DE102019124427A1 - Clutch disc with a rotation axis for a friction clutch - Google Patents

Abstract

The invention relates to a clutch disc (1) with an axis of rotation (2) for a friction clutch (3), having at least the following components: - a torsion damper flange (4); - a driving disc (5); - a counter disc (6); - a Axial fastening device (7), by means of which the drive plate (5) and the counter plate (6) are axially and torque-rigidly connected to one another; - a friction ring (8) between the torsion damper flange (4) and the drive plate (5) or the counter plate (6); and - a plate spring (9) for exerting an axial force (10) on the friction ring (8) for frictional engagement. The clutch disc (1) is primarily characterized in that the friction ring (8) is positioned in a predetermined position by means of the axial fastening device (7) and the disc spring (9) is positioned in a predetermined position by means of the friction ring (8) Installation security for a disc spring of a torsional vibration damper is achieved even in a confined space.

Description

The invention relates to a clutch disk with an axis of rotation for a friction clutch, a friction clutch with such a clutch disk for a drive train, a drive train with such a friction clutch, and a motor vehicle with such a drive train.

Clutch disks, for example for a friction clutch of a motor vehicle, with a torsional vibration damper are known from the prior art. In one embodiment, such a torsional vibration damper comprises a friction device, for example as a hysteresis element. Such a friction device is set up to dissipate vibration energy, so that a more even torque transmission from an input side to an output side of a friction clutch is achieved.

In some applications, the installation space for such a friction device in a clutch disc is very tight. As a result, there is a risk that the plate spring tongues will be out of place during assembly and, for example, get into a riveting area. It is then not guaranteed that the disc spring is fully functional and / or the quality assurance in the assembly is complex.

Proceeding from this, the present invention is based on the object of at least partially overcoming the disadvantages known from the prior art. The features according to the invention emerge from the independent claims, for which advantageous configurations are shown in the dependent claims. The features of the claims can be combined in any technically meaningful manner, in which case the explanations from the following description and features from the figures, which include additional embodiments of the invention, can also be used.

• - einen Torsionsdämpferflansch;
• - eine Mitnehmerscheibe;
• - eine Gegenscheibe;
• - eine Axialbefestigungseinrichtung, mittels welcher die Mitnehmerscheibe und die Gegenscheibe axial und drehmomentsteif miteinander verbunden sind;
• - einen Reibring zwischen dem Torsionsdämpferflansch und der Mitnehmerscheibe oder der Gegenscheibe; und
• - eine Tellerfeder zum Ausüben einer Axialkraft auf den Reibring für einen Reibschluss.

The invention relates to a clutch disc with an axis of rotation for a friction clutch, having at least the following components:

• - a torsion damper flange;
• - a drive plate;
• - a counter disc;
• - An axial fastening device, by means of which the driver disk and the counter disk are connected to one another axially and in a torque-stiff manner;
• - A friction ring between the torsion damper flange and the drive plate or the counter plate; and
• - A disc spring for exerting an axial force on the friction ring for frictional engagement.

The clutch disc is primarily characterized in that the friction ring is positioned in a predetermined manner by means of the axial fastening device and the disc spring is positioned in a predetermined manner by means of the friction ring.

In the following, reference is made to the named axis of rotation if the axial direction, radial direction or the circumferential direction and corresponding terms are used without explicitly otherwise indicating. Unless explicitly stated otherwise, ordinal numbers used in the preceding and following description are only used for clear distinction and do not reflect any order or ranking of the components identified. An ordinal number greater than one does not necessarily mean that another such component must be present.

The clutch disc proposed here is set up for conventional use in a friction clutch, that is to say for frictionally releasable torque transmission in a friction package. Such a friction package comprises at least one clutch disk and a pressure plate and a counterplate for each clutch disk, or in the case of a double clutch, for example, a common central plate instead of two counterplates. The counter plate is also referred to as a flywheel (due to its additional function). The counter plate and the pressure plate are connected to one another in a rotationally fixed manner and are connected to the input side in a torque-proof manner, the clutch disc being connected to the output side in a torque-proof manner.

