FR2830587A1 - CLUTCH DISC AND CLUTCH HAVING SUCH A DISC - Google Patents

Abstract

Clutch disc and multi-disc clutch comprising at least one friction lining support (90, 92) and lining elements (40, 42; 70. 72) fixed to this support (90, 92). friction (40, 42; 70, 72) is connected to the support (90, 92) in a radial region not cooperating in friction.

Description

Technical area

  The present invention relates to a clutch disc no-

  especially for a multiple clutch device comprising at least one friction lining support and at least one lining element

  s of friction fixed on at least one friction lining support.

  For such clutch discs there are generally elements

  ring or segment-type friction lining elements fixed to at least one friction lining support. The fixing is generally done by rivets passing through the friction elements. At the level of the heads of

  o screws the friction lining elements have cavities or lama-

  ges so that the heads are in principle drowned and do not exceed the

  friction surface of friction lining elements.

  Especially when using multi-clutch devices

  In addition, the friction linings are highly stressed in friction and thus suffer relatively high wear. The friction wear of the linings in the case of the fasteners described above must however only occur at the level of the rivet heads because otherwise the rivets are applied in

  friction against the pressure plates and risk damaging them.

  The present invention aims to develop means o allowing to increase the authorized or possible wear of the linings of

friction in a simple way.

  To this end, the invention relates to a friction lining of the

  type defined above, characterized in that the fry filling element

  tion is connected to the friction lining support in a radial area which

s does not cooperate in friction.

  Thanks to the integral fixing of the packing elements of

  friction in an area in which these elements do not act

  tion, even if the friction lining elements are worn relatively strongly, the members used for fixing do not cooperate in friction with an opposite friction surface of another part such as for example

  the pressure plate. This allows further wear of the seals.

  friction res whose thickness remains otherwise unchanged and thus the

  usage time will be much longer.

  It is for example possible to provide that at least one element of the friction lining has a connecting part projecting from

  the radial zone acting in friction and this connecting projection allows the connection

  its with the friction lining holder. According to the embodiment of the invention, thanks to the simplicity of embodiment of the invention, at least one

  friction lining element is riveted to the carrier support

friction friction.

  According to an alternative embodiment, to fix a friction lining element on the friction lining support, there is provided at least one member forming a fixing clip and which protrudes from the element

  friction lining, in its radial zone outside the radial zone

  diale acting by friction to hold this element on the lining support

friction type.

  It can advantageously be provided that at least one organ

  o the clamp is made in one piece with the garment support

  friction friction. In the case of a very simple construction to produce in particular in sheet metal, the member constituting a clamp is formed, in

  bending radially projecting segments of material and app-

  starting at the friction lining support.

  s According to another variant, due to the smaller number of parts, there is a very advantageous embodiment according to which an integral fixing of a friction lining element is carried out on a friction lining support in that the friction lining element comprises a segment of material which at least passes through the support o friction lining port by cooperating therewith to hold the element

  friction lining to the friction lining holder.

  In addition, in addition to the connection possibilities described above

  above or in place of these connection possibilities, at least one is glued

  friction lining element to a friction lining support.

  s According to another advantageous development of the invention, in the case of clutch discs, the friction lining support carries at least one friction lining element in an external radial zone and is connected to a connecting member in a inner radial zone, and the friction lining support is elastically deformable at least in its radial zone between the friction lining element and the radial fixing inside the connecting member. This allows to integrate the function of a packing spring or elasticity to compensate for nutation movements or axis offsets in the disc.

clutch according to the invention.

  3s The present invention further relates to a clutch with

  friction having a clutch disc according to the invention.

  The invention also relates to a friction clutch, in particular a multiple clutch with at least one clutch disc having a friction lining device fixed to at least one friction lining support by the fixing members, and the disc of which clutch can be tightened at its friction lining device between a pressure plate device and a complementary support device, the pressure plate device or / and the device

  support comprising in the radial area of the fixing members, a

  vity realized in the peripheral direction.

  The consequence of such a cavity or counterbore is that, after wear by friction of the friction linings, the cracking members penetrate into this cavity and do not come to bear, for example, against the pressure plate device. It also allows you to continue

wear of friction linings.

