FR2505426A1 - CLUTCH DEVICE - Google Patents

Abstract

IN A CLUTCH DEVICE INCLUDING A FLYWHEEL 5, A THRUST PLATE 2 AND A CLUTCH DISC 12, 6, A SPRING DIAPHRAGM 1 IS, IN THE AXIAL DIRECTION, ARRANGED BETWEEN THE PLATE AND A PART 3A CARRYING A PIVOT 3B OF THE CLUTCH HOUSING 3 IN A WAY TO AXIALLY TIGHTEN THE PLATE AGAINST THE DISC AND IT AGAINST THE FLYWHEEL. THE SPRING DIAPHRAGM MAY TIP ON THE PIVOT CARRIED BY THE HOUSING. MEANS 7 ARE PROVIDED TO STRATEGY THE PLATE IN DIRECTION OF THE SPRING DIAPHRAGM. PIVOT 3B IS IN CONTACT ONLY WITH THE FACE OF THE PIVOT, WHICH IS FACING THE OPPOSITE OF THE PLATE. THE RESPECTIVE CHARACTERISTICS OF THE SPRING DIAPHRAGM AND THE MEANS THAT STRESS THE PLATE ARE SUCH THAT THE SPRING DIAPHRAGM IS KEPT IN CONTACT WITH THE PIVOT WHEN IT TILTS INTO THE RELEASE POSITION.

Description

The present invention relates to a device for em-

  clutch which comprises a flywheel having an axis and a

  contact face, a fixed casing relative to the flywheel

  tor, a part of which, which carries a pivot, is located axially-

  opposite the said contact face and at a certain distance from it, a thrust plate situated, in the axial direction, between the flywheel and the part of the casing

  pivot bearing, axially movable relative to the

  lant and said part of the housing, integral in rotation with the flywheel and provided with a contact face turned towards that of the latter, a set of clutch discs for transmitting the torque of the flywheel

  to the movement output member of the clutch device

  ge or vice versa, comprising a clutch disc, the two opposite faces of which, turned in the direction of the axis, respectively come into engagement with the contact face

  of the flywheel and that of the thrust plate, a di

  spring-cage located axially between the push plate

  and the part of the housing which carries the pivot, the radially outer part of which is in contact with the plate

  thrust, the radially intermediate portion of which is

  ted by means of pivoting on the par-

  tie of the pivot-bearing casing, the said means extending in the form of a circle around the axis of the clutch device, and the radially inner part of which is movable parallel to the aforementioned axis, from a clutch position to a declutching position closer to the flywheel,

  the elastic force of the spring diaphragm opposing the

  axial placement of the radially inner part of the

  clutch position to the clutch position, the di-

  spring-cage tilting on the pivoting means during the axial movement of the radially inner part

  and the radially outer part moving axially-

  ment in response to the axial displacement of the radial part-

  inner ment, parallel to the aforementioned axis, of a posi-

  clutch, in which the thrust plate is

  biased towards the flywheel, in a disengaged position

  ge, more distant from this steering wheel, and from the biasing means

  supported by the flywheel, the housing or a

  linked to one or the other, which tend to apply

  the thrust plate against the radially outer part

  the diaphragm-spring. A clutch device of this type is known from

  the description given in the patent application

  in R F A DE-OS 27 58 733 In this device, it is pre-

  seen from tangential leaf springs which connect the plate

  thrust on the flywheel-and on the crankcase to make it so-

  lidaire in rotation thereof These tangent leaf springs

  they exert an axial oriented biasing force

  lying on the thrust plate so as to maintain the latter

  deny in contact with the radially outer part of the diaphragm spring The thrust plate therefore accompanies

  constantly the radially outer part of the diaphragm-

  spring in its axial movement The pivoting means

  provided on the part of the housing which forms a pivot are

  formed so as to be in contact with both sides of the

  diaphragm-spring which are rotated in the axial direction.