The input side denotes the side via which a torque is introduced in a main operating state, and the output side denotes the side via which a torque is queried in a main operating state. In some applications, reverse operation is possible or even an operating state that is the same or more frequent than a torque transmission from the input side to the output side. The input side is connected in a torque-stiff manner, for example, to an engine shaft of a drive machine, for example to a combustion shaft of an internal combustion engine. The output side is (then) connected to a transmission input shaft in a torque-resistant manner. To the clutch disc for a frictional torque transmission between the To press the pressure plate and the counter plate, the pressure plate can be moved axially so that it can be pressed axially against the clutch disc. For the frictional engagement, the clutch disk has a friction surface which is arranged radially on the outside and which can be axially compressed between the counterplate and the pressure plate, so that a torque can be releasably transmitted in a frictionally engaged manner. The friction surface is held by a drive plate, for example glued and / or riveted. Furthermore, a counter-disk is provided, which is connected to the drive disk axially and in a torque-resistant manner by means of an axial fastening device. The drive plate and the counter plate are also generally referred to below as the disks. A torsion damper flange is connected to the drive plate and the counter plate in a damped, torque-transmitting manner, for example by means of at least one, preferably a plurality of, damper spring (s).

For damping, a (first) friction ring is (permanently) frictionally pressed axially against the torsion damper flange, so that the torsional vibration energy is dissipated from the system in the form of friction (heat). In order to achieve a predetermined torsional vibration damping, a predetermined frictional force is desired, that is, a predetermined axial pressure of the friction ring against the torsion damper flange, that is, a predetermined axial force is necessary to generate the frictional engagement. This axial force is held by a structurally, so as a result of a set axial distance, axially pretensioned disc spring. In one embodiment, the plate spring is axially supported on the rear of the drive plate. In one embodiment, the plate spring is axially supported on the rear of the counter disk. In a further embodiment, a further friction ring is provided between the torsion damper flange and the respective other disk (for example the counter disk), preferably without a further disk spring.

In order to accommodate the disc spring in the mostly confined space in such a way that assembly is simple and the functionality of the mounted clutch disc is ensured, it is desirable for the disc spring to be positioned in a predetermined manner with tight positioning tolerances. At the same time, it is not desirable for the plate spring to be in frictional contact (at least in a region of the tilting movement) with an element of one of the disks and / or the axial fastening device. It is now proposed here that the disc spring be positioned in a predetermined manner only indirectly via the axial fastening device. The friction ring is positioned in a predetermined manner by means of at least one corresponding positioning receptacle directly above the axial fastening device, for example in a form-fitting manner. The positioning receptacle is preferably set up in such a way that the friction ring is positioned in a predetermined manner with as little play as possible in the circumferential direction (with close tolerances).

For example, contact between the positioning receptacle and a corresponding (positioning-effective) surface of the axial fastening device is permissible. The disc spring is now positioned in a predetermined position directly above the friction ring. Thus, a positioning of the plate spring without direct contact and thus without (frictional) contact relative to the axial fastening device is positioned in a predetermined manner. The plate spring is preferably positioned with a positive fit relative to the friction ring.

It is further proposed in an advantageous embodiment of the clutch disc that the axial fastening device is formed by at least one stepped bolt and the friction ring forms a through opening for each stepped bolt.

A stepped bolt, here preferably used as a spacer bolt, has sections over its length with different diameters, so that the disks are axially and torque-rigidly fixed to one another, preferably a predetermined distance is set up between the driver disk and the counter disk, preferably by means of at least two shoulders in a form-fitting manner is set. For example, the end of the stepped bolts are deformed, for example riveted, for connection to the drive plate and the counter plate. By reshaping the stepped bolt, the counter disk and the driver disk are connected to one another in an axially and torque-resistant manner. If centering of the friction ring (and preferably also the plate spring) is to be achieved at the same time by means of the stepped bolts, it is advantageous if three or more stepped bolts are provided. To transmit a high torque and / or a high degree of tilting rigidity between the two disks, it is advantageous to provide five or more stepped bolts. In one embodiment, in addition to the at least one stepped bolt, at least one further, for example axially aligned sheet-metal-formed element, which is formed from at least one of the disks and forms the axial fastening device together with the stepped bolt. In an alternative embodiment, the axial fastening device is designed free from, that is to say without, bolts.