  In such an embodiment, it is proposed to give the

  vity or counterbore a shape which preferably decreases along a conical path up to the bottom zone of the cavity so that with already extensive wear, when clutch operations are carried out, the plate

  pressure or the support device can easily separate from the

than clutch.

  Drawings o The present invention will be described below in more detail with the aid of embodiments shown in the attached drawings in which: - Figure 1 is a partial longitudinal section of a friction clutch according to invention; s - Figure 2 is a detail view of the friction clutch of Figure 1; - Figure 3 is an axial view of a clutch disc showing in the different dials, different connection configurations of the friction linings on a friction lining support; - Figure 4 is a detail view corresponding to a variant embodiment of the coupling of a friction lining on a friction lining support; - Figure 5 is a view corresponding to that of Figure 4 showing another variant of coupling a friction lining to a friction lining support; ss - Figure 6 is a detail view showing the attachment of a friction lining support to a connecting member; FIG. 7 shows a simple clutch with cavities in the friction faces; - figure 8 shows a double clutch with friction linings

  riveted outside the friction zones.

  Description of the embodiments

  Figure 1 shows a first embodiment of a

  s double clutch generally bearing the reference 10. The double clutch

  ble 10 comprises a casing formed of several parts and bearing overall-

  refer to 12. A disc-shaped part 14 which can be the flywheel, the secondary mass of a two-mass flywheel, a drive plate or the like, ensures the coupling in ro

  o tation of the double clutch 10 on the engine shaft for example the crankshaft

  quin of an internal combustion engine. A housing part 16 with a

  radially outer segment 17, extending essentially in the di-

  axial rection is connected by several screws 18 to the part 14 in the form of a dis-

  than. An annular segment 20, projecting radially, the housing part 16 forms a reaction zone for the two clutch zones 22, 24 of the double clutch 10 which will be described in more detail below. Another housing part 26 is integrally connected by its radially outer segment 28 and which also extends essentially in the radial direction, by means of several screws 30 to the housing part 16. A segment 32 of the housing part 16 , annular, directed radially inwards, constitutes a support or a rotation bearing

  for an actuating mechanism 34 via a bearing 36.

  The first clutch zone 22 of the double clutch 10 comprises a pressure plate 38 provided on an axial side of the zone

  s support 20 of the housing 12 or formed by it. Between this plateau of pres-

  sion 38 and the bearing or reaction zone 20 are the friction linings 40, 42 forming the friction surface device 44 of a clutch disc 46 of the first clutch zone 22. In its radial zone inside, the clutch disc 46 includes a hub 48 for the neck, integral with rotation on a first output shaft or input shaft

gearbox 51.

  In its outer radial zone, the pressure plate 38 has radial projections 50 at several points on its periphery; these radial projections pass through corresponding orifices in the part of tiered boxes 16, having peripheral play. These projecting parts 50 are connected by tie rods 52, integrally, by an actuating member 54 for example of annular shape. The actuating member 54 is biased by the intermediate radial zone 56 of an actuating force transmission element 58. This element bears in its external radial zone against the external side of the segment 32 of the part of housing 26 and is ground licit in its inner radial zone 60 by an actuation zone 62 of the actuation mechanism 34. The actuating force transmission element 58 in the example of embodiment of a clutch normally closed can be constituted for example by a diaphragm; however in the case of a normally open clutch in which the actuating mechanism does not generate a disengaging force but a clutch force it may, for example also include a device o with transmission lever with several lever elements spread across the

peripheral direction.

  The second clutch zone 24 comprises, on the other axial side of the reaction or support zone 20, a pressure plate 64. Between the pressure plate 64 and the support zone 20 is the device for friction surfaces 66 of a clutch disc 68 of the second zone 24 and its friction linings 70, 72. In its inner radial zone, the clutch dis 68 is connected in rotation by a hub 76 to a second gearbox input shaft 78, essentially concen

  to the first gearbox input shaft 51.

  An actuating force transmission element 80 of the second clutch zone 24, for example made as a diaphragm, bears radially in the middle against the housing part 26 and acts by its external radial zone, the pressure plate 64 Radially inside, the actuating force transmission element 80 is designed to be biased by an actuating zone 82 of the actuating mechanism 34. The actuating force transmitting element 80 may include an actuating lever device in the case of an em

normally open clutch.