  These pivoting means are therefore of a relative design.

  highly complex and they include not only a nervu-

  re circular on the part of the casing forming a pivot, ribbed

  re which is in contact with the face of the spring diaphragm remote from the thrust plate but also a plurality of retaining members connected to the part of the casing forming a pivot, which pass through the spring diaphragm and come into contact with the face of this last turn towards the plateau

thrust.

  The main object of the invention is to realize

  a clutch device of the same type, but of a design

  simpler and lower manufacturing cost.

  It also aims to provide an em-

  clutch with greater operational safety.

  To this end, in the clutch device according to the invention, the pivoting means are shaped

  so as to be in contact only with the face of the dia-

  spring sentence which is far from the thrust plate

  in addition, the respective characteristics of the diaphragm-res-

  fate and means which act on the thrust plate

  towards the latter are such that the radially in-

  spring diaphragm is kept in contact

  with the pivoting means when its radial part-

  Inner position is in the disengaged position.

  lesson, the pivoting means are much less complicated

  It must be borne in mind that in the clutch system 4

  ge known of this type, the positioning of the diaphragm-res-

  goes out between the opposite pivoting members is an operation

  very careful ration, all the more so as to avoid any idle stroke of the spring diaphragm between the means

  opposite swivel The diaphragm must also

  spring be supported between them to avoid any

  wear and tear over the life of the clutch and

  thus provide great operational safety.

  Various embodiments of pivoting means are

  known by the description which is made for example

  in German patent 17 75 116 and in the applications for

  patent in FRG DE-AS 20 29 334 and DE-AS 21 32 730.

  In a more elaborate embodiment of the invention

  tion, the respective characteristics of the diaphragm-res-

  fate and means which act on the thrust plate

  are such that the spring diaphragm is held in con-

  tact with the pivoting means during part of the axial stroke of the radially inner part of the latter adjacent to the declutching position of said part Preferably, the spring diaphragm is kept in contact with the pivoting means throughout axial travel of its radially inner part, between the clutch position and the declutching position of

this part.

  In any case, the invention will be well understood from 1 '

  using the following description, with reference to the drawing

  schematic annexed, representing, by way of nonlimiting examples, several embodiments of this device: Fig 1 is an axial sectional view of a known clutch device, of the type described in German patent NI 27 58,733, in the engaged state;

  Fig 2 is a view similar to that of fig 1, re-

  having the same clutch device in the disengaged state; Fig 3 is an axial sectional view of the clutch device according to the invention, in the engaged state;

  Fig 4 is a view similar to that of fig 3, re-

  having the same clutch device in the disengaged state;

  Fig 5 is a more detailed sectional view of the dis-

  positive clutch according to the invention, representing a first embodiment of the biasing means of the thrust plate;

  Fig 6 is a side view and partially in section

  pe, along arrow A of fig 5; Fig 7 is a view similar to that of fig 5,

  but representing a second embodiment of the means

  stressing plate for the thrust plate; Fig 8 is a side view similar to that of fig 6, but showing the device according to the invention

  with a third embodiment of the biasing means

  tation of the thrust plate; Fig 9 is a side view similar to that of fig 6, but showing the device according to the invention

  with a fourth embodiment of the biasing means

tation of the thrust plate;

  Fig 10 is a graph showing the force é-

  elastic P of the spring which opposes the axial displacement of the radially inner part of the spring diaphragm and

  the force F of the biasing plate biasing means

  based on the axial position of the radiating part

  the outer diaphragm spring.

