FR2590949A1 - CLUTCH DISC FOR FRICTION CLUTCH FOR MOTOR VEHICLE - Google Patents

Abstract

An inner part of hub 1 is connected in rotation by means of teeth 7, 15, with play, to an outer part of hub 13, elastically coupled to a drive disc 19 provided with friction linings 17, via a torsional oscillation damper 21 for operating under load. The two hub parts 1, 13 are elastically coupled by a torsional oscillation damper 25 for idle operation, which is arranged on the side of the first damper 21 and which comprises two annular flanges 57, 59, having at their periphery support lugs 63, 65. A friction device 27 can be mounted in the region of the damper 25, which makes it possible to have relatively large friction surfaces, while retaining a reduced axial size. (CF DRAWING IN BOPI)

Description

"CLUTCH DISC FOR CLUTCH

A FRICTION OF A MOTOR VEHICLE "

  The present invention relates to a clutch disc for a motor vehicle friction clutch, said disc comprising: a) an inner portion. hub with teeth

  externally limited on each side by annular shoulders

lar,

  (b) an outer hub part, surrounding the

  hub and having an internal toothing in engagement with the external toothing, which provides a connection

  in rotation between the outer hub portion and the

  inside the hub, while maintaining a rotational

  predetermined, c) a drive disc provided with friction linings and rotatably mounted at a limited angle of rotation relative to the outer hub portion, d) a torsion damping damper, provided

  for charging operation, with two parts of

  weavers with respect to each other and

  being elastically one on the other via

  of a plurality of springs, one of the damping parts

  being connected to the outer part of the hub and

  the other damper part being connected to the disk of

  dragging, one of the shock absorbing parts comprising

  two lateral flanges spaced apart from one another

  axial connection and connected to each other, while the other damper portion comprises an intermediate flange, disposed between the two side flanges and taking support

  on these via springs.

  e) a torsional oscillation damper provided for the no-load operation, and disposed on the side of one of the lateral flanges farthest from the intermediate flange, with two shock-absorbing parts rotating relative to one another; other and resiliently abutting each other via a plurality of springs, one of the damper portions being connected to

  the outer part of the hub and the other part of damping

  being connected to the inner hub portion.

  A clutch disc of this type is known from German Patent No. 1,680,049. This clutch disc comprises an inner hub portion intended to be coupled.

  to the input shaft of the gearbox with

  rotation on said shaft, but with possibility of axial displacement relative to said shaft, the outer hub portion being rotatably mounted at a limited angle of rotation around the inner portion

  hub. The outer hub portion has a den-

  internal thread which determines, by its engagement with the external toothing of the inner hub portion, the play of rotation between the two hub parts. The disc

  with friction linings, is itself

  even linked in rotation with the outer hub part,

  in an elastic way, through the damping

  torsion oscillations sized for the function

  in charge. This torsional oscillation damper comprises two lateral flanges, fixed to the outer hub portion, and an intermediate flange

  disposed between the two lateral flanges and

  on a limited angle of rotation relative to the outer hub portion, the intermediate flange being

  integral with the drive disk. This intermediate flange

  diaire bears elastically on the lateral flanges by means of several springs, distributed according to

  the circumferential direction. The oscillation damper-

  torsion for load operation includes

  another friction device, sized for this function

  in charge, which dampens the elastic oscillations

  torsion ticks of the drive disk compared to

the outer part of the hub.

  On the side (towards the axis) of the part

  outer hub, there is a pre-damper

  torsion cilations, or oscillation damper for

  the idle operation, which is dimensioned for this function

  vacuum coupling and resiliently coupling the outer hub portion to the inner hub portion by

  through several springs. The bone damper

  torsion cations for idle operation

  a flange attached to the inner hub portion, on the side of the external toothing of this part, and two cover flanges arranged on either side of the previous flange and held by an axial extension of the outer hub portion . The two flanges of recovery are supported on the first flange by

  through the springs of the oscillation damper-

  torsion for empty operation. This amor-

  weaver acts only inside the set of rotation determined by the inner and outer teeth of the two hub parts, and it does not intervene after

  this game was compensated for by the relative movement of teeth

  res. In the known clutch disc mentioned above,

  the shock absorber of torsional oscillations for the function-

  is relatively expensive, because of its structure, and it has a relatively

important in the axial direction.

  German Patent Application Publication No. 3,142,842 discloses another clutch disc for a motor vehicle friction clutch, the hub of which is rotatably connected to a drive disk carrying the friction linings. , through

  of a torsional oscillation damper for the function

  multi-stage charging, the drive disc

  drag that can rotate at a limited angle of rotation relative to the hub. The oscillation damper

  torsion comprises two sets of springs, which are

  placed all around the hub, between two disc parts, following two concentric circles of different diameters, so with a spacing in the radial direction. From these disk portions protruding support segments which take up one above the other, overlapping in the axial direction between the springs.

  and on which the springs rest, during a rotational

  relative drive disc relative to the hub. The torsional oscillation damper of this other known clutch disk is relatively wide, and

  it consists of relatively numerous pieces.

