GB2183790A - Clutch assembly for a motor vehicle friction clutch - Google Patents

Abstract

A friction clutch comprises an inner hub (1) and an outer hub (13) coupled with play in rotation through a toothing (7, 15). A drive disc (19) is coupled with the outer hub (13) rotationally elastically through an under-load torsional vibration damper (21). An idling torsional vibration damper (25) which couples the outer hub (13) rotationally elastically with the inner hub (1) is arranged axially laterally of the under-load torsional vibration damper (21) and comprises two annular discs (57, 59), from the external circumference of which support lugs (65, 67) are bent off axially towards one another. The springs (67) of the idling torsional vibration damper (25) are held in the circumferential direction between the axially bent-off support lugs (63, 65). An idling friction device (27) can be accommodated in the region of the idling torsional vibration damper (25). <IMAGE>

Description

SPECIFICATION Clutch assembly for a motor vehicle friction clutch The invention relates to a clutch assembly for a motor vehicle friction clutch having the features of the opening statement of Patent Claim 1.

A clutch assembly of this kind is known from German Patent No. 1,680,049. The clutch disc comprises an inner hub for coupling fast in rotation but axially displaceably with the input shaft of the gear, on which hub an outer hub is mounted rotatably. through a limited angle of rotation. The outer hub engages with an internal toothing, making the rotational play available, in an external toothing of the inner hub. A drive disc provided with clutch friction linings is in turn connected rotationally elastically with the outer hub through an under-load torsional vibration damper dimensioned for operation under load.The under-load torsional vibration damper comprises two side discs secured on the outer hub and an intermediate disc rotatable axially between the side discs in relation to the outer hub through a limited angle of rotation, which intermediate disc is connected with the drive disc. The intermediate disc is supported rotationally elastically on the side discs through several springs distributed in the circumferential direction. The under-load torsional vibration damper comprises a friction apparatus dimensioned for operation under load which damps rotationally elastic vibrations of the drive disc in relation to the outer hub.

Axially laterally of the outer hub there is arranged a preliminary or idling torsional vibration damper dimensioned for idling operation, which couples the outer hub rotationally elastically through several springs with the inner hub. The idling torsional vibration damper comprises a hub disc secured axially laterally of the external toothing on the inner hub and two cover discs arranged axially on both sides of the hub disc and held on an axial extension piece of the outer hub. The two cover discs are supported through the springs of the idling torsional vibration damper on the hub disc.

The idling torsional vibration damper is effective exclusively within the rotational play fixed by the internal toothing and the external toothing, and is bridged over by the toothings after this rotational play is taken up.

The idling torsional damper of the known clutch disc is comparatively expensive as regards construction and occupies relatively much space in the axial direction.

From Fed. German Inspection Document 3,142,842 a further clutch disc for a motor vehicle friction clutch is known the hub of which is rotationally elastically connected through a multi-stage under-load torsionai vibration damper with a drive disc carrying the clutch friction linings and rotatable in relation to the hub through a limited angle of rotation.

The torsional vibration damper comprises two sets of springs which are arranged with radial spacing on diameters of different sizes around the hub axially between two disc parts. From the disc parts support segments protrude towards one another which overlap axially between the springs and on which the springs are supported in the circumferential direction in the relative rotation of the drive disc and the hub. The torsional vibration damper of the known clutch disc is comparatively wide and consists of comparatively many individual parts.

It is an object of the invention to provide a way in which the idling vibration damper of the Clutch assembly as initially explained can be simplified and reduced in size in the axial direction. In accordance with the invention this problem is solved by the features stated in the characterising part of Patent Claim 1.

The idling torsional vibration damper as proposed within the scope of the invention comprises two damper parts formed as annular discs, which carry lugs bent off axially towards one another in the region of their external circumference which hold the springs of the idling torsional vibration damper between them in the circumferential direction. In distinction from the idling torsional vibration damper as known from German Patent No.

1,680,049, only two annular discs are required. The springs of the idling torsional vibration damper can be arranged without problem on a circle of comparatively large diameter, whereby the mechanical loading of the parts is reduced and the production costs are diminished. Furthermore it is possible to accommodate more springs than in conventional torsional vibration dampers, so that higher end torques and greater relative angles of rotation can be realised. Moreover the construction space, increased in the radial direction, can be exploited better for the accommodation of springs of different strengths for a graduated idling spring characteristic curve.

The springs of the idling torsional vibration damper are expediently guided radially in elongated impressions of the annular disc placed remote from the outer hub. In this way the axial space of the clutch disc radially within the diameter circle of the springs can be kept narrow in the axial direction and is available for the stroke of the clutch releaser.