  Figures 1 and 2 each represent half

  top view of an axial section of an em-

  diaphragm spring clutch of known type In the figure

  1, the clutch device is shown in the em-

  brayé The casing l is rigidly linked to a motor disc or flywheel 5 and surrounds the clutch disc 12

  fitted with seals 6, the thrust plate 2 and the dia-

  spring diaphragm 1 The clutch disc 12 is integral in rotation with the output shaft 13 The flywheel 5 is, in turn, integral in rotation with the input shaft or crankshaft 14 The spring diaphragm 1 is under initial tension, so it tends to become more

  conical that in the disassembled state of the device The ra-

  external dialing of the diaphragm-spring is supported

  against the plate 2 along a circumference of diameter

  tre D The radially intermediate part of this same diameter

  spring diaphragm rests on a circular rib 3 b of the casing 3 along a circumference of diameter d It follows that two opposite forces A and B act on the diaphragm spring 1, forces which are of equal size,

but in opposite directions.

  In addition, return springs 7, which constitute the biasing means of the plate, are distributed over the periphery of the clutch device; these springs are hooked by one of their ends to the flywheel 5 and, by their other end, to the plate 2 and they exert

  on the latter a force F The plate 2 is subjected in or

  be at a force C, which represents the clamping force of the friction linings 6 between the flywheel 5 and the thrust plate 2 The spring diaphragm 1 also has elastic tongues 4, which extend inwards in the radial direction and define a radially inner part of the spring diaphragm A declutching mechanism R acts on these tongues 4 In the engaged state shown in FIG. 1, the mechanism R exerts no force on the tongues 4 To better understand how it works such a device, here is the order of magnitude

  forces that come into play: we will attribute to the two

  these A and B a size of 3800 N, the springs 7 taken

  seems to have a total force of 300 N and the force C of ser-

  rage is 3500 No Thus, the two support forces A and B

  are of opposite directions and of equal size; the strength of

  rage applied between the plate 2 and the flywheel v is equal to the force between the diaphragm-spring 1 and the plate (3800 N) minus the force E (300 N) of the return springs 7, this force C is therefore equal to 3500 N. The clutch device which has just been described is shown in the disengaged state in FIG. 2 In this figure, it can be seen that the clutch disc 12 and its linings 6 are no longer in contact with the plate 2 and the flywheel 5 The declutching mechanism R exerts a force

  P on the radially inner ends of the tongues-

  tes 4 of the diaphragm-spring 1 This force P will be assigned a magnitude of 1250 N While the force P is established, the internal torque of the diaphragm-spring 1 decreases, at the same time the abutment force between the latter and the casing 2 in the zone of diameter d is reduced and, from the balance of the torques, the diaphragm-spring 1 changes point of support and it now takes support against the side

  opposite of a wire ring 26 supported by rivets 27.

  The support force B now acts in the opposite direction to that in which it was exerted in FIG. 1 and, in the example described here, it has a magnitude of 950 N The support force A retains the same direction , but it only has a magnitude equal to that of the force of the return springs 7, i.e. 300 N A balance of forces occurs

  therefore also in the disengaged state, the two forces A and B act

  on the same side on the spring diaphragm 1 and being

  seems of a magnitude equal to that of the declutching force

  ge P, which acts on the opposite side So, in this cons-

  known truction of diaphragms-springs, it is necessary that these are supported on both sides in the

  circular pivot zone on the casing 3, diameter zone

  meter d Not only does this double support require a name-

  considerable bre of individual pieces, location

  for these parts in the housing and in the diaphragm-res-

  fate and high costs for their assembly, but there is also a problem of wear of the spring diaphragm in its

  pivoting area, wear which results in a run-

  empty, to be deducted from the declutching stroke.

  FIGS. 3 and 4 illustrate the principle construction of the diaphragm-spring clutch device according to the invention It will be assumed that the conditions are the same as in the device described with reference to

