GB2232225A

GB2232225A - A clutch disc assembly

Info

Publication number: GB2232225A
Application number: GB9011962A
Authority: GB
Inventors: Gerhard Bittenbring; Wolfgang Grosspietsch; Werner Wisner; Erich Scheer; Thomas Schubert; Ernst Muller; Hilmar Gobel; Adolf Ziegler; Andreas Foerster
Original assignee: Fichtel and Sachs AG
Current assignee: ZF Sachs AG
Priority date: 1989-06-03
Filing date: 1990-05-29
Publication date: 1990-12-05
Anticipated expiration: 2010-05-29
Also published as: DE3918214C2; GB9011962D0; FR2652138B1; GB2232225B; DE3918214A1; FR2652138A1

Description

4 1 1-1 A CLUTCH DISC ASSEMBLY This invention relates to a clutch disc

assembly having a disconnectible idling damper. Such a clutch disc assembly is known, for example, from DE- OS 2 950 146.

An object of the invention is to provide a more compact construction of such a clutch disc assembly, the manufacture and also the tuning facility being in addition simplified.

According to the invention there is provided a clutch disc assembly- for a motor vehicle clutch comprising (a) a hub, (b) a lining carrier provided with friction linings and adapted to rotate about a common axis of rotation and in relation to the hub, (c) a load-rotational oscillation damper dimension for load operation and disposed in the torque transmission path between the lining carrier and the hub and comprising a hub disc coupled to the hub having limited rotary clearance, and, disposed axially on either side of the first hub disc two first side plates connected to each other and connected rigidly to the lining carrier and a plurality of firs t springs which couple the first side plates in rotationally elastic manner to the first hub disc, (d) disposed in the torque transmission path between the first hub disc and the hub and dimensioned for idling operation, an idling oscillation damper with, connected rigidly to the hub a second hub disc, two second side plates rotationally rigidly 11-1 3 - 2 connected to each other and to the first hub disc and disposed axially on either side of the second hub disc, and at least one second spring coupling the second side plates in rotationally elastic manner to the second hub disc and which is disposed at a smaller radial distance from the axis of rotation than the first springs, (e) a locking device with at least one locking member adapted for movement into a position in which it locks the idling oscillation damper and away f rom a position which released the idling damper, in a torque transmission path between the first hub disc and the hub, characterised in that the second hub disc and the second side plates are disposed axially between the first hub disc and one of the two first side plates and in that the locking member is mounted on one of the hub discs and cooperates with an abutment on the other hub disc.

By incorporating the idling damper into the space between the hub disc and a cover plate on the load damper, both a more compact construction and also an outwardly better protected damper can be achieved. Furthermore, disposing the locking device directly between the two hub discs of the two damper arrangements results in a very compact construction.

1 1 1 According to a further feature of the invention, there is provided as a locking device and constructed as a lever at least one centrifugal weight which is controlled by centrifugal force and a coil spring, the turns of which extend in a plane at right-angles to the axis of rotation of the clutch disc, directly beside the centrifugal weight. Such a disposition of the centrifugal weight return means permits of a quite minimal space requirement while at the same time ensuring a compact construction of centrifugal weight. In addition, a coil spring is particularly suitable for the present application since it makes it possible to show a very flat spring characteristic. This flat spring characteristic permits of a precise switching behaviour.

A possible structural development advantageously envisages disposing in the hub disc of the load damper a bearing pin for holding a centrifugal weight which at the same time ensures rotationally rigid entrainment in respect of the two side plates or cover plates of the idling damper, and with this construction the centrifugal weight, in the operative position, has an extension which engages a depression disposed in the outer region of the hub disc of the idling damper.