In this embodiment, the friction ring is designed with such a radial extension that the friction ring with the at least one stepped bolt overlaps radially (and in the circumferential direction, that is, flat). As a result of this large radial expansion of the friction ring, it has great torsional rigidity. In the material of the Friction rings are formed for the at least one stepped bolt, preferably in each case, a through opening. The through-opening is designed at least in the circumferential direction with as little play as possible on the (corresponding shank of the) stepped bolt, so that very precise positioning of the friction ring is achieved. In one embodiment in which the friction ring is to be centered, the through opening is preferably designed with a small amount of play radially on the outside and / or radially on the inside with respect to the stepped bolt. The radial position, that is to say the centering, of the friction ring is thus achieved in a predetermined manner when the friction ring is mounted.

The friction ring preferably forms one, preferably the only, friction surface to the torsion damper flange radially outside of the at least one stepped bolt. With the friction surface of the friction ring arranged radially on the outside, the disc spring is designed with the friction ring-side, ie front-side, bearing surface facing radially outward and the disk-side, ie rear-side, bearing surface radially inward.

It is also proposed in an advantageous embodiment of the clutch disc that the friction ring has at least one tab with an axial extension and the plate spring forms a corresponding tab receptacle for at least one of the tabs, the cup spring being positioned in a predetermined manner by means of the tab and the corresponding tab receptacle.

So that the assembly of the clutch disc can be carried out easily and reliably, the disc spring must be securely (for example vibration-proof) positioned in a predetermined manner. For this purpose, it is proposed here that the tabs are in engagement with the corresponding tab receptacles with an axial extension. The tabs are preferably integrated into the friction ring and / or the tab receptacles are integrated into the disk spring, particularly preferably (each) formed in one piece with the friction ring or with the disk spring. A form-fitting connection is formed with the tab and the tab receptacle. This ensures that the disc spring does not shift during the assembly process. This ensures that the disc spring does not get into the later assembly area of the axial fastening device. This means that incorrect assembly with regard to the disc spring (and the friction ring) is ruled out. For example, the axial fastening device is a stepped bolt according to an embodiment of the previous description. So that the plate spring is correctly pre-positioned and centered, it is advantageous if three or more of the tabs and the tab receptacles are provided. For easier assembly, the number of tabs and tab receptacles of the axial fastening device preferably corresponds to, for example, five of the tabs and five of the (corresponding) tab receptacles with five stepped bolts. In the assembled state of the clutch disc, a single tab is preferably in engagement with a single (corresponding) tab receptacle. The tabs and the tab receptacles are preferably arranged on a radially outer edge of the friction ring and / or the plate spring.

It is also proposed in an advantageous embodiment of the clutch disc that the friction ring forms a pair of tabs in at least one of the stepped bolts and the plate spring correspondingly forms a corresponding pair of tab receptacles for the respective stepped bolt.

Two of the tabs and two (corresponding) of the tab receptacles for the predetermined positioning of the plate spring each form a pair in this embodiment. A single one of the tabs and a single one of the tab receptacles are preferably in engagement with one another. A plurality of so-called disk spring tongues extend radially inward at the radially outer edge when there is axial force-transmitting contact between the friction ring and the disk spring and radially inside the stepped bolt when there is axial force-transmitting contact between the friction ring and the disk spring radially outside. The plate spring tongues are each arranged in pairs in the circumferential direction, preferably closely, adjacent to the left and right of a stepped bolt.

In one embodiment, a plurality of damper springs designed as helical springs is provided. The spring axes of these damper springs are preferably oriented tangentially. The stepped bolts and the (center of the spring axis or spring ends of the) damper springs are preferably arranged in the circumferential direction on a common circle, with a plate spring tongue preferably being arranged immediately adjacent to a stepped bolt and (one spring end) one of the damper springs. One of the tab receptacles is preferably arranged in a radial extension of one of the plate spring tongues, that is to say in a common radial extension. In an alternative embodiment, damper springs are designed with a different diameter than the stepped bolts and / or in a different design, for example as helical helical springs.