In a preferred form of embodiment the clutch assembly in addition to a friction device dimensioned for operation under load also comprises an idling friction device dimensioned for idling operation, in order to reduce load-change impacts in the transition from the idling range into the under-load range and also vibrations and noises. The idling friction device is expediently accommodated in the region of the idling torsional vibration damper utilising the space axially available between the two annular discs.

In a first variant of the idling friction device the annular disc of the idling torsional vibration damper placed remote from the external toothing is utilised for friction force generation. The friction device comprises two annular friction discs arranged on opposite sides of this annular disc and rotatable in relation thereto, which are connected fast in rotation with one another and with the other annular disc by connection elements. The friction discs clamp the annular disc in between them by reason of their inherent elasticity or by reason of an additional, axially acting spring of annular disc form.For the axial connection of the friction discs with one another or with the spring of annular disc form it is possible to provide rivet connections, snap connections or bayonet connections, the connection elements of which pass through openings of the annular disc clamped in between the friction discs.

The connection elements can at the same time also take over the rotation-fast coupling of the friction discs with the other annular disc of the torsional vibration damper, in that they engage in openings of this annular disc.

In a second variant of the idling friction device one of the annular discs of the idling torsional vibration damper is connected with a coaxial thrust sleeve, while the other annular disc is connected with a radially elastic expanding sleeve coaxial with the thrust sleeve.

The expanding sleeve is radially initially stressed against the thrust sleeve by spring means, to increase friction force. Such a friction device has an exactly defined friction radius and an angle of rotation not limited by stops or the like. The spring means can be the inherent elasticity of the expanding sleeve.

However a separate radially expanding spring ring is expediently provided. The thrust sleeve expediently radially outwardly encloses the expanding sleeve to that the friction force increases with rising centrifugal force. The part of the thrust sleeve coming into frictional contact with the expanding sleeve is expediently arranged between the annular discs of the torsional vibration damper, but can also be provided axially outside.

Examples of embodiment of the invention are to be explained in greater detail below by reference to drawings, wherein:- Figure 1 shows a partial axial view of a clutch disc for a motor vehicle friction clutch; Figure 2 shows a partial axial longitudinal section through the clutch disc, seen along a line ll-ll in Fig. 1; Figure 3 shows a partial axial longitudinal section through the clutch disc, seen along a line Ill-Ill in Fig. 1; Figure 4 shows a partial axial section through a first form of embodiment of an idling friction device usable in the clutch disc according to Fig. 1, seen along a line IV-IV in fig. 5; Figure 5 shows a partial axial longitudinal section through the friction device, seen along a line V-V in Fig. 4;; Figure 6 shows a first variant of the idling friction device according to Figs. 4 and 5, seen in a partial axial longitudinal section; Figure 7 shows a second variant of the friction device according to Figs. 4 and 5, seen in a partial axial longitudinal section; Figure 8 shows a partial axial cross-section through a second form of embodiment of an idling friction device usable in the clutch disc according to Fig. 1, seen along a line VIII-VIII in Fig. 9; Figure 9 shows a partial axial longitudinal section through the friction device, seen along a line IX-IX in Fig. 8; Figure 10 shows a partial axial cross-section through a third form of embodiment of an idling friction device usable in the clutch disc according to Fig. 1, seen along a line X-X in Fig. 11;; Figure 11 shows a partial axial longitudinal section through the friction device, seen along a line Xl-Xl in Fig. 10; Figure 12 shows a partial axial cross-section through a fourth form of embodiment of an idling friction device usable in the clutch disc according to Fig. 1, seen along a line XII-XII in Fig. 13; Figure 13 shows a partial axial longitudinal section through the friction device, seen along a line XIII-XIII in Fig. 12; Figure 14 shows a partial axial elevation of a fifth form of embodiment of an idling friction device usable in the clutch disc according to Fig. 1; Figure 15 shows a partial axial longitudinal section through the friction device, seen along a line XV-XV in Fig. 14;; Figure 16 shows a partial axial cross-section through a sixth form of embodiment of an idling friction device usable in the clutch disc according to Fig. 1, seen along a line XVI-XVI in Fig. 17; Figure 17 shows a partial axial longitudinal section through the friction device, seen along a line XVII-XVII in Fig. 16 and Figure 18 shows a partial axial longitudinal section through a variant of the friction device according to Figs. 16 and 17.