The bearing bolt has thereby a first guidance diameter in the region of the centrifugal weight which is greater than the adjacent diameter in the riveting zone between hub disc and the cover plate of the idling damper associated with this latter for reciprocal rigid connection. In the direction of the other cover plate of the idling damper, the bearing bolt is likewise provided with corresponding stepped diameters in order to produce a riveting arrangement and in order to keep free an axial space for the coil spring. Thus, the bearing bolt serves both as a 11 rotationally rigid connection between the hub disc of the load damper and the cover plates of the idling damper and also as a means of guiding the centrifugal weight. The second cover plate of the idling damper is provided with an axially bent over flap radially outside the centrifugal weight which serves as an abutment in the operative position, its end being guided in an aperture in the first cover plate.

Provided radially within the centrifugal weight is a further axially bent over flap to serve as an abutment for the inoperative position, being bent axially out of one of the two cover plates of the idling damper.

A further structural development envisages the locking device which consists of at least one centrifugal weight, being so constructed that the centrifugal weight is rotatably mounted directly on a radial extension of the hub disc of the idling damper, the centrifugal weight being substantially U-shaped, its two substantially peripherally extending arms engaging around the two sides of the extension and having a riveted journal to serve as a pivotable mounting in a bore in the extension and in the operative position having an extension which engages an inwardly directed matching contour of the hub disc of the load damper which is disposed radially outside the centrifugal weight. From the loading point of view, this arrangement is very favourable since the centrifugal weight is disposed centrally of the hub disc of the idling damper. The matching contour into which the centrifugal weight engages when in the operative position consists of a component which is riveted onto the hub disc of the load damper and which has, bent over substantially at a rightangle, a flap which extends radially outside the A centrifugal weight. This flap passes through a corresponding window in the hub disc and is fixed here without clearance on two peripherally remote edges. With this construction, the extension of the centrifugal weight which produces the locking action is, in respect of its axis of rotation, disposed on the side of the centre of gravity and the flap on the hub disc of the load damper is at the same time constructed as an abutment, in the operative position.

For simpler manufacture, the centrifugal weight is constructed in two parts - with a base part consisting of an arm and, disposed in one piece therewith and thereon, a weight part which in an axial direction is longer than the thickness of the hub disc in the region of the radial extension, and a cover which forms the second arm and which is connected to the base part by a rivet in the region of the weight part. For axially friction-free accommodation of the coil spring, a second guidance diameter is provided on the journal and this is greater than the first guidance diameter, the axial extension of the second guidance diameter being greater than the thickness of the material of the coil spring.

In consideration of the relatively minimal material thickness of the coil spring provided, the inner end of the coil spring is expediently just clamped. With this type of f ixing, there is no need to drill a relatively thin hole; instead, the substantially tangentially extending end of the spring projects into a depression which is, for example, in the f orm of a portion of a circle and which, in the second guidance diameter, is of open construction on the side facing the cover or the cover plate, its axial extension being slightly smaller than the material thickness of the spring. Thus, the end of the spring can be axially clamped by the riveting process.

The invention will be explained in greater detail hereinafter with reference to a plurality of embodiments. In detail, the accompanying drawings show:

Figs.1 & 2 the principle of the two main embodiments; Figs.3 to 5 the partial longitudinal section III-III, the partial view corresponding to the section IV-IV and a detail of the spring fixing; Figs.6 to 8 the partial longitudinal section VI-VI, the partial view according to section VII-VII and a detail in respect of the construction and fixing of the centrifugal weight.

Fig. 1 shows in principle the construction according to Figs. 3 to 5. A clutch disc 1 has its hub 5 rotationally rigidly disposed on a gear shaft, not shown, both being able to rotate about the axis of rotation 3. The clutch disc 1 comprises a load damper and an idling damper. The load damper consists of the hub disc 11 which, by means of teeth 12, is fitted with clearance in a peripheral direction onto the hub 5. The clearance in the teeth 12 is as great as the range of action of the idling damper. On both sides of the hub disc 11 there are side plates or cover plates 9 and 10 which are connected to each other in rotationally rigid fashion, one of them carrying the friction linings 4. For reciprocal rotationally elastic connection, a plurality of peripherally distributed springs 6 are provided which are disposed in corresponding windows in the hub disc 11 and in the cover plates 9 and 10. The idling damper of the clutch disc 1 is disposed between the hub disc 11 and one cover plate 10. It 1 c consists of a hub disc 13 which is rotationally rigidly connected to the hub 5, two side plates or cover plates 15 and 16 disposed one on each side of the hub disc 13 and springs 7 which are likewise accommodated in corresponding windows in hub disc and cover plates. Furthermore, at least one centrifugal weight 19 is provided which is constructed as a doublearmed lever, which is effective between the hub disc 11 of the load damper and the hub disc 13 of the idling damper. Figs. 3 to 5 show the details of the embodiment.

