DE102017127215A1 - Clutch disc with a rotation axis - Google Patents

Abstract

The invention relates to a clutch disk (1) having an axis of rotation (2) for a hysteresis-damped vibration-damped operation in a friction clutch (18), comprising at least the following components:
- A Reibschlusskranz (3) for transmitting a torque when pressed Gegenreibschlusskranz (4);
- A torque terminal (5) permanently connected to the Reibschlusskranz (3) for transmitting a torque;
- A torque damper (6) which is arranged in the torque flow between the Reibschlusskranz (3) and the torque port (5) and an input side (7) and an output side (8);
- A friction ring (9) which is fixed against rotation on the output side (8) of the torque damper (6);
- An intermediate ring (10) which is in frictional contact with the friction ring (9) and rotationally fixed to the input side (7) of the torque damper (6) is connected; and
- An axial spring (11), which permanently clamped exerts an axial force on the intermediate ring (10). The clutch disc (1) is primarily characterized in that the intermediate ring (10) has a radial guide surface (12, 13) for the friction ring (9) and / or for the axial spring (11).
With the clutch disc proposed here, a centering of the friction ring and an axial spring for a torque damper with hysteresis behavior can be ensured in a simple manner in a cost-effective and space-saving manner.

Description

The invention relates to a clutch disc having an axis of rotation for a hysteresis-vibration-damped operation in a friction clutch, a friction clutch with such a clutch disc, a drive train with such a friction clutch, and a motor vehicle with such a drive train.

Friction clutches are known from the prior art in which at least one friction pack comprising at least one friction plate and a corresponding clutch disc is provided and in which at least one clutch disc a torque damper is integrated. As a result, incoming or generated vibrations in the torque transmission, for example, during the closing process of the Reibpakets be reduced. For many applications, a hysteresis of the damping is required in addition, so that the effect of the torque damper is delayed at least in one direction of torque transmission. In a preferred embodiment, the hysteresis is achieved in that the torque is passed over a friction pair, which is permanently compressed by means of an axial spring, such as a plate spring, with a predetermined axial force. About the friction surface, axial force and the coefficient of friction, a maximum transmittable limit torque is adjustable. As a result, this friction pair moves only when the limit torque is exceeded against the axial force and the friction is reduced. The torque damper is then so twisted with reduced friction to perform the damping in itself. This causes a hysteresis behavior in this torque flux between the full engagement of the friction pair and the disengaged state with reduced friction. Because now the torque damper oscillates back and forth in an attenuation case, this hysteresis is repeated.

This friction pairing for generating the hysteresis behavior is to be implemented in a cost-effective and space-consuming manner in order to meet the requirements of the market. Therefore, a friction lining is often provided as a rubber ring between the input side and the output side of the torque damper, against which a corresponding friction disc is pressed by means of a plate spring. The radial position of the rubber ring and the diaphragm spring must be ensured over the service life during operation. However, it is desirable to make as little or no changes to the torque damper design as possible over a torque damper without hysteresis behavior.

On this basis, the present invention has the object, at least partially overcome the known from the prior art disadvantages. The features of the invention will become apparent from the independent claims, to which advantageous embodiments are indicated in the dependent claims. The features of the claims may be combined in any technically meaningful manner, and to this end, the explanations of the following description and features of the figures may be used, which include additional embodiments of the invention.

• - einen Reibschlusskranz zum Übertragen eines Drehmoments bei angepresstem Gegenreibschlusskranz;
• - einen Drehmomentanschluss dauerhaft verbunden mit dem Reibschlusskranz zum Übertragen eines Drehmoments;
• - einen Drehmomentdämpfer, welcher im Drehmomentfluss zwischen dem Reibschlusskranz und dem Drehmomentanschluss angeordnet ist und eine Eingangsseite und eine Ausgangsseite aufweist;
• - einen Reibring, welcher an der Ausgangsseite des Drehmomentdämpfers rotationsfest befestigt ist;
• - einen Zwischenring, welcher in reibendem Kontakt mit dem Reibring steht und mit der Eingangsseite des Drehmomentdämpfers rotationsfest verbunden ist; und
• - eine Axialfeder, welche dauerhaft verspannt eine Axialkraft auf den Zwischenring ausübt.

