GB2137291A

GB2137291A - Friction clutch

Info

Publication number: GB2137291A
Application number: GB8407813A
Authority: GB
Inventors: Lothar Huber
Original assignee: LuK Lamellen und Kupplungsbau GmbH
Current assignee: LuK Lamellen und Kupplungsbau GmbH
Priority date: 1983-05-26
Filing date: 1984-03-26
Publication date: 1984-10-03
Also published as: NL8402403A; SE8403868D0; SE446027B; SE8403868L; GB8407813D0; GB2137291B

Abstract

A friction clutch for a motor vehicle has a clutch carrier plate (3) which can be secured to the crankshaft (2) of an engine, an axially movable pressure plate (4), a diaphragm spring (5) which is disposed between the pressure plate (4) and the clutch carrier plate (3) and which is supported with radially outward regions against the clutch carrier plate (3) and which engages with radially further inwardly disposed regions the pressure plate (4). Provided between the pressure plate 4 and the clutch carrier plate 3 are torque transmitting leaf springs (26). A counter-pressure plate (12) is axially and non-rotatably secured to the clutch carrier plate (3) by way of spacer means (13). A clutch plate (10, 11) is disposed between the pressure plate (4) and the counterpressure plate (12). To make the clutch at lower cost or smaller or, with given conditions in respect of space, to increase the friction diameter and thus the working capacity, as well as improving operation and increasing service life, the spacer means (13) is formed as a sheet metal member and engages clampingly around the counterpressure plate (12) on the side remote from the engine. <IMAGE>

Description

SPECIFICATION Friction clutch The invention relates to a friction clutch, in particular for motor vehicles, comprising a clutch carrier plate which can be secured to the crankshaft of an internal combustion engine, an axially movable pressure plate, a diaphragm spring which is disposed between the pressure plate and the clutch carrier plate and which bears with radially outward regions against the diaphragm spring and which with radially further inwardly disposed regions engages the pressure plate, wherein torque transmission means are provided between the pressure plate and the clutch carrier plate, a counter-pressure plate which can be axially and non-rotatably fixed to the clutch carrier plate by way of spacer means, and a clutch plate which is to be disposed between the counterpressure plate and the pressure plate.

In such constructions, the space bridging means for forming the space between the counterpressure plate and the clutch carrier plate, which accommodates the clutch plate (at least the friction linings thereof), the pressure plate and the diaphragm spring, are generally axial lugs which are cast on the counterpressure plate which comprises cast iron or, if the clutch carrier plate also comprises cast iron, such axial projections or lugs may also be provided on the clutch carrier plate.As however the lugs or projections which are formed from cast iron must be of relatively large radial dimensions (inter alia for the reason that a high level of bursting strength is required and for technical casting reasons), a relatively large amount of space in the radial direction is therefore required or, under given conditions in respect of space available, the friction engagement diameter cannot be increased. However, the space required by the clutch in the radial direction is also important for the reason that the starter is disposed on the side of the clutch which is remote from the engine and, the greater the radial extent of the clutch, the further is the starter necessarily disposed from the transmission or the axis thereof, and also correspondingly requires space at that location.

Another construction in which the counterpressure plate is a virtually flat plate made from a cast iron and the clutch carrier plate is a sheet metal member has spacer bridging means in the form of axially directed extension portions on the clutch carrier plate which, as already mentioned, comprises sheet metal, and the clutch carrier plate and the counterpressure plate are held together by means of screws which are disposed in the radial space between the axial extension portions and the clutch plate. Such a construction does not provide any advantages whatever, at least in regard to the problems of radial space, in comparison with the construction previously described above, especially as the radial wall thickness of the spacer bridging means is also relatively large, more specifically, corresponding to the relatively great thickness of the sheet metal of the clutch carrier plate.

In accordance with another proposal which however has not been published, the spacer means is a separate sheet metal member which is fixed to the clutch carrier plate and wherein the counter-pressure plate is held in position in the axial direction by a spring ring or circlip which is fitted into a groove in the spacer member. Torque is transmitted by radial arm portions of the counterpressure plate extending into openings in the spacer member. Such a construction is relatively expensive to produce and complicated in construction and manufacture and, as a result of the relatively large wall thickness of the spacer member, as is required by virtue of the spring ring used, a large amount of space in the radial direction is again required and the clutch is as a result also correspondingly heavy and expensive.