Figs. 1 to 3 show a clutch disc of a motor vehicle friction clutch having an inner hub 1 which is couplable fast in rotation but axially displaceably through an internal toothing 3 with an input shaft (not shown), rotatable about a rotation axis 5, of a gear. The inner hub 1 carries an external toothing 7 which is limited axially on both sides by tooth shoulders 9, 11 facing axially away from one another. An outer hub 13 coaxially enclosing the external toothing 7 of the inner hub 1 engages with an internal toothing 15 in the external toothing 7 and couples the outer hub 13 fast in rotation but with predetermined play in rotation with the inner hub 1.An annular drive disc 19 provided axially on both sides with friction linings 17 encloses the outer hub 13 rotatably through a limited angle of rotation and is rotationally elastically coupled with the outer hub 13 through an underload torsional vibration damper 21 dimensioned for operation under load. An underload friction device 23 dimensioned for operation under load damps rotational vibrations occurring in the relative rotation between the drive disc 19 and the outer hub 13. The clutch disc further comprises an idling torsional vibration damper 25 dimensioned for idling operation and effective between the outer hub 13 and the inner hub 1, which damper couples the outer hub 13, within the rotational play determined by the external toothing 7 and the internal toothing 15, rotationally elastically with the inner hub 1.An idling friction device dimensioned for idling operation and indicated diagrammatically in Figs. 2 and 3 by a chain line 27 can be allocated to the idling torsional vibration damper 25 and damps the rotational vibrations occurring in idling operation between the outer hub 13 and the inner hub 1.

If there is adequate inherent friction the idling friction device 27 can be omitted. However preferred developments of the idling friction device 27 will be explained in greater detail below.

In operation the idling torsional vibration damper 25 is effective as a pre-damper and damps the rotational vibrations occurring at small relative angles of rotation between the drive disc 19 and the inner hub 1. At the relative angles of rotation occurring in idling operation the under-load torsional vibration damper 21 is ineffective by reason of the comparatively great friction torque of the friction device 23. At great relative angles of rotation between the drive disc 19 and the inner hub 1 the rotational play between the external toothing 7 and the internal toothing 15 is taken up and the idling torsional vibration damper 25 is by-passed.

The under-load torsional vibration damper 21 comprises two side discs 31, 33 secured with rivets 29 to the outer hub 13, which radially inwardly overlap the tooth flanks 9, 11 of the external toothing 7 radially and directly axially fix the outer hub 13 on the inner hub 1. Radially outwards the side discs 31, 33 protrude beyond the outer hub 13 and are connected with one another by distance rivets 35. The side discs 31, 33 enclose between them an annular intermediate disc 37 firmly connected with the drive disc 19, the distance rivets 35 penetrating the intermediate disc 37 and limiting the relative angle of rotation of the under-load torsional vibration damper. The intermediate disc 37 can be an integral, radial prolongation of the drive disc 19.In windows 39 of the intermediate disc 37 for one part and axially oppositely arranged windows 41, 43 of the side discs 31 and 33 for the other part there are seated helical compression springs 45 which are stressed in the relative rotation of the drive disc 19 and the outer hub 13 and connect the drive disc 19 rotationally elastically with the outer hub 13. As Fig. 1 shows the springs 45 are arranged with spacing from one another in the circumferential direction essentially on a common diameter circle.

The under-load friction device 23 comprises two friction rings 47, 49, arranged axially on both sides of the intermediate disc radially within the circle of arrangement of the springs 45, and an axially acting spring'51, for example a dished spring, axially between the side disc 33 axially adjacent to the idling torsional vibration damper 25 and the thrust ring 49. Between the spring 51 and the thrust ring 49 there is arranged a thrust ring 53 connected fast in rotation but axially displaceably with the side disc 33. Axially between the friction ring 47 and the other side disc 31 there is provided a thrust ring 55 connected fast in rotation but axially displaceably with this side disc.The spring 51 supported with its inner circumference on the side disc 33 clamps the slightly axially displaceable intermediate disc 37 in between the friction linings 47, 49 the force path of the spring being closed by way of the side disc 31 and the rivets 29, 35 to the side disc 33.

The idling torsional vibration damper 25 comprises two annular discs 57, 59 arranged with axial spacing from one another. The annular disc 57 rests on the side disc 33 and is secured by means of the rivets 29 on the outer hub 13 and/or by means of rivets or welded connections (not shown further) on the side disc 33. The other annular disc 59 is secured with its internal circumference for example by caulkings 61 on the inner hub 1.