The invention relates to a clutch disk having an axis of rotation for a hysteresis-damped vibration-damped operation in a friction clutch, comprising at least the following components:

• a Reibschlusskranz for transmitting a torque in pressed Gegenreibschlusskranz;
• - A torque terminal permanently connected to the frictional ring for transmitting a torque;
• - A torque damper, which is arranged in the torque flow between the frictional ring and the torque port and having an input side and an output side;
• - A friction ring, which is fixed against rotation on the output side of the torque damper;
• - An intermediate ring, which is in frictional contact with the friction ring and is rotatably connected to the input side of the torque damper; and
• - An axial spring which permanently exerting an axial force on the intermediate ring exerts.

The clutch disc is mainly characterized in that the intermediate ring has a radial guide surface for the friction ring and / or for the axial spring.

In the following, reference will be made to the aforementioned axis of rotation, if the axial direction, radial direction or the direction of rotation and corresponding terms are used without explicit reference.

The clutch disc is set up for a friction pack, wherein at least one corresponding friction plate is provided, which is axially compressible with the clutch disc. For this purpose, the clutch disc has a friction ring, which has, for example, a friction lining, and the corresponding friction plate a Gegenreibschlusskranz. The Reibschlusskranz and the Gegenreibschlusskranz are axially brought into contact with each other and thus form a friction pairing. When applying a contact pressure on this friction pair is multiplied over the mean radius and the coefficient of friction, a torque purely friction and releasably transferable. In many applications, the Reibschlusskranz between two Gegenreibschlusskränzen is compressible, the Gegenreibschlusskränze are each formed on an axially fixed counter-plate and an axially displaceable pressure plate. In many applications, the clutch disc forms a rotationally fixed connection with a transmission shaft, while the corresponding friction plate forms a rotationally fixed connection with a motor shaft. This rotation-resistant connection is formed by means of a torque connection. Such a torque connection is, for example, a hub with a spline, so that the clutch disc for mounting on a corresponding shaft can be pushed.

In this clutch disc, a torque damper is now further provided, which is arranged in the torque flow between the frictionally engaging ring and the torque connection. When interposed, the torque damper is also to be considered when the damper mass is connected in parallel to the mechanical connection course, because the resulting (counteracting) damping torque is fed back into the torque flow between the friction ring and the torque port. In one embodiment, the torque damper is mechanically interposed and there is a rotational relative movement between the Reibschlusskranz and the torque connection in the damping case. The rotation-resistant connection is therefore to be regarded as a connection which can not be interrupted directly as a result of an actuation, which transmits a torque with (virtually) lossless in a main load case. Only in the case of damping and when a hysteresis behavior occurs does a part of the energy of the torque to be transmitted dissipate. Preferably, however, the damper mass is connected in parallel in the mechanical connection course and there is no free rotation between the frictional ring and the torque connection, but a (usually low) torsion.

The torque damper has an input side and an output side, wherein the input side is preferably rotationally fixedly connected to the Reibschlusskranz and the torque terminal. The output side includes the damper mass. In another embodiment, the input side are arranged on the ring side and the output side in the torque flow on the connection side. The input side is then rotationally fixed to the frictional ring and connected the output side rotationally fixed to the torque port. Alternatively, the arrangement is reversed.

Both the input side and the output side are preferably designed in each case as at least one driver disk, wherein these preferably overlap radially. Between the input side and the output side, a damping element, such as a damping coil spring, arranged and the output side comprises a damper mass. For a suitable damping element, reference is made to the variety of known means.

Furthermore, a friction ring is now provided, which is fixed against rotation on the output side of the torque damper. The friction ring has at least one friction surface, which is preferably elastomeric. This friction surface is facing an intermediate ring, which is in frictional contact with the friction ring and is rotatably connected to the input side of the torque damper. This friction pair is compressed by means of an axial spring, for example a plate spring, in that the axial spring is installed between the intermediate ring and the input side in a spring-loaded manner. Thus, the axial spring is permanently clamped and therefore exerts an axial force on the intermediate ring. Friction ring, intermediate ring and axial spring together form a hysteresis device, by means of which the torque damper exhibits a hysteresis behavior or, in other words, the damping is hysteresis-afflicted. It is not excluded that additional elements are used for a different or supplementary, ie superponed, hysteresis behavior.