Figs. 3 and 4 show the partial longitudinal section IIIIII or the partial view corresponding to the section IV-IV through a clutch disc with a load and an idling damper and with a centrifugal force dependent bridging of the idling damper. Both damping devices are disposed on a common hub 105 which is rotationally rigid on a gear shaft, not shown, all the parts being able to rotate about an axis of rotation 103. Mounted on the hub 105 is a hub disc 111 which is part of the load damper. The hub disc 111 has teeth 112 by which it is fitted onto the hub 105, the teeth 112 having a clearance in a peripheral direction corresponding to the range of action of the idling damper. The hub disc 111 is axially enclosed on both sides by respective cover plates 109 and 110, there being between the two parts the springs 106 and which are effective in a peripheral direction. Not essential to the invention are the f riction means 121 or 122 shown in Fig. 3 and which, in conjunction with the springs 106, complete the load damping device. Disposed between the cover plate 110 and the hub disc 111 are the parts of the idling damper which consist of the hub disc 113, the bilaterallydisposed cover plates 115 and 116 and corresponding springs 107. The hub disc 113 is rigidly connected to the hub 105. As can be seen especially from Fig. 4, the 1 l- - windows 136 in the hub disc 113 are provided to accommodate the springs 107 while the windows 135 in the hub disc Ill are intended to accommodate the springs 106. In the space radially outside the hub disc 113 there is in a peripheral sense at least one centrifugal weight 119 guided by a bearing bolt 125 which is rigidly disposed in the hub disc 111 and thi axis 123 of which extends parallel with the 'axis of rotation 103. The bearing bolt has in the region of the centrifugal weight 119 a first guidance diameter 128 on which the centrifugal weight is rotatably mounted. In the direction of the hub disc 111 of the load damper, the bearing bolt 125 has a diameter 129 which is smaller than the first guidance diameter 128 so that the step which is thus created allows the cover plate 115 of the idling damper to be rigidly riveted to the hub disc 111 of the load damper. Adjacent the first guidance diameter there is, pointing away from the hub disc 111, a second guidance diameter 130 which has a smaller diameter than the first guidance diameter 128. Furthermore - pointing away from the hub disc 111 - the bearing bolt 125 has once again a smaller diameter 131 which is provided for riveting to the cover plate 116 of the idling damper. By reason of the step between the two diameters 130 and 131, the cover plate 116 is axially fixed and by reason of the correspondingly great axial extension of the second guidance diameter 130, the necessary axial clearance is provided for the coil spring 124 which is disposed therein. This coil spring 124 is disposed concentrically of the axis 123 of the bearing bolt 125 and its radially inner spring end 138 is fixed, for example, in an axial bore 141 in the cover plate 116. In accordance with Fig. 4, the radially outer spring end 139 is fixed, for example, in a substan-tially radially extending bore 142 in the centrifugal weight 119. The 1 c cover plate 116 of the idling damper is, radially outside the centrifugal weight 119, provided with an axially bent over flap 132 which engages around the centrifugal weight and the end of which engages a corres- ponding aperture 145 formed by the other cover plate 115. Together with the abutment edge 146, this flap 132 represents a fixing in the operative position of the centrifugal weight 119. In the position of rest, the centrifugal weight 119 has an abutment edge 147 which is fixed in respect of-a flap 133 which is bent out of one of the two cover plates 115 or 115 and which points in an axial direction.