• - zumindest ein axial verpressbares Reibpaket umfassend Reibplatten und zumindest eine Kupplungsscheibe nach einer Ausführungsform gemäß der obigen Beschreibung, über welches im verpressten Zustand ein Drehmoment übertragbar ist;
• - eine Eingangsseite zum Aufnehmen eines Drehmoments; und
• - eine Ausgangsseite zum Abgeben eines Drehmoments,

wobei die Eingangsseite mit der Ausgangsseite einzig mittels des Reibpakets drehmomentübertragend verbunden ist.According to a further aspect, a friction clutch for a drive train is proposed, having at least the following components:

• - at least one axially compressible friction package comprising friction plates and at least one clutch disc according to an embodiment according to the above description, via which a torque can be transmitted in the compressed state;
• an input side for receiving a torque; and
• - an output side for delivering a torque,

wherein the input side is connected to the output side in a torque-transmitting manner solely by means of the friction pack.

The friction clutch is designed to releasably transfer torque in a drive train from its input side to its output side, and preferably vice versa. For this purpose, an axially compressible friction package is provided between the input side and the output side (connected in a torque-proof manner), which is composed of at least two friction plates and at least one clutch disc according to an embodiment as described above. In a preferred embodiment, a single clutch disc is provided between a first friction plate, an axially movable pressure plate, and a second friction plate, preferably an axially fixed counterplate, and can be pressed in between for frictional torque transmission by means of a pressure force. As a result of the contact pressure, a frictional force arises over the two-dimensional friction pairings between the area of the clutch disc predetermined for frictional engagement and a (respective) corresponding counter-friction area of the respective friction plate, which, multiplied by the mean radius of the friction surface formed, results in a transferable torque. Multiplied by the number of friction pairings, this gives roughly the transferable (maximum) total torque of the friction clutch. In the unpressed state of the friction pack, no torque or only a permissible low drag torque can be transmitted between the input side and the output side. The friction clutch is designed, for example, as a double clutch with two friction packs, with the respective counter-plate preferably being formed by a common central plate.

The input side is set up to absorb a torque, for example connected to a drive machine (indirectly or directly) in a torque-proof manner. The output side is set up to output a torque, for example connected to a transmission input shaft (indirectly or directly) in a torque-proof manner. The input side is preferably also set up to output a torque, for example for recuperation of deceleration energy in a motor vehicle, and the output side is correspondingly also set up to absorb a torque. It should be pointed out that the input side and the output side are preferably designated according to the main torque curve, but this is not mandatory. In a preferred embodiment, the output side of the friction clutch is formed by the shaft connection of the clutch disc. In a preferred embodiment, the input side of the friction clutch is directly connected to the machine shaft, for example a crankshaft, in a torque-proof manner, preferably by means of a flange connection.

The friction clutch proposed here has a compact and cost-effective design with (at least) one clutch disc that can be produced in a simple and quality-assured manner.

• - eine Antriebsmaschine mit einer Maschinenwelle;
• - zumindest einen Verbraucher; und
• - eine Reibkupplung nach einer Ausführungsform gemäß der obigen Beschreibung,

wobei die Maschinenwelle mittels der Reibkupplung lösbar mit dem zumindest einen Verbraucher drehmomentübertragend verbunden ist.According to a further aspect, a drive train is proposed having at least the following components:

• - a drive machine with a machine shaft;
• - at least one consumer; and
• - A friction clutch according to an embodiment according to the description above,

wherein the machine shaft is releasably connected to the at least one consumer in a torque-transmitting manner by means of the friction clutch.