Here it is now proposed to ensure the radial guidance of the friction ring and / or the axial spring on the intermediate ring, so that the friction ring and / or the axial spring to the axis of rotation of the clutch disc are permanently centered over the entire life and in any state. This is achieved in that the intermediate ring has a radial guide surface for the friction ring and / or for the axial spring, preferably for both. This makes it possible to use a conventional friction ring and a conventional torque damper, because only the intermediate ring integrally takes over this radial guide for at least one of the two components for hysteresis. The intermediate ring itself is preferably centered adjacent to the torque connection. Alternatively, the intermediate ring is centered on the input side of the torque damper.

According to an advantageous embodiment of the clutch disc, the intermediate ring has at least one axial flange, by means of which the Intermediate ring in a corresponding circumferential stop, preferably an opening, the input side of the torque damper axially freely displaceable engages.

By means of the axial flange, the intermediate ring is securely fixed in rotation to the input side. As a result, a rotational relative movement of the arranged between the washer and the input side axial spring is safely excluded. In one embodiment, the washer is centered by means of the axial flange. Preferably, however, the input side, for example a driver disk, and intermediate disk are each separately, ie centered parallel to one another on the torque connection, so that there is no tolerance chaining.

According to an advantageous embodiment of the clutch disc is a radial guide surface, preferably arranged for the friction ring, on the outer edge of the intermediate ring and formed by means of impact.

The guided component can be safely centered by means of a radial guide surface on the outer edge, circumferential or interrupted. In particular, a soft friction ring is well centered secured against an evasive movement via an outer edge guide and an elastic stress under the axial force is not or at least reduced converted into an expansion radially outward, but implemented in an expansion radially inward and in the axial direction. By the production process collision, it is possible to maintain the sheet thickness of the blank (nearly), so that a sufficient wall thickness of the Radialführungswandung with the radial guide surface at an axially relatively thin, namely about the same thickness, intermediate disc inexpensive, and preferably purely forming and post-processing, manufacturable , Preferably, the washer is made of a metal, preferably steel, and forms the friction surface corresponding to the friction ring with the metal surface.

According to an advantageous embodiment of the clutch disc, a radial guide surface, preferably for the axial spring, arranged on the inner edge of the intermediate ring and formed by deep drawing.

By means of a radial guide surface on the inner edge, circumferential or interrupted, a rigid guided component can be securely centered. In particular, a plate spring is secured via an inner edge guide for its intrinsic radial evasive movement freely and yet well centered. By the manufacturing process deep drawing a central region, it is possible to maintain the plate thickness of the blank (near), so that a sufficient wall thickness of Radialführungswandung with the radial guide surface at an axially relatively thin, namely about the same thickness, intermediate disc cost, and preferably reshaping and punching and Spanfrei, manufacturable. Preferably, the washer is made of a metal, preferably steel, and forms the friction surface corresponding to the friction ring with the metal surface. Particularly preferably, the intermediate ring at the outer edge forms the radial guide surface for the friction ring and at the inner edge (opposite) the radial guide surface for the axial spring, preferably a plate spring. With such a radially opposing arrangement on the axially opposite sides of the intermediate disc, a desired axial wall thickness can be manufactured easily from a tool that is thin with respect to the axial wall thickness.

According to an advantageous embodiment of the clutch disc, the friction ring is formed from a plastic, preferably from an elastomeric plastic or from an elastomer.

According to this embodiment, the friction ring is made entirely of a plastic, preferably with a suitable friction property for the friction pairing with the washer and the output side. Such a friction ring is inexpensive manufacturable and easy to install. In addition, the friction ring is insensitive to abrasion, because by the solid material design, the newly created due to the abrasion during operation surface has unchanged or at least equally good friction properties. For some applications, it is advantageous to add to the plastic aggregate and / or disordered or ordered reinforcing fibers. Thus, taking into account the tight cost specifications, an extension of the service life can be achieved.