  The coupling in rotation of the pressure plates 38, 64 on the housing device 42 can be done for example by tangential leaf springs which can have on the one hand coupling zones offset axially with the pressure plate 38, 64 to create an auto amplifier effect and which on the other hand may include the box device

tier 12.

  3s In the example of the double clutch 10 shown in FIG. 1, for the two clutch discs 46, 68 the friction linings 40, 42 or 70, 72 carried by the friction lining supports 90, 92 respectively by means of rivets 94, 96 are fixed to the lining support 90, 92 for example to connecting members 98, 100 in the form of an annular disc, by a riveting produced in an integral connection. It should be noted that the connecting members 98, 100 can also be torsional oscillation dampers in the shape of a star, rays or real

s s in another way.

  The nature of the coupling of the friction linings 40, 42 or 70, 72 with the friction lining supports 90, 92 is shown in FIG. 3 in the upper right dial. In this case, the friction lining support 90 is for example produced in the form of an annular segment which carries friction linings 40, 42 also in the form of an annular segment; it should be noted that the friction lining support 90 as well as the friction linings 40, 42 can be continuous in the peripheral direction. It can be seen that the fixing rivets 94 are located in the radial zone of the friction linings 40, 42 s which act by friction, by clamping between the pressure plate 38 and the reaction zone 20. The same remark also applies to the fastening elements 96 in the case of the clutch disc 74. So that, despite the wear of the various friction linings, it is possible to prevent the rivets or the fastening elements 94, 96 from coming to bear against the friction members corresponding, that is to say the pressure plates 38, 68 or the support zone, a cavity or countersink 102, 104, 106, 108 has been provided for these elements in the radial zone of the rivets or fixing elements. tion 94, 96, in a peripheral direction, in an annular position around the axis of rotation A. 2s These counterbores 102, 104, 106, 108 decrease in a conical shape towards the bottom. In the outer radial zone of these mages, the friction linings will not be worn by friction because they do not act by friction due to the existence of the countersinks 102, 104, 106, 108. This means that although radially outside and radial so inside inside in the fixing elements 94, 96, the friction linings 40, 42, 70, 72 are worn by friction, it is ensured that in this radial zone in which the rivets, there remains sufficient axial housing for these rivets to prevent contact between these elements and the pressure plates 38, 64 or s the support zone 20 after wear. Furthermore, the conical embodiment countersinks 102, 104, 106, 108 continues in the peripheral direction, facilitates the reciprocal separation of the parts comprising these countersinks and the clutch discs during clutch release operations. This conical shape generally going by decreasing counterbores 102, 104, 106, 108 further facilitates the separation of the surfaces applied against one another in friction during the declutching operation. For corresponding counterbores with mainly parallel walls, there is basically the risk that due to the inherent elasticity of the friction linings, these, especially at high rotational speeds, widen radially, slightly and in the measure o we form an annular spacer penetrating into the respective rib and which generates a certain hooking effect between the parts applied on one another and this hooking effect opposes the separation

0 or declutching.

  In the exemplary embodiment according to FIG. 1, the members serving for fixing to the friction linings on the friction lining support, that is to say the rivets 94, 9 6 are situated outside the zones of the friction linings which act by friction. For this, in the rivet area, we have the counterbores already mentioned so that there can be no friction contact between the friction linings and thus a setting

  _ works from the point of view of friction.

  FIG. 7 shows a clutch 10 ′ constituted here by a simple clutch and which by comparison with the example of FIG. 1 corresponds essentially to the clutch zone 24 appearing in the right part of FIG. 1. The housing part 26 is connected radially to the outside to a flywheel 11 intended to be coupled to a motor shaft. In the pressure plate 64 and in the flywheel 11, there are the countersinks 106, 108 already described with reference to FIG. 1; in this case, these counterbores are produced in the radial zone in which the friction linings 70, 72 are fixed to the support 92 by rivets 96. Thus in this clutch 10 ′ constituted by a simple clutch, the same

  advantages than in the previous example.