The present invention was based on the problem of eliminating inter alia the abovementioned disadvantages of the known friction clutches and providing friction clutches which are distinguished by being of smaller radial size or, with given conditions, by the possibility of increasing the friction engagement diameter, as well as being distinguished by reliability in operation, simpler and less expensive manufacture, and a long working life.

In accordance with the present invention, that is achieved in that the spacer means which is formed as a sheet metal member and which can be fixed to the clutch carrier plate engages clampingly around the counterpressure plate on the side which is remote from the engine. By virtue of that arrangement, the spacer means may be made of considerably smaller thickness of sheet metal, than in the case of the previously disclosed constructions, which in turn constitutes a saving in regard to radial space or permits an increase in friction diameter, as well as providing for a reduction in weight and, as also referred to hereinbefore, affording possible ways of achieving simpler and less expensive manufacture and also ensuring reliability in operation and a long working life.

It is advantageous for the sheet metal member to be in the form of a hat-like or cup-like member, wherein the sheet metal member can be secured for example by screwing to the clutch carrier plate, by means of the edge portion of the sheet metal member, which is in the nature of a hat brim-like configuration.

A clutch of that kind can then be produced and assembled in a particularly simple and inexpensive manner.

It may also be advantageous for the sheet metal member to secure the counterpressure plate both in the axial direction and in the peripheral direction, therefore also taking over the torque transmission function. The counterpressure plate which may comprise for example a casting may be pressed into the hat-like or cup-like sheet metal member. A relatively simple manner of ensuring transmission of torque can be achieved by the counterpressure plate being provided on its at least approximately cylindrical outer periphery with axially extending grooves, with indentations in the at least approximately cylindrical peripheral region of the sheet metal member being formed in relation to such grooves. A particularly desirable construction can be achieved by the individual groove regions and the individual indentations contacting each other at two contact regions.In that arrangement, the contact regions may be disposed respectively on two sides of the point of the indentations, which is at the greatest depth therein.

Another advantageous way of providing for the transmission of torque is afforded by a rivet connection, wherein the portions of the sheet metal member, which is of a hat-like or cup-like configuration, said portions engaging in a radial direction around the counterpressure plate, are connected to the counterpressure plate by way of the rivet connection. It has been found that a particularly advantageous rivet connection is one which is formed by rivets which are fitted in the axial direction.

The rivet connection may be for example in the form of a blind rivet connection. For that purpose, the rivets may be formed by means of hollow rivet pins or pegs which are formed integrally on the sheet metal member. A rivet connection of that kind can be made by the hollow rivets, facing in the axial direction, being formed on the at least approximately radially directed portions of the sheet metal member which clampingly engages around the counterpressure plate, whereafter the counterpressure plate is pressed into the hatshaped or cup-shaped sheet metal member, the hollow rivets engaging into corresponding blind bores and the hollow rivets thereafter being spread in the radial direction thereof and towards the walls of the blind bores.

However, the rivet connection, which is made in the axial direction, between the sheet metal member and the counterpressure plate may also be formed by means of individual rivet elements which are hollow and which are introduced into a blind bore in the counterpressure plate, wherein at least a portion of the section, which is in the blind bore, of each rivet element, is spread radially towards the contours of the blind bore.

The blind bores may each have at least one undercut configuration or profiled configuration which increases the diameter thereof and into which the rivet elements are plastically deformed by being radially spread therein.

The profiled configurations may be for example of a screwthread-like nature.

However, the operation of spreading an at least substantially hollow rivet element may also be effected by driving in a spreader pin which remains in the bore of the rivet element. The spreader pin may be tapered at its end which is towards the friction surface.

The rivet element may be a hollow rivet member with a head formed thereon, which bears against the respective radially directed region of the portion which engages radially behind the counterpressure plate. However, the head of the rivet may also be formed upon or after driving in the spreader element, by a rivet punch impinging on the corresponding region of the hollow rivet during or after the operation of driving in the spreader element. In that connection, it may be of particular advantage for the spreader pin, which remains in the rivet element, to have a tapering portion at its end which is remote from the friction surface, and for the head of the rivet to be peened over radially towards said portion.