• - eine Eingangswelle;
• - eine Ausgangswelle; und
• - ein Reibpaket, umfassend eine Kupplungsscheibe nach einer Ausführungsform gemäß der obigen Beschreibung und zumindest eine korrespondierende Gegenplatte, wobei mittels eines axialen Verpressens der Kupplungsscheibe mit der zumindest einen Gegenplatte ein Drehmoment reibschlüssig übertragbar ist,

wobei die Eingangswelle und die Ausgangswelle mittels des Reibpakets lösbar hysteresebehaftet gedämpft drehmomentübertragend verbunden sind.According to a further aspect, the invention relates to a friction clutch for a drive train, comprising at least the following components:

• an input shaft;
• an output shaft; and
• a friction pack comprising a clutch disk according to an embodiment according to the above description and at least one corresponding counterplate, wherein by means of an axial compression of the clutch disk with the at least one counterplate a torque can be transmitted frictionally,

wherein the input shaft and the output shaft are connected by means of the friction package releasably hysteresis damped transmitting torque.

The friction clutch is adapted to detachably transfer a torque from an output shaft to a load and vice versa. This is usually achieved via the (at least one) friction pack, which has an axially displaceable, in the Generally with the output shaft rotation-resistant, pressure plate which can be pressed against at least one corresponding coupling disc. As a result of the contact force results in a frictional force over the friction surface, which multiplied by the average radius of the friction surface results in a transmissible torque.

For many applications, it is advantageous to use a damped clutch disc, so that the torque to be transmitted overlapping torsional vibrations close to the cause, such as the crankshaft of a reciprocating engine with few, for example three, piston as the output shaft, and / or directly at the causer, namely the stick-slip Effect on fast, in particular manual, engagement of the pressure plate to dampen. For a hysteresis behavior that improves the response, it is advantageous to provide the above-described cost-effective friction pair of friction ring, intermediate ring and axial spring, because it can be incorporated into a torque damper without or with few structural changes compared to a torque damper without hysteresis behavior. In addition, the required additional axial space, especially when forming from a metal sheet by means of collision and deep drawing, low or so low that only free space is occupied, so the installation space-neutral executable.

According to a further aspect, the invention relates to a drive train, comprising a drive unit with an output shaft, at least one consumer and a friction clutch according to an embodiment according to the above description, wherein the output shaft for torque transmission by means of the friction clutch with the at least one consumer is detachably connectable.

The drive train is set up to transfer a torque which is provided by a drive unit, for example an energy conversion machine, preferably an internal combustion engine or an electric drive machine, and output via its output shaft, for at least one consumer so that it can be switched on and off. An exemplary consumer is at least one drive wheel of a motor vehicle and / or an electric generator for providing electrical energy. Conversely, a recording of an inertial energy introduced, for example, by a drive wheel can also be implemented. The at least one drive wheel then forms the drive unit, wherein its inertial energy by means of the friction clutch to an electric generator for recuperation, ie for the electrical storage of the braking energy, with a suitably equipped drive train is transferable. Furthermore, in a preferred embodiment, a plurality of drive units are provided which are connected in series by means of the friction clutch or connected in parallel or can be operated decoupled from one another, or whose torque is releasably available for use available. Examples are hybrid drives of electric drive machine and internal combustion engine, but also multi-cylinder engines, in which individual cylinders (groups) are switchable.

To selectively transmit the torque and / or by means of a gearbox with different ratios or to separate a transmission, the use of the friction clutch described above is particularly advantageous. The friction clutch allows a near-causal damping of superimposed torsional vibrations at a simultaneously achievable by means of hysteresis behavior good response. In this case, the clutch disc requires little to no additional axial space and design adjustments to a hysteresis-free design are not necessary or have little effect on the manufacturing cost.

According to a further aspect, the invention relates to a motor vehicle, comprising at least one drive wheel, which is drivable by means of a drive train according to an embodiment as described above.