  Figures 1 and 2, i.e. the dimensions are felt

  similarly identical and it is necessary to provide the same force for applying pressure to the linings of the clutch disc. We immediately realize that the diaphragm-spring 1 only bears against the casing 3; no other support element of any kind is provided in the diameter area

  d on the opposite side of the spring diaphragm In the em-

  disconnected from the device, the spring diaphragm 1 is supported

  tre the thrust plate 2 along a circumference of diameter D and on the casing 3 along a circumference

  in diameter d The forces A and B, which act on the dia-

  spring sentences 1 are here also of opposite directions and of equal size, but they are larger than in the known device about 5000 N The total force F of the return springs 7 is also-significantly greater; she

  in this case is 1500 N As this force F is

  from the force of application of pressure C, the latter is equal to 3500 N, the difference between the

  force A and force F This force is therefore the same

  deur that in the known device In the disengaged state, the declutching force Pl of a magnitude of 1250 N, provided by the declutching mechanism (not shown), acts here

  also on the inner end of each elastic tab-

  tick 4 Under the effect of this force P the diaphragm-

  spring 1 rocking on the casing i along a circumference

  diameter d, so that the disc 12 and its gar-

  friction nitrides 6 are released, since the internal torque of the diaphragm-spring has decreased and

  the plate is kept constantly applied against it

  ci by the force F of the return springs 7 The force A ex-

  drilled by the plate 2 on the diaphragm-spring lcorres-

  pond to the force F of the return springs 7, at the level of 1500 N It results from the difference between the force A and the release force P a stop force B of a level of

  250 N, with which the diaphragm spring 1, in the de-

  locked, constantly leans on the housing 32 We can thus remove, without replacing them, all the support means on the left side of the diaphragm-spring We are assured

  that in all states of the device during its operation

  tition, the diaphragm spring, under the effect of the forces which act on it, presses against the casing 3 In this regard, it should be noted that in the known construction, the lever arm a (fig 2) is a decisive factor for the internal torque of the diaphragm-spring to be

  defeated by the declutching force P while in the dis-

  positive according to the invention, it is the lever arm b (fig. 4) which is the decisive factor, which, because of its greater length, makes it possible to bring the device to I '

  disengaged state with the same force P even with the diaphragm

  reinforced spring, force P being able to overcome the couple

  interior of the latter The relations of the race of

  clutch remain the same in Figures 3 and 4 as in fig-

  res 1 and 2, since in both cases the diaphragm

  me-spring 1 rocker on a circumference of diameter d.

  The fact that during the declutching operation, under all operating conditions, the force A exerted by the plate on the diaphragm spring is, due to the greater force of the springs 7, greater than the declutching force P guarantees that the diaphragm-spring 1 rests freely on the casing l along a circumference of

  diameter d Contrary to what happens in the dispo-

  known sitive, so it is possible, by increasing the strength

  F of springs Z from 300 N to 1500 N, approximately, and increasing

  as the initial tension of the diaphragm-spring 1 of approximately

  %, from 3800 N to 5000 N, approximately, to guarantee u-

  side of the spring diaphragm on the clutch housing

  2 even during declutching and therefore to remove the ri-

  vets 27 and ring 26, without replacing them with equiva-

  slow. In the embodiment shown in Figures 5

  and 6, the return springs 8 have the form of springs-

  approximately tangential blades, which, on the one hand, are fixed to noses 16 of the thrust plate 2 and, on the other hand

  hand, rest elastically against the flywheel 5.

  These return springs 8 provide all the force F with the order of magnitude indicated with reference to FIGS. 3 and 4 The joining in rotation of the plate 2 and the casing

  j is, in this case, provided by the noses 16, which, sail-

  radially outward, penetrate into or-

  corresponding grooves 18 of the casing 3 and are guided

in these openings.

  The embodiment shown in Figure 7 is

  similar to the previous two, but in this case the

  recall spells 9 are in the form of coil springs

  working in compression Here too, these springs are

  draws, on the one hand, on the flywheel 5 and, on the other, on noses 16 of the thrust plate 2, noses which penetrate into openings 18 of the casing 3 It goes without saying that it is also possible to '' securing in rotation the plate and the housing using other elements, for example by means of traditional radial or tangential leaf springs, well known to the specialist in this sector

technical.

