresponding breakthroughs may be provided in the respective other friction lining and friction lining.

The preferred connection of the first and second friction lining carrier 12, 13 to the stop element 15 takes place according to embodiments of the clutch disc 1, however, by a common connecting element 23 which extends through the stop element 15 and the two disc springs. For this purpose, the disc springs corresponding breakthroughs, as can be seen from Figs. 2 and 3. The first and the second friction lining carrier 12, 13 are in this embodiment indirectly connected to the stop element 15 via the connecting element 23 (ie connected to the stop element 15) by the connecting element 23, the first and the second friction lining support 12, 13 interconnected and the Stop element 15 and the two disc springs is held by this connection between the first and the second friction lining carrier 12, 13, also with the help of the driver elements 20th

In general, the first and optionally the second friction lining carrier 12, 13 are connected in each case exclusively via a connecting element 23 to the stop element 15 in a direct or indirect manner. It can thus be formed together with the spring elements 14 is a "fulcrum" or pivotal mounting for the friction linings 10, 1 1, whereby they can be better brought to the respective friction partner to the plant.

The common connecting element 23 can be, for example, a one- or two-part rivet, or a screw with a nut, etc. The first friction linings 12 and the second friction linings 13 are preferably made from a metallic or metal-ceramic sintered material customary for this purpose. However, it is also possible to produce these from other materials, such as resin-bonded fiber materials. These other types of friction linings are described in detail in the relevant literature, so reference is made to this point.

With regard to the usable adhesive for the formation of the above-mentioned adhesive joints, reference is also made to the relevant literature, since the bonding of friction linings is known per se.

The first and second friction lining 12, 13 may be made of an iron-based material, for example, a steel, in particular a structural steel or a tempera tungsstahl. But it can also be brazing sheets, for example made of an iron-based material, in example of a steel, in particular a structural steel or a tempering steel, ver used.

The spring elements 16 may consist of a, in particular heat-resistant, spring steel.

In the embodiment of the clutch disc 1 described above, the stop element 15 on the opening 16 for partially receiving the two plate springs. The disc springs can also be supported on an annular web, which is formed on a breakthrough 16 limiting side wall. It can also be provided that no breakthrough 16 but one or both sides only one recess is provided, in which the respective plate spring is partially received. It can further be provided that the Tel lerfedem are not partially received in a breakthrough or depression, son nes that the at least one plate spring on an outer surface 24, 25 of the Anschla gelementes 15, in the direction of the respective friction lining 12, 13 shows, supports. However, the arrangement of the disc springs shown in Figures 2 and 3 is the preferred because da with the disc springs in the assembled state of the friction assembly 8 are held in place and the opening 16 in the stop element 15 is easy to produce.

Only for the sake of completeness it should be mentioned that the at least one connecting element 23 does not have to be arranged extending through the plate spring (s). In Figs. 4 to 8 further and possibly independent embodiments of the clutch disc 1 are shown in fragmentary form, again with the same parts the same reference numerals or component names as in the preceding Figs. 1 to 3 verwen be used. In order to avoid unnecessary repetition, reference is made to the detailed description of FIGS. 1 to 3 and reference is made thereto.

4 shows a section through a friction assembly 8 of a variant of the clutch disc 1, wherein the plate spring, which is partially disposed between the first Reibbelagsträ ger 12 and the stopper member 15, has a larger diameter than the plate spring, partially between the second Reibbelagsträger 13 and the Anschla gelement 15 is arranged. The stop member 15 may have an annular web 26 on the side wall surrounding the opening 16, so that so these sides wall is formed with egg ner stage. The diaphragm spring with the larger diameter is applied to the step on a surface adjacent to the end surface, while the smaller Tellerfe the aniiegt with its front side on the end face of the annular web 26, as shown in Fig. 4 Darge is.

In Fig. 5 it is shown that it is possible, please include in a variant of the coupling slide 1, that a plate spring only the first friction lining support 12 (Fig. 2) is assigned. The second friction lining carrier 13, however, is rigidly connected to the stop element 15, as shown in Fig. 5. This connection can be made, for example, by inverting the at least one driver element 20 or by means of a rivet, etc.

In Fig. 4, a further embodiment of the clutch disc 1 is shown, in which the first and the second friction lining 12, 13 in the region of the connecting element 23 for the connection of the first and the second friction lining carrier 12, 13 with the Anschlagele element 15 a recess 27 for Receiving the connecting element 20, ie a connec tion element head 28, have. These depressions 27 are preferably as deep as corresponds to the height of the connecting element heads 28, so that in each case a connecting element head 28 is completely received in a recess 27, as shown in Fig. 4. It is also possible that the stop element 15 has a raised portion which extends in the direction of the second friction lining carrier 13 or in the direction of the first friction lining carrier 12. The raised area may be designed, for example, as a "ringwall" around the opening 16 in the stop element so as to limit the maximum possible travel, or in the region of attachment of the second friction bearing carrier 13 to the stop element 15

6, a variant of a clutch disc 1 is shown. FIGS. 7 and 8 show the carrier element 5 and a friction lining carrier 12 for this clutch disk

In contrast to the embodiment of the clutch disc according to FIGS. 1 to 3, in this embodiment the carrier element 5 is designed to extend outward in the area of the wing-like friction assemblies 8 and also forms the stop element 15 between the friction lining carriers 12, 13 (see also FIG. 2) Carrier element 5 and the Abstützele elements 15 of the clutch disc 1 are thus made in one piece, as best seen in Fig. 7 can be seen. In other words, therefore, the stop elements 15 are integrally formed in the carrier element 5. Although this has the disadvantage that thus the carrier element 5 is larger and more punching waste accumulates. But riveting processes for the connection of the support elements 15 and the carrier element 5 accounts for this. This in turn reduces inaccuracies on the basis of the riveting processes, so that overall the component accuracy can be increased.

