GB2183787A - Clutch assembly for a motor vehicle friction clutch - Google Patents

Abstract

The clutch assembly for a motor vehicle friction clutch comprises an inner hub (1) for coupling with the gear input shaft, on which an outer hub (13) is mounted rotatably, through a toothing (7), through an angle of rotation limited by a rotation play of the toothing (7). An under- load torsional vibration damper (21) provided with a friction device (23) and dimensioned for operation under load couples a drive disc (19) rotationally elastically with the outer hub (13). An idling torsional vibration damper (25) dimensioned for idling operation and arranged axially laterally of the toothing (7) couples the outer hub (13) rotationally elastically with the inner hub (1). With the idling torsional vibration damper (25) there is associated an idling friction device (27) which is arranged axially laterally of the springs (71) of the idling torsional vibration damper (25) in an annular space limited by tooth shoulders (9) of the toothing (7) and at least one side disc (31, 33) of the under-load vibration damper (21). <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 assembly includes an inner hub for coupling fast in rotation but axially displaceably with the input shaft of the gear, on which an outer hub is mounted rotatably through a limited angle of rotation. The outer hub engages with an internal toothing, which makes the play in rotation available, in an external toothing of the inner hub. A drive disc provided with clutch friction linings is in turn rotationally elastically connected 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 and connected with the drive disc.The intermediate disc is supported on the side discs through several springs distributed in the circumferential direction. The underload torsional vibration damper comprises a friction device dimensioned for operation under load, which damps rotationally elastic vibrations of the drive disc in relation to the outerhub.

Axially laterally of the outer hub there is arranged a preliminary or idling torsional vibratuion damper dimensioned for idling operation which rotationally elastically couples the outer hub with the inner hub through several springs. The idling torsionai vibration damper comprises a hub disc secured on the inner hub axially laterally of the external toothing and two cover discs arranged axially on both sides of the hub disc and held on an axial extension of the outer hub. The cover discs are supported on the hub disc through the springs of the idling torsional vibration damper. The idling torsional vibration damper is effective exclusively within the play in rotation fixed by the internal toothing and the external toothing and is by-passed by the toothings after this play in rotation is taken up.

In order to reduce idling noises ordinarily the idling angle of rotation is made relatively large. However this measure has the consequence that load alternation impacts in the transition from the idling range into the underload range become more intense, so that vibrations and noises occur in the under-load range. In order to counter-act this, the idling torsional vibration damper has an idling friction device. The friction device consists essentially of friction rings arranged axially on both sides of the hub disc and initially stressed against the hub disc by the axially resiliently formed cover discs.

The idling friction device of the known clutch assembly transmits displacement force exerted upon the drive disc in clutch engage ment. This stresses the friction rings of the idling friction device and has a disadvanta geous effect upon the spring properties of the cover discs.

It is an object of the invention to improve the idling friction device of the known clutch assembly so that with small space require ments definite friction values are maintained within a long life.

In accordance with the invention this prob lem is solved by the features stated in the characterising part of Patent Claim 1.

In distinction from the idling friction device as known from German Patent No.

1,680,049, the friction device is arranged not between the cover discs of the idling torsional vibration damper, but axially laterally of the springs of the idling torsional vibration damper at least with a part of its axial overall length in an annular space which is defined by tooth shoulders of the inner hub and faces of the side disc adjacent to the tooth shoulders, of the under-load torsional vibration damper. The idling friction device comprises a separate, axi ally acting spring which generates the friction force of the idling friction device. The idling friction device also exploits the space in the axial direction in any case required for the un der-load torsional vibration damper.Since the idling friction device comprises a separate spring for the generation of the friction force, exactly defined friction values can be gener ated with comparatively long life.

The annular space provided to receive the 'idling friction device can be accommodated completely between the side discs of the un der-load torsion damper, especially in an annu lar recess of at least one of the two side discs, or in an annular space formed by shor tening of the outer axial toothing of the inner hub. In this form of embodiment axial faces of the external toothing or of the side discs can be exploited not only for the supporting of the axial spring forces but also as friction faces.

In a preferred development of the invention in which the side discs of the under-load tor sional vibration damper are secured on the outer hub, it is provided that the two side discs radially overlap the tooth shoulders of the external toothing of the inner hub and thus fix the outer hub axially on the inner hub. The displacement forces occurring in clutch en gagement are transmitted in this development independently of the idling torsional vibration damper through the comparatively stable side discs of the under-load torsional vibration damper, which has an advantageous effect upon the life of the idling torsional vibration damper and its friction device. One of the two side discs of the under-load torsional vibration damper however overlaps the external toothing of the inner hub in the radial direction.only partially.The components of the idling friction device protrude into the annular space enclosed by the internal circumference of the radially shortened side disc.

The axial force of the spring of the idling friction device can be taken up in various manners. In a first variant the idling friction device can be clamped in between the tooth shoulders of the external toothing of the inner hub for one part and an axially opposite abutment face of a part additionally fitted on the inner hub. This part can be for example an additional securing ring or a part of the idling torsional vibration damper, for example its hub disc. For the friction force generation thrust discs braced axially against one another by the spring are provided of which at least one is coupled fast in rotation but axially displaceably with the inner hub and at least one with the outer hub, preferably through the side disc of the under-load torsional vibration damper.

