FR2613446A1 - Torsion damping device with a movement-transmitting member - Google Patents

Abstract

Torsion damping device provided with an interposed member including two movable cheeks 138, 140. In accordance with the present invention, the two movable cheeks 138, 140 are connected to one another by at least transmission member 239 pivoting with respect to them so that a radial displacement of one of the movable cheeks 138, 140 gives rise to a pivoting of the transmission member and to a radial displacement in the opposite direction of the other movable cheek 138, 140.

Description

 The present invention relates generally to torsion damping devices, in particular clutch friction for motor vehicles, of the type comprising, at least three coaxial parts two to two rotatably mounted relative to each other in the limits of a determined angular displacement sector and against elastic means, namely a first part comprising a hub, a second part comprising a hub plate with, between it and the hub, means of engagement with play, and a third part comprising at least one flange, which transversely forms an annular part around the hub but without relation to the latter.

 As is known, the elastic means interposed between the hub web and the hub are of relatively low stiffness. This can lead to an almost instantaneous and therefore noisy tilting of the hub web relative to the hub, when the driver releases, more or less suddenly, the action which he exerted on the accelerator pedal. Such a phenomenon can also occur in urban driving when when approaching a red light the user releases his action on the pedal, then re-accelerates when the light turns green.

 To overcome these drawbacks, provision was made in patent application FR-A-2,566,497 of June 22, 1984, and in its addition FR-A-2,582,765 of May 31, 1985, arrangements with an interposing device under in the form of two movable flanges, mounted head to tail, each comprising a toothing by which they are adapted to come, in service, each engaged with a complementary toothing provided on the hub.

 Thus, at low torque values, when the interposition member is in the service position, the above mentioned elastic means of low stiffness are prevented from acting alone.

 There has been described in the request for addition certificate FR-A-2 582 765, an arrangement in which an intermediate flange, radially fixed, is interposed between the mobile flanges.

In the disclosed works, in the above
mentioned request, an elastic means connects one of the movable flanges to the intermediate flange, while another elastic means connects the other movable flange to the intermediate flange.

 In addition, guide means are provided for guiding the radial movement of the movable flanges means preventing any angular movement between the movable flanges and the intermediate flange.

 Such an embodiment makes it possible to synchronize the radial movement of the two flanges, this in order to allow them to be put into the action position at a determined speed of rotation of the rotary parts of the torsion damper used.

 Although satisfactory, such an arrangement can have drawbacks.

 Indeed, for example, as a result of seizure phenomena, one of the flanges can become stuck while the other moves. Similarly, one of the elastic means can rupture so that one of the flanges can move before the other.

 In all these cases, one of the flanges may not come into engagement with the hub to the detriment of a malfunction of the torsion damper, or even of ruptured organs.

 The object of the present invention is to overcome these drawbacks and therefore to create an arrangement which synchronizes the radial movement of the flanges whatever the circumstances.

 According to the invention, a torsion damping device of the above-mentioned type is characterized in that the two movable flanges are connected to each other by at least one movement transmitting member pivoting relative to them, so that a radial displacement of one of the movable flanges causes a pivoting of the tran-smission member and a radial displacement in the opposite direction of the other flange.

 Thus taking advantage of a relative movement of the transmission member with respect to the movable flanges, the displacement of one of the flanges automatically causes the displacement of the other flange in all circumstances, so that the transmission member actuated by one of the flanges constitutes an actuator for the other flange.

 According to another characteristic, the pivoting transmission member is radially fixed and is mounted to rotate relative to the movable flanges around the axis of the assembly.

 The transmission member can, for example, be centered directly and kept radially fixed on the toothing of the hub, belonging to the intermeshing means. When this transmission member is a metal flange, this centering can be achieved by forming returns axial directed in opposite direction with respect to 1 other.

 Alternatively, the transmission member can be centered around the axis of the assembly by small columns carried by the hub web.

 According to another characteristic, drive means are provided between the transmission member and each of the movable flanges.