  The lower right dial of Figure 3 shows an alternative embodiment for fixing the friction linings 40, 42, 70, 72 on the respective support lining support 90, 92. It can be seen in this case that the friction lining support 92 of the clutch disc 46 shown here is segmented even more. It should also be noted that any peripheral extension of such a support for the friction lining 92 can be provided. The friction linings 40, 42 (the friction lining 40 is shown here) have in several peripheral positions, connecting projections 110, 112 located radially outside or inside the area in which the friction linings can cooperate in friction by coop eration with the pressure plates 38, 64 or the area d support or reaction 20. As also

  in these radial zones in which the elements of cash are provided

  tion 94, 96, the complementary friction members such as for example the pressure plates 38, 64 and the support zone 20 must not have

  friction surface, cavities or counterbore may be provided

  res, correspondents; when there is wear of the friction linings, these

  vities or countersinks allow the entry of unworn segments by friction of the

  friction linings 40, 42, 70, 72.

  o As further shown in Figure 3, the projecting connecting members 110, 112 may be provided both radially outside and radially inside; in the same peripheral zone it is possible to have a connecting projection directed both radially outwards and

radially inward.

  s The lower left dial in FIG. 3 shows, in combination with FIG. 4, another type of attachment of a friction lining; this is the friction lining 40 on a friction support 90. It can be seen in FIG. 4 that the friction lining support 40 obtained for example by stamping a sheet metal part, there are seg

  fixing clamp elements 114, 116 located radially on the outside and

  dialing inside. These segments cover the area of the friction lining 40 which is not active in friction, and is located radially inside or radially outside to hold this area integrally on the lining support 90. To have in this embodiment, friction garments 40, 42 on the two axial sides of the support 90 of the friction linings, it is possible to provide clamp clamp segments

  retainers 114, 116 which extend offset in the peri-direction

  spherical, each time on an axial side or the other.

  Another variant of fixing the friction linings on so a friction lining support appears in the upper part of the

  upper left dial according to figure 3 and according to figure 5. Here the gar-

  friction nitrides 40 located on the two axial sides of the holder

  friction lining 90 comprise protruding parts of material 118 which come to take in cavities or cutouts 120, complementary or associated, of the friction lining support 90 and create an axial coupling connection by form. We can provide for example a profile in

  undercut with dovetail section. Such cutouts of my-

  tiere may be provided offset in the periphery direction as for the friction linings 40, 42. An important advantage of this type of embodiment is that it does not have to provide any fasteners. The complete production of these segments of material 118 with the different friction linings can be done for example in that one

  applies friction linings 40, 42 in the form of roughly

  third against the friction lining support 90 to press them with it and cook them, for example by raising the temperature. During this operation, the friction linings 40, 42, 70, 72 take their final shape and at the same time the material segments 118 are created.

  o which provide the fixing effect by a form link.

  In the lower part of the upper left dial of Figure 3, in conjunction with Figure 6, there is another alternative embodiment

  fixing a friction lining 40, 42 on a lining support

  friction type 90 respective. It will be indicated that the two friction linings 40, 42 which deviate from one another in the axial direction, each have a separate lining support 90 and are connected to the connecting members 98 in the form of an annular disc. . The friction linings 40, 42 are joined integrally by bonding to the lining support 90. It is noted here that, as for the figures described above, the friction lining supports 90 carry the friction linings 40, 42 by fixing them in their radial outer and inner radial area to the connecting member 98. In particular in a sheet metal embodiment having a spring elasticity, an elasticity is thus introduced into the clutch disc which can perform both the role of a spring of packing and s also compensate for nutation movements in the event of axis offset or

  relative tilt of the axis. Different configurations are envisaged-

  ble. In connection with the friction lining 40 it can be seen that in the unsolicited state

  cited by a corresponding shaping of the friction lining support 90 or of the form already presented above, the different segments

  which appear in FIG. 3 of the friction lining 40 or the different

  rents segments or elements can be aligned conically. As a result, when the clutch is engaged, the mean friction radius is shifted outward more than in the case in which, as for the friction lining 42, appears in FIG. 6, which in the unsolicited state or

  3s disengaged has a planar orientation.

  We also notice in particular thanks to the segmenta-

  tion appearing in Figure 3 and which is advantageously provided, both for the friction linings for the friction lining support, that one can achieve a free deformability very advanced without creating

  of constraint element inside the friction linings themselves.