It has been found that a particularly advantageous configuration in respect of the sheet metal member is one in which the sheet metal member has radially directed edge portions which, as already mentioned above, may be in the nature of the brim of a hat-like shape and by means of which the sheet metal member is secured to the clutch carrier plate and wherein moreover the annular toothed starter ring is mounted on the side of the edge portions which is remote from the clutch carrier plate. In that arrangement, the starter ring, with the sheet metal member, may be secured to the clutch carrier plate by way of the edge portion of the sheet metal member, by means of a common fixing element.For that purpose, screwthreaded bores may be provided in the clutch carrier plate, into which are fitted screws which pass through the starter ring and the hat brim-like edge portions of the sheet metal member.

It may also be advantageous if, as viewed in the peripheral direction, a section of the edge portion of the sheet metal member, with which same lies against both the starter ring and also the clutch carrier plate, is followed by a section of the edge portion, which is spaced from the toothed ring. That arrangement provides the possibility of ventilation of the friction clutch, in a particularly advantageous manner. It may also be desirable for the hat brim-like edge portion, the toothed ring and the clutch carrier plate to be of such a construction that, as viewed in the peripheral direction, a section of the edge portion of the sheet metal member, with which same bears against the clutch carrier plate, is followed by a section of the edge portion in which there is a spacing between same and the clutch carrier plate.

It may also be advantageous for the radially directed edge portions of the sheet metal member, that is to say, the hat brimlike edge, to carry at least one co-operating profiling for a centering means which is fixed in the clutch carrier plate. By virtue of that arrangement, the pre-assembled unit of counterpressure plate/clutch plate/pressure plate and sheet metal member with toothed ring can be centered in a particularly simple fashion.

It may be advantageous for the centering pin in the clutch carrier plate to be provided in the direct vicinity of the fixing location for the plate or leaf springs which transmit the torque between the pressure plate and the clutch carrier plate. The centering pin may then be at least partially covered in the radial direction by the plate springs, on the outward side of the clutch carrier plate, which is towards the engine, thereby securing it to prevent it from sliding out axially when fitting the clutch.

An advantageous embodiment may also be one in which the rivet for fixing the plate springs to the clutch carrier plate and a centering pin for centering the spacer means or the components connected thereto are fixed in the same region of the clutch carrier plate. In that arrangement, it may be of particular advantage for the plate spring fixing rivet and the centering pin to be formed by a common element.

It may also be advantageous for free spaces or through openings to be provided in the at least approximately cylindrical region of the hat-shaped or cup-shaped sheet metal member, at least approximately at the level of the friction linings of the clutch plate, to ensure suitable ventilation.

However, the sheet metal member which serves as spacer bridging means and for holding or fixing the counterpressure plate and for the transmission of torque between the clutch carrier plate and the counterpressure plate may also be of such a configuration that it does not engage clampingly around the counterpressure plate with a continuous edge portion thereof, but bar portions may extend from the hat brim-like edge or from the axially extending portions of the spacer means, wherein the rivet connection to the counterpressure plate is formed in the radially directed regions, which engage behind the counterpressure plate, of the above-mentioned bar portions.

Further advantageous possible forms of the invention and in relation thereto are set forth in Figures 1 to 8.

In the drawings: Figure 1 shows a sectional view of a friction clutch unit according to the invention, Figure la is a view on an enlarged scale in section taken along line la-la, Figure 2 is a view in the direction of the arrow II in Figure 1, Figure 3 is a view in section taken along line Ill-Ill in Figure 2, Figure 4 is a further detail according to the invention, Figure 5 is a view similar to that shown in Figure 2, but of another embodiment according to the invention, Figure 6 is a view in section taken along line VI-VI in Figure 5, Figure 7 is a view in section taken along line VII-VII in Figure 5, and Figure 8 is a further embodiment in accordance with the invention, in a view corresponding to the section taken along line VI-VI in Figure 5.