  The object of the invention is to provide a solution

  which, in a clutch disk of the kind indicated in

  duction, simplifies the structure of the

  1C0 torsion-tions for vacuum operation, and allows to reduce the dimensions of this damper in

the axial direction.

  For this purpose, in the clutch disk object of

  the invention, the two parts of the oscillation damper

  torsion conditions for idle operation are

  annular flanges, which comprise in their peripheral region legs folded on each other.

  others in the axial direction and now between them,

  the circumferential direction, the springs of this

  shock absorber of torsional oscillations for the functioning

empty.

  So, unlike the oscillation damper-

  torsion ratios for the vacuum operation known from German Patent 1 680 049, the corresponding damper

  of the clutch disc according to the invention only requires

  two annular flanges. The springs of this amortization

  tors can be distributed unequally over a single circle of relatively large diameter, which decreases

  the mechanical loading of the damping components

  and reduces manufacturing costs. In addition, there can be housed in this damper springs more numerous than in the usual torsion damping dampers, which allows to have couples

  higher extreme rotation or rotation angles

  relative importance. In addition, the increase

  In the radial direction, it is easier to mount springs of different forces to obtain a "stepped" vacuum operating characteristic. Advantageously, the springs of the torsion splash damper for the vacuum operation are guided in the radial direction by bent portions

  elongate, formed on the most distant annular flange

  attached to the outer hub portion. In this way, the axial dimensions of the clutch disk, inside

  of the circle in which the springs are arranged,

  can be reduced which allows to have a race

  more important for the clutch stop.

  In a preferred embodiment of the invention,

  In addition to the friction device dimensioned for the load operation, the clutch disk further comprises a friction device designed for operation in a vacuum, in order to reduce jolts.

  due to the change of load during the operation of the

  unladen operation at load, and also reduce oscillations and noise. The friction device for the vacuum operation is advantageously incorporated by taking advantage of the space available between

  the two annular flanges, in the region of the damping

  torsion oscillations for operation at

empty.

  In a first variant of the device for

  for vacuum operation, the ring flange

  of the torsional oscillation damper for the function

  emptying, which is farthest from the outer toothing of the inner hub part, is used

  to generate the friction force. The money device

  tion comprises here two annular friction discs, disposed on either side of the annular flange considered and rotatably mounted relative to this flange, the two friction discs being rigidly connected in rotation with each other, as well as with the other annular flange, by means of connecting members. Friction discs are

2 590949

  tight on either side of the annular flange, either by the effect of their own elasticity, or by the action of a

  additional ring-shaped spring, acting in

  axial position. For the axial connection of the two friction disks, one with the other or with the annular spring, it is possible to envisage a riveting or a clipping or even bayonet mountings, with connecting members that pass through openings in

  the annular flange enclosed by the friction discs.

  O10 The connecting members can simultaneously provide for the rotational coupling of the friction discs with the other annular flange of the torsion oscillation damper, by clinging in openings arranged

on this other flask.

  In a second variant of the friction device for the vacuum operation, one of the annular flanges

  of the torsional oscillation damper for the function

  empty circuit is connected to a support bushing

  posed coaxially while the other annular flange

  is connected to an expandable socket with a -

  elasticity in the radial direction and coaxial to the socket

  support. The expandable sleeve is preloaded

  radial arrangement, against the support sleeve, by spring means. Such a friction device acts according to a radius defined exactly, and on a torsion angle which is not limited by any stop or the like. The spring means may be constituted by the elasticity

  clean of the expandable sleeve. However, it is

  tageux to provide a special annular spring, acting in a radial direction. The support sleeve is

  preferably disposed outside the expanding sleeve.

  sible, so that the friction force increases at the same time as the centrifugal force. The portion of the bearing bushing which comes into frictional contact with the expandable bushing is advantageously located between the annular flanges of the torsional vibration damper, but it may also be located outside the

  annular flanges (in the axial direction).

  Anyway, the invention will be better understood, and other characteristics will be highlighted, to

  using the following description, with reference to the drawing

  schematic annexed representing, as examples not

  limiting some forms of execution of this disk of em-

  clutch for friction clutch of a motor vehicle: Figure 1 is a front view, partial, of a clutch disc according to the invention; Figure 2 is a half-sectional view through the axis of the clutch plate, along the line II-II of Figure 1; Figure 3 is a half-sectional view through the axis of the clutch disc, along the line III-III of Figure 1; Figure 4 is a partial cross-sectional view

  the axis, along the line IV-IV of Figure 5, of a first

  embodiment of the friction device for the idle operation usable in the clutch plate according to FIG. 1; Figure 5 is a half-sectional view through the axis of this friction device, along the line V-V of Figure 4; Figure 6 shows a first variant of the friction device of Figures 4 and 5, partially in section through the axis; Figure 7 shows a second variant of the friction device of Figures 4 and 5, partial sectional view passing through the axis; FIG. 8 is a partial cross-sectional view along the axis, along the line VIII-VIII of FIG. 9, of a second embodiment of the friction device for the idling operation that can be used in the clutch disc according to FIG. 1; Figure 9 is a half-sectional view through

  the axis of this friction device, along line IX-

IX of Figure 8;