As can be seen from Fig. 7, the Trägement ement 5 for each friction assembly 8 a total of eight openings or recesses 21, which are each grouped around the central Federelementauf 17. These recesses 21 in turn serve to receive the participants with elements 20, each of which Reibbelagträger 12 has four, as seen in FIG 8 to see it. The driver elements 20 are divided into two corner regions of the friction lining carrier 12. This pairwise division is not mandatory. It can also be arranged per Eckbe rich friction lining 12 each a driver element 20.

The driver elements 20 may be carried out deep-drawn or the thermoforming be backed with a bolt. The clutch disc 1 is used in particular in a dry-running clutch, preferably in a dry-running clutch for a truck or a tractor.

The exemplary embodiments show possible embodiments, wherein it should be noted at this point that combinations of the individual embodiments are also possible with each other.

For the sake of order, it should finally be pointed out that for a better understanding of the structure of the clutch disk 1, this is not necessarily shown to scale.

Bezugszeicfaenaufstellung

clutch disc

body

torsion spring

recess

support element

scope

Aufmeb erei ch

friction unit

rivet

friction lining

spring element

stop element

breakthrough

Spring element receptacle

diameter

dogging

recess

height

connecting element

surface

ring land

Deepening

Fastener head

Claims

P a n t a n s p r e c h e

1 clutch disc (1) for a friction clutch, comprising a scheibenför shaped base body (2) with a carrier element (5), wherein the carrier element (5) has an outer circumference (6), distributed over the plurality of receiving areas (7) for wing-like Friction assemblies (8) are arranged, wherein the friction assemblies (8) are connected to the carrier element (5), the friction assemblies (8) each having a first friction lining (10) and a second friction lining (11), wherein the first friction linings (10 ) on first Reibbe bearing supports (12) and the second friction linings (11) on second Reibbelagsträgem (13) are angeord net, and wherein further depending at least one spring element (14) between the first and the second Reibbelagsträgem (12, 13) is arranged, characterized in that between the first and second Reibbelagsträgem (12, 13) each have a stop element (15) is arranged, on which the at least one spring element (14) is supported and / or in which the at least ei ne spring element (14) is partially received, and with which the first and two th Reibbelagsträger (12, 13) are connected or connected to this, wherein the Anschla gelemente (15) further connected to the carrier element (5), that further first friction lining carrier (12) exclusively via a respective connecting element (23) with the Anschla gelementen (15) are connected and that the spring elements (14) are preferably formed as Tellerfe countries.

2. clutch disc (1) according to claim 1, characterized in that the two-th friction lining carrier (13) exclusively via a respective connecting element (23) with the stop elements (15) are connected.

3. clutch disc (1) according to claim 1 or 2, characterized in that between the second Reibbelagsträgem (13) and the stop elements (15) also Fe derelemente (14), in particular disc springs, are arranged.

4. clutch disc (1) according to claim 2 or 3, characterized in that the first and the second friction lining carrier (12, 13) via a respective common connecting element (23) with the stop elements (15) are connected.

5. clutch disc (1) according to one of claims 1 to 4, characterized in that the connecting elements (23) with which the first friction lining carrier (12) with the stop elements (15) are connected, in each case by a breakthrough in the Fe derelementen (14), in particular the disc springs, extend therethrough

6. clutch disc (1) according to one of claims 3 to 5, characterized in that the connecting elements (23) with which the second friction lining carrier (13) with the stop elements (15) are connected, in each case by a breakthrough in the Fe derelementen (14), in particular the dividing springs extend therethrough.

7. clutch disc (1) according to one of claims 3 to 6, characterized in that the spring elements (14), in particular the disc springs, which are arranged between the first Reibbelagsträgem (12) and the stop elements (15) have a larger diameter , as the spring elements (14), in particular the disc springs, the rule between the second Reibbelagsträgem (13) and the stop elements (15) are arranged

8. clutch disc (1) according to one of claims 1 to 7, characterized in that the second friction lining carrier (13) are rigidly connected to the stop elements (15).

9. clutch disc (1) according to one of claims 1 to 8, characterized in that the first and the second friction lining carrier (12, 13) in the region of Verbindungsele elements (23) for the connection of the first and the second friction lining carrier (12, 13) each having a recess (27) for receiving the connecting elements (23) with the stop elements (15).

10. clutch disc (1) one of claims 1 to 9, characterized in that the stop elements (15) each have an elevated portion which in the direction of the second friction lining carrier (13) or in the direction of the first friction lining carrier (13) stretch.