The friction clutch 1 comprises a clutch carrier plate 3 which is secured to a crankshaft 2 of which part is shown, an axially movable pressure plate 4, a diaphragm spring 5 which is disposed between the pressure plate 4 and the clutch carrier plate and which bears with radially outward regions 6 against support regions 7 of the clutch carrier plate 3 and which engages the pressure plate 4 with radially further inwardly disposed regions 8, by way of contact cams or projections 9.The diaphragm spring 5 is installed in the prestressed condition and loads the friction linings 10 of the clutch plate 11 towards the counterpressure plate 1 2 which is axially and nonrotatably connected to the clutch carrier plate 3 by way of a spacer means or spacer bridging means 1 3. The spacer bridging means 1 3 is a sheet metal shaped member which is of a hat-like or cup-like shape and which is secured by way of its edge portion 14 to the clutch carrier plate 3, by means of countersunk screws 1 5. The countersunk screws 1 5 also secure the toothed ring 1 6 which is pushed or pressed onto the at least approximately axially extending portions 1 7 of the sheet metal member 1 3. The counterpressure plate 1 2 is pressed into the hat-shaped or cup-shaped spacer bridging member 1 3 and has radially directed portions 1 8 by means of which it clampingly engages over the counterpressure plate so that the pressure plate is thereby fixed in the axial direction.Groove-like or channel-like portions 1 9 which engage radially inwardly from the at least approximately axially extending portions 18 of the hatshaped or cup-shaped sheet metal member 1 3 into portions 20 in the counterpressure plate, which are also in the form of grooves or channels, ensure that the counterpressure plate 1 2 is firmly fixed in the cup-shaped or hat-shaped component in the peripheral direction, thereby providing for the transmission of torque.Figure 1a shows that the axially extending grooved portions 1 9 of the sheet metal member 1 3 and the regions 20 of the counterpressure plate 1 2 are in contact with each other along two contact areas K, that is to say, on respective ones of the two sides of the point of the indentations 1 9, which is at the greatest depth in the radial direction.

Engagement and disengagement of the clutch is effected by a central pushrod 21 which actuates a pressure disc 22 and thus the diaphragm spring 5.

The pressure plate 4 has axial lugs or projections 23 which are disposed at least substantially within the radial extent of the friction linings 10 and which pass through the clutch carrier plate 3, through apertures 24 therein. An end face 25 of the lugs 23 serves as a fixing location for the plate or leaf springs 26 which are provided outside the clutch space which is taken up by the clutch carrier plate 3 on the one hand and the counterpressure plate 1 2 on the other hand, and which are disposed on the side of the space outside the clutch, which is towards the engine side A. The other fixing location 27 for the springs 26 is on the clutch carrier plate 3, more specifically, also on the outward side of the clutch, that is towards the engine side A.The fixing location 27 is on a bulged portion 28 in the clutch carrier plate 3, that bulged portion being directed towards the engine side A, while as viewed in the peripheral direction and towards the fixing location 25-the portion 28 is followed by a portion 29 which is set back in the axial direction.

The springs 26 are secured to the clutch carrier plate 3 by means of rivets 30. Disposed in opposite relationship to the head 31 of the rivet 30 is a flat support surface 32 on the pressure plate, that support surface serving as a contact surface for the rivet 30 in the riveting operation. In that connection, the arrangement may be such that the rivet 30 has a setting head 31 formed thereon and the head 33 which is on the outward side A of the clutch is formed as a closure head, wherein the region 31 which is formed as the setting head bears against the face 32 during the riveting operation.However, the rivet connection may also be of such a nature that the head 33 is the setting head, the rivet is passed through the spring 26 and the opening in the clutch carrier plate 3 and the head 31 is formed as the closure head, the support surface 32 acting in practice as a riveting punch during the riveting operation. At any event, the spacing between the face 32 and the head 31 is so selected as to ensure a satisfactory disengagement or lift movement of the pressure plate 4, even in the new condition of the clutch.

The springs 26 are riveted to the pressure plate by way of a blind rivet connection 34, a rivet element 36 being inserted into a blind bore 35 which is provided with undercut portions (not shown in detail), such as for example a screwthread. The rivet element 36 comprises a hollow body 37 which initially projects beyond the plate springs 26, with a portion which is shown in broken lines. A spreader element 38 which is larger in diameter than the internal bore in the hollow body is driven into the illustrated position in the hollow body 37, with the tapered portion 39 of the spreader element, which is towards the friction surface of the pressure plate, leading in the driving-in operation, whereby the hollow body 37 is enlarged and spread into the undercut configurations.The spreader pin also has, at its end which is remote from the friction surface of the pressure plate 4, a tapering portion 40 which, when the head 41 is formed, is virtually covered or enclosed thereby so that the spreader pin 38 which remains in the hollow body is satisfactorily secured in position therein.