 Thanks to this characteristic, the transmission member can be arranged either between the two movable flanges, or outside of them.

 For example, the drive means may include tabs engaged in openings.

 The tabs can come from the transmission member and the openings can be formed in the movable flanges or vice versa. For example, the openings can be notches formed laterally in the edge of the movable flanges.

 Advantageously, the arrangement of the drive means is symmetrical for a good distribution of the forces. In the case of legs in one piece with the transmission member, these are diametrically opposite.

 Between each of the movable flanges and the transmission member, there are interposed elastic return means for actuating the movable flanges at a determined speed.

 In the case where these elastic means consist of a coil spring, the latter is hooked to the mobile flange concerned, by means of an L-shaped tab, formed by means of a return to the square of the mobile flange .

 Of course, provision is made for clearance accordingly.

 All of these provisions encourage automatic mounting of the torsion damper.

 Contrary to the provision of the Prior Art, taking into account the presence of the transmission member engaged with the movable flanges, only two buttonholes are provided per movable flange.

 The punctures are placed in the region of the movable flange comprising the notches by which the latter engages on small columns connecting the two flanges to each other, which the third part usually has. Preferably, these punctures are produced by slicing the lateral edges of these, then local stamping. These arrangements make it possible to obtain a puncture of great robustness, as well as good guiding precision thanks to the cut side edges.

 As a corollary, material is removed from the lower part of said movable flange and the puncture guide window of the other mobile flange is placed in said lower part.

 All these provisions, reinforced by the presence of the transmission member, advantageously make it possible to overcome the presence of a counterweight carried by the movable flange. If necessary, it is possible to add flyweight rivets. Of course, the weights of the prior art having a stiffening action, we can, as a precaution, add material at the radial edge of the recess of the flange, near the bottom of the notch thereof.

The characteristics and advantages of the invention will become apparent from the description which follows, with reference to the accompanying drawings in which
FIG. 1 represents a partially cut away front elevation view of a device according to application FR-A-2 582 765;
Figure 2 is an axial sectional view along line II-II of the device shown in Figure 1;
Figure 3 is a perspective view of the three flanges of the interposing member, shown in isolation, of the Prior Art;
Figure 4 is a section along line VI-VI of a portion of the interposing member shown in Figure 1;
Figure 5 is an enlarged view of a detail delimited by the insert 5 of Figure 3;
Figure 6 is a perspective view of the three flanges of the interposing member according to the invention, shown in isolation;
FIG. 7 represents a partially cut away front elevation view of a variant of a device according to the present invention;
Figure 8 is a front view of the transmission member according to the alternative embodiment of Figure 7
Figure 9 is a sectional view along line IX
IX of Figure 8;
Figure 10 is a sectional view along line XX of Figure 9;
Figure 11 is a front view of one of the movable flanges according to the alternative embodiment of Figure 7;
Figure 12 is a sectional view along line XII
XII of figure 11.

 These figures illustrate by way of example, the application of the invention to a clutch friction for a motor vehicle, of the type described in the above-mentioned application FR-A-2 582 765.

 As a reminder, this friction comprises at least three coaxial parts A, B, C, two to two rotatably mounted relative to each other, within the limits of a determined angular displacement sector.

 The first part A comprises a hub 10, the second part B a hub cover 12, which transversely forms an annular part around the hub 10, with, between it and the hub 10, means of engagement with clearance 13.

 The third part C comprises at least one flange 23 commonly known as a guide washer. This flange 23 transversely forms an annular part around the hub but without relation to it, that is to say without intermeshing means such as those provided between the web 12 and the hub 10.

 As is known, the hub 10, by means of grooves 11, for example, is intended to be secured in rotation to the input shaft of the gearbox, while the flange 23 is secured to '' a friction disc 26, comprising a web 27 carrying two friction linings 29, by which disc 26 it is intended to be secured in rotation, by tightening the friction linings 29 between a pressure plate and a reaction plate (not shown), with a driving shaft, here the motor shaft of the vehicle.