Briefly, the bridging of the idling damper functions in the following way:

Fig. 1 shows the inoperative position of the clutch disc. The clearance of the tooth system 112 is distributed on both sides of the corresponding teeth. When torque is applied during traction by the vehicle corresponding to the arrow F and when a greater torque than corresponds to the capacity of the idling damper is being transmitted, the tooth system 112 is clearance free in the traction direction so that at a rotary speed which is, for example, above the idling speed, the centrifugal weight 119 sees its eccentrically mounted centre of- gravity pivot outwardly against the force of the coil spring 124, the extension 126 correspondingly pivoting radially inwardly and comifig to a standstill virtually without clearance opposite the inner contour 127 of the hub disc 113. This position is accurately fixed by the abutment edge 146 and the flap 132. In this condition which, according to the speed of rotation, is established at driving torque, it is possible when the throttle is suddenly removed that the idling damper may be blocked in terms of operation so that C' only the load damper operates and the so-called "load change beat" is avoided. With a corresponding drop in rotary speed and upon change over to traction, the centrifugal weight is able to pivot back again into its position of rest as shown in Fig. 4.

With regard to Fig. 41 it should be further mentioned that a window 134 is shown in the hub disc 111. of the load damper and in it there is a spacer piece 137. Window and spacer piece establish the maximum possibility of rotation between the hub disc 111 and the cover plates 109 and 110 of the load damper.

Fig. 5 shows an advantageous alternative fixing of the inner spring end 140 of the coil spring 124. In order to circumvent the relatively thin bore 141 required in Fig. 3, here the spring end 140 is clamped axially. For this purpose, the second guidance diameter 130 of the bearing bolt 124 is provided with a depression 144 shaped like a portion of a circle. Starting from the second guidance diameter 130, this depression 144 is open as it points away from the first guidance diameter 128 and has a maximum radial extension which corresponds substantially to the material cross-section of the coil spring 124. Thus, the depression 144 lies substantially on the diameter of the rivet diameter 131. In an axial direction, this depression 144 is slightly smaller than the material cross-section of the coil spring 124 so that upon riveting of cover plate 116 and bearing bolt 125 the spring end 140 is clamped axially.

Fig. 2 is a view showing the principle of a clutch disc 2 the details of which are explained hereinafter with reference to Figs. 6 to 8. The coupling disc 2 comprises 1 k an idling damper and a load damper, both of which are disposed on a hub 5 which is rotationally rigid on a gear shaft, not shown. All the parts are able to rotate about the axis of rotation 3. The load damper consists of a hub disc 11 which is connected to the hub 5 via a tooth system 12 with clearance in a peripheral direction. The amount of the clearance corresponds to the range of action of the idling damper. Disposed on both sides of the hub disc 11 are side plates or cover plates 9 and 10, one of which carries the friction linings 4. Both are connected rigidly to each other while being kept spaced apart. Disposed in corresponding windows in the hub disc 11 and in the cover plates 9 and 10 there are springs 6 which, when torque is applied, permit of reciprocal rotation. Between the hub disc 11 and one cover plate 10 there is an idling damper which consists of a hub disc 14, side plates or cover plates 17 and 18 disposed on both sides thereof and springs 7. The hub disc 14 of the idling damper is rigidly mounted on the hub 5 and the two cover plates 17 and 18 are rotationally rigidly connected to the hub disc 11 of the load damper. Between the radially outer zone of the hub disc 14 of the idling damper and the hub disc 11 of the load damper there is at least one centrifugal weight 20 which, above a specific rotary speed, brings about a blocking of the idling damper in that a rigid connection is established between the two hub discs 11 and 14. Consequently, the hub disc 11 is no longer able to take effect within the clearance of its teeth-12.