The portion 42 of the clutch carrier plate 3-in the direction in which the plate spring extends to the rivet 30-said region 42 being adjacent to the fixing region at the lugs 23, on the pressure plate side, is a calibrated region and serves as an abutment for the plate springs 26. The spacing between the abutment region 42 and the oppositely disposed region of the plate springs is so selected that, although axial movement of the pressure plate 4 is permitted, at least approximately as far as the maximum position of wear of the friction linings 10 of the clutch plate 11, nonetheless over-extension of the springs 26 is avoided if only the pressure plate 4, the diaphragm spring 5 and the clutch carrier plate 3 are assembled.

For installation in the proper position of the cup-shaped spacer or mounting means 1 3 and the counterpressure plate 1 2 which is connected thereto, upon fitting of those parts and the clutch plate 11 on the clutch carrier plate 3, fitted in the clutch carrier plate 3 is a centering pin 43 which engages into a centering bore 44 however, the centering contour may also be a radially extending slot. The centering contour 44 is provided in a pocket 45, which projects in the axial direction towards the engine, in the region of the edge portion 14 of the spacer bridging means, wherein the region 45 is in turn provided in the region of the bulged portion 28 in the clutch carrier plate 3.

The clamping pin or the clamping sleeve 43 may be provided at least approximately in the region of the springs 26, wherein the springs 26, as shown in broken lines in the bottom region in Figure 1, at least partially cover over the pin 43 with a cover portion 46 thereby ensuring that it is satisfactorily held in position and cannot be pressed out when assembling the spacer or mounting means 1 3.

Figure 4 shows that the fixing rivet for connecting the springs 26 to the clutch carrier plate 3 and the centering means for the spacer or mounting means 1 3 may also be formed by a common element 47. The element 47 has an abutment shoulder 48, a centering region 49 and the closure head 50 which is formed on the plate spring side. The centering contour 44 is here illustrated in the form of a radial slot which is open in an outward direction. However, it could also be in the form of a radially elongate slot which terminates before the outside contour of the cover means. That eliminates any effects which could occur due to slight radial movements when pressing on the toothed ring.

Reference is made to Figures 5 to 8 to show that at least the radially extending portion 1 8 shown in Figure 1 is not of a peripherally closed configuration, but the embodiments shown in Figures 5 to 8 provide that from the hat brim-like edge 14, there first extend portions 1 7a which are at least approximately cylindrical, that is to say, which extend axially, and which are of a peripherally closed configuration. Adjoining same are portions 51 which extend in a bar-like configuration and which have radially extending portions 1 8a that engage behind the counterpressure plate 12.

For the purposes of torque transmission, instead of the profiled means 19/20 in Figures 1 and 2, this construction has a rivet connection 52 by way of rivets which point in the axial direction.

The rivet connection 52 shown in Figure 6 is formed in a similar manner to the rivet connection 34, that is to say, also in the form of a blind rivet connection. In this case also, a rivet element 53 which comprises a hollow body 54 and a spreader element 56 which projects into the stepped bore 55 is intr6- duced into the bore 57 in the region 1 8a and into the blind bore 58 in the counterpressure plate 12. The blind bore 58 has radial undercut portions.After the spreader pin 56 which is provided with the wedge-like or conical portion 59 has been driven into the rivet element, in which case the means anchoring the rivet element 53 in the blind bore is formed by displacement of the material of the hollow body 37, the cap-shaped component 1 3 is sure to be satisfactorily non-rotatably connected to the counterpressure plate 1 2.

The rivet head 60 is formed after the spreader element 56 has been driven in, or in the last phase of the driving-in operation, in which respect the wedge-shaped or conical portion 61 which is remote from the friction surface of the counterpressure plate 1 2 is at least partially enclosed by peening over portions of the hollow body inwardly in a radial directon, and thereby secured in the axial direction.

The rivet connection 52 shown in Figure 8 is formed by the hollow rivets 62 which are formed on the portion 1 8a and which are expanded in their radial direction after the counterpressure plate has been fitted into the sheet metal member and after the rivet pins 62 have been accommodated in the corresponding blind bores 63.