In a second variant the external toothing of the inner hub can be axially shortened in relation to tooth flanks of the internal toothing of the outer hub, the idling friction device being clamped in axially between the tooth flanks of the internal toothing and an annular flange which axially oppositely limits the annular space and is secured to the outer hub or even the side disc connected with it. The axial force of the idling friction device is taken up in this variant by the outer hub and the annular flange connected with it. The friction device again includes thrust discs, of which one is connected fast in rotation but axially displaceably with the outer hub and the other with the inner hub.

In a third variant the axial force of the idling friction device is taken up by a flanged sleeve which carries atone end a flanged disc utilised as friction face or as carrier for a friction ring and at the other end stop elements for supporting the spring. The flanged sleeve can be connected fast in rotation either with the inner hub or with the outer hub. In developments in which the flanged sleeve is connected with the inner hub, one of the side discs of the under-load torsional vibration damper can be utilised as friction counter-face of the flanged disc. For the rotation-fast connection with the inner hub a thrust ring can be provided which is coupled fast in rotation through lugs protruding radially inwards from its internal circumference both with the flanged sleeve and with the inner hub. Alternatively the flanged disc can be utilised for securing to the outer hub.As counter-friction face for the flanged disc a thrust ring rotatable in relation to the flanged sleeve can be provided which again is coupled fast in rotation with the inner hub through a radially inwardly protruding lug.

The stop elements supporting the spring of the idling friction device can consist of a crimped-over edge of the flanged sleeve. In order to facilitate assembly the stop elements can also be formed as radially protruding lugs.

The spring is provided with matching re cesses, so that it can be pushed over the lugs on to the flanged sleeve and secured by rota tion on the flanged sleeve after the style of a bayonet catch. In order to prevent subsequent unintentional rotation, axial securing projec tions or the like can be formed either on the spring or on the flanged sleeve.

Examples of embodiment of the invention are to be explained in greater detail hereinafter by reference to drawings, wherein :- Figure 1 shows a partial axial view of a clutch assembly for a motor vehicle friction clutch; Figure 2 shows a partial axial longitudinal section through the clutch assembly, seen along a line ll-ll in Fig. 1; Figure 3 shows a partial axial longitudinal section through a first form of embodiment of an idling friction device usable with the clutch assembly according to Fig. 1; Figure 4 shows a partial axial cross-section through the idling friction device, seen along a line IV-IV in Fig. 3; Figure 5 shows a partial axial longitudinal section through a second form of embodiment of an idling friction device usable with the clutch assembly according to Fig. 1, seen along a line V-V in Fig. 6;; Figure shows a partial axial cross-section through the friction device, seen along a line VI-VI in Fig. 5; Figure 7 shows a partial axial longitudinal section through a variant of the idling friction 'device according to Fig. 5; Figure 8 shows a partial axial longitudinal section through a third form of embodiment of an idling friction device usable with the clutch assembly according to Fig. 1, seen along a line VIII-VIII in Fig. 9; Figure 9 shows an axial cross-section through the friction device according to Fig. 8; Figure 10 shows a partial axial longitudinal section through a fourth form of embodiment of an idling friction device usable with the clutch assembly according to Fig. 1, seen along a line X-X in Fig. 11; Figure 11 shows an axial cross-section through the friction device according to Fig.

10; Figure 12 shows a partial axial longitudinal section through a fifth form of embodiment of an idling friction device usable with the clutch assembly according to Fig. 1, seen along a line XII-XII in Fig. 13; Figure 13 shows an axial cross-section through the friction device according to Fig.

12; Figure 14 shows a partial axial longitudinal section through a variant of the idling friction device according to Fig. 12, seen along a line XIV-XIV in Fig. 15; Figure 15 shows an axial cross-section through the friction device according to Fig.

14; Figure 16 shows a partial axial longitudinal section through a sixth form of embodiment of an idling friction device usable with the clutch assembly according to Fig. 1, seen along a line XVI-XVI in Fig. 17; Figure 17 shows an axial view of the friction device according to Fig. 16; Figure 18 shows a partial axial longitudinal section through a variant of the idling friction device according to Fig. 16; Figure 19 shows a partial axial longitudinal section through a flanged sleeve usable with the idling friction device according to Figs. 16 to 18, seen along a line XIX-XIX in Fig. 20; Figure 20 shows a partial axial view of the flanged sleeve according to Fig. 19; Figure 21 shows a partial axial view of a dished spring usable in combination with the flanged sleeve according to Fig. 19, in the friction device;; Figure 22 shows a partial axial view of a variant of the flanged sleeve in Fig. 19; Figure 23 shows a partial radial view of the flanged sleeve, seen along a line XXIII-XXIII in Fig. 22, and Figure 24 shows a variant of the flanged sleeve as shown in Fig. 23.