Figs. 6 and 7 show as partial longitudinal section VI-VI or a partial view corresponding to the section VII-VII through the alternative according to Fig. 2. The hub disc 205 is rotationally rigid on a gear shaft, not shown, and is able to rotate about the axis of rotation 203 1 Disposed on the hub 205 is a hub disc 211 of a load damper, both parts being connected with clearance in a peripheral direction via teeth 212. This clearance, as is well known, corresponds to the range of effect of the idling damper. On both sides of the hub disc 211 there are cover plates 209 and 210 which are rotationally elastically coupled to the hub disc 211 and the way they function in principle is described in Fig. 2. Between the hub disc 211 of the load damper and one cover plate 210 there is the idling damping device consisting of a hub disc 214 which is rigidly connected to the hub 205, then, disposed on both sides of the hub disc 214, cover plates 217 and 218 as well as corresponding springs 207 in the windows of both sub-assemblies. Furthermore, two friction devices 221 and 222 are provided which certainly have nothing to do with the way the shut-down of the idling damper functions.

The hub disc 214 of the idling damper comprises a radial extension 252 provided with a bore which extends concentrically of the axis 223 and thus parallel with the axis of rotation 203 and which serves to hold a pivotable centrifugal weight 220. As can be seen especially in Fig. 8, this centrifugal weight 220 which is constructed as a lever consists of a plurality of parts. The base part 254 comprises an arm 256 and, disposed in one piece thereon, a weight part 255 adjacent to which there is a second arm constructed as a cover 257. Both parts are connected to each other by a rivet 258. The two arms 256 and 257, when in the installed situation, extend substantially tangentially and extend to both sides of the radial projection 252 of the hub disc 214. In the region of the two arms 256 and 257, a rivet journal 253 is disposed which passes through the bore in the radial extension 252 and constitutes the mounting of the centrifugal weight 220.

1 In its middle portion, the journal 253 has a first guidance diameter 259 which is inserted without clearance into the bore in the extension 252. In the direction towards the arm 256, the first guidance diameter 259 is followed by a smaller diameter 260 which, via an axial abutment, serves for riveting to the arm 256. On the opposite side, the first guidance diameter 259 is followed by a second guidance diameter 262 which has a larger outside diameter than the first guidance diameter 259 while its axial extension is at least somewhat greater than the material thickness of the coil spring 224. Immediately adjacent the second guidance diameter 262 there is once again a smaller diameter 261 so that at the axial shoulder between the two diameters 261 and 262, riveting of the journal 253 can take place in respect of the arm 257. The space radially outside the second guidance diameter 262 is provided to accommodate the coil spring 224 which in this way is in an axial direction kept clear of friction forces between the extension 252 and the arm 257. In the present case, the coil spring has its inner end 238 inserted into an axially extending bore 241 while its radially outer end 239 is inserted into a radially outwardly open depression 243 in the arm 257 of the centrifugal weight 220. The centrifugal weight 220 is maintained by the pretensioning force of the coil spring 224 in a position of rest which is shown in Fig. 7, an abutment edge 247 of the centrifugal weight 220 coming to bear on an edge 251 of the hub disc 214. Radially outside the centrifugal weight 220, there extends a part of the component 248 which is fixed on the hub disc 211 of the load damper. This component 248 is placed on that side of the hub disc 211 which is remote from the centrifugal weight 220 and is riveted by use of a rivet 263. It extends radially outwardly and is provided with a substantially axially angled over flap 249 1 k n which passes through a window 234 in the hub disc 211 and for fixing purposes bears on two oppositely disposed window edges without clearance. With a radially inwardly directed edge 250, the f lap 249 serves as a path limiter for the operative position of the centrifugal weight 220 with its abutment edge 246. Adjacent the edge 250 of the flap 249 a matching contour 227 extends radially oblique inwardly and, together with the extension 226 of the centrifugal weight 220, it constitutes the locking device for the idling damper. Furthermore, Fig. 7 at least gives an indication of how the windows 235 in the hub disc 211 are constructed for the torsion springs 6 and the disposition of the windows 236 in the hub disc 214 is likewise shown. The abutment for maximum rotation of the load damper is here illustrated by spacers 237 which are disposed in the two cover plates 209 and 210 and which cooperate with peripheral edges of the window 234.