  Figure 10 is a partial cross-sectional view of

  characterized in that the axis, along the line X-X of Figure 11, of a third embodiment of the friction device for the idling operation used in the clutch disc according to Figure 1; Figure 11 is a half-sectional view through the axis of this friction device, along the line XI-XI of Figure 10;

  Figure 12 is a partial cross sectional view of

  characterized in that the axis, along the line XII-XII of Figure 13, of a fourth embodiment of the friction device for the idling operation used in the clutch disc according to Figure 1; Figure 13 is a half-sectional view through the axis of this friction device, along the line XIII-XIII of Figure 12; Figure 14 is a partial front view of a fifth embodiment of the friction device for the idle operation usable in the clutch disc according to Figure 1; Figure 15 is a half-sectional view through

  the axis of this friction device, along line XV-

XV of Figure 14;

  Figure 16 is a partial cross-sectional view of

  disposed at the axis along the line XVI-XVI of Figure 17, a sixth embodiment of the friction device for the operation-vacuum used in the clutch disc according to Figure 1; Figure 17 is a half-sectional view through the axis of this friction device, according to the line XVII-XVII of Figure 16; Figure 18 shows a variant of the friction device of Figures 16 and 17, partially in sectional view

passing through the axis.

  FIGS. 1 to 3 show a clutch disc belonging to a friction clutch of a motor vehicle, the disc comprising a part

  inner hub 1 which has integral grooves

  3 for its rotational connection, allowing axial translation, with the input shaft of a gearbox, not shown, which is rotatably mounted along an axis of rotation 5. The inner hub portion 1 comprises a toothing external 7 which is limited to each

  side, in the axial direction, by two annular shoulders

  toothed teeth 9 and 11 which are turned in opposite directions.

  An outer hub portion 13, coaxially surrounding the inner hub portion 1, has an internal toothing 15 which is engaged with the external toothing 7; the meshing of the teeth 7 and 15 ensures a connection in rotation between the outer hub portion 13 and the inner hub portion 1, while leaving between these

  two parts a predetermined rotation game.

  A drive disk 19 of annular shape,

  seen from friction linings 17 on both sides,

  re the outer portion of hub 13 and is rotatably mounted around this portion, at an angle of rotation

  limit. The drive disk 19 is coupled in rotation

  elastically with the outer part of hub 13, via a shock absorber of oscillations of

  Twist 21 sized for load operation.

  A friction device 23, also sized for load operation, absorbs the torsional oscillations occurring in the relative movement between the drive disk 19 and the outer hub portion 13. The clutch disk further comprises a shock absorber

  of torsional oscillations sized for the function

  unladenly, and acting between the outer hub portion 13 and the inner hub portion 1, by elastically coupling these two hub portions 13 and 1, within the limits of the rotation clearance defined by the

  external teeth 7 and the internal toothing 15. At this damping

  torsion oscillations 25 for the vacuum operation can be associated, as shown schematically in Figures 2 and 3 at 27 by a dotted line,

  a friction device sized for the operation

  empty, which absorbs the torsional oscillations

  falling into the empty running between the party

  outer hub 13 and inner hub portion 1.

  In the case where the internal friction is sufficient, the friction device 27 for the vacuum operation can be eliminated. Various embodiments of this friction device 27 will be described in detail

lower.

  During operation, the oscillation damper

  torsion fractions for the internal vacuum operation

  comes as a pre-damper, and it damps the torsional oscillations that occur during small relative rotations between the drive disc 19 and the part

  1. For the relative rotations

  In the no-load operation, the torsional oscillation damper 21 for the load operation does not intervene because of the relatively high frictional torque of the friction device 23. In the case of relative rotations of large amplitude between the drive disk 19 and the inner hub portion 1, the clearance of rotation between the external toothing 7 and the internal toothing 15 is compensated, and the torsion damping damper 25 for the operation at

empty does not intervene anymore.

  The torsional oscillation damper 21 for the load operation comprises two lateral flanges

  31 and 33, which are secured by means of rivets 29 on the

  outer hub tie 13, which by their inner edges

  cover the annular shoulders 9 and 11 of the den-

  7 and which, also by their inner edges, directly provide an axial connection between the outer hub portion 13 and the inner hub portion

  1. The two side flanges 31 and 33 enclose a flange

  intermediate annulus 37 rigidly connected to the drive disc 19, the two lateral flanges 31 and 33 being joined together by means of rivets 35 which form

  spacers and which, crossing openings-mena-

  in the intermediate flange 37, limit the relative rotation angle of the torsional oscillation damper 21 for load operation. The intermediate flange 37 can be made in one piece

  with the drive disc 19, extending this

  only on its periphery. The intermediate flange 37 has windows 39 located opposite windows 41 and 43 respectively formed in the side flanges 31 and 33. Helicoidal compression springs 45, housed on the one hand in the windows 39 of the intermediate flange 37, and in the corresponding windows 41 and 43 of the lateral flanges 31 and 33, are solicited

  in the relative rotational movement of the drive disk.