  Figure 8 shows a clutch system

  spring sentence seen in the direction of arrow A in the figure This view partially shows the casing 3 and the plate

  sheet 2 They are secured in rotation by means of

  11 tangential leaf springs 11 distributed on the peri

  These springs 11 are, in this case, lo-

  located in a recessed part 15 of the wall of the casing 3 and they are fixed by rivets, on the one hand, to the casing 3 and, on the other hand, to the noses 17 of the plate 2, noses which extend radially in the recessed parts 15 The rivets 20, which serve to fix the leaf springs II on the noses 17 are extended, their extension extending opposite the flywheel (not shown), penetrating through an opening 22 in the recessed part 15 of the

  casing 3 and being provided with a head 19, so that a res-

  return spell 10 in the form of an elastic washer can be interposed between this head 19 of each rivet and a flange

  defined by the recessed part 1 These return springs

  pel 10 provide the force F with the order of magnitude of which it is spoken with reference to Figures 3 and 4 This

  force P can also be supplied in part by the springs-

  tangential blades 11 This embodiment is interesting

  health by the simplicity of the assembly and the possibility of modifying the desired elastic force by using various

  return springs 10 or by changing their number.

  Figure 9 shows an arrangement similar to that

  which has just been described with reference to FIG. 8 The so-

  the rotation of the plate 2 and the casing 3 is ensured by tangential leaf springs 11, which connect the said casing to the noses 17 of the plate Hollow rivets 21 are fixed to the noses 17 They each have an extension which extends towards the flywheel They pass through suitable openings 24 in flanges 25 of the casing, so that frustoconical elastic washers, which

  constitute the return springs 10 and are arranged in-

  be the tangential leaf springs 11 and the flanges M may

  wind produce the force F with the order of magnitude of which it is spoken with reference to Figures 3 and 4 Here too, the force F can be provided by the return springs 10

  alone, or in part by these return springs and in part

  tied by tangential leaf springs 11.

  It is obviously possible, in principle, to pass-

  use additional springs and comply with the

  tangential blade spells so that they provide to them

  only the relatively high force F It is then necessary to use

use multi-leaf springs.

  Figure 10 shows graphically the value of

  riation of forces F and P as a function of the axial displacement of the thrust plate The curve illustrating the variation there

  of the declutching force P corresponds to that of the diaphragms

  mes-springs or tapered elastic washers of the current type In this graph, x represents the distance between the plate 2 and the flywheel 5, x 1 represents the magnitude of this distance when the device is in the engaged state (fig 3) and that the linings 6, new, have their entire thickness x 2 represents the magnitude of this distance when the device is in the engaged state and that

  the linings 6 have reached, through wear, the minimum thickness

  admissible male, and x represents the size of this dis-

  when the device is in the disengaged state It remains

  emerges from FIG. 10 only when the thickness of the linings

  res decreases, the release force P increases, which

  can consider as a favorable aspect of the device.

  It can also be noted in Figure 10 that the force F of the res-

  recall spells 7 is always greater than the strength of

  declutching P, the difference being substantially constant between-

  tre x 2 and M, so that the spring diaphragm is securely held in contact with the housing without wear

excessive.

  In FIG. 3, 5 a designates the contact face of the

  the engine, 2 a denotes a contact face of the thrust plate, 6 a denotes a first contact face of the clutch disc and 6 b denotes a second contact face of this disc 3 a denotes a pivot bearing part of the casing 2 , while 3 b denotes a circular rib which acts as a pivot In FIG. 3, the return spring 7

  defines the means which act on the thrust plate.

  The declutching force P in FIG. 4 corresponds to the forces

  elastic which oppose the axial displacement of the tongues-

  tes 4 from the position shown in Figure 3 to that re-

produced in Figure 4.

  As is obvious and as is clear from what

  the invention is not limited to the forms of execution

  tion which have just been described by way of example only.

  lement; on the contrary, it embraces all the varian-

* your achievement.

