FR2499182A1 - Torsional vibration damper for friction clutch - has two pairs of spring flanges with torsion springs for plates in hub - Google Patents

Abstract

The clutch consists of a head (A) with two diametrically opposed, dove-tailed grooves (19) and an outer rotating casing (B) carrying a clutch plate (12). The hub is driven by the outer element (B) through pairs of spring flanges (20) and two torsion springs (30). The spring flanges are of two thicknesses and diametrically opposed. The flanges fit into the dove-tailed grooves (19) in the hub (A). An abutment (26) on the outer casing locates in a notch (27) on the spring flange and dampens the torsional vibrations as the drive is engaged.

Description

CAS The present invention relates generally to devices

  torsional dampers of the kind comprising at

  at least two coaxial parts rotatably mounted one relative to

  port to another within the limits of an angular deflection

  finished and against elastic means interposed circum-

ferentially between them.

  So if we know, such a shock absorbing device

  Zion usually enters into the constitution of a clutch friction, in particular for a motor vehicle, one of its rotary parts then carrying a friction disc intended

  to be secured in rotation with a first shaft, in practice

  that a driving shaft, the output shaft of the engine in the case of a motor vehicle, while the other of its rotary parts is carried by a hub intended to be secured in rotation with a second shaft, in practice a shaft driven, 1 input shaft of a gearbox in the case of such

motor vehicle.

  Such a device makes it possible to ensure transmission

  regulated torque of the torque applied to one of its parts

  rotating ties when the other is itself the object of a

  full of rotation, that is to say to filter the vibrations suscep-

  tends to arise all along the cinematic chain

  tick on which it is inserted, which goes from the engine to the trees

  wheel ordered in the case of a motor vehicle.

  Most often, in the damping devices of tor-

  of this type, elastic means with circumferential action

  tielle are constituted by springs, of the type springs with

  sausage, which are generally elongated tangentially with respect to

  wearing at a circumference of the assembly, and which are each lo-

  partly in a window provided for this purpose in a first room, a veil for example, belonging to one of the

  two rotary parts concerned, and partly in a fe-

  ours made for this purpose in one or more other parts, guide washers for example, belonging to the other

of said rotating parts.

  Such coil springs in this case constitute elements

  circular circumferential action elastic elements

lairement.

  One of the problems to be solved in the realization, of dis-

  positive torsional dampers of this type resides specified-

  lying in the necessity that there is to find the necessary place

  be able to install these coil springs in an es-

  pace, which is also radially determined by the data

  imposed imposed construction, and which is already congested, even though the number of these springs can be important and that the implementation of each of them inevitably leads to a weakening of the rooms in which the windows

  necessary for their homes are cut out.

  - Another problem to be solved in the production of torsion damping devices using,

  for elastic elements with circumferential action, res-

  sausage spells, lies in the difficulty of adjusting

  at best the stiffness of these to the operating characteristics

  to ensure for the whole, this problem cannot

  in practice be overcome only by the implementation of res-

  sausage spells of different stiffness, which, on the one hand,

  involves, in an expensive way, the manufacturing and the

  kage of such coil springs. of different stiffnesses, and what, on the other hand, leads, during the implantation of these

  within a torsion damping device, at a certain

  no complication of manufacturing and mounting for the various

constituents of it.

  It has however already been proposed, for the constitution

  elastic elements with circumferential action of

  kill elastically deflected arms at such coil springs

  formable or elastic elements with circumferential action-

carrying him with such arms.

  This is the case, in particular, in the American patent

No 2.114.247.

  In this American patent, two elastically deformed arms

  tables are used, which each result from the winding

  helically of a sensitive cross-section bar-

  square, and each of which, by a first portion is linked

  in rotation at a first of the two rotating parts concer-

  born, and, by a second portion, is engaged with the two-

  th of these, said first proportion being, for its

  connection in rotation with said first rotary part, sim-

  fully axially engaged in an axially provided groove

  for this purpose at the periphery of the hub that this pre-

1st rotating part.

  But, besides that, in this American patent, the shaping of the bar from which each of the elastically deformable arms used is made up is relative-

  awkward, the diameter along which the winding is made-

  corresponding corresponding being particularly difficult to control, and expensive, such elastically deformable stockings have

  inevitably a significant axial size.

  These elastically deformable arms cannot therefore easily be staggered axially, without significantly increasing, and in practice prohibitive, the bulk

axial of the assembly.