The annular disc 57 carries on its external circumference several support lugs 53 arranged with spacing from one another and bent axially away from the side disc 33. The annular disc 59 carries pairs of further support lugs 65 on its external circumference, both radially inside and radially outside the support lugs 63. Between support lugs 63, 65 lying oppositely in the circumferential direction there are arranged helical compression springs 67 which are resiliently stressed in the rotation of the outer hub 13 in relation to the inner hub 1. The springs 67 couple the outer hub 13 rotationally elastically with the inner hub 1 within the idle play of the toothings 9, 15. In the circumferential direction between the support lug pairs 65 the axially outer annular disc 59 is provided with impressions 69 which fix and guide the springs 67 both radially and axially outwards.

In the clutch disc as explained with refer ence to Figs. 1 to 3, torsional vibrations occurring in idling are damped by the inherent friction of the components of the clutch disc.

In order to achieve higher friction values it is possible, as indicated in Figs. 2 and 3, for an idling friction device dimensioned for idling operation to be provided. Several forms of embodiment of the idling friction device 27 usable in the clutch disc according to Figs. 1 to 3 are to be explained below. In the explanations parts of like effect are designated with the reference numerals of Figs. 1 to 3 and provided with a letter for distinction. For explanation reference is made to the description of Figs. 1 to 3. It is common to all configurations that the idling friction device requires relatively little axial space and is not stressed by the displacement forces exerted on- the clutch disc in the engagement of the friction clutch.Figs. 4 to 15 show friction devices in which the axially outer annular disc 59 is utilised to generate the friction torque and is clamped in axially between two friction faces initially stressed axially resiliently against one another. Figs. 16 to 18 show friction devices in which the friction torque is generated by means of a radially resiliently loaded friction sleeve.

Figs. 4 and 5 show an idling friction device 27a with two annular friction discs 71, 73 arranged axially on both sides of the axially outer annular disc 59a, which friction discs rest on the annular disc 59a through friction rings 75, 77 radially within the support lugs 65a. Axially between the friction disc 71 and the annular disc 57a an annular spring 79 is arranged which in the region of its external circumference is firmly connected through distance rivets 81 with the external circumference of the axially outer friction disc 73.The distance rivets 81 here pass through circumferentially elongated openings 83 of the annular disc 59a which are produced by the punching clear of the radially inner support lugs 65a and a relative rotation is possible between the friction rings 71, 73 and the annular disc 59a at least by the amount of the rotational play of the toothings 7a and 15a of the inner hub la and the outer hub 13a respectively. The axially inner friction disc 71 is guided by means of openings 85 on its external circumference fast in rotation but axially displaceably on the distance rivets 81. The annular spring 79 comprises a plurality of axially resilient tongues 87 protruding radially inwards from its inner circumference which generate the axial spring force of the friction device 27a.Furthermore from the annular spring 79 there protrude lugs 89 axially bent off towards the annular disc 57a which engage in openings 91 of the annular disc 57a and connect the annular spring 79 and thus the friction discs 71, 73 fast in rotation with the annular disc 57a. To reduce the axial space requirement the heads of the rivets 29a are seated in recesses 93 of the annular disc 57A and the annular disc 57a is secured on the side disc 33a by additional counter-sunkheaded rivets indicated at 95. In place of the counter-sunk-headed rivets 95 other securing means can be selected, for example spot welds or the like. If other connection means between the friction rings 71, 73 and the annular disc 57a are selected, the annular spring 79 can also be arranged on the axially outer side of the friction device 27a. Other springing means can also be used, for example leaf springs.The advantage of the idling friction device according to Figs. 4 and 5 is that with comparatively slight construction expense a large friction area and a large mean friction radius are rendered possible. Furthermore the maximum angle of rotation of the friction device 27a is comparatively large.

Fig. 6 shows a variant 27b of the friction device 27a which differs from the friction device 27a essentially only in the rotation-fast coupling of the annular disc 57b with the axially acting annular spring 79b and the two friction rings 71b and 73b. Parts of like effect are provided with the reference numerals of Figs. 4 and 5, increased by the letter b. For explanation reference is made to Figs. 4 and 5. In place of the lugs 89 the friction device 27b comprises rivets 97 which engage with their heads 99 in an opening 101 of the annular disc 57b and couple the friction discs 71b, 73b and the spring 79b fast in rotation with the annular disc 57b.A distance sleeve 103 arranged axially between the annular spring 79b and the friction disc 73b and enclosing the rivets 97 ensures the desired spacing of these parts and guides the friction disc 71b fast in rotation but axially displaceably.