Figs. 1 and 2 show a clutch assembly 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 a gear input shaft (not shown) which is rotatable about a rotation axis 5. 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 1 5 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 with friction linings 17 axially on both sides encloses the outer hub 13 rotatably and is rotationally elastically coupled, rotatably through a limited angle of rotation in relation to the outer hub 13, 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 torsional vibrations occurring in the relative rotation between the drive disc 19 and the outer hub 13. The clutch assembly 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 rotationally elas tically with the inner hub 1 within the play in rotation determined by the external toothing 7 and the internal toothing 15.With the idling torsional vibration damper 25 there is further associated an idling friction device 27 dimen sioned for idling operation, which damps the torsional vibrations occurring in idling oper ation between the outer hub 13 and the inner hub 1 and is to be explained in greater detail hereinafter. Fig. 2 shows the idling friction de vice merely diagrammatically indicated by a chain line. In operation the idling torsional vi bration damper 25 is effective as preliminary damper and damps the rotational vibrations occurring in the case of 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 tor que of the friction device 23.In the case of great relative angles of rotation between the drive disc 19 and the inner hub 1 the rota tional 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 on the outer hub 13, which radially inwardly overlap the tooth flanks 9, 11 of the external toothing 7 radially and fix the outer hub 13 axially on the inner hub 1. The side discs 31, 33 protrude radially outwards beyond the outer hub 13 and enclose be tween them an annular intermediate disc 37 firmly connected through rivets 35 with the drive disc 19. In windows 39 of the interme diate disc 37 for one part and axially oppo sitely arranged windows 41 and 43 of the 'side discs 31 and 33 respectively for the other part there are seated helical compres sion springs 45 which are stressed in the rela tive 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 offset in relation to one another in the circum ferential direction substantially on a common diameter circle.

The under-load friction device comprises two friction rings 47 and 49 arranged axially on the two sides of the intermeduate disc, of which the one is arranged axially between the drive disc 19, connected with the intermediate disc 49, and the side disc 31 and the other is arranged between the intermediate disc 37 and a thrust ring 51 of disc form. The thrust ring 51 is coupled fast in rotation but axially displaceably with the side disc 33 through axi ally bent-over noses 53 and is initially stressed towards the opposite side disc 31 by a plurality of radial leaf springs 55. The leaf springs 55 carry at their free ends axially bent-over lugs 57 which abut, through open ings 59 of the side disc 33, on the thrust ring 51. The leaf springs 55 are secured by means of the rivets 29 on the outer hub 13.

The idling torsional vibration damper 25 comprises a hub disc 61 secured on the inner hub 1 at an axial distance from the axially adjacent side disc 33, also two cover discs 63 and 65 arranged on axially opposite sides of the hub disc 61, which are connected fast in rotation with one another and with the outer hub 13 by axial -extensions 67 of a carrier disc 69 secured on the outer hub 13 by means of the rivets 29. Similarly to the springs 45, in axially mutually oppositely arranged windows of the hub disc 61 for the one part and of the cover discs 63, 65 for the other part there are seated helical compression springs 71 which, in the relative rotation of the outer hub 13 and the inner hub 1, are resiliently stressed and couple the outer hub 13 rotationally elastically with the inner hub 1.

Several forms of embodiment of the idling friction device 27 which are usable with the clutch assembly according to Figs. 1 and 2 are to be explained below. In the explanations parts of like effect are designated with the reference numerals of Figs. 1 and 2 and provided with-a letter for distinction. For the explanation reference is made to the description of Figs. 1 and 2.It is common to all configurations that the idling friction device comprises a separate, axially acting spring for the friction force generation and engages, axially laterally of the springs 7-1 of the idling torsionai vibration damper 25, in an annular space defined by the tooth shoulders 9, 11 of the external toothing 7 and either the inner circumference or an axial face of at least one of the side discs 31 or 33 Figs. 3 and 4 show an idling friction device 27a entirely limited by the side discs 31a and 33a. The side discs 31a and 33a are provided with annular recesses 73 and 75 in the region of the external toothing 7a, which together with the tooth shoulders 9a and 1 lea form two annular spaces axially on both sides of the external toothing 7a.Support rings 77 and 79 abutting on the tooth shoulders 9a, 11 a are loosely inserted into the annular spaces.

The axial face of the recess 75 of the side disc 33a is supported, through a friction lining 81 which is loosely inserted or is fitted on the support ring 79, upon the support ring 79 and through the latter on the tooth shoulder 1 lea.

Axially between the support ring 77 and the axial face of the recess 73 a thrust ring 83 is arranged which is supported through a further friction lining 85, loosely inserted or fitted on the support ring 77, upon the support ring 77 and through the latter on the tooth shoulders 9a. The thrust ring 83 is guided fast in rotation but axially displaceably on the side disc 31a through noses 87 protruding axially from its internal circumference, and is initially stressed towards the external toothing 7a by a dished spring 89 clamped in between the axial face of the recess 73 and the thrust ring 83. The dished spring 89 is guided fast in rotation on the noses 87 and generates the friction force of the idling friction device.

As an alternative to the form of embodi ment as represented in Figs. 3 and 4, the recesses 73, 75 can also be prepared by bending out of the side discs 31a, 33a or by shortening of the external toothing 7a of the inner hub 1a.

In the form of embodiment as represented in Figs. 3 and 4 the displacement force ex erted upon the drive disc in clutch engage ment is transmitted through the friction lining 81 to the inner hub 1a. In the forms of em bodiment of the idling friction devices as ex plained below the friction device is not ar ranged in the transmission path of the dis placement force from the drive disc to the inner hub. The side discs of the under-load torsional vibration damper are supported di rectly on the tooth shoulders of the external toothing of the inner hub, and the spring of the idling friction device is supported exclu sively on the inner hub or the outer hub or construction elements secured on an additional flanged sleeve.