Claims (23)

CLAIMS -   1. Clutch device, which comprises   (a) a flywheel (5) having an axis and a contact face   tact, (b) a casing (3) fixed relative to the flywheel (5), a part (3 a) of which carries a pivot, is situated axially opposite said contact face (5 a) and has a certain distance from it, (c) a thrust plate (2) located, in the axial direction, between the flywheel (5) and the part (3 a) of the housing which carries the pivot, axially displaceable relative to the   flywheel and to said part of the housing, integral in   tation of the flywheel and provided with a contact face (2a) facing that (5a) of the latter,   (d) a clutch disc assembly, comprising a dis-   that the clutch (12), the two opposite faces (6a, 6b) of which are turned in the direction of the axis, respectively engage with the contact face (5a) of the flywheel and that (2 a) of the thrust plate, (e) a spring diaphragm (1) located axially between the thrust plate (2) and the part (3 a) of the casing which carries the pivot, of which the radially outer part (D)   is in contact with the thrust plate, the part of which   radially intermediate tie (d) is mounted by the   intermediate pivot means (3 b) on the part which carries the pivot, the said means extending in the form of a circle around the axis of the clutch device,   and whose radially inner part (4) is displaced   cable parallel to the aforementioned axis, from a clutch position to a declutch position closer to the   motor tack, the elastic force of the diaphragm-res-   fate opposing the axial displacement of the ra-   internal dialing from the clutch position to the disengaging position, the diaphragm-spring (1) rocking on the pivoting means (3 b) during the axial movement of said radially internal part (4) and   the radially outer part moving axially-   ment in response to the axial displacement of the ra-   internal alignment, parallel to the aforementioned axis,   a clutch position (x 1), in which the plate   thrust plate (2) is biased towards the flywheel   tor (5), in a disengaged position (x 3), further from this flywheel, and   (f) biasing means (7) supported by the   the motor (5) and the casing (3) and which tend to   bend the thrust plate (3) against the radially outer part (D) of the spring diaphragm, characterized in that the pivoting means (3b) are shaped so as to be in contact only with the   face of the spring diaphragm (1) which faces towards the   installed on the thrust plate (2), and in that the characteristics   respective dimensions of the spring diaphragm (1) and the means   ens (7) which urge the thrust plate are such that the diaphragm-spring is kept in contact with the   pivoting means when its radially integrated part   lower (4) is in the disengaged position.   2 Device according to claim 1, character-   risé in that the diaphragm-spring (1) is kept in contact with the pivoting means (3 b) during a   part of the axial travel of its radially inner part   lower (4) adjacent to the declutching position of said part (4)   3. Device according to claim 1, character-   rised in that the radially inner part (4) of the spring diaphragm (1) is kept in contact with the pivoting means (3b) throughout its axial travel, between the clutch position and the disengage position of this part.   4. Device according to claim 1, character-   laughed at in that the force (F) of the means (7) which urge   the thrust plate (2) is greater than the elastic force   axially oriented tick (P) when the radial part-,   inner diaphragm (4) of the spring diaphragm (1) is in position declutching position.   5. Device according to claim 1, character-   laughed in that the force (F) of the means (7) which urge the thrust plate is greater than the elastic force   (P) oriented axially when the radially in-   posterior (4) is in any axial position in part of its axial travel adjacent to its declutching position.   6. Device according to claim 1, character-   laughed at in that the force (F) of the means (7) which urge   the thrust plate (2) is greater than the elastic force   that (P) oriented axially when the radially inner part (4) of the spring diaphragm (1) is in any axial position along its total travel   between its declutching position and its clutch position.   7 Device according to claim 1, character-   laughed in that the axially oriented elastic force (P)   varies along the travel of the radially outer part   upper (D) of the spring diaphragm (1) between its clutch position and its disengaging stroke and in that the force (F) of the elastic means (F) which urge the thrust plate (2) varies along the party run   radially outer (D) of the spring diaphragm (1) in-   be its clutch position and its declutch position,   the strength of the biasing means being always greater than   superior to the axially oriented elastic force.   