  19 and the outer hub portion 13, these springs 45 providing a connection in elastic rotation between the drive disc 19 and the outer hub portion 13. As shown in Figure 1, the springs are distributed, at intervals, following the same circle

of determined diameter.

  The friction device 23 for the load operation comprises two friction rings 47 and 49, arranged on either side of the intermediate flange 37, inside the circle in which are distributed

  the springs 45 and a spring 51 acting in direct

  axially, for example a spring washer, arranged

  between the lateral flange 33 located closest to the amor-

  torsion oscillator 25 for the operation of

  empty, on the one hand, and the friction ring 49, on the other hand. Between the spring 51 and the friction ring 49 is inserted a bearing ring 53, rotatably connected with the lateral flange 33 but movable axially relative thereto. It is also provided, between the friction ring 47 and the other lateral flange 31, a bearing ring 55 rotatably connected with this lateral flange 31,

  but movable axially with respect to said flange. The res-

  fate 51, which is supported by its inner edge against the

  side flange 33, elastically squeezes the flange

  37, which is slightly movable axially, between the friction rings 47 and 49, the transmission of the

  spring force being effected by means of the

  than lateral 31 and rivets 29 and 35 to the flange

lateral 33.

  The torsional oscillation damper 25 for the vacuum operation comprises two annular flanges 57 and 59 disposed at a distance from each other (in the axial direction). The annular flange 57 is applied against the lateral flange 33, and it is fixed to the outer hub portion 13 by means of the rivets 29 and / or secured to the side flange 33 by means of rivets or not shown welds. The annular flange 57 has, at its periphery, a plurality of support lugs 63 situated at a distance from one another and bent in the axial direction so as to move away from the lateral flange 33. The annular flange 59 comprises, at its periphery, other paired support lugs 65, which are, relative to the foregoing lugs 63, one closer to the axis 5 and the others further from the axis 5. Between the lugs 63 and 65 consecutive (in the circumferential direction) are arranged helical compression springs 67 which are biased elastically during the relative rotational movement of the outer hub portion 13 relative to the inner hub portion 1. The springs 67 thus elastically couple the outer hub portion 13 with the inner hub portion 1, within the limits of the set of rotation defined by the teeth 7 and 15. The outermost annular flange 59 (in the direction of the axis 5) is still provided at its periphery, between

  pairs of support legs 65, of arched parts allon-

  which maintain and guide the

  springs 67, both radially and

axial position.

  In the clutch disk described with reference to FIGS. 1 to 3, the torsional oscillations appearing

  during idling operation are damped by rubbing

  components of this clutch disc.

  To obtain high coefficients of friction, it is possible, as shown in FIGS. 2 and 3, to provide a friction device sized for operation.

  empty. In the following, we describe several forms of

  friction device 27 for the operation of the

  The parts or parts providing the same functions will be designated by the same numerical references as in FIGS. 1 to 3, with the addition of a letter to distinguish them. according to the embodiments, and the explanation of these various embodiments is

  refers to the general description made above with

  see Figures 1 to 3. All special configurations

  The fact that the friction device for the vacuum operation has a small bulk in the axial direction, and that the thrust forces exerted on the clutch disk during Actuation of the friction clutch, are not affected by this friction device for the idling operation. FIGS. 4 to show friction devices in which the outermost annular flange 59 (in

  axial direction), is used to generate the

  friction, being clamped between two friction surfaces subjected to an elastic prestress tending to bring them closer to one another. FIGS. 16 to 18 show friction devices in which the friction torque is generated by means of a socket

  resiliently biased friction in the radial direction.

  Figures 4 and 5 show a device for

  27a for the vacuum operation, with two friction discs 71 and 73 which are arranged on either side of the outermost annular flange 59a (in

  the axial direction), and which apply against this flas-

  than annular 59a via rings of rub-

  75 and 77 within the corresponding circle

  with support legs 65a. An annular spring 79a is dis-

  placed between the friction disc 71 and the annular flange 57a, and is rigidly connected by spacer rivets 81 to the periphery of the outermost friction disc 73 (in the axial direction). Spacer rivets 81 pass through circumferentially elongated openings 83 formed in the annular flange 59a, which result from the cutting of the bearing lugs 65a located closest to the axis 5a, and which allow a relative rotation of the friction discs 71 and 73 with respect to the annular flange 59a of an amplitude corresponding at least to the rotation clearance between the corresponding teeth 7a and 15a of the inner hub portion 1a and the outer hub portion 13a . The friction disk 71 located the innermost

  (in the axial direction) is connected in rotation with the rivets-

  spacers 81, at its periphery, by openings 85

  which allow an axial displacement of this disk of

  71. The annular spring 79 has a plurality of resilient tongues 87, extending radially toward the axis 5a and subjecting the friction device 27a to

  an elastic force in the direction of this axis. The res-

  Annular fate 79a also comprises folded tabs 89, turned towards the annular flange 57a and introduced into openings 91 of this annular flange 57a, to rotate the friction discs 71 and 73 into rotation.