Figs. 5 and 6 show an idling friction device 27b which is accommodated in an annular space axially adjacent to the idling torsional vibration damper 25b. The annular space is limted axially by the tooth shoulders 11 b of the external toothing 7b adjacent to the tor sional vibration damper 25b for the one part and the cover disc 63b for the other and radi ally at least partially by the internal circumfer ence 91 of the side disc 93. The side disc 33b overlaps the tooth shoulders 1 lib in the 'radial direction only partially. Two annular thrust discs 93, 95 are arranged axially side by side in the annular space.The thrust discs 93, 95 carry on their internal circumference radially inwardly protruding noses 97, 99 which engage in axial grooves 101 on the external circumference of the inner hub 1 b and couple the thrust discs 93, 95 fast in rotation but axially displaceably with the inner hub 1b.

Axially between the thrust discs 93, 95 a further annular thrust disc 103 is arranged which engages with a nose 105 radially protruding from its external circumference in a recess 107 on the internal circumference 91 of the side disc 33b and couples the thrust disc 103 fast in rotation but axially displaceably with the side disc 33b. Friction rings 107, 109 are arranged axially on both sides of the thrust dist 103 between the thrust disc 103 and the thrust discs 93, 95. On the side of the thrust disc pack axially remote from the tooth shoul ders 11 b a dished spring 111 is arranged which bears with its external circumference on the thrust disc 95 and with its internal circumference through a support ring 113 on the flanged disc 61b of the inner hub 1b.The support ring 113 passes through an annular gap formed between the internal circumference of the cover disc 63b and the inner hub 1 b. The dished spring 111 clamps the thrust disc 103, connected through the side disc 33b with the outer hub 13b, in between the thrust discs 93, 95 connected with the inner hub 1 b. The thrust disc 93 is here supported on the tooth shoulders 11 b and the force path of the dished spring 111 is closed by way of the inner hub 1b, the hub disc 61b and the support ring 113.

Fig. 7 shows a variant 27c of the friction device 27b according to Fig. 5, which differs from this friction device essentially in that the dished spring 111 c is clamped in axially between the tooth shoulders 1 1c of the external toothing 7c and the thrust disc 93c axially adjacent to the tooth shoulders 11 c. In place of the support ring 113 the thrust disc 95c axially adjacent to the hub disc 61c carries on its internal circumference axially bent-off noses 115 or a neck interrupted by the lugs 99c, which is axially supported on the hub disc 61c.The dished spring 11 1c again clamps the thrust disc 105c, connected through the side disc 33c with the outer hub 13c, in between the thrust discs 93c and 95c connected with the inner hub ic. The force path is closed by way of the thrust disc 95c, the noses 115, the hub disc 61 c, the inner hub 1 c and the tooth shoulders 1 1c to the dished spring 11 1c. Reference is made to the description of Figs. 5 and 6 for further explanation of the components provided with reference numerals of those Figures.

Figs. 8 and 9 show a further variant of an idling friction device 27d in which the spring force path again is closed exclusively by way of the inner hub 1 d. The idling friction device 27d is arranged on the side of the external toothing 7d of the inner hub 1 d axially remote from the springs 71d of the idling torsional vibration damper 25d. The friction device 27d is arranged axially between the tooth shoulders 9d of the external toothing 7d and a radially slotted resilient securing ring 119 inserted into a ring groove 117 of the inner hub 1d. It again comprises two annular thrust discs 121, 123 arranged axially side by side each of which carries on its internal circumference at least one radially inwardly protruding lug 125 and 127 respectively.The lugs 125, 127 engage in axial grooves 129 of the inner hub 1d and couple the thrust discs 121, 123 fast in rotation but axially displaceably with the inner hub 1d. An annular thrust disc 131, from the external circumference of which a lug 133 protrudes radially, is arranged axially between the thrust discs 121, 123. The lug 133 engages in a recess 135 of the side disc 31d, which with its internal circumference 137 radially outwardly encloses the thrust discs in the form of an annular space. The lug 133 couples the thrust disc 123 fast in rotation but axially displaceably with the side disc 31d and thus the outer hub 13d. Axially between the securing ring 119 and the thrust disc 123 a dished spring 139 is arranged which is supported with its internal circumference on the securing ring 119 and with its external circumference on the thrust disc 123.The dished spring 139 clamps the thrust disc 131 axially in between the thrust disc i21, 131. The force path is closed from the thrust disc 121 abutting on the tooth shoulders 9d by way of the inner hub 1 d and the securing ring 119 to the dished spring 139. Similarly to the idling friction devices 27b and 27c of Figs. 5 to 7, the friction device 27d according to Figs. 8 and 9 is also distinguished by an axially especially narrow style of construction. Since the securing ring 119 is freely accessible, the friction device can be fitted easily. The friction device 27d too can if desired be provided with friction rings arranged axially between the thrust disc 131 and each of the two thrust discs 121 and 131.

Figs. 10 and 11 show an idling friction device 27e which is distinguished by especially few components. The friction device 27e is again arranged on the side of the external toothing 7e of the inner hub 1e axially remote from the idling torsional vibration damper 25e and is accommodated in an annular space formed by the internal circumference 141 of the side disc 31e. In the annular space an annular thrust disc 142 is arranged from the internal circumference of which at least one lug 145 protrudes radially inwards.The lug 145 engages in an axial groove 147 of the inner hub 1e and couples the thrust disc 143 fast in rotation but axially displaceably with the inner hub 1 e. Axially between the thrust disc 143 and tooth shoulders 149, this time of the internal toothing 15e of the outer hub 13e, a further thrust disc 151 is arranged, from the external circumference of which at least one lug 153 protrudes radially outwards.