The drive train proposed here comprises a friction clutch in one embodiment according to the above description, the friction clutch transferring torque from the drive machine or its machine shaft to at least one consumer, for example the drive wheels in a motor vehicle, switchable, i.e. releasable, by means of an externally applied pressure force on the friction package , accomplished. This by no means excludes reverse torque transmission from the consumer to the machine shaft, in a motor vehicle, for example, to use the engine brake to decelerate the motor vehicle. The prime mover is, for example, an internal combustion engine. In one embodiment, the input side of the friction clutch is connected to the machine shaft in a torque-proof manner and the output side (at least indirectly, for example via a transmission) is connected to the at least one consumer in a torque-proof manner.

The drive train proposed here comprises a friction clutch with a compact and inexpensive design, the at least a clutch disc can be produced easily and with a reliable quality.

According to a further aspect, a motor vehicle is proposed, having at least one drive wheel for propelling the motor vehicle, which drive wheel can be driven by means of a drive train according to an embodiment according to the description above.

The installation space is particularly small in motor vehicles due to the increasing number of components and it is therefore particularly advantageous to use a drive train of small size. With the desired so-called downsizing of the prime mover with a simultaneous reduction in operating speeds, the intensity of the disruptive torsional vibrations is increased, so that it is a challenge to achieve effective damping of such torsional vibrations, which is determined by the design of the prime mover.

This problem is exacerbated in the case of passenger cars in the small car class according to the European classification. The aggregates used in a passenger car of the small car class are not significantly reduced in size compared to passenger cars of larger car classes. Nevertheless, the space available for small cars is much smaller. The motor vehicle proposed here has a drive train with a compact and cost-effective design, the at least one clutch disc being easy to manufacture and quality assured.

Passenger cars are assigned to a vehicle class according to, for example, size, price, weight and performance, this definition being subject to constant change according to the needs of the market. In the US market, vehicles in the subcompact car class are assigned to the subcompact car class according to the European classification, and in the British market they correspond to the supermini class or the city car class. Examples of the small car class are a Volkswagen up! or a Renault Twingo. Examples of the small car class are an Alfa Romeo MiTo, Volkswagen Polo, Ford Ka + or Renault Clio.

• 1: eine Kupplungsscheibe in einer Schnittansicht in einem vormontierten Zustand;
• 2: eine Kupplungsscheibe in einer perspektivischen Darstellung ohne Tellerfeder;
• 3: eine Kupplungsscheibe in einer perspektivischen Darstellung mit Tellerfeder;
• 4: eine Kupplungsscheibe in einer Schnittansicht im montierten Endzustand; und
• 5: ein Antriebsstrang in einem Kraftfahrzeug mit einer Reibkupplung.

The invention described above is explained in detail below against the relevant technical background with reference to the accompanying drawings, which show preferred embodiments. The invention is in no way restricted by the purely schematic drawings, it being noted that the drawings are not dimensionally accurate and are not suitable for defining size relationships. It is shown in

• 1 : a clutch disc in a sectional view in a preassembled state;
• 2 : a clutch disc in a perspective view without a plate spring;
• 3 : a clutch disc in a perspective view with a plate spring;
• 4th : a clutch disc in a sectional view in the assembled final state; and
• 5 : a drive train in a motor vehicle with a friction clutch.

In 1 is a clutch disc 1 with an axis of rotation 2 shown in a sectional view in a pre-assembled state. On the opposite pane 6th lies (here) another friction ring 25th axially (here optionally directly). The axial fastening device 7th , here for example by means of a plurality of spacer bolts 30th formed is in the counter disc 6th for a later, here non-positive, connection axially in the counter disc 6th plugged in. The other friction ring 25th is by means of the fret area 28 of the spacer bolt 30th axially positioned.

The torsion damper flange 4th , which with a shaft connection 27 here is optionally (directly and positively) connected in a torque-stiff manner, lies axially (here optionally directly) on the further friction ring 25th so that the other friction ring 25th here as shown below the torsion damper flange 4th is arranged. Through the torsion damper flange 4th the spacer bolts extend axially through it 30th , with this (in overlap with the collar area 28 ) each have an arcuate opening (not visible here in the illustration) in the torsion damper flange 4th is provided to a relative swing in the circumferential direction 36 around the axis of rotation 2 to enable. On the torsion damper flange 4th a (first) friction ring lies axially opposite (i.e. above, as shown) 8th at. The (first) friction ring 8th is by means of the spacer bolt 30th radial (and here also in the circumferential direction 36 ) in a predetermined position, and preferably also centered. At the radially outer edge 37 of the friction ring 8th lies a disc spring 9 at. With the help of the disc spring 9 is in the fully assembled state, here by means of the interaction of the drive plate 5 (compare 4th ) and the disc spring tongues 29 an axial force 10 applied to the friction rings 8,25 and thus a predetermined frictional engagement with a predetermined frictional force between the torsion damper flange 4th and the friction ring 8th , as well as here the other friction ring 25th generated.