Most motor vehicles today have a front-wheel drive and therefore preferably arrange the drive unit, for example an internal combustion engine or an electric drive machine, in front of the driver's cab and transversely to the main drive direction. The space is particularly small in such an arrangement and it is therefore particularly advantageous to use a friction clutch small size. Similarly, the use of a friction clutch in motorized two-wheeled, for which a significantly increased performance is required with the same space.

This problem is exacerbated in passenger cars of the small car class according to European classification. The functional units used in a passenger car of the small car class are not significantly reduced compared to passenger cars larger car classes. Nevertheless, the available space for small cars is much smaller. The drive train described above has a friction clutch or a hysteresis-damped clutch disc of particularly small axial size. At the same time, the production costs are low.

Passenger cars are assigned to a vehicle class according to, for example, size, price, weight and power, and this definition is subject to constant change according to the needs of the market. In the US market, cars of the class small cars and microcars are classified according to European classification of the class of Subcompact Car and in the British market they correspond to the class Supermini or the class City Car. Examples of the micro car class are a Volkswagen up! or a Renault Twingo. Examples of the small car class are an Alfa Romeo Mito, Volkswagen Polo, Ford Fiesta or Renault Clio.

• 1: im Schnitt eine Reibkupplung mit gedämpfter Kupplungsscheibe;
• 2: in einer perspektivischen Schnittansicht eine gedämpfte Kupplungsscheibe mit Hystereseverhalten;
• 3: im Schnitt ein Drehmomentanschluss mit Drehmomentdämpfer;
• 4: in perspektivischer Ansicht ein Zwischenring;
• 5: in einer weiteren perspektivischen Ansicht der Zwischenring gemäß 4;
• 6: in einer Schnittansicht ein Ausschnitt eines Drehmomentdämpfers; und
• 7: ein Antriebsstrang in einem Kraftfahrzeug mit Reibkupplung.

The above-described invention will be explained in detail in the background of the relevant technical background with reference to the accompanying drawings, which show preferred embodiments. The invention is not limited by the purely schematic drawings in any way, it being noted that the drawings are not dimensionally accurate and are not suitable for the definition of size ratios. It is shown in

• 1 : on average a friction clutch with damped clutch disc;
• 2 in a perspective sectional view of a damped clutch disc with hysteresis behavior;
• 3 : on average a torque connection with torque damper;
• 4 in perspective view, an intermediate ring;
• 5 in a further perspective view of the intermediate ring according to 4 ;
• 6 in a sectional view a section of a torque damper; and
• 7 : a drive train in a motor vehicle with friction clutch.

In 1 is a simple friction clutch 18 with a rotation axis 2 shown in section. By means of the friction clutch 18 is an input shaft 20 with an output shaft 21 detachable torque transmitting connectable. The input shaft 20 is with a counter plate 23 , bolted here, connected to transmit torque. The output shaft 21 is with a torque connection 5 , connected here by means of a spline, torque transmitting. For transmitting a torque about the rotation axis 2 is a clutch disc 1 here between the axially fixed counter plate 23 and an axially engageable pressure plate can be pressed. The pressure plate includes the Gegenreibschlusskranz 4 for frictional contact with the pressure plate side part of the Reibschlusskranzes 3 the clutch disc 1 , The Gegenreibschlusskranz 4 is by means of an actuating device, of which here an actuating spring 32 executed as a plate spring can be seen, axially against the corresponding part of the Reibschlusskranzes 3 the clutch disc 1 pressed and the other part of the Reibschlusskranzes 3 is characterized against the axially fixed counter-plate 23 pressed. This is the compressible friction package 22 educated. The clutch disc 1 here includes a torque damper 6 which is an input side 7 on the side of the friction ring 3 and an exit side 8th on the side of the torque connection 5 having. In this configuration, so the frictional ring 3 and the torque connection 5 by means of a damper device, such as a ring spring, in the case of damping (swinging) freely against each other rotated.