The lug 153 engages in a recess 155 on the internal circumference 141 of the side disc 31e and couples the thrust disc 1 51 fast in rotation but axially displaceably with the side disc 31e and thus the outer hub 13e. The tooth shoulders 149 of the internal toothing 15e protrude in the axial direction beyond the tooth shoulders 9e of the external toothing 7e. A dished spring 1 57 is supported with its external circumference on the protruding tooth shoulders 149. With its internal circumference the dished spring 157 is supported on the thrust disc 151 and clamps the thrust disc 143 in between the thrust disc 1 51 and a support flange 161 secured through rivets 1 59 on the side disc 31 e. Friction rings 163, 165 are arranged between the thrust disc 143 connected fast in rotation with the inner hub 1e, for the one part, and the thrust disc 151 and the support flange 161 for the other part.

The force path of the friction device 27e is closed from the support flange 161 by way of the side disc 31e to the tooth shoulders 149 of the internal toothing 15e.

The idling friction devices as explained below differ from those explained above essentially in that the force path of the spring generating the friction force is conducted by way of a separate flanged sleeve. Figs. 12 and 13 show an idling friction device 27f in which an annular space in the form of an annular recess 167 of the side disc 31f is formed between the tooth shoulders 9f and the side disc 31f lying axially opposite to the idling torsional vibration damper 25f. A flanged sleeve 169 concentrically enclosing the inner hub 1f and passing through an annular gap remaining between the inner hub if and the internal circumference of the side disc 31f carries at its one end a flanged disc 171 engaging radially outwards in the annular gap and abutting through a friction ring 173 on the axial face of the recess 167.At its other end the flanged sleeve 169 carries a radially outwardly bentover crimped edge 175. Axially between the crimped edge 175 and an outer axial face of the side disc 31f there is arranged a thrust disc 177 annularly enclosing the flanged sleeve 169, from the internal circumference of which disc several lugs 179 extend through axial slots 181. The lugs 179 engage in axial grooves 183 of the inner hub if and connect the thrust disc 177 fast in rotation but axially displaceably with the inner hub 1f. The lugs 179 furthermore connect the thrust disc 177 fast in rotation but axially displaceably with the flanged sleeve 169. A dished spring 185 which is supported with its internal circumference on the crimped edge 175 and with its external circumference on the thrust disc 177 is arranged axially between the thrust disc 177 and the crimped edge 175.The dished spring 185 braces the thrust disc 177, which is connected fast in rotation with inner hub 1f, through a friction ring 187 against the outside of the side disc 31f. The force path is closed from the inside of the side disc 31f by way of the thrust ring 173, the flange ring 167, the crimped edge 175 to the dished spring 185.

For the fitting of the friction device 27f the crimped edge 175 is bent over, with the friction device pre-fitted. In place of the crimped edge 175 bending tabs can also be provided.

It is understood that instead of the recess 167 it is also possible for the side disc 31f to be bent out or for the internal toothing 7f and the external toothing 15f to be axially shortened to form the annular space.

Figs. 14 and 15 show a variant 279 of the friction device 27f. The friction device 279 differs essentially only in the configuration of the dished spring 1859 and the configuration of the flanged sleeve 1 69g provided with radially outwardly bent-over lugs 1759 for supporting the dished spring 1859. For explanation therefore reference is made to the description of Figs. 12 and 13, the same reference numerals being used.

The flanged sleeve 1699 carries several lugs 1759 offset in relation to one another in the circumferential direction. The dished spring 1859 is provided on its internal circumference with recesses 189 matching the lugs 1759, which permit of fitting the dished spring axially on to the flanged sleeve 1 69g over the lugs 1839. By twisting of the dished spring 1 65g it is engaged on the lugs 1759. Fig. 15 shows the engaged position. In order to prevent unintended twisting and release of the dished spring 1859, at least one lug 191 protrudes from its external circumference, engages in a recess 193 on the external circumference of the thrust disc 1779 and connects the dished spring 1859 through the thrust disc 1679 fast in rotation with the flanged sleeve 169g.

In place of the rotation-fast connection by means of lugs 191 it is also possible to provide twist-securing devices effective on the internal circumference of the dished spring, as explained below by reference to Figs. 19 to 22.

Figs. 16 and 1 7 show a further variant 27h of an idling friction device in which, similarly to the friction devices 27f and 279, a flanged sleeve is used for clamping in the spring. The flanged sleeve designated by 195 protrudes from axially outside into an annular space limited axially by the tooth shoulders 9h and radially by the internal circumference 197 of the side disc 31h. The flanged disc 195 carries at its end axially remote from the tooth shoulders 9h a flanged disc 199 which is secured through rivets 201 on the side disc. At its end axially adjacent to the tooth shoulders 9h the flanged sleeve 195 coaxially surrounding the inner hub 1 h is provided with a crimped edge 203 protruding radially outwards just like the flanged disc 199.An annular thrust disc 205 carrying a radially inwardly protruding lug 207 on its internal circumference is mounted on the flanged sleeve 195 axially between the crimped edge 203 and the flanged disc 199.