In 2 is the clutch disc 1 according to 1 shown in perspective. In contrast to 1 is the disc spring 9 not shown. The (first) friction ring 8th is by means of the axial fastening device 7th prepositioned. The (first) friction ring 8th shows on its outer edge 37 Tabs 12th with axial extension and has a corresponding number of through openings 11 on. At least one of the through openings 11 is for centering the (first) friction ring 8th by means of the relevant spacer bolt 30th furnished. The tabs 12th are arranged so that they are on the outer edge 37 in the circumferential direction 36 between the spacer bolts 30th lie. A plurality of damper springs are located between the individual bolts 26th arranged, which are set up to dampen torsional vibrations.

In 3 is the clutch disc 1 shown in perspective. Compared to 2 in this illustration is the disc spring 9 immediately on the radially outer edge 37 of the (first) friction ring 8th at. This is positioned so that the tab mounts 13th and the tabs 12th of the (first) friction ring 8th interlock directly in a form-fitting manner. This is the disc spring 9 relative to the friction ring 8th not rotatable. This positioning prevents the diaphragm spring tongues 29 into the riveting area of the spacer bolt during the next assembly step 30th reach. This prevents incorrect assembly. As in 2 described are in free spaces in the circumferential direction 36 between the standoffs 30th Damper springs 26th arranged, which are designed as coil springs and form a common circle with the spacer bolts 30th are arranged tangentially aligned. The disc spring tongues 29 are between the damper spring 26th and the spacer bolt 30th arranged. Thus extend on both sides of the spacer bolt 30th the disc spring tongues 29 the disc spring 9 from the radially outer edge 37 radially inwards. As in 2 are the tabs 12th at the radially outer edge 37 of the (first) friction ring 8th . In the circumferential direction 36 between the tabs 12th are the spacer bolts 30th arranged. In this preferred embodiment there are spacer bolts per 30th two tabs each 12th and tab mounts 13th provided, so these are arranged in pairs.

In 4th is the clutch disc 1 out 1 shown in a fully assembled state in a sectional view. The standoffs 30th the axial fastening device 7th are reshaped, for example riveted. On the plate spring 9 there is now a drive plate 5 at. By means of the formed spacer bolt 30th are the drive plate 5 and the counter disc 6th axially and torque-rigidly connected to one another. As in 1 described, there is a frictional connection between the (first) friction ring 8th or the further friction ring 25th and the torsion damper flange 4th by means of the axial force generated as a result of the structural prestress 10 the disc spring 9 which directly on the (first) friction ring 8th works. Which side of the torsion damper flange 4th the disc spring 9 is arranged, plays for the function of the friction device (including the disc spring 9 and the friction rings 8.25) do not matter. The disc spring 9 is alternatively arranged on the opposite side of the disc. In the left area of the 4th is the in 2 described damper spring 26th shown.