  with the annular flange 57a. To reduce the clutter

  in the axial direction, the heads of the rivets 29a are housed in recesses 93 of the annular flange 57a, and this annular flange 57a is fixed to the side flange 33a by means of countersunk countersunk rivets, indicated at 95. These rivets 95 may be replaced by other fastening means, such as for example welding spots or the like. The annular spring 79 may also be placed on the other side of the friction device 27a, providing for a modification of the connecting means between the friction rings 71 and 73 and the annular flange 57a. It is also possible to use other spring means, for example leaf springs. The advantage of the friction device for the vacuum operation according to FIGS. 4 and 5 lies in the fact that it provides a large friction surface and a large average friction radius, for a relatively low manufacturing cost. In addition, the maximum torsion angle

  friction device 27a is relatively large.

  FIG. 6 shows a variant 27b of this friction device 27a, which differs essentially from it in the means of rotationally connecting the annular flange 57b with the annular spring 79b acting in the axial direction, as well as with the two friction rings. 71b and 73b. The elements providing the same functions are here designated by the same references as those of Figures 4 and 5, but with the letter "b" instead of the letter "a", and the

  descriptioh also refers to Figures 4 and 5. The

  friction device 27b comprises, in place of tabs 89, rivets 97 which, by their heads 99, are engaged in an opening 101 of the annular flange 57b and which rotate the friction discs 71b and 73b and the spring 79b, with the annular flange 57b. A bushing 103, disposed around each rivet 97 between the annular spring 79b and the friction disc 73b, maintains the desired spacing between these elements and provides sliding guidance of the friction disc.

71b, in the axial direction.

  Figure 7 shows a variant 27c of the previous

  friction device 27b, which differs from it

in that its friction discs 71c and 73c themselves have an elasticity in the axial direction and, by this spring effect, keep the annular flange 59c clamped between them, by means of the friction rings 75c and 77c. The annular spring 79b is here removed, and it is the friction disc 71c which

  is made integral with the friction disk 73c through

  intermediate rivets 97c and the spacer sleeve 103c.

  The rivet head 99c rotates the friction discs

  71c and 73c with the annular flange 57c. For a more complete explanation we can refer to the figures

  4 to 6 and the corresponding description, where the elements

  performing the same functions are designated by the benchmarks.

  The advantage of the friction device 27c is its size

  particularly reduced in the axial direction.

  Figures 8 and 9 show a device for

  27d for the vacuum operation, in which there is provided, on the side of the annular flange 59d farthest from the annular flange 57d, a friction disc rotatably mounted relative to the annular flange 59d,

  and applied against this annular flange 59d through

  The friction disc has, at its periphery, tabs 109 folded towards the annular flange 57d, which are introduced into openings 111 of the annular flange 59d formed by the cutting of the support lugs. 65d located closest to axis 5d. Between the two annular flanges 57d and 59d

  is formed, on the legs 109, a bend 113 which is directed

  ge 5d towards the axis and on which is supported the periphery of a spring 115 of annular shape, provided with ears 117 projecting radially. The spring 115 is supported by its part closest to the axis on the annular flange 59d, by means of a friction ring 119. The annular flange 59d is thus elastically prestressed between the spring 115 and the friction disc. 105. The free ends 121 of the

  tabs 119 are engaged in openings 123 of the flange.

  than annular 57d, to bind in rotation the friction disc 105, as well as the spring 115, with the annular flange 57d. The connection in rotation between the spring 115 and the friction disc 105 is provided by bent noses 125, formed on either side of the ears 117 and projecting in the axial direction. Between two consecutive lugs 117, the spring 115 has notches 127 which, during the assembly of the friction device 27d, first mount the spring angularly offset position on the legs 109, and then immobilize the prestressed state relative to the legs 108, by a rotation. It is understood that all the tabs 109 are not necessarily engaged, by their free ends, in openings of the flange

annular 57d.

  Another friction device 27e for the function

  unladen, consisting of parts in particular

  reduced, is shown in Figures 10 and 11.

  In this embodiment, two friction discs 131 and 133, forming springs, are arranged on each side.

  on the other hand, the outermost ring flange 59e

  in the axial direction), the portions of the disks 131 and 133 closest to the axis 5e elastically enclosing the annular flange 59e, with the interposition of friction rings 135 and 137. The friction disc 133 farthest from the flange annular 57e has, at its periphery, folded tabs 139 whose free ends 141 are introduced into openings 143 of the annular flange 57e, and which rotate the friction disc 133 and the annular flange 57e. The tabs 139 pass through openings 145 of the annular flange 59e, which result from the cutting of the bearing lugs 65e located closest to the axis 5e. Between the two annular flanges 57e and 59e, the lugs 139 comprise a bend 147 directed towards the axis, on which the periphery of the friction disc 131 forming a spring rests. The openings 145 are dimensioned such that the friction discs