Fig. 7 shows a variant 27c of the friction device 27b which differs from the friction device 27b essentially in that its friction discs 71c and 73c are made axially resilient and clamp the friction disc 59c inbetween them through friction rings 75c and 77C by reason of their inherent elasticity. The annular spring 79b is thereby eliminated and the friction disc 79c is connected axially fast with the friction disc 73c through the rivets 97c and the distance sleeve 103c. The rivet head 99c again connects the friction discs 71c, 73c fast in rotation with the annular disc 57c. For further explanation reference is made to Figs. 4 to 6, parts of like effect being designated by the same reference numerals. The advantage of the friction device 27c is its especially narrow construction in the axial direction.

Figs. 8 and 9 show an idling friction device 27d in which on the side of the annular disc 59d axially remote from the annular disc 57d there is arranged a friction disc 105 rotatable in relation to the annular disc 59d, which friction disc rests through a friction ring 107 on the annular disc 59d. On its external circumference the friction disc 105 carries lugs 109 bent off axially towards the annular disc 57d which pass through the openings 111 of the annular disc 59d produced in the punching clear of the radially inner support lugs 65d.

Axially between the annular discs 57d and 59d on the lugs 109 there is formed a radially inwardly protruding cranked portion 113 on which a spring 115 of annular disc form is axially supported with lugs 117 protruding radially outwards from its outer circumference.

The spring 115 is supported with its radially inner region through a friction ring 119 on the annular disc 59d. The annular disc 59d is thereby clamped in axially resiliently between the spring 115 and the friction disc 105. With their free ends 121 the lugs 109 engage in openings 123 of the annular disc 57d and couple the friction disc 105 and the spring 115 fast in rotation with the annular disc 57d.

Axially bent-forward noses 125 circumferentially on both sides of the lugs 117 ensure the rotation fast connection of the spring 115 with the friction disc 105. In the circumferential direction between adjacent lugs 117 the spring 115 is provided with recesses 127 which permit of fitting the spring 115 with offset angle upon the lugs 109 and securing it in the initially stressed condition by twisting on the lugs 109, in the assembly of the friction device 27d. It is understood that it is not necessary for all lugs 109 to engage with their free ends in openings of the annular disc 57d.

Figs. 10 and 11 show a further idling friction device 27e consisting of especially few individual parts. In this form of embodiment axially resilient friction discs 131, 133 are arranged on both sides of the axially outer annular disc 59e and clamp the annular disc 59e axially resiliently between them with their radially inner regions through friction rings 135, 137. The friction disc 133 lying remote from the annular disc 57e carries axially bent-off lugs 139 on its outer circumference which engage with their free ends 141 in openings 143 of the annular disc 57e and connect the friction ring 133 fast in rotation with the annular disc 57e. The lugs 139 pass through openings 145 of the annular disc 59e which are produced by punching clear of the radially inner support lugs 65e.Axially between the annular discs 57e and 59e the lugs 139 are provided with a radially inwardly projecting cranked portion 147 on which the axially resilient friction ring 131 is supported with its external circumference. The openings 145 are dimensioned so that the friction rings 131, 133 can rotate in relation to the annular disc 59e at least by the rotational play of the toothings of outer hub and inner hub. The lugs 139 engage in recesses 149 on the external circumference of the friction disc 131 for the rotation-fast connection of the two friction discs 131, 133. In order that the friction discs 131, 133 can be fitted on one another, at a distance from each recess 149 a further but radially deeper recess 151 is provided which permits the axial fitting of the friction disc 131 on the lugs 139.The recesses 149 and 151 are connected by a rising edge 153 which rises from the recess 151 to the radially outer edge of the recess 149. The lugs 139 are made radially resilient and are deflected in relation to one another until they snap into the recesses 149, by the rising edges 153 in the turning of the friction discs 131, 133.

Figs. 12 and 13 show a further constructionally very simple idling friction device 27f.

The friction device 27f comprises axially inherently elastically resilient friction discs 155, 157 arranged axially on both sides of the outer annular disc 59f which clamp the annular disc 59f in axially resiliently between them through friction linings 159, 161. From the external circumference of the two friction discs 155, 157 there protrude lugs 163 and 165 respectively which are bent towards the annular disc 57f in a comparatively large arc rendering axial spring properties possible. The lugs 163, 165 engage commonly in an opening 167 of the annular disc 57f and of the side disc 33f and guide the friction discs 155, 157 fast in rotation on the annular disc 157f.