 It will be noted that two flanges or guide washers 23 are provided being disposed axially on either side of the hub web 12. These guide washers 23 are connected by balusters 24 passing through with play, by means of notches 25 , the hub cover 12.

 The backlash engagement means 13 comprise for the hub 10, a toothing 15 and, for the hub veil 12, a toothing 16, the teeth of which are nested with circumferential clearance (JT for the drawing direction, JR for the retro direction ) with those of the teeth of the teeth 15.

 These teeth 15-16 are formed respectively in the edge of the inner periphery of the hub veil and in a flange 14, carried by the hub 10, radially projecting at its outer periphery.

 Two springs 18, of relatively low stiffness, are interposed between the hub web 12 and the hub 10 (a single spring 18 is visible in Figure 1).

 These springs 18, of the coil spring type, are each housed partly in a recess taken in the toothing 15 and partly in a recess taken in the toothing 16.

 21 and 22 show respectively a shoulder of the hub 10 and a shoulder of the web 12 for support of a circumferential end of the spring 18 by means of a support pin 20.

 Elastic members 33A, 33B, in this case coil springs, are housed in windows 34A, 34B, web 12 and 35A, 35B, guide washers 23.

 Here, the windows are established in correspondence with one another being of identical circumferential development. As a variant, the circumferential developments may be different for a stepped intervention of the springs. In practice, the elastic means 33A, 33B, constituted by the elastic members 33A, 33B, have a stiffness greater than that of the elastic means 18.

 Between the hub 10 and the hub web 12, there is also an interposing member 37, which, sensitive to centrifugal force, is mounted movable between a standby position, for which it is inactive, and, beyond a speed of determined rotation, or critical speed, a service position for which, intervening between the two said rotary parts, for at least one direction of rotation, it urges, in said direction of rotation, at least a portion of the elastic means with circumferential action 33A, 33B, other than those 18 acting normally therebetween. Return means 65 are able to urge said interposing member 37 towards said waiting position.

 More specifically, the interposing member comprises two movable flanges 138, 140, which, mounted radially movable, each have teeth 39 by which they are adapted to come into engagement, in the service position, with complementary teeth 40 provided for this effect on the hub 10.

 These movable flanges comprise at least one tab 42 (FIG. 3), called the support tab intended to allow them to act on at least a portion of the elastic means 33A, 33B established circumferentially between the web 12 and the hub 10.

 The flanges 138, 140 are mounted head to tail with respect to each other and they are engaged by buttonholes 43 on lugs 44 carried axially projecting by the hub plate 12.

 Each of the buttonholes has a straight section 49, and a curved section 48, elongated circularly, which is centered on the axis of the assembly.

 An intermediate flange 139 is disposed between the two movable flanges 138, 140. This flange 139 is radially fixed and is engaged to do this, by means of buttonholes 43 ′, on the lugs or guide posts 44.

 The flanges 140, 139, 138 extend between the hub cover 12 and a contraveille 46 connected to the cover 12 by the lugs or balonnettes 44.

 Of course, this louver 46 has recesses identical to the windows 34A of the web 12, for housing the springs 33A.

 The teeth provided on the movable flanges 138, 140 result from the cutting of the edge of the opening 45, through which each of said flanges 138, 140, is engaged on the hub, 10.

 Each of these so-called flanges 138, 140 has diametrically opposite recesses 55, 55 ', by which it is engaged on the springs 33A. These recesses 55, 55 ′ are superimposed, in plan, with the windows 34A of the web 12 and the contra-wall 48 with a slight circumferential offset, as indicated by the arrow F1 in FIG. 1 corresponding to the normal direction of rotation, of the edge 57 recesses opposite the other edge, upstream, forming by itself the support tab 42.