In order to ensure good ventilation and cooling of the friction clutch, shown in Figure 1, in the region of the at least substantially cylindrically extending wall portion 17, and at the radial level of the friction linings 10, is an aperture 64 of which there are a plurality distributed around the periphery of the arrangement.

However, the sheet metal member 1 3 may also be of such a construction that instead, as shown in Figures 5 to 8, the radially inwardly facing portion 1 8a extends in a continuous configuration, as shown in Figures 1 to 4, and wherein at least the edge portions 14 are of a bar-like configuration adjoining an at least substantially closed cylindrical portion 1 7 (as in Figure 1).

It will also be seen from Figure 1 that the hat brim-like edge portion 14 extends in a corrugated or wavy configuration, wherein a section 1 4b of the edge portion of the sheet metal member, with which it bears against both the starter ring and against the clutch carrier plate 3, is followed by a section of the edge portion or a pocket 45, with a space being provided between the section 44a of the edge portion and the toothed ring 16.

In addition, also as viewed in the peripheral direction, the edge is of such a configuration that a section 44a with which it bears against the clutch carrier plate 3 is followed by an edge portion section 65, with a spacing between same and the clutch carrier plate 3.

Claims

1. A friction clutch, in particular for motor vehicles, comprising a clutch carrier plate which can be secured to the crankshaft of an internal combustion engine, an axially movable pressure plate, a diaphragm spring which is disposed between the pressure plate and the clutch carrier plate and which bears with radially outward regions against the diaphragm spring and which with radially further inwardly disposed regions engages the pressure plate, wherein torque transmission means are provided between the pressure plate and the clutch carrier plate, a counterpressure plate which can be axially and non-rotatably fixed to the clutch carrier plate by way of spacer means, and a clutch plate which is to be disposed between the counterpressure plate and the pressure plate, wherein a sheet metal shaped member which can be secured to the clutch carrier plate serves as the spacer means, characterised in that the sheet metal member (13) engages clampingly around the counterpressure plate (12) on the side (B) which is remote from the engine.

2. A friction clutch according to claim 1 characterised in that the sheet metal member (13) is of a hat-like or cup-like configuration.

3. A friction clutch according to claim 1 or claim 2 characterised in that the counterpressure plate (12) is fixed by way of the sheet metal member (13) both in the axial direction and in the peripheral direction.

4. A friction clutch according to one of claims 1 to 3 characterised in that the counterpressure plate (12) is pressed into the hatlike or cup-like sheet metal member (13).

5. A friction clutch according to one of claims 1 to 4 characterised in that the counterpressure plate (12) has grooves (20) extending in the axial direction on its at least approximately cylindrical outer periphery (17), indentations (19) in the at least approximately cylindrical peripheral region of the sheet metal member (13) being formed in relation to said grooves (20).

6. A friction clutch according to claim 5 characterised in that the individual groove regions (20) and the individual indentations (19) are in contact with each other at two contact regions (K).

7. A friction clutch according to claim 5 or claim 6 characterised in that the contact regions (K) are disposed on respective sides of the point of the respective indentations (19), which is at the greatest depth.

8. A friction clutch according to one of claims 1 to 7 characterised in that the regions (18, 18a) of the hat-like or cup-like sheet metal member (18), which engage around the counterpressure plate (12) in the radial direction, are connected to the counterpressure plate (12) by way of a rivet connection (52).

9. A friction clutch according to claim 8 characterised in that the rivet connection is formed by rivets (53, 62) which extend in the axial direction.

10. A friction clutch according to claim 9 characterised in that the rivet connection is a blind rivet connection (52).

11. A friction clutch according to claim 9 or claim 10 characterised in that the rivets are formed by means of hollow rivet pins (62) which are formed integrally on the sheet metal member (13 at 18a).

12. A friction clutch according to one of claims 1 to 11 characterised in that the sheet metal member has radially directed edge portions (14) by way of which it is secured to the clutch carrier plate (3) and that the annular starter ring (16) is mounted on the side of the edge portions which is remote from the clutch carrier plate.

1 3. A friction clutch according to claim 1 2 characterised in that the starter gear ring (16) and the sheet metal member (13) are secured to the clutch carrier plate (3) by way of the edge portions (14) of the sheet metal member (13), by a common fixing element (15).