  131 and 133 can rotate relative to the annular flange

  59e, at an angle corresponding at least to the play of rotation between the teeth of the inner and outer hub parts. To rotate the two

  friction discs 131 and 133, the legs 139 are engaged

  in recesses 149 formed at the periphery of the friction disc 131. In order to allow the two friction discs 131 and 132 to be mounted on each other, further recesses 151, which are offset relative to one another, are provided.

  to the recesses 149 and deeper than these, which allow

  bring the axial supply of the friction disk 131 to the tabs 139. Each recess 151 is connected to the recess 149 adjacent by a rising ramp 153, starting from one side of the recess 151, and ending at the edge la more external (radially) of the recess 149. The tabs 139 have a radial elasticity, and they undergo a deformation under the action of the ramps 153, during the rotation of the disk 131 relative to the disk 133, before coming clipping into the recesses 149. Figures 12 and 13 show another device

  27f for vacuum operation, structural

  very simple. The friction device 27f comprises, on either side of the outermost annular flange 59f, two friction discs 155 and 157, forming springs, which resiliently enclose the annular flange 59f, with the interposition of friction linings. 159 and 161. At the periphery of the two friction discs 155 and 157 protrude respective tabs 163 and 165, which are bent in the direction of the annular flange 57f, forming a relatively large arc which provides axial elasticity properties. . The corresponding legs 163 and 165 are introduced together into common openings 167 of the annular flange 57f and / or the side flange 33f, and thus provide the rotational connection between the friction discs 155 and 157 and the annular flange 57f. Each tab 165 attached to the

  friction disk 157 located the outermost tran-

  poured an opening 169 of the annular flange 59f, and

  present, at its free end introduced into the opening

  167, an elbow 171 facing the axis 5f, against

  which supports the free end of the corresponding tab 163

  ponding. To make the assembly, the silver discs

  prestressed structures 155 and 157 are rotated one

  port to the other, until the legs 163 and 165 rest on each other. Then, these tabs 163 and 165 are pushed into the openings 167, and the annular flange 59f is mounted on the inner hub portion lf. It is understood that all the tabs 163 and 165 are not necessarily engaged in the openings 167; some of these tabs can also be supported on each other outside the annular flange

57f.

  FIGS. 14 and 15 show a friction device 27g for the vacuum operation, comprising on both sides of the annular flange 59g two friction disks 173 and 175, which enclose the annular flange.

  59g with interposition of friction linings. The disc

  Friction 173, located between the annular flanges 57g and 59g, has folded tabs 177 on its inner edge, which pass through openings in the annular flange 59g and whose free ends have elbows 179 facing outwards. Between the elbows

  179 and the outermost friction disc 175

  (in the direction of the axis 5g) is compressed a spring washer 181 which generates the frictional force, axially oriented, of the friction device 27g. At the periphery of the friction disc 175 located most

  the outside protrude from the folded legs 183, which

  pouring openings 185 of the annular flange 59g and which are introduced into openings 187 of the annular flange 57g and / or the side flange 33g. The friction disk 173 is connected in rotation with the tabs 183, but it can slide axially with respect to these tabs, which themselves rigidly connect in rotation

  two friction discs 173 and 175 with the annular flange

  57g. The openings 185 are dimensioned such

  so that the friction discs 173 and 175 can

  relative to the annular flange 59g at an angle corresponding at least to the amount of rotation between the outer hub portion 13g and the inner hub portion lg. The mounting of the friction discs 173 and 175 is achieved by bending the elbows 179, after assembly of the components of the friction device 27g. Instead of bent parts, it is also possible to provide "bayonet-type" connections, in which the elements to be supported on one another are immobilized,

  relative to each other by a rotary motion.

  Figures 16 and 17 show a device for

  27h for the idling operation in which, unlike

  In accordance with the previously described embodiments, the friction torque is generated by forces acting

  in the radial direction. The friction device 27h com-

  takes a bearing sleeve 189 mounted coaxially with the axis of rotation 5h of the inner hub portion 1h, between the two annular flanges 57h and 59h. The bearing bush 189 is fixed to the outermost annular flange 59h by means of a plurality of tabs 191 spaced from each other in the circumferential direction. An expandable bushing 201 is attached to the innermost annular flange 57h, or to the hub outer portion 13h, an annular spring 203 acting on the expandable bushing 201 in a radial direction to press this expandable bushing 201 against the inner face of the bearing bush 189. The expandable sleeve 201 is split axially, and

  is fixed on the outer hub portion 13h by the

  intermediate a tab 207 diametrically opposed to its slot and held by means of one of the rivets 29h. The advantage of this friction device is that the friction torque is precisely defined by the existence of a constant friction radius, and that the friction torque increases with the rotation speed because the centrifugal force, so becomes stronger in the load operation, which reduces the

  jerks during load variations.