In 5 is purely schematically a motor vehicle 24 with a drive train 14th Shown in plan view, with a prime mover in a transverse frontal arrangement 20th , for example an internal combustion engine, with its motor axis 31 transverse to the longitudinal axis 32 and in front of the driver's cab 33 of the motor vehicle 24 is arranged. The powertrain 14th is for driving the left propulsion wheel 22nd and the right propulsion wheel 23 by means of a torque output from the prime mover 20th furnished. The torque is transmitted by means of a friction clutch 3 interruptible, which between the machine shaft 21 and the transmission input shaft 34 (a transmission) is arranged. The friction clutch 3 includes a friction package here 15th , an entry page 18th and an exit page 19th . The friction package 15th here includes a clutch disc 1 , a first friction plate 16 (Pressure plate) and a second friction plate 17th (Counter plate). The counter plate 17th is axially fixed, with the pressure plate 16 axially displaceable and with the counter plate 17th , and thus with the machine shaft 21 Is connected in a torque-rigid manner. Using the pressure plate 16 there is a frictional connection between the pressure plate 16 the clutch disc 1 and the counter plate 17th made possible, the contact force by means of an external actuating device (not shown here), for example manually by means of a clutch pedal from the driver's cab 33 , generated (normally open) or canceled (normally closed). In the pressed state of the friction package 15th is thus a torque between the input side 18th and the exit page 19th transferable.

With the clutch disc proposed here, a high level of installation security for a plate spring of a torsional vibration damper is achieved even in the case of a confined installation space.

List of reference symbols

1

Clutch disc

2

Axis of rotation

3

Friction clutch

4th

Torsion damper flange

5

Drive plate

6th

Counter disc

7th

Axial fastening device

8th

(first) friction ring

9

Disc spring

10

Axial force

11

Through opening

12th

Tab

13th

Tab mount

14th

Powertrain

15th

Friction package

16

Pressure plate

17th

Counter plate

18th

Entry page

19th

Exit page

20th

Prime mover

21

Machine shaft

22nd

left propulsion wheel

23

right propulsion wheel

24

Motor vehicle

25th

another friction ring

26th

Damper spring

27

Shaft connection

28

Waistband area

29

Belleville spring tongue

30th

Spacer bolts

31

Motor axis

32

Longitudinal axis

33

Driver's cab

34

Transmission input shaft

35

Clutch friction lining

36

Circumferential direction

37

radially outer edge

Claims (7)

Clutch disc (1) with an axis of rotation (2) for a friction clutch (3), having at least the following components: - a torsion damper flange (4); - A drive plate (5); - a counter disc (6); - An axial fastening device (7), by means of which the driver disk (5) and the counter disk (6) are connected to one another axially and in a torque-rigid manner; - A friction ring (8) between the torsion damper flange (4) and the drive plate (5) or the counter plate (6); and - a disc spring (9) for exerting an axial force (10) on the friction ring (8) for frictional engagement, characterized in that the friction ring (8) is positioned in a predetermined manner by means of the axial fastening device (7) and the disc spring (9) is positioned by means of the Friction rings (8) is positioned in a predetermined manner. Clutch disc (1) Claim 1 , wherein the axial fastening device (7) is formed by at least one stepped bolt and the friction ring (8) forms a through opening (11) for each stepped bolt. Clutch disc (1) Claim 1 or 2 , wherein the friction ring (8) has at least one tab (12) with axial extension and the plate spring (9) forms a corresponding tab receptacle (13) for at least one of the tabs (12), the plate spring (9) by means of the tab (12 ) and the corresponding tab receptacle (13) is positioned in a predetermined manner. Clutch disc (1) Claim 2 and 3 wherein the friction ring (8) forms a pair of tabs (12) in at least one of the stepped bolts and the plate spring (9) correspondingly forms a corresponding pair of tab receptacles (13) for the respective stepped bolt. Friction clutch (3) for a drive train (14), having at least the following components: - At least one axially compressible friction package (15) comprising friction plates (16, 17) and at least one clutch disc (1) according to one of the preceding claims, via which a torque can be transmitted in the compressed state; - An input side (18) for receiving a torque; and - An output side (19) for outputting a torque, the input side (18) being connected to the output side (19) in a torque-transmitting manner solely by means of the friction pack (15). Drive train (14) having at least the following components: - a drive machine (20) with a machine shaft (21); - At least one consumer (22,23); and - a friction clutch (3) after Claim 5 , the machine shaft (21) being releasably connected to the at least one consumer (22, 23) in a torque-transmitting manner by means of the friction clutch (3). Motor vehicle (24), having at least one propulsion wheel (22, 23) for propelling the motor vehicle (24), which by means of a drive train (14) after Claim 6 is drivable.

Images