In 2 is a clutch disc 1 shown in perspective in section, as for example, but only among others, in a friction clutch 18 according to the in 1 shown configuration can be used. Again, the clutch disc 1 a torque damper 6 with an input side 7 and a home page 8th on, with the input side 7 firmly with the friction ring 3 is connected and designed as a drive plate. Notwithstanding the in 1 shown clutch disc 1 is with the clutch disc shown here 1 the exit side 8th to the torque connection 5 mechanically connected in parallel and designed only as a flywheel. This means that so the Reibschlusskranz 3 and the torque connection 5 by means of a damper device, here a plurality of generally parallel-connected block springs, in the case of damping (oscillating) are not rotated against each other, but with each other by means of the input side 7 are firmly connected. In the case of damping, under certain circumstances, a (vibrating) torsion of the components between the friction ring can occur 3 and the torque connection 5 and / or relative slippage between the frictional ring 3 and the Gegenreibschlusskranz 4 , Here is a friction ring 9 and one by means of an axial spring 11 , which is designed as a plate spring, against the friction ring 9 pressed intermediate ring 10 intended. The intermediate ring 10 is here by means of a plurality of axial flanges 14 in corresponding circumferential stops 15 against a relative twisting towards the input side 7 secured. This is shown and described in detail below.

In 3 is the torque connection 5 the clutch disc 1 according to 2 shown in section. The friction ring 9 lies axially between the intermediate ring 10 and a not shown here corresponding friction surface of the output side 8th of the torque damper 6 (see 2 ). The axial spring 11 is between the washer 10 and the input side 7 of the torque damper 6 (see 2 ) arranged axially biased. This will be the washer 10 with a preset by the installation situation predetermined axial biasing force against the friction ring 9 pressed. This results in a hysteresis depending on whether the axial spring 11 due to an exceeding (vibration) torque lifts or not. Is the intermediate ring 10 against the friction ring 9 with full preload force of the axial spring 11 pressed so there is a higher resistance to a relative rotation of the input side 7 to the exit side 8th before, as if the axial force on the friction ring 9 reduced or canceled. Here it can be seen that the intermediate ring 10 on the outer edge 16 an outer radial guide surface 12 for the friction ring 9 forms and at the inner edge 17 an inner radial guide surface 17 for the axial spring 11 formed. The intermediate ring 10 itself is here on the torque connection 5 centered. So that's both the friction ring 9 as well as the axial spring 11 at each operative axial position of the washer to the torque port 5 or centered to the axis of rotation. A relative twisting between the washer 10 , the axial spring 11 and the torque connection 5 is by means of the axial flanges 14 (with little play) prevented (compare 2 ).

In 4 is in a perspective view from the side of the friction ring 9 (see 3 ) the intermediate ring 10 in an embodiment as shown in FIG 2 and 3 shown. Here's the one on the outer edge 16 arranged outer radial guide surface 12 for the friction ring 9 executed circumferentially interrupted and preferably formed by means of collision. The at the inner edge 17 an inner radial guide surface 17 for the axial spring 11 circumferentially closed and formed by deep drawing. Each of these features is purely optional.

In 5 is in a perspective view from the side of the axial spring 11 (see 3 ) the intermediate ring 10 according to 4 shown. It is easy to see that the radial wall thickness of the material at the outer edge 12 with the outer radial guide surface 16 and the radial wall thickness of the material at the inner edge 13 with the inner radial guide surface 17 based on the axial material thickness of the intermediate ring 10 is very high, even higher than this is adjustable.

In 6 is a section of a torque damper 6 on average at the intermediate disc 10 shown in the details as they are in 2 is shown. Here you can see how the washer 10 by means of the axial spring 11 against the friction ring 9 pressed. Here is the friction ring 9 between the washer 10 and the output side 8th (here as flywheel) of the torque damper 6 pressed. The axial spring 11 is between one of the two drive disks on the input side 7 biased arranged. Alone by means of a biasing force of the axial spring 11 overcoming relative torque between the output side 8th and the input side 7 is the washer 10 axially lifted and thus the torsion resistance reduced. At the same time is the friction ring 9 over the outer radial guide surface 16 and the axial spring 11 over the inner radial guide surface 17 in any operational axial position of the washer 10 to the axis of rotation 2 centered.