  Furthermore, if they were thus staggered axially, it

  would not fail to result in the development of a composition

  significant radial elastic health.

  In practice, they are arranged axially in the same

  transverse plane, they can only extend circumferentially-

in the same direction.

  This meaning is of course chosen to correspond to a "pull" operation of the assembly, that is to say to a

  increasing evolution of the torque transmitted from one of the ro-

  tatives concerned to each other, for which the elastic arms-

  deformable implemented are stressed in winding.

  However, these elastically deformable arms are suitable from

  when malfunctioning in "retro" operation of said assembly, that is

  that is to say a decreasing evolution of said couple, since they are

then solicited in progress.

  Finally, in US Patent No. 2,114,247, the elastically deformable arms used extend continuously from one of the rotary parts concerned to the other, so that they intervene between them from the start of the travel

  angular between them, and therefore also for low values

  their of the torque transmitted from one of these rotating parts to 1 '

  other than for the high values of this couple.

  Thus, the elastic means with circumferential action

  intervening between said rotary parts have the same radius

  deur throughout the angular movement between them.

  Now, in practice, it is desirable that, on the one hand, these elastic circumferential means have a

  relatively low stiffness for low values of

  ple, especially for good absorption of point noise

  dead when stationary, and that, on the other hand, they present a reason

  relatively high value for the higher values of this torque, which the arrangement described in the

U.S. Patent No. 2,114,247.

  I1 is also provided, in the French patent application filed on November 3, 1980 under No. 80 23447, of

  use, for elastic elements with circumferential action

  radial, one or more suitably cut flanges, which extends transversely, and which are likely to be

axially staggered.

  But, in this French patent application, which in fact has other provisions, the flanges thus used for the constitution of elastic elements with circumferential action, complement other elastic elements with circumferential action consisting of in conventional manner by coil springs, and, for their connection in rotation with one of the rotary parts concerned, they are

  most often directly positively attached to it

this.

  The present invention has a general maneuver for

  throw a provision which, associating some of the characteristics

  ques previous, allows, following a development of these

this, to make a new use of it.

  More specifically, it relates to a torsion damping device, in particular clutch friction, of the kind comprising at least two coaxial parts mounted to rotate relative to one another, within the limits of a

  determined angular displacement, and elastic means

  circumferentially bent between said rotatable parts

  ves, called for convenience elastic means with circumferential action

  differential, this torsional damping device.

  laughed in that, in combination, on the one hand, said elastic circumferential action means comprise at least two

  elastic elements with circumferential action staggered axia-

  each of which, by a first portion, is linked in rotation

  tion to a first of said rotary parts, and, by a

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  second portion, is adapted to be engaged, or to engage, with the second of these, and, on the other hand, for its connection in rotation with said first rotary part, each of said elastic elements with circumferential action is , by its said first portion, engaged with an axially elongated interlocking means that comprises said first

  rotary part, said first portion comprising for this purpose

  fet a means of nesting complementary to the previous one.

  In practice, elastic elements with circumferential action.

  differential thus set. artwork are of similar configurations

  stackable and differ from each other, or from each other

others, by their elasticity.

  For example, these are flanges, which extend

  versally and have the same cut, but which have

different thicknesses.

  In.variant, they can be pin springs,

  different cross sections, all suitably con-

  formed according to similar configurations.

  In either case, the same tool may favor

  wisely and economically be put in. work for the realization

  sation of such elastic elements with circumferential action

  of the same type but with different elasticities.

  In addition, in one. and the other case, the elastic elements

  that circumferential action to be implemented for the constitution of a torsion damping device can

  advantageously, depending on the overall characteristics to be obtained

  nir for it, be chosen, in the manner of the weights of a bunch of weights, from a plurality of elastic elements with circumferential action of different elasticities, so that the overall elasticity to be obtained can thus advantageously

be adjusted as best as possible.

  Finally, due to the complementary nesting means

  axially elongated provided between these elastic elements to ac-

  circumference and one of the rotating parts concer-

  born, for their connection in rotation therewith, at least some of these elastic elements with circumferential action

  may be free from any permanent link with the two-

  th of said rotary parts, so that, during assembly

  of the whole, their placement in it results before-

  tagging with a simple axial engagement on said first

rotating part.

  This axial engagement, which is very similar to stacking, can advantageously, according to a development of the invention, be extended to the friction means also intervening between the two rotary parts concerned, the

  axially elongated interlocking means comprising the first

  re said