8. Device according to claim 7, character-   laughed at in that the axial distance separating one from the other   be the contact faces (6 a, 6 b) of the clutch disc   varies during the lifetime of the latter between a   their maximum when the disc is in new condition and a minimum admissible value, when the disc is worn, in   what this axial distance determines the positions of em-   respective clutch (x 1, x 2) of the radially ex-   (D) and the radially inner part (4) of the diaphragm spring (1), in that the characteristics of the latter and of the means (7) which act on the thrust plate (2) are such that the difference between the force (F) of these means, on the one hand, and the elastic force (P), on the other hand, is substantially constant along the respective strokes of the radially inner part (4) and the radially outer part (D) between their respective clutch positions, corresponding to the minimum admissible value of the distance between the contact faces   disc, and their respective clutch release positions.   9. Device according to claim 1, character-   risé in that the thrust plate (2) is connected to one or the other of the flywheel (5) and of the casing (3) by leaf springs (11) which allow an axial displacement of the   said plate relative to the steering wheel (5), the ground means   license of the platform being constituted, at least in part, by the leaf springs (11).   10 Device according to claim 1, character-   laughed in that the means (7) which stress the plate   thrust (2) are means apart from those which solida-   riser in rotation said plate (2) and the flywheel (5).   11 Device according to claim 1, character-   laughed in that the push plate is provided with noses (16) which project radially outwards and extend through recesses (18) in the housing (3), the means (81 which urge the push plate being supported, on the one hand, by the said noses and, on the other, by one or 1 '   other from the crankcase and flywheel.   12. Device according to claim 11, character-   laughed in that the thrust plate (2) is connected to the   the motor (5) by the noses (16) which engage in the   recesses (18) and secure it in rotation to said vo- lant.   13. Device according to claim 11, character-   laughed in that the means (8) which urge the plate   thrust include helical compression springs axially oriented cold tubes.   14. Device according to claim 11, character-   laughed in that the means which urge the thrust plate comprise leaf springs (8) substantially in arc shape.   15. Device according to claim 14, character-   risé in that the leaf springs (8) in the shape of an arc of a circle are connected to the noses (16) by the top of the arc and   are in contact with the flywheel (5) by their ends moths.   16 Device according to claim 11, character-   in that the casing (3) is provided with flange parts (15) substantially perpendicular to the axis of the flywheel   motor and in that the means (10) which urge the plate   thrust plate (2) are supported on the one hand, by the   nose (17) and, on the other, by said parts forming bri- from (15).   17 Device according to claim 16, character-   laughed in that the means which urge the thrust plate (2) comprise ankle elements (20)   attached to a respective nose (17) and which pass through an opening   frame (22) in a respective flange portion (15),   as well as solicitation means working in combination   pressure (10), which surround the ankle element (20) respective.   18. Device according to claim 17, character-   in that the nose (17) is closer to the flywheel (5) than the flange part (15), in that a spring support head (19) is provided on the dowel element ( 20) at its end remote from the nose (17), and   what the solicitation means working in compression   sion (10) are, in the axial direction, located between the head   (19) spring support and the flange portion (15).   19. Device according to claim 17, character-   laughed in that the nose (17) is further from the flywheel   tor (5) that the flange part (15) and in that the biasing means working in compression (10) are, in the axial direction, located between the part forming flange (15) and nose (17).   20. Device according to claim 17, character-   laughed at in that the dowel elements are ri- hollow vets (21).   21. Device according to claim 20, character-   risé in that the hollow rivets comprise a part which extends radially outwards and in that one end of the means of compression stress (10) is supported by this party.   22. Device according to claim 17, character-   in that the biasing means working in compression (10) each comprise at least one pair of frustoconical elastic washers.   23. Device according to claim 1, character-   in that the spring diaphragm (1) and the means which act on the thrust plate (2) are subjected to a   initial tension in the respective clutch positions   of the radially inner part (4) and of the part   radially outer tie (D) of the spring diaphragm.