In principle, the mode of action of the switch-off device according to Figs. 6 to 8 does not differ from the previous description. Here, too, a torque greater than that applied by the idling damper has to be accommodated and a corresponding rotary speed has to be available so that the centrifugal weight 220 pivots about its pivoting axis 223 against the force of the coil spring 224, its extension 226 engaging the matching contour 227 of the flap 249. Thus, the idling damper is bridged and does not have to be traversed if there is an abrupt change in torque.

z 1

Claims

CLAIMS:

A clutch disc assembly with a torsion vibration damper for a) a hub (5; 105; 205) b) a lining carrier provided with friction linings (4) and adapted to rotate about a common axis of rotation (3; 103; 203) and in relation to the hub (5; 105; 205) a load-rotational oscillation damper dimension.-for load operation and disposed in the torque transmission path between the lining carrier and the hub (5; 105; 205) and comprising a hub disc (11; 111; 211) coupled to the hub (5; 105; 205) via teeth (12; 112; 212) having limited rotary clearance, and, disposed axially on either side of the first hub disc (11; 111; 211) two first side plates (9 10; 109, 110; 209, 210) connected to each other and connected rigidly to the lining carrier and a plurality of first springs (6; 106; 206) which couple the first side plates (9y 10; 109 110; 209 210) in rotationally elastic manner to the first hub disc (11, 111; 211) disposed in the torque transmission path between the first hub disc (11; 111; 211) and the hub (5; 105; 205) ^ and dimensioned for idling operation, an idling rotational oscillation damper with, connected rigidly to the hub (5; 105; 205) a second hub disc (13; 113; 213), two second side plates (15, 16; 1151 116; 215 216) rotationally rigidly connected to each other and to the first hub disc (11; 111; 211) and disposedaxially on d) 1 I- i 1 16 - either side of the second hub disc (13; 113; 213), and at least one second spring.(7; 107; 207) coupling the second side plates (15, 16; 1152 116; 215 216) in rotationally elastic manner to the second hub disc (13; 113; 213) and which is disposed at a smaller radial distance from the axis of rotation (3; 103; 203) than the first springs (6; 106; 206); a) a locking device with at least one locking member (19,.20;.119, 220) adapted for movement into a position in which it locks the idling oscillation damper and away from a position which releases the idling damper, in a torque transmission path between the first hub disc (11; 111; 211) and the hub (5; 105 205), characterised in that the second hub disc (13; 113; 213) and the second side plates (15, 16; 1159 116; 2159 216) are disposed axially between the first hub disc (11; 111; 211) and one of the two first side plates (9, 10; 1092 110; 2092 210) and in that the locking member (19 20; 119; 220) is mounted on one of the hub discs (11, 13; 1119 113; 2117 213) and cooperates with an abutment (127; 227) on the other hub disc.

2.

A clutch disc assembly according to claim 1, characterised in that the locking device is constructed as a centrifugal weight lever (119; 220) mounted on one hub disc (111; 213) by means of a bearing bolt ( 125; 253) to pivot axially parallel with the axis of rotation (103; 203) of the hub (105; 205) and in that the restoring spring is constructed as a coil spring (124; 224) which encloses the bearing bolt (125; 253) and which is disposed in a plane at z k - right-angles to the axis of rotation of the hub (105; 205) and directly alongside the centrifugal weight lever (112; 220).

A clutch disc assembly according to claim 3, characterised in that the bearing bolt (125)' of the centrifugal weight lever (119) projects away from the first hub disc (111) towards the second hub disc (113), the centrifugal weight lever (119) comprising an extension (126) which in the locked position of the centrifugal weight lever (119) engages a depression (127) in the region of the outer periphery of the second hub disc (113).

A clutch disc assembly according to claim 3, characterised in that the bearing bolt (125) connects the second side plates (115, 116) rigidly to the first hub plate (111) and is stepped for axial fixing, the diameter of a first guide area (128) which mounts the first guide area (128) is greater than the diameter of a first riveting zone (129) which connects the first hub disc (111) to the axially adjacent second side plate (115), being greater than the diameter of a second rivet zone (131) supporting the other second side plate (116).

5.