In 7 is a powertrain 19 comprising a drive unit 24 shown here as a three-cylinder internal combustion engine, an output shaft 25 (For example, an input shaft 20 ), a friction clutch 2 and a torque transmitting connected left drive wheel 27 and right drive wheel 28 , shown schematically. The powertrain 19 is here in a motor vehicle 26 arranged, wherein the drive unit 24 with its motor axis 31 transverse to the longitudinal axis 30 in front of the driver's cab 29 is arranged.

With the clutch disc proposed here, a centering of the friction ring and an axial spring for a torque damper with hysteresis behavior can be ensured in a simple manner in a cost-effective and space-saving manner.

LIST OF REFERENCE NUMBERS

1

clutch disc

2

axis of rotation

3

Reibschlusskranz

4

Gegenreibschlusskranz

5

torque connection

6

torque damper

7

input side

8th

output side

9

friction ring

10

intermediate ring

11

axial spring

12

outer radial guide surface

13

inner radial guide surface

14

axial flange

15

circumferential abutment

16

outer edge

17

inner edge

18

friction clutch

19

powertrain

20

input shaft

21

output shaft

22

Reibpaket

23

counterplate

24

power unit

25

output shaft

26

motor vehicle

27

left drive wheel

28

right drive wheel

29

cab

30

longitudinal axis

31

motor axis

32

actuating spring

Claims (8)

Clutch disc (1) having an axis of rotation (2) for a hysteresis-damped vibration damped operation in a friction clutch (18), comprising at least the following components: - a Reibschlusskranz (3) for transmitting a torque at pressed Gegenreibschlusskranz (4); - A torque terminal (5) permanently connected to the Reibschlusskranz (3) for transmitting a torque; - A torque damper (6) which is arranged in the torque flow between the Reibschlusskranz (3) and the torque port (5) and an input side (7) and an output side (8); - A friction ring (9) which is fixed against rotation on the output side (8) of the torque damper (6); - An intermediate ring (10) which is in frictional contact with the friction ring (9) and rotationally fixed to the input side (7) of the torque damper (6) is connected; and - an axial spring (11) which permanently exerts an axial force on the intermediate ring (10) exerts, characterized in that the intermediate ring (10) has a radial guide surface (12,13) for the friction ring (9) and / or for the axial spring ( 11). Clutch disc (1) after Claim 1 , wherein the intermediate ring (10) has at least one Axialflansch (14), by means of which the intermediate ring (10) in a corresponding peripheral stop (15), preferably an opening, the input side (7) of the torque damper (6) axially freely slidably engages. Clutch disc (1) after Claim 1 or 2 , wherein a radial guide surface (12,13), preferably for the friction ring (9), on the outer edge (16) of the intermediate ring (10) is arranged and formed by means of impact. Clutch disc (1) according to one of the preceding claims, wherein a radial guide surface (12,13), preferably for the axial spring (11), on the inner edge (17) of the intermediate ring (10) is arranged and formed by deep drawing. Clutch disc (1) according to one of the preceding claims, wherein the friction ring (9) is formed from a plastic, preferably from an elastomer-like plastic or from an elastomer. Friction clutch (18) for a drive train (19), comprising at least the following components: an input shaft (20); - An output shaft (21); and - A friction pack (22) comprising a clutch disc (1) according to one of the preceding claims and at least one corresponding counter-plate (23), wherein by means of an axial compression of the clutch disc (1) with the at least one counter-plate (23) a torque is frictionally transferable , wherein the input shaft (20) and the output shaft (21) by means of the Reibpakets (22) releasably hysteresebehaftet damped torque transmitting connected. Drive train (19) comprising a drive unit (24) with an output shaft (25), at least one consumer (27,28) and a friction clutch (18) according to Claim 6 , wherein the output shaft (25) for torque transmission by means of the friction clutch (18) with the at least one consumer (27,28) is detachably connectable. Motor vehicle (26), comprising at least one drive wheel (27,28), which by means of a drive train (19) to Claim 7 is drivable.

Images