The lug 165 protruding from the axially outer friction disc 157 passes through an opening 169 of the annular disc 59f and carries within the opening 167 a radially inwardly protruding angled portion 171 on which the lug 163 is supported with its free end. For assembly the initially stressed friction discs 155, 157 are turned in relation to one another until the lugs 165, 163 are supported on one another. Then the lugs 163, 65 are pushed into the opening 167 and the annular disc 59f is fitted on the inner hub 1f. It is understood that not all lugs 163, 165 have to engage in associated openings 167. Some of the lugs can also be supported on one another outside the annular disc 57f.

Figs. 14 and 14 show an idling friction apparatus 279 having two friction discs 173, 175 arranged axially on both sides of the annular disc 59g, which enclose the annular disc 599 axially between them through interposed friction linings. The friction disc 173 placed between the annular discs 579 and 59g carries axially bent-off lugs 1 77 on its internal circumference which pass through openings of the annular disc 1599 and carry radially outwardly bent angled portions 179 on their free ends. Axially between the angled portions 179 and the outer friction disc 175 there is clamped a dished spring 181 which generates the axial friction force of the friction apparatus 27g.Axially bent-off lugs 183 protrude from the external circumference of the outer friction disc 175 and engages through openings 185 of the annular disc 59g in openings 187 of the annular disc 579 and of the side disc 33g.

The friction disc 173 is connected fast in rotation but axially displaceably with the lugs 183. The lugs 183 in turn connect the two friction discs 173, 175 fast in rotation with the annular disc 579. The openings 185 are of such large dimensions that the friction discs 173, 175 are rotatable in relation to the annular disc 59g at least by the amount of the play in rotation between the outer hub 139 and the inner hub lg. The assembly of the friction discs 173, 175 is effected by crimping over the angled portions 179 after the assembling of the components of the friction device 279. In place of angled portions for crimping over it is also possible to provide connections of bayonet-catch type in which the components to be supported axially against one another are secured by rotation in relation to one another.

Figs. 16 and 17 show an idling friction device 27h in which, in contrast to the form of embodiment as explained above, the friction torque is generated by radially acting forces.

The friction device 27h comprises a thrust sleeve 189, coaxial with the rotation axis 5h of the inner hub 1h, placed axially between the two annular discs 57h and 59h. The thrust sleeve 189 is secured through several circumferentially distributed lugs 191 on the axially outer annular disc 59h. With the inner annular disc 57h or the outer hub 13h there is connected an expanding sleeve 201 which is stressed radially outwards against the internal circumference of the thrust sleeve 1 89 by a radially initially stressed annular spring 203 through a friction lining 205. The expanding sleeve 201 is axially slotted and secured on the outer hub 13h through a lug 207 lying diametrically opposite to the slot, by means of one of the rivets 29h.The advantage of this friction device is that the friction moment is exactly defined by a constant friction radius and increases by reason of the centrifugal force with increasing rotation rate, that is becomes larger in the under-load range, whereby the impacts of load change are reduced.

Fig. 18 shows a variant 27i of the idling friction device 27h, which differs from the friction device 27h essentially only in that the thrust sleeve 189i is connected with the axially inwardly disposed annular disc 57i and the expanding sleeve 201i is connected with the axially outer annular disc 59i. For further explanation reference is made to the description of Figs. 16 and 17, the same references being used. The thrust sleeve 189i is held fast in rotation on the annular disc 57i through axially protruding noses 211 of the thrust sleeve 189i engaging in openings 209. The expanding sleeve 201i connected fast in rotation with the annular disc 59i carries a radial stiffening flange 213 from which there protrude several tongues 215 engaging in the thrust sleeve 189i. The radially acting spring 203i stresses the tongues 215 through friction linings 205i radially outwards against the internal surface of the thrust sleeve 189i.

The thrust sleeve and the expanding sleeve of the friction devices as explained above can also be arranged axially outside the two annular discs. Alternatively the thrust sleeve can also be provided radially within the expanding sleeve, the radially acting annular spring being arranged radially outside and initially stressed inwards. In this case however the friction moment decreases with increasing rotation rate.