  It is further noted that the embodiments described above can be used in the two clutch zones 22, 24 of the double clutch 10 shown in FIG. 1 and the cavities appearing in FIG. 1, which are provided. noticeably ra

  dialing in the middle of the friction linings is no longer necessary.

  With reference to the embodiment shown in FIG. 4, it is noted that in the case of separate friction linings, for each friction lining, the clamping pliers segments 114, 116 can be produced in the peripheral direction under the form of more or less closed and continuous edge zones. In addition, the clamping clip segments can be made as separate parts. In the embodiment according to FIG. 5, for the different friction linings of each clutch disc, separate friction lining supports can be provided, which gives a corresponding mounting sen

just as in Figure 6.

  Figure 8 shows a double clutch 10 which corresponds essentially to its construction to that of Figure 1. Unlike the embodiment of Figure 1, the friction linings 40, 42 of the clutch dis 46, the friction linings 70, 72 of the clutch disc are connected to the friction lining supports 90, 92 respectively associated, outside the zones connected by the rivets 94, 96 and acting by friction. Under these conditions there are no counterbores appearing in Figure 1 in the pressure plates or in segment 20

located in the meantime.

  The embodiments according to the invention make it possible, even in the event of heavy wear of the friction linings, to avoid a reciprocal contact of the members participating in the fixing of the friction linings to a friction lining support and of the friction op

  laid, that is to say for example a pressure plate.

3s

Claims (7)

  1) Clutch disc in particular for a multi-clutch device   ple comprising at least one friction lining support (90, 92) and at least one friction lining element (40, 42; 70, 72) fixed on at least one friction lining support (90, 92), characterized in that the friction lining element (40, 42; 70, 72) is connected to the friction lining support (90, 92) in a radial region which does not cooperate in friction. 2) Clutch disc according to claim 1, characterized in that the friction lining element (40, 42; 70, 72) comprises at least one connecting projection (110, 120) which protrudes from the radial zone acting in cash   tion, and which connects the element to the friction lining support (90, 92).   3) Clutch disc according to claim 1, characterized in that the friction lining element (40, 42; 70, 72) is connected to the support of   o friction lining (90, 92) by riveting.   4) Clutch disc according to claim 1, characterized by at least one member forming a fixing clamp (114, 116) which protrudes at: 5 at least one friction lining element (40, 42; 70, 72) in its zone outer radial beyond the radial area acting by friction to fix the friction lining element against the friction lining support friction (90, 92).   o 5) clutch disc according to claim 4, characterized in that at least one member forming a fixing clamp (114, 116) is produced in a   one piece with the friction lining holder (90, 92).   6) Clutch disc according to claim 5, characterized in that at least one member forming a fixing clip (114, 116) is obtained by folding the segment of material from the friction lining support (90, 92) radially projecting.   s 7) clutch disc according to claim 1, characterized in that the friction lining element (40, 42; 70, 72) comprises a segment of material (118) passing through at least by area the lining support friction (90, 92), and cooperating therewith by a connection by the form o to hold the friction lining element (40, 42; 70, 72) on the support friction lining (90, 92).   8) A clutch disc according to claim 1, characterized in that s the friction lining element (40, 42; 70, 72) is glued to the support of friction lining (90, 92).   9) Clutch disc according to claim 1, characterized in that o the friction lining support (90, 92) carries at least one friction lining element (40, 42; 70, 72) in an outer radial zone and is connected to a connecting member (98, 100) in an inner radial zone, and the friction lining support (90, 92) is elastically deformable: s at least in its radial zone between the friction lining element (40,   42; 70, 72) and the internal radial attachment to the connecting member (90, 92).    ) Friction clutch, in particular a multiple clutch comprising at least one clutch disc (46, 68) with a friction lining device (40, 42; 70, 72) fixed to at least one friction lining support (90, 92) by fasteners (94), the clutch disc (46, 68) being able to be tightened at the level of its friction lining device (40, 42; 70, 72) between a pressure plate device (38, 64) and a support device (20), 3s characterized in that the pressure plate device (38, 64) and / or the support (20) comprises in the radial zone fixing members ( 94), a cavity (102, 104, 106, 108), peripheral.   11) Friction clutch, in particular multiple clutch, according to claim 10, characterized in that the cavity (102, 104, 106, 108) preferably has a narrowing