  Finally, FIG. 18 shows a variant 27i of the last friction device 27h for operation

  empty. This variant differs from the previous

  This is because the bearing bush 189i is connected to the innermost annular flange 57i, while the expandable bushing 201i is connected to the outermost annular flange 59i. . For a more complete explanation,

  will refer to the description made with reference to the figures

  16 and 17, the corresponding elements being designated by the same numerical references. The support bush 189i is

  here immobilized in rotation with respect to the annular flange

  57i by means of nose 211 which project directly

  axial direction and which are introduced into openings 209i of the annular flange 57i. The expandable sleeve 201i, connected in rotation with the annular flange 59i, comprises

  a stiffening collar 213, to which

  several tongues 215 of axial direction, introduced

  picks inside the bearing bush 189i. The res-

  203i fate, acting in the radial direction, exerts on the tongues 215 a thrust directed outwards, to push these tongues against the inner face of the bearing bush 189i, with the interposition of linings

friction 205i.

  The bearing sleeve and the expandable sleeve of the previously described friction devices may also be arranged outside (in the direction of the axis) of the two annular flanges. Alternatively, the bearing sleeve may also be placed inside the expandable sleeve, in which case the annular spring acting in the radial direction is disposed outside and exerts a thrust directed towards the center of the device; in the latter case, however, the friction torque decreases

  when the speed of rotation increases.

Claims (25)