Claims (26)

1. Clutch assembly for a motor vehicle friction clutch, comprising: a) an inner hub (1) having an external toothing (7) limited axially on both sides by axial shoulders (9, 11).

b) an outer hub (13) enclosing the inner hub (1) with an internal toothing (15) engaging in the external toothing (7) and coupling the outer hub (13) fast in rotation but with predetermined play in rotation with the inner hub (1), c) a drive disc (19) provided with clutch friction linings (17) and rotatable in relation to the outer hub (13) through a limited angle of rotation, d) an under-load torsional vibration damper (21) dimensioned for operation under load with two mutually relatively rotatable damper parts (31, 33, 37) supported rotationally elastically on one another through several springs (45), of which parts one (31, 33) is connected with the outer hub (13) and the other (37) with the drive disc (19) and of which one comprises two side discs (31, 33) arranged with axial spacing from one another and connected with one another and the other damper part comprises an intermediate disc (37) arranged between the side discs (31, 33) and supported through the springs (45) on the side discs (31, 33), e) an idling torsional vibration damper (25) arranged axially laterally of one of the side discs (31, 33) on the side axially remote from the intermediate disc (37) and dimensioned for idling operation, with two relatively mutually rotatable damper parts (57, 59) rotationally elastically supported on one another through several springs (67), of which parts one (57) is connected with the outer hub (13) and the other (59) with the inner hub (1), characterised in that the two damper parts of the idling torsional vibration damper (25) are formed as annular discs (57, 59) which carry, in the region of their external circumference, lugs (63, 65) bent axially towards one another which hold the springs (67) of the idling torsional vibration damper (25) between them in the circumferential direction.

2. Clutch assembly according to Claim 1, characterised in that the annular disc (59) situated remote from the outer hub (13) is firmly connected at its inner circumference with the inner hub (1) and comprises, in a circumferen tial direction between its lugs (65), outwardly domed portions (69) elongated in the circumferential direction which radially guide the springs (67).

3. Clutch assembly according to Claim 1 or 2, characterised in that one of the two annular discs, especially the annular disc (59) placed axially remote from the outer hub (13), comprises lugs (65) arranged by pairs with radial spacing, and in that the lugs (63) of the other annular disc (57) in each case engage in each case radially between the pairs of lugs (65).

4. Clutch assembly according to one of Claims 1 to 3, characterised in that the axially mutually oppositely disposed lugs (63, 65) overlap axially.

5. Clutch assembly according to one of Claims 1 to 4, characterised in that the underload torsional vibration damper (21) comprises an under-load friction device (23) dimensioned for operation under load and the idling torsional vibration damper (25) comprises an idling friction device (27) dimensioned for idling operation.

6. Clutch assembly according to Claim 5, characterised in that the idling friction device (27a-g) comprises two annular friction discs (71, b, c, 73, b, c; 105, 115; 131, 133; 155, 157; 173, 175) arranged on opposite sides of the annular disc (59a-g) situated remote from the outer hub (13a-g), clamping the annular disc (59a-g) axially resiliently between them and rotatable in relation to this annular disc (59a-g), which friction discs are connected fast in rotation with one another and with the other annular disc (57a-g) by connection elements (81, 89; 97; 109; 139; 163, 165; 177, 183).

7. Clutch assembly according to Claim 6, characterised in that the connection elements (81, 89; 97; 109; 139; 163, 165; 177, 183) connect the two friction discs (71, b.c. 73, b.

c; 105, 115; 131, 133; 155, 157; 173, 175) with one another in the region of their external circumference through openings (83; 111; 145; 169; 185) of the annular disc (59a-g).

8. Clutch assembly according to Claim 6 or 7, characterised in that an axially acting spring disc (79, b) is arranged on the side of one of the friction discs (71, b) axially remote from the other friction disc (73, b), in that the spring disc (79, b) and the other friction disc (73, b) are firmly connected by distance members (81; 97, 103) through openings (83) of the annular disc (59a) and in that the one friction disc (71, b) is guided fast in rotation but axially displaceably on the distance members (81; 97, 103).

9. Clutch assembly according to Claim 6 or 7, characterised in that at least one of the two friction discs (71c, 73c) is formed as an axially acting spring disc and in that the two friction dics (71c, 73c) are firmly connected by distance members (97, 103) through openings at the annular disc (59c).

10. Clutch assembly according to Claim 8 or 9, characterised in that the distance members each comprise a distance sleeve (103, c) and a connection rivet (97, c) penetrating the sleeve (103, c), the head (99, c) of which rivet engages in an opening (101) of the annular disc (57b, c) connected with the outer hub and couples the friction discs (57b, c; 59b, c) fast in rotation with this annular disc (57b, c).

11. Clutch assembly according to Claim 6 or 7, characterised in that at least one of the two friction discs is formed as an axially acting spring disc (115; 131, 133; 155, 157) in that the friction disc (105; 133; 157) placed axially remote from the external toothing carries axially bent-over lugs (109; 139; 165) which pass through openings (111; 145; 169) of the annular disc (59d-f) placed axially remote from the external toothing and engage for the rotation-fast guidance of the friction disc in openings (123; 143; 167) of the annular disc (57d-f) axially adjacent to the external toothing, and in that at least one part of the lugs (109; 139; 165) comprises a radially angled-off portion (113; 147; 171) on which the friction disc (115; 131; 155) axially adjacent to the external toothing is axially supported.