 The intermediate flange 139 has two diametrically opposed notches 55 ′. Each flange 138, 139 carries a counterweight 58, which extends along the edge of said flange opposite to the toothing 39, and has two notches 80, 80 ', each arranged on these two lateral edges. The notch 80 ′ has a radially outer flank 81 which is generally oblique with respect to the tangent to the circumference passing through the end of this flank. This flank 81 is able to cooperate with a column 24 to facilitate the passage of the movable flange from its rest position to its action position.

 The flanges 138, 139, 140, are kept in contact with one another under the stress of elastic means with axial action 64, here a Belleville washer, which bear on the hub web 12 and stress the flange 140 in veil direction 46.

Of course, in a manner known per se, friction means 72, tared elastically by a washer 74 are provided between the guide washer 23 and the counterfoil 46. Likewise, friction means 71, tared elastically by a washer 70, are provided between the above
mentioned washer 23 and the collar 14 of the hub.

The other guide washer 23, that which carries the friction disc 27 by means of the balusters 24, is centered by a bearing 30, comprising a transverse flange 31, linked in rotation with said washer 23, for example, by bosses engaged in notches provided therein.

 Each movable flange 138, 140 has a fastening tab 69, while the intermediate flange has two fastening tabs 62, which are diametrically opposite, that is to say arranged on a diagonal. These fasteners are used to attach the above-mentioned return means 65. These return means 65, here in the form of a coil spring, are arranged parallel to the diametrical plane of the assembly, and connect a fastening tab 69 to a tab attachment 62.

These return springs bring the flanges 138, 140 back from their action position to their service position and allow said mobile flanges to move apart beyond a certain threshold. For radial guidance, each flange 138, 140 has a flat 99, called a guide, engaged in windows 100 of the intermediate flange 139 and 101 of the other movable flange 138, 140. The windows 101 are higher than the windows 100 which prevent a displacement of the intermediate flange 139 circumferentially with respect to the movable flanges 138, 140. For the other details, refer to the above
mentioned request FR-A-2 582 765.

 According to the invention, the intermediate flange 139 is eliminated and the two movable flanges 138, 140 are connected to each other by at least one movement transmission member 239 pivoting relative to them, so that a radial displacement of one of the movable flanges 138, 140, causes the transmission member to pivot and a radial displacement in the opposite direction of the other movable flange.

 Such a transmission member is visible in Figure 7 and is interposed here between the two movable flanges 138, 140. Replacing the intermediate flange 139 so it mounts in the clutch friction of Figures 1 to 5 and for simplicity the same references that in said figures will be used for identical elements.

 In the embodiment shown the pivoting transmission member 239 is radially fixed, being here centered, relative to the axis of the assembly, by the edge of its central opening 145 on the teeth 15 of the hub 10. It generally has the shape of a washer and carries, in diametrically opposite positions, two arms 240, 240 ′ each provided with a square return 241, 242, each extending axially. These square or leg returns 241, 242 are directed axially in the opposite direction and are capable of each engaging, respectively, in an opening 243, of the movable flange 139 and 244 of the movable flange 140.

 These openings 243, 244, here consist of notches or notches 243, 244, and are each formed laterally on the edge of one of the radial edges of the movable flange concerned.

 As shown in FIG. 6, these notches 243, 244 are diametrically opposite one with respect to the other, and have dimensions adapted to the square returns 241, 242 of the arms 240, 240 ′.

 As in the embodiment of FIGS. 1 to 5, a return spring 65, under prestressing, is provided between the pivoting transmission member 239 and each of the movable flanges 138, 140. These springs are arranged parallel to the diametral plane of the 'together and each connect a fastening tab 69, of one of the movable flanges 138, 140, to a fastening opening 246 that each arm 240, 240' has for this purpose.

 As will be understood, all of the square returns (or legs) and notches form training means. Any radial movement of one of the flanges 138, 140 causes pivoting of the transmission member 239 and a radial movement in the opposite direction of the other flange.

 It will be appreciated that this transmission member 239 is simplified compared to the flange 139 of the prior art by being devoid of recesses of the type 55 ′ of FIG. 3, buttonholes 43 ′ and windows 100. This member is thus More reliable.