  A clutch disc for a motor vehicle friction clutch, comprising: a) an inner hub portion (1) with external toothing (7) bounded on each side by annular shoulder members (9, 11), b ) an outer hub portion (13), surrounding   the inner hub portion (1) and having a tooth   internal re (15) engaged with the external toothing (7), which ensures a rotational connection between the outer hub portion (13) and the inner hub portion (1), while providing a predetermined set of rotation,   c) a drive disk (19) provided with   friction bearings (17) and rotatably mounted at a limited angle of rotation with respect to the hub outer portion (13); d) a torsional vibration damper (21) provided for load operation with two shock-absorbing portions (31,33; 37) rotating relative to one another and resiliently abutting each other via a plurality of springs (45); one of the damper portions (31,33) being connected to the outer hub portion (13) and the other damper portion (37) being connected to the drive disc (19), one of the parts of the damper damper comprising two lateral flanges (31,33) spaced from each other in the axial direction and   connected to each other, while the other part of amor-   weaver comprises an intermediate flange (37) disposed between the two lateral flanges (31,33) and supported on them by means of the springs (45), e) a torsion damping damper (25) provided for the idle operation, and arranged on the side of one of the farthest side flanges (31,33)   of the intermediate flange (37), with two parts of damping   (57,59) rotating relative to each other and   elastically leaning against one another through   a plurality of springs (67), one of the damper portions (57) being connected to the outer hub portion (13) and the other damper portion (59) being connected to the inner portion hub (1), characterized in that the two parts of the torsional oscillation damper (25) for the vacuum operation are formed as annular flanges (57, 59), which comprise in their peripheral region legs (63,65) folded one on the   others in the axial direction and now between them,   the circumferential direction, the springs (67) of this torsional oscillation damper (25) for the empty operation.   Clutch disc according to Claim 1, characterized in that the annular flange (59) farthest from the outer hub portion (13) is fixed   rigidly, by its inner edge, on the inte-   hub (1), and in that the annular flange (59) has at its periphery, between its legs (65), elongate bent portions (69) which guide the springs. (67) in the radial direction.   3. clutch disc according to claim 1 or 2, characterized in that one of the two annular flanges and more particularly the annular flange (59) furthest from the outer hub portion (13) comprises tabs (65). ) associated in pairs and shifted in a radial direction, and in that the lugs (63) of the other annular flange (57) take place, each   between the two offset legs of a pair of legs (65).   4. Clutch disc according to any one of   Claims 1 to 3, characterized in that the legs   (63,65) of the two annular flanges (57,59) located in   vis-a-vis, overlap in an axial direction.   5. Clutch disc according to any one of   Claims 1 to 4, characterized in that the damper   of torsional oscillations (21) for the operation in   load comprises a friction device (23)   born for this functioning in charge, and in that the amor-   torsion oscillator (25) for the operation   unladen arrangement comprises a friction device (27) of   sioned for this vacuum operation.   Clutch disc according to claim 5, characterized in that the friction device (27a to 27g) for the vacuum operation comprises two annular friction discs (71, b, c, 73, b, c; 105, 115; 131, 133, 157, 173, 175) disposed on either side of the annular flange (59a-g) farthest from the outer hub portion (13a-g), and elastically enclosing this annular flange (59a-g), which are rotatably mounted with respect to this annular flange (59a-g) and which are rigidly connected to each other, as well as to the other annular flange (57a-g), by means of connecting members ( 81.89; 97; 109; 139; 163; 165; 177.183).   Clutch disc according to Claim 6, characterized in that the connecting members (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) to each other in the region of their periphery, passing through openings (83; 111; 145; 169; 185) formed in the annular flange (59a-g); enclosed by these friction discs.   Clutch disc according to Claim 6 or 7, characterized in that on the side of one of the friction discs (71, b) furthest from the other friction disc (73) is provided. , b), an annular spring 79, b)   acting axially, in that the annular spring   (79, b) and the other friction disk (73, b) are rigidly connected to one another by spacers (81; 97,103) which pass through openings (83) in   the annular flange (59a), and in that the first disc   friction (71, b) is connected in rotation with the   toises (81; 87,103), but slidably mounted to these.   Clutch disc according to claim 6 or 7, characterized in that at least one of the two friction discs (71c, 73c) is designed as an annular spring acting in the axial direction, and in that both friction discs (71c, 73c) are rigidly connected to one another by spacers (97, 103) which pass through   openings in the annular flange (59c).   10. Clutch disc according to claim 8 or   9, characterized in that the spacers comprise, each   one, a spacer sleeve (103, c) and a rivet of   its (97, c) surrounded by the spacer sleeve and having its head (99, c) engaged in an opening (101) of the annular flange (57b, c) connected to the outer hub portion, for rotating the disks in rotation friction (71b, c;   73b, c) with this annular flange (57b, c).   Clutch disc according to Claim 6 or 7, characterized in that at least one of the two friction discs is designed as an annular spring acting in the axial direction (115; 131, 133; 155; 157). the friction disc (105; 133; 157) furthest from the internal toothing has folded tabs (109; 139; 165) which pass through openings (111; 145; 169) of the annular flange (59d-f); farthest   outer teeth and which are engaged in opening   tures (123; 143; 167) of the annular flange (57d-f) closest to the external toothing, for rotationally connecting the friction disc with said annular flange, and in that at least a portion of the flanges (109 139; 165) have a centrally directed bend (113; 147; 171) on which the friction disc (115; 131;   ) closest to the external toothing.   Clutch disc according to Claim 11, characterized in that the friction disc (115; 131) is supported by its periphery on the abovementioned bend (113; 147). Clutch disc according to Claim 12, characterized in that the friction disc (115) closest to the external toothing is provided at its periphery with radially protruding ears (117) and resting on the elbows (113).   Clutch disc according to Claim 13,   characterized in that are formed on the hard disk   (115) nearest to the external toothing, and on both sides of the ears (113), the projecting protrusions (125) which provide the connection in   rotation between the two friction discs (105, 115).   Clutch disc according to Claim 12, characterized in that the tabs (139) have a radially elasticity, in that the disc   friction (131) closest to the external toothing present   te, for each lug (139), two adjacent recesses (149, 151) of distinct depths, one of which (151) allows the axial supply of the friction disc (131) and the other (149) is provided for pressing on the aforesaid bend (147), and in that the two recesses (149, 151) of each pair are connected to each other by an upward ramp (153), which starts from the first recess (151) and leads to the other recess (149) and which, in a relative movement   of rotation, makes the tab (139) of the first recess   (151) to the other recess (149).   Clutch disk according to claim 11,   characterized in that the bend (171) is formed at the end   free of each leg (165) introduced into the opening   ture (167) of the annular flange (57f) and that the   friction disk (155) closest to the external teeth   dull (7f) has folded tabs (163), which are optionally inserted into the openings (167) of the   ring flange (57f) and are supported by their   placed on the elbows (171), to ensure the connection in rotation.   Clutch disc according to claim 6, characterized in that one of the two friction discs (173) has on its inner edge first folded tabs (177) which pass through the openings of the flange.   ring (59g) and the ends of which have   outwardly facing (179), in that a pinion (181) acting in the axis direction is compressed between these elbows (179) and the other friction disc (175), and that second folded tabs (183) protrude at the periphery of one of the two friction discs (175) and are introduced into apertures (187) of the annular flange (57g) closest to the external toothing. Clutch disc according to claim 17, characterized in that the second folded tabs (183) of the friction disc (175) furthest from the toothing.   external through openings (185) of the annular flange.   wire (59g) located between the two friction discs (173,), and in that the friction disk (173) closest to the external toothing is rotatably connected with the second tabs (183), with the possibility of sliding in the axial direction.   Clutch disc according to claim 17 or   18, characterized in that the first legs (177) belong to   stick to the friction disc (173) closest to the external toothing.   Clutch disc according to claim 5, characterized in that the friction device (27h, i) for the vacuum operation comprises a bearing sleeve (189, i) coaxially connected to one of the annular flanges ( 57h; 59i), an expandable sleeve (201, i) connected to the other annular flange (57i, 59h) and coaxial with the support sleeve (189, i), and spring means (203, i) exerting a radial action on the expanding sleeve   (201, i) to press it against the bearing bush (189li).   Clutch disc according to claim 20, characterized in that the bearing bush (189, i) surrounds the expandable sleeve (201, i).   Clutch disc according to Claim 20 or 21, characterized in that the spring means are in the form of an annular spring (203, i).   acting in a radial direction.   23. Clutch disc according to any one of   20 to 22, characterized in that the sleeve   support. 109, i) is arranged between the two flanges annular (57h, i, 59h, i).   24. Clutch disk according to any one of   Claims 20 to 23, characterized in that the socket   expansible (201) is slotted axially, and in that it comprises a fixing lug (207) which is diametrically opposite to her slit.   25. Clutch disc according to any one of   Claims 20 to 23, characterized in that the socket   expandable (201i) has a flange (213) and a plurality of   tongues (215) of axial direction, attached to the collar lerette (213).