A clutch disc assembly according to claim 4, characterised in that the coil spring (124) is disposed -between the centrifugal weight lever (119) and one of the second side plates (115, 116), particularly between the centrifugal weight lever (119) and the second side plate (116) which is remote from the first hub disc (111).

A clutch disc assembly according to claim 5, characterised in that the coil spring (124) engages around a second guide zone (130), the diameter of which is smaller than the diameter of the first guide zone (128) while being greater than the diameter of the adjacent riveting zone (131).

7.

8.

9.

A clutch disc assembly according to one of claims 3 to 6, characterised in that one of the second side discs (115 116), particularly the second side disc (116) which is remote from the first hub disc (111) has radially outside the second hub disc (113) an axially bent over lug (132) which engages an aperture (145) in which ever is the other second side plate (115) and forms an abutment for the centrifugal weight lever (119) in its locked position.

A clutch disc assembly according to one of claims 3 to 67 characterised in that one of the second side plates (115 116) has a further axially bent over lug (133) on the side of the centrifugal weight lever (119) and which forms an abutment for the centrifugal weight lever (119) in its released position.

A clutch disc cgssembly according to claim 2, characterised in that the centrifugal weight lever (220) is mounted by means of the bearing bolt (253) on the second hub disc (214) and, in the locked position, abuts a component (248) of the first hub disc (211). which forms as locking abutment and which projects axially from the second hub disc (213).

10. A clutch disc assembly according to claim 9, characterised in that the centrifugal weight lever (220) is 1 X k substantially U-shaped and has, on both sides of the second hub disc (213) and extending substantially in the peripheral direction of the second hub disc (213), two arms (256, 257) mounted by means of the bearing bolt (253) to pivot on an extension (252) of the second hub disc (213) which projects substantially radially from the second hub disc (213).

A clutch disc assembly according to claim 9 or 10, charac- terised in that the component (248) is riveted on that side of the first hub disc (211) which is remote from the second hub disc (213), to bear on the first hub disc (211) and comprises, engaging axially through a window (234) of the first hub disc (211) and constituting the abutment (227), a lug (249) which in a peripheral direction bears on both sides without clearance on edges of the window (234).

12.

13.

A clutch disc assembly according to one of claims 9 to 11, characterised in that the centrifugal weight lever (220) is constructed in two parts and consists of a base part (254) which comprises one of the arms (256) and a weight part (255) disposed in one piece thereon and extending beyond the width of the second hub disc (213), and also comprising, forming the second arm, a cover (257) riveted on the base part (254) in the region of the weight part (255).

A clutch disc assembly according to one of claims 10 to 12, characterised in that the coil spring (224) is disposed between the centrifugal weight lever (220) and one of the arms (256,257) of the centrifugal weight lever (220).

11 1 1 15.

A clutch disc assembly according to claim 13, characterised in that the bearing bolt (253) is stepped for axial fixing, the diameter of a first guide zone (259) which traverses the second hub disc (213) being greater than the diameter of a first riveting zone (260) supporting the base part (254) and being smaller than the diameter of a second guide zone (262) disposed between the cover (257) and the second hub disc (213) and enclosed by the coil spring (224) and in that the diameter of a riveting zone (261) of the bearing bolt (253) which supports the cover (257) is smaller than the diameter of the second guide zone (22).

A clutch disc assembly according to ore of claims 2 to 14, characterised in that the bearing bolt (125) is stepped and in that the inner end (140) of the coil spring (124) is clamped in an axially open substantially tangentially extending groove (144) in a step of the bearing bolt (125) merging into a riveting zone (131) so that it is clamped between the latter and an adjacent part (116).

16. A clutch disc assembly substantially as described with reference to the accompanying drawings.

Published 1990 at The Patent Office. State House. 66 71 HighHolborn.Lor. dcnWClR 4TP-F-urther copies inaybeobtaaned from The Patent Office. Sales Branch. St Maxy Cray. Orpington, Kent BR5 3RD. Printed by Multiplex techniques Rd, St Mary Cray, Kent, Con. 1/87