The lug 207 engages through an opening 209 of the flanged sleeve 195 in an axial groove 211 of the inner hub 1h and couples the thrust disc 205 fast in rotation but axially displaceably with the inner hub 1h. The opening 209 of the flanged sleeve 195 is of such wide.dimensions in the circumferential direction that the thrust disc 205 can rotate in relation to the flanged sleeve 195 at least through an angle of rotation equal to the rotational play of the external toothing 1 5h in relation to the internal toothing 7h. Axially between the thrust disc 205 and the crimped edge 203 there is arranged a dished spring 213 which is supported with its internal circumference on the crimped edge 203 and with its external circumference through a thrust ring 215 on the thrust disc 205.The thrust ring 215 carries on its internal circumference a radially inwardly protruding lug 217 which likewise engages in the opening 209 of the flanged sleeve 195. However the width of the lug 217 is so dimensioned that the thrust ring 215 is guided fast in rotation but axially displaceably on the flanged sleeve 195. Axially on both sides of the thrust disc 205, friction rings 219, 221 are arranged between the thrust disc 205 and the flanged disc 199 and between the thrust disc 205 and the thrust spring 215. The dished spring 213 clamps the thrust ring 205, which is connected fast in rotation with the inner hub 1h, between the flanged disc 199 and the thrust ring. The force path of the dished spring 213 is closed by way of the flanged sleeve 195.

Fig. 18 shows a variant 27i of an idling friction device which differs from the friction device 27h merely in the nature of the securing of the flanged disc 1 99i of the flanged sleeve 195i. Using the same reference numerals, for further explanation of the friction device 27i reference is made to the description of Figs. 16 and 17. The flanged disc 199i carries on its external circumference lugs 219 bent axially to the side disc 31 i, which engage through openings 221 of the side disc 31i and are swaged at their free ends, as illustrated at 223. In place of the swaging 223, spot welds or hard solder connections can also be provided.

Variants for the supporting of the dished spring supported on a crimped edge of a flanged sleeve, as shown in Figs. 16 to 18, are to be explained below with reference to Figs. 19 to 22. The variants can also be used for the supporting of the dished spring as shown in Figs. 12 to 15.

Figs. 19 to 21 show a flanged sleeve 225, similar to the flanged sleeves 169 and 195, which comprises at one end several radially protruding lugs 229 arranged with spacing in the circumferential direction, for the axial supporting of a dished spring 227 generating the friction force of an idling friction device. The dished spring 227 is provided on its internal circumference with corresponding recesses 231 arranged at the angular interval of the lugs 229. The recesses 231 permit the axial fitting of the dished spring 227 on to the flanged sleeve 225. After fitting on, the dished spring 227 is rotated in relation to the flanged sleeve 225, and projections 233 remaining between the recesses 231 come to abut on the lugs 229. As shown best by Fig.

21, on both sides of the projections 233 noses 235 are formed with a spacing from one another corresponding to the circumferential width of the lugs 229 and reach axially past the lugs 229 and secure the dished spring 227 in the circumferential direction on the flanged sleeve 225 against undesired rotation. Radial noses 237 can be formed on the external circumference of the dished spring 227 and facilitate rotating in installation.

Figs. 22 and 23 show a variant of the rotation-securing arrangement for a dished spring 227k supported on a flanged sleeve 225k.

The variant differs only in the nature of the securing in rotation, so that for further explanation reference is made to the description of Figs. 19 to 21, the same reference numerals being used. In place of the noses 235 formed on the dished spring 227 in Figs. 19 to 21 for securing in rotation, shoulders 239 facing one another in the circumferential direction are formed in the circumferential direction on both sides of the lugs 229k of the flanged sleeve 225k and receive between them the lug 233k remaining between the recesses 231k of the dished spring 227k, to secure the dished spring 227k against rotation. In Fig. 23 the shoulders 239 are formed by an impression pressed in a direction axially away from the dished spring 227k into the lugs 229. Fig. 24 shows a variant 2291 of the shoulders 2391 formed for the securing of the lugs 2331 of the dished spring against rotation. The shoulders 2391 are formed by punched-out, axially bent-over end zones of the lugs 2291.

Claims (24)

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 tooth shoulders (9, 11) facing axially away from one another, b) an outer hub (13) enclosing the inner hub (1) and coupled with the inner hub (1) fast in rotation but with a pre-determined play in rotation through an internal toothing (15) engaging in the external toothing (7), c) an annular lining-carrier disc (19) rotatable in relation to the outer hub (13), d) an under-load torsional vibration damper (21) dimensioned for operation under load having two damper parts (31, 33, 37) rotatable in relation to one another through a limited angle of rotation and supported on one another rotationally elastically through several springs (45), of which damper parts one (37) is connected fast in rotation with the lining carrier disc (19) and the other (31, 33) is connected fast in rotation with the outer hub (13) and one of the two damper parts comprises two annular side discs (31, 33) arranged with axial spacing from one another which enclose the outer toothing (7) of the inner hub (1) axially between them and on which tooth shoulders (9, 11) are axially fixed and the other of the two damper parts comprises an intermediate disc (37) arranged axially between the two side discs (31, 33), and with an under-load friction device (23) effective in the relative rotation of the damper parts (31, 33, 37), e) an idling torsional vibration damper (25) dimensioned for idling operation with two damper parts (61, 63, 65) arranged axially laterally of the under-load torsional vibration damper (21) and supported rotationally elastically on one another through several springs (71), of which damper parts one (61) is connected fast in rotation with the inner hub (1) and the other (63, 65) is connected fast in rotation with the outer hub (13), and having an idling friction device (27) effective in the relative rotation of the inner hub (1) and the outer hub (13), characterised in that the idling friction device (27) is arranged axially laterally of the springs (71) of the idling torsional vibration damper (25) which rotationally elastically couple the damper parts (61, 63, 65) at least partially in an annular space defined by tooth shoulders (9, 11) of the inner hub (1) or of the outer hub (13) and faces (73, 75; 91; 137; 141; 167; 197) of the side discs (31, 33) of the under-load torsional vibration damper (21) adjacent to the tooth shoulders (9, 11) and comprises a separate axially acting spring (89; 111; 139; 157; 185; 213) generating the friction force of the idling friction device (27).