 It will be noted that, as a variant, taking into account the existence of the returns 241, 242, the transmission member 239 can be arranged outside the two movable flanges 138, 139. Advantageously, the transmission member is produced at from a metal flange by cutting and folding.

 Figures 7 to 12 show another variant according to the present invention still with movable flanges 138, 140 mounted head to tail.

 In these, the movement transmission member 239 generally has the form of a parallelogram with central opening 145, and is provided with openings 246, for hooking the springs 65, offset radially with respect to the square returns 241, 242, one being arranged in the vicinity of the upper left corner of the member 239, the other in the vicinity of the lower right corner of said member (Figure 8).

 The openings 246 are thus diametrically opposite one with respect to the other. This radial offset of the openings 246 makes it possible to lengthen the length of the return spring 65, which is favorable to the life of the latter. Of course, provision is made for clearances 247 for the passage of said springs.

 As can be seen more particularly in FIG. 8, the circular central opening 145 of said member 239 is interrupted by the clearances 247 and said member 239 has a symmetrical shape.

 For its radial retention and its centering relative to the toothing 15 of the hub 10, this transmission member 239 has, at its opening 145, axial returns 248, 249, extending in opposite directions for better stability of that -this. Of course, said transmission member 239 can be centered by means of the balusters 44. In fact, it suffices to give the external periphery of said member 239 an annular shape, as shown in Figure 8, for contact with the balusters 44.

 For mounting the other end of the spring, each flange 138, 140, has an L-shaped tab 250, formed by means of a return to square 251 of the movable flange. In practice, the base of the L is turned towards the center of the flange. This tab 250 replaces the fastener 69 of Figures 1 to 5. Of course, there is a clearance 253 in each movable flange 138, 140, to allow easy mounting of the springs 65. Like the transmission member 239, the flanges mobiles are made from a metal flange by cutting and folding.

 Each movable flange 138, 140, has only two buttonholes 43. These are diametrically opposite. Each buttonhole has a curved section 48, which, generally circumferentially elongated, is centered on the axis of the assembly, and a straight section 49, which, disposed at one of the circumferential ends of the section 48, extends substantially parallel in the plane of the assembly passing through the median zone of such a flange 138, 140.

 For the buttonhole located on the side opposite to the toothing 39, said straight section 49 extends in the direction opposite to said toothing 39 from the curved section 48, on the other hand, for the other buttonhole 43, that disposed on the side of the toothing 39, it extends on the side thereof. Be that as it may, the two sections 48 are connected to each other by widely rounded connecting leaves.

 The toothing 39 of each flange 38 results in practice from a cutting of the edge of its central opening. In the embodiment shown, it is reduced to a single tooth 50, framed by two recesses 51. Jointly, the toothing 40 formed on the hub 10 is reduced, for each flange 138, 140 to a single groove 53 formed axially, between two axial bosses 54 at the periphery of the flange 14 of said hub 10.

 Preferably, the teeth of the complementary teeth 39, 40 have slightly oblique flanks on a radius of the assembly passing through the middle zone, and rounded edges, to facilitate their mutual engagement as well as their subsequent disengagement.

 Unlike the embodiments of FIGS. 1 to 5, the guide punctures 99 are formed in the part of the movable flange opposite to that having the toothing 39. In practice, a single puncture is provided and it is arranged in the vicinity of the lower end the opening 55 of said flange 138, 140, while being disposed on the other side of the transverse plane of symmetry relative to the buttonhole 43. This puncture is therefore associated with the portion of the movable flange 138, 140 having notches 80, 80 ', which here are identical.

 As a corollary, the window 101 provided for the flat of the other movable flange is arranged in a position diametrically opposite the flat 99 relative to the axis of the assembly.

 It will be noted that the edge 57 of the opening 55 ′ has been cut off, the material having been removed.

 As will be understood, all these provisions promote a reduction in weight of the portion of the movable flange carrying the toothing 39 and an increase in weight of the other portion, that in which the notches 80, 80 ′ are made.