12. Clutch assembly according to Claim 11, characterised in that the angled portion is formed as a cranked portion (113; 147) on which the friction disc (115; 131) is supported in the region of its circumference, especially its external circumference.

13. Clutch assembly according to Claim 12, characterised in that the friction disc (115) adjacent to the external toothing comprises radially protruding lugs (117) supported on the cranked portions (113).

14. Clutch assembly according to Claim 13, characterised in that laterally of the cranked portions (115) in the circumferential direction projections (125) protrude axially from the friction disc (115) adjacent to the external toothing and connect the two friction discs (105, 115) fast in rotation with one another.

15. Clutch assembly according to Claim 12, characterised in that the lugs (139) are made radially resilient, in that the friction disc (131) adjacent to the external toothing comprises for each of the lugs (139), side by side in the circumferential direction, a pair of recesses (149, 151) with different radial extents, of which in each case a first (151) permits the axial passage of the cranked portion (147) and the second in each case is supportable with its edge on the cranked portion (147) and is limited by stop shoulders facing one another in the circumferential direction and in that the recesses (149, 151) of the pair merge into one another through a rising edge (153) of the friction disc (131) leading from the first (151) to the second (149) recess, which edge transfers the lug (139) from the first recess (151) to the second (149) in a relative rotation.

16. Clutch assembly according to Claim 11, characterised in that the angled portion (171) is provided on the end of the lug (165) engaging in the opening (167) of the annular disc (57f) and in that the friction disc (155) adjacent to the external toothing (7f) carries axially bent-over lugs (163) which engage likewise in the openings (167) of the friction disc (57f) for rotation-fast guidance and are supported with their ends on the angled portions (171).

17. Clutch assembly according to Claim 6, characterised in that from the internal circumference of one (173) of the two friction discs there axially protrude axial first lugs (177) passing through openings of the annular disc, which carry radially outwardly bent-over angled portions (179) on their ends, in that an axially acting spring (181) is supported axially between the angled portions (179) and the other (175) of the two friction discs and in that second axial lugs (183) which engage in an opening (187) of the annular disc (579) adjacent to the external toothing, protrude from the external circumference of one (175) of the two friction discs.

18. Clutch assembly according to Claim 17, characterised in that the second lugs (183) of the friction disc (175) disposed remotely from the external toothing engage through openings (185) of the annular disc (59g) placed between the friction discs (173, 175) and in that the friction disc (173) adjacent to the external toothing is guided fast in rotation but axially displaceably on the second lugs (183).

19. Clutch assembly according to Claim 17 or 18, characterised in that the first lugs (177) protrude from the friction disc (173) axially adjacent to the external toothing.

20. Clutch assembly according to Claim 5, characterised in that the idling friction device (27h, i) comprises a thrust sleeve (189, i) coaxially connected with one (57h; 59i) of the annular discs, a radially elastic expanding sleeve (201, i) coaxial with the thrust sleeve (189, i) and connected with the other annular disc (57i; 59h) and a spring means (203, i) stressing the expanding sleeve (201, i) radially against the thrust sleeve (189, i).

21. Clutch assembly according to Claim 20, characterised in that the thrust sleeve (189, i) radially externally encloses the expanding sleeve (201,i).

22. Clutch assembly according to Claim 20 or 21, characterised in that the spring means is formed as a radially acting spring ring (203, i).

23. Clutch assembly according to one of Claims 20 to 22, characterised in that the thrust sleeve (189,i) is arranged substantially axially between the two annular discs (57h, 59h, i).

24. Clutch assembly according to one of Claims 20 to 23, characterised in that the expanding sleeve (201) is axially slotted and carries diametrically oppositely to the slot a radially protruding securing flange (207).

25. Clutch assembly according to one of Claims 20 to 23, characterised in that the expanding sleeve (201i) is formed as a flanged sleeve having a radially protruding closed annular flange (213) at one end of a repeatedly axially slotted sleeve part (215).

26. Clutch assembly as claimed in Claim 1 substantially as described with reference to Figs. 1-6, Figs. 1-5 and 7, Figs. 1-4, 8 and 9 or Figs. 10+11, Figs. 12 and 13, Figs. 14 and 15, Figs. 16, 17 or Figs. 16, 17 and 18.