2. Clutch assembly according to Claim 1, characterised in that the side discs (31a, 33a) of the under-load torsional vibration damper are firmly connected with the outer hub (13a) and in that axially on both sides of the external toothing (9a) of the inner hub (1a) annular spaces (73, 75) are provided which, lying opposite to the tooth shoulders (9a, 1 lea) of the inner hub (1 a), are axially limited by the side discs (31a, 33a), and in that the idling friction device (27a) contains in one of the annular spaces (73) a thrust ring (83) connected fast in rotation but axially movably with the adjacent side disc (31a) and the annular, axially acting spring (89) axially between the thrust ring (83) and this side disc (31a).

3. Clutch assembly spaces (73, 75) contains a support ring (77, 79) of disc form abutting on the tooth shoulders (9a, 1 lea) and a friction ring (81, 85) axially between the support ring (77, 79) and the axially adjacent side disc (31a, 33a).

4. Clutch assembly according to Claim 3, characterised in that the support rings (77, 79) are loosely inserted.

5. Clutch assembly according to Claim 1, characterised in that the side discs (31b, c, d, 33b, c, d) of the under load torsional vibration damper are connected firmly with the outer hub (13b, c, d), in that the internal circumference (91; 137) of one of the two side discs (33b, c; 31d) merely partially radially overlaps the tooth shoulders (1 1b, c; 9d) adjacent to it of the external toothing (7b, c, d) for the formation of the annular space, in that the inner hub (1b, c, d) carries an abutment face (61b, c; 119) axially facing the tooth shoulders (1 it, c; 9d) in the region of the annular space axially at a distance from the tooth shoulders (ill, c; 9d) and in that the idling friction device (27b, c, d) is arranged axially between the tooth shoulders (ill, c; 9d) and the abutment face (61b, c; 119) and comprises at least one first thrust ring (93, 95; 121, 123) connected fast in rotation but axially movably with the inner hub (1b, c, d), a second thrust ring (105; 131) connected fast in rotation but axially movably with the side disc (33b, c; 31d) and the annular spring (111; 139) which clamps the thrust rings axially against one another.

6. Clutch assembly according to Claim 5, characterised in that the idling torsional vibration damper (25b, c) comprises a hub disc (61b, c) secured axially laterally of the external toothing (7b, c) and with axial spacing from the tooth shoulders (ill, c) on the inner hub (1b, c) and two cover discs (63b, c, 65b, c) arranged axially on both sides of the hub disc (61b, c), connected with the outer hub (13b, c) and supported rotationally elastically on the hub disc (61b, c), in that at least -cover disc (63b, c) axially adjacent to the external toothing (7b, c) forms an annular gap between itself and the inner hub (1b, c), and in that the idling friction device (27b, c), arranged axially between the tooth shoulders (ill, c) of the external toothing (7b, c) and the cover disc (63b, c) forming the annular gap, is axially supported through the annular gap on the hub disc (61b, c).

7. clutch assembly according to Claim 6, characterised in that the second thrust ring (105) is arranged axially between two first thrust rings (93, 95) and in that the annular spring (111) is clamped axially between one of the two first thrust rings (93, 95) and either the tooth shoulders (ill) of the abutment face (61b).

8. Clutch assembly according to Claim 7, characterised in that the annular spring (111) is supported on the hub disc (61b) through a sleeve (113) which passes coaxially through the annular gap.

9. Clutch assembly according to Claim 7, characterised in that the first thrust ring (95c), placed remote from the annular spring (11 1c), carries an extension (115) reaching axially through the annular gap and supported on the hub disc (61c).

10. Clutch assembly according to Claim 5, characterised in that the abutment face is provided on a securing ring (119) provided on the inner hub (1d) especially on the side of the external toothing (7d) especially on the side of the external toothing (7d) axially remote from the idling torsional vibration damper (25d).

11. Clutch assembly according to Claim 10, characterised in that the second thrust ring (131) is arranged axially between two first thrust rings (121, 123).

12. Clutch assembly according to Claim 1, characterised in that the side discs (31e, 33e) of the under-load torsional vibration damper are firmly connected with the outer hub (13e), in that the internal circumference (141) of one of the two side discs (31e) only partially radially overlaps the tooth shoulders (9e) adjacent to it, for the formation of the annular space, in that an annular flange (161) limiting the annular space at an axial distance from the internal toothing (15e) of the outer hub (13e) and protruding radially inwards beyond the side disc (31e) is connected with the outer hub (13e), in that the internal toothing (15e) comprises tooth shoulders (149) protruding axially beyond the tooth shoulders (9e) of the external toothing (7e) and in that the idling friction device (27e) is clamped in axially between the annular flange (161) and the tooth shoulders (149) of the internal toothing (15e) and comprises a thrust ring (143) connected fast in rotation but axially movebly with the inner hub (1e), a second thrust ring (151) connected fast in rotation but axially movably with the side disc (31e) and the annular spring (157) which clamps the thrust rings axially against one another.