 These provisions make it possible to dispense with the presence of a counterweight 58 projecting axially from FIGS. 1 to 5. As a precaution, material is added in the lateral edge of the window 55 delimiting the tab 42. As can be seen in the figure 11, this addition of material gives said radial edge a convex shape in its portion opposite the bottom of the notch 80 ′, so that the thickness of material between said bottom and said radial edge is increased. Bringing the column 24 into contact with the bottom of the notch 80 ′ therefore does not risk damaging the flange 138, 140.

 It will be appreciated, if necessary, that it is possible to add rivets forming weights by means of the openings 252 provided in the vicinity of the notches 80, 80 ′. It will be noted that here the puncture, after slicing and stamping, locally forms a continuous deep stamping by being domed, and therefore more resistant than that of FIGS. 1 to 5.

In addition, only its lateral edges are cut, which improves the guiding and torque transmission functions of said flat tire.

 It will be noted that the lateral openings 243, 244 have the following form: they comprise a first section 260, perpendicular to the generally transverse lateral edge 261 of the movable flange, a bottom 262 having a part 263 perpendicular to the section 260 and an inclined part 264, by relative to the part 263, to allow the rotation of the transmission member 239. this shape in diere of the bottom 262 makes it possible to increase the thickness of material, between said bottom 262 and the central opening 45 of said movable flange 138, 140. In addition, good guidance between the transmission member 239 and the movable flanges 138, 140 can be obtained. Of course, it is with a slight radial clearance that the tabs 241, 242, engage in the notches 243, 244. In the rest position, contact occurs between the section 260 and the edge of said tab 241 or 242 under spring action 65.

 The torsion damper operates in a similar manner to the entire device disclosed in the aforementioned application FR-A-2 566 497, and of course the circumferential development of the section 48 of the buttonholes 43 is made at least, angularly, to the entire circumferential clearance JT, JR, interlocking means with clearance occurring between the hub web and the hub.

 As a reminder, it will be recalled that as soon as the critical speed, determined in particular by the return springs 65, is reached, each of the flanges 138, 140 moves radially under the stress of the centrifugal force of which it is the object, while being guided during this first phase of radial displacement by the columns 44 with which it is engaged, while passing as if they then traversed the straight section 49 of the corresponding buttonholes.

 If for such a critical speed the toothing 39 of each of the flanges 138, 140 is found to be circularly facing the corresponding toothing 40 of the hub 10, such a flange 138, 139 then passes into the service position, for which, at the end of its radial displacement it is engaged, by sadite toothing 39, with said corresponding toothing 40 of the hub 10. Consequently, each of the flanges 138, 140 can pivot around the axis of the assembly relative to the web ~ of hub 12, - the balusters 44 then traversing the curved section 48 of the buttonholes 43. During such a pivoting, each of the flanges interfere, by its support tabs 42, with the windows 34A of the hub web 12 in exit, it is thus able to act on the springs 33A to request intervention. It will be noted that it is only in the first phase that the rotary transmission member 239 intervenes because once the flanges 138, 139 are in the service position, no pivoting movement of the transmission member 239 relative to the movable flanges 138, 140 does not occur because these are secured in rotation with the hub 10.

 It will be noted that each of the movable flanges causes, thanks to its notch 243, 244, the tabs 241, 242 of the transmission member 239 by rotating it around the axis of the assembly. Good synchronization of the radial displacements of the flanges 138, 140 is obtained whatever the circumstances. Indeed, if one of the springs 65 is broken, or if seizure phenomena appear between one of the mobile flanges and the transmission member 239, the other mobile flange will cause rotation of the transmission member 239 and therefore automatically a radial displacement of the other movable flange in the opposite direction.