14. A friction clutch according to claim 12 or claim 1 3 characterised in that screwd threaded bores are provided in the clutch carrier plate (3) for securing the toothed ring (16) and the sheet metal member (13) by way of the edge portions (14) of the latter, by means of screws (15).

1 5. A friction clutch according to one of claims 1 2 to 14 characterised in that, as considered in the peripheral direction, an edge portion section (14b) of the sheet metal member (1 3), with which said member bears both against the starter ring (16) and against the clutch carrier plate (3) is followed by an edge portion section (44a) which is spaced from the starter ring.

1 6. A friction clutch according to one of claims 12 to 16 characterised in that, as viewed in the peripheral direction, an edge portion section (44a) of the sheet metal member (13), with which same bears against the clutch carrier plate, is followed by an edge portion section (65) in which there is a spacing between same and the clutch carrier plate (3).

1 7. A friction clutch according to one of claims 1 to 1 6 characterised in that the sheet metal member has radially directed edge portions (18) which carry a co-operating profiled means (44) for a centering means (43) which is fixed in the clutch carrier plate (3).

1 8. A friction clutch according to one of claims 1 to 1 7 characterised in that apertures or through openings (64) are provided in the at least approximately cylindrical portion (17) of the cup-like or hat-like sheet metal member (13) at least approximately at the level of the friction linings (10) of the clutch plate (11).

19. A friction clutch according to one of claims 1 to 1 8 characterised in that the hatlike or cup-like sheet metal member (13) has bar portions (51) which are distributed around the periphery thereof.

20. A friction clutch according to claim 1 9 characterised in that the bar portions (51) extend from radially directed edge portions (14) which are of a hat brim-like configuration or at least approximately cylindrically extending portions (17a) which are provided adjoining said radially directed edge portions (14).

21. A friction clutch according to one of claims 1 to 20 characterised in that the radially extending edge portions (13) are of a barlike configuration.

22. A friction clutch according to claim 21 characterised in that the bar portions extend substantially from the at least approximately cylindrically extending portions (17) of the sheet metal member (13).

23. A friction clutch in particular according to one of claims 8 or the following claims characterised in that the rivet connection (52) between the sheet metal member (13) and the counterpressure plate (12) is formed by means of hollow rivet elements (54, 62) which are each inserted into a respective blind bore (58, 63) in the counterpressure plate (12) and at least a portion of the section of each rivet element (53, 62), which is disposed in the blind bore, is spread radially towards the contours of the blind bore.

24. A friction clutch according to claim 23 characterised in that the blind bores (58, 63) each have at least one undercut configuration or profiled configuration which increases the diameter thereof and into which the rivet elements (54, 62) are plastically deformed by being radially spread.

25. A friction clutch according to claim 24 characterised in that the profiled configurations are of a screwthread-like nature.

26. A friction clutch according to one of claims 23 to 25 characterised in that the spreading action is produced by driving in a spreader pin (56) which tapers at its end which is towards the friction surface and which remains in the bore (55) of the rivet element (54).

27. A friction clutch according to one of claims 23 to 26 characterised in that the rivet element (54) is a hollow rivet body with a head formed thereon.

28. A friction clutch according to one of claims 23 to 27 characterised in that, at its end which is remote from the friction surface, the spreader pin (56) has a tapering portion (61) and the head (60) of the rivet (53) is peened over radially towards said portion (61).

29. A friction clutch according to one of claims 1 4 and the following claims characterised in that the centering pin (43) is provided in the clutch carrier plate (3) in the direct vicinity of the plate spring fixing location (27).

30. A friction clutch according to claim 29 characterised in that the centering pin (43) is at least partially covered by the plate springs (26) in the radial direction on the outward side (A), which is towards the engine, of the clutch carrier plate.

31. A friction clutch according to at least one of the preceding claims characterised in that the rivet (30) for fixing the plate springs (26) to the clutch carrier plate (3) and a centering pin (43) for centering the spacer means (13) or the components connected thereto are fixed in the same region of the clutch carrier plate (3).

32. A friction clutch according to claim 31 characterised in that the plate spring fixing rivet and the centering pin (43) are formed by a common element (47).