13. Clutch assembly according to Claim 1, characterised in that the side discs of the under-load torsional vibration damper are firmly connected with the outer hub (13f, g), in that the internal circumference of one (31f, g) of the two side discs radially overlaps the tooth shoulders (9f, g) adjacent to it and carries a radially inwardly protruding ring part at an axial distance from the tooth shoulders (9f, g) of the external toothing (7f, g), in that a flanged sleeve (169) coaxially passing through the ring part carries axially on one one side of the ring part a radially outwardly protruding annular flanged disc (171) overlapping the ring part and stop elements (175) on the other side of the ring part, and in that axially between the ring part and the stop elements (175) there is arranged a thrust ring (177) connected fast in rotation but axially movably both with the flanged sleeve (169) and with the inner hub (1f, g) and axially between the thrust ring (177) and the stop elements (175) there is arranged the annular, axially acting spring (185).

14. Clutch assembly according to Claim 13, characterised in that the thrust ring (177) carries on its internal circumference at least one radially inwardly protruding lug (179) which engages through an opening (181) of the flanged sleeve (169) in a groove (183) of the inner hub (1f, g).

15. Clutch assembly according to Claim 14, characterised in that the stop elements are formed as radially outwardly protruding support lugs (183g) arranged with spacing from one another in the circumferential direction of the flanged sleeve (169g) and in that the annular spring is formed as dished spring (1859) and comprises on its internal circumference recesses (189) matching the support lugs (1839) and in that the dished spring (1859) abuts on the support lugs (1839) with zones placed between the recesses (189) and further is supported fast in rotation on the thrust ring (177g).

16. Clutch assembly according to Claim 1, characterised in that the side discs (31h, i, 33h, i) of the under-load torsional vibration damper are connected fast with the outer hub (13h, i), in that the internal circumference (197) of one (31h, i) of the two side discs only partially radially overlap the tooth shoulders (9h, i), adjacent to it, of the inner hub (1h, i), for the formation of the annular space, in that in the annular space there engages coaxially a flanged sleeve (195) which carries at one end a radially outwardly protruding flanged disc (199) firmly connected with the outer hub (13h, i) and at its other end stop elements (203) and in that axially between the flanged disc (199) and the stop elements (203) there is arranged a thrust ring (205) rotatable in relation to the flanged sleeve (195) and connected fast in rotation but axially movably with the inner hub (1h, i) and axially between the thrust ring (205) and the stop elements (203) the annular, axially acting spring (213) is arranged.

17. Clutch assembly according to Claim 16, characterised in that the flanged disc (199) is secured to the side disc (31h, i), forming the annular space, of the under-load torsional vibration damper.

18. Clutch assembly according to Claim 16, characterised in that the stop elements are formed as radially outwardly protruding support lugs (229) arranged with spacing from one another in the circumferential direction of the flanged sleeve (225) and in that the annular spring is formed as dished spring (227) and comprises recesses (231) matching the support lugs (229) on its internal circumference and in that the dished spring (227) is supported fast in rotation on the support lugs (229) of the flanged sleeve (225) with zones (233) placed in the circumferential direction between the recesses (231).

19. Clutch assembly according to Claim 18, characterised in that the dished spring (227) comprises, in the circumferential direction between the recesses (231), arresting projections (235) engaging axially between the support lugs (229).

20. Clutch assembly according to Claim 18, characterised in that the flanged sleeve (225k) comprises, in the circumferential direction between the support lugs (229k, I), arresting projections (239) engaging axially in the recesses (231k).

21. Clutch assembly according to Claim 14 or 16, characterised in that the stop elements are formed by a crimping over (175, 203) of the end of the flanged sleeve (169; 195) remote from the flanged disc (171, 199).

22. Clutch assembly according to one of Claims 5 to 21, characterised in that the thrust ring (93, 95; 121, 123; 143; 177; 205) connected with the inner hub (1 b-i) carries on its internal circumference at least one radially inwardly protruding lug (97, 99; 125, 127; 145; 179; 207) which engages in an axial groove (101; 129; 147; 183; 211) of the inner hub (1 b-i).

23. Clutch assembly according to one of Claims 5 to 12, characterised in that the thrust ring (103; 131; 151) connected with the outer hub (13b-e) carries on its external circumference at least one radially outwardly protruding lug (105; 133; 153) which engages in a recess (207; 135; 159) on the internal circumference of the side disc (33b; 31d, e) of the under-load torsional vibration damper.

24. Clutch assembly as claimed in Claim 1 substantially as described with reference to Figs. 1-4, Figs. 1,2,5,6 and 7, Figs. 1,2,5 and 7, Figs. 1, 2, 8 and 9, Figs. 1,2,10 and 11, Figs. 1,2,12,13,14 and 15, Figs.

1,2,16,17 and 18, Figs. 1,2,19,20,21 and 22, or Figs. 1,2,23 and 24 of the accompanying drawings.