Below the critical speed, for example at idle speed, the shock absorber operates as follows
the hub cover 12 moves relative to the hub 10, against the elastic means 18 of low stiffness, the flanges 23 being secured in rotation to the hub cover 12 by the elastic means 33A, 33B, of higher stiffness. During this phase, the movable flanges, held in their rest position by the springs 65, have no action. After the play between the teeth 15, 16 has been taken up, the hub cover 12 rotates with the hub 10, and the flanges 23 become movable relative to the hub cover 12, against the elastic means 33A, 33B. During this second phase, above the critical speed, the movable flanges 138, 140, can move in the manner described above.

 Of course, the present invention is not limited to the exemplary embodiments described but encompasses all variant embodiments.

 In particular, o-n can provide anti-seize coatings between the flanges and the transmission member.

These coatings can be based on chromium. Likewise, the hub can be produced by sintering, which makes it possible to provide several teeth for each flange and for the hub.

 Instead of drive means produced in the form of lugs penetrating into notches, one can provide pins engaging in openings conformed for this purpose. The tabs may be integral with the movable flanges and be engaged in openings of the transmission member.

 Finally, to increase the contact area between the tabs 241, 242, and the notches 243, 244, each flange and each tab can be provided with folds, as shown in dotted lines in FIG. 6.

Claims (9)

 1) Torsion damping device, in particular for motor vehicles comprising a hub (10), at least one hub web (12), which transversely forms an annular part around the hub (10) with, between it and said hub (10) , backlash engagement means (13) and elastic circumferential action means (18), at least one flange (23), coupled to the hub web (12) by elastic circumferential action means (33A, 33B) , which transversely forms an annular part around the hub (10), but without relation to the latter, an interposing member (37) comprising two movable flanges (138, 139), sensitive to centrifugal force, mounted movable between a waiting position for which they are inactive, and, beyond a determined rotation speed, a service position, for which acting between the hub (10) and the hub web (12), for a direction of relative rotation at least of these, they urge, in said direction of rotation, a por tion at least of elastic means with circumferential action other than those acting normally between them, and return means (65) capable of urging said moving flanges (138, 139) towards their said waiting position, characterized in that the two movable flanges (138, 139) are connected to each other by at least one transmission member (239) pivoting relative to them, so that a radial displacement of one of the movable flanges (138, 140) causes the transmission member to pivot and move radially in the opposite direction to the other movable flange (138, 140).  2) A torsional damping device according to claim 1, because it is activated in that the pivoting transmission member is mounted radially fixed and rotatable relative to the movable flange (138, 140) around the axis of the assembly.  3) Torsion damping device according to any one of claims 1 or 2, characterized in that drive means (241, 242, 243, 244) are provided between the transmission member (239) and each of the flanges mobile (138, 140).  4) A torsion damping device according to claim 3, characterized in that from one movable flange (138, 140) to the other, the drive means are arranged symmetrically.  5) Torsion damping device according to the  claim 4, characterized in that the means  of training consist of a leg (241, 242) engaged  in an opening (243, 244) of the movable flange (138,  140).  6) A torsion damping device according to any one of the preceding claims, characterized in that for attachment of the elastic return means (65), each movable flange has a tab in the form of L formed by virtue of a return to square (251) thereof.  7) A torsion damping device according to any one of the preceding claims, in which each movable flange has buttonholes, for engagement on balusters (44) connecting the hub web (12) to a contraveil (46), a flat tire ( 99) suitable for engaging in a window of the other movable flange for radial guidance thereof, as well as a toothing (39) for engagement with a corresponding toothing (40) provided on the hub (10), characterized in that the puncture is disposed in the radial portion of the movable flange opposite to that having said tooth (39).  8) A torsion damping device according to claim 7, characterized in that the punctured (99) has a domed shape with two side edges cut.  9) A torsion damping device according to any one of the preceding claims, in which each movable flange comprises, on the side radially opposite its teeth (39), a window-shaped recess adjacent to a notch (80 ') for passage of the balusters (24) connecting to one another the two flanges (23) that has the third part C, characterized in that the portion of the radial edge of the window (55) facing the bottom of the notch (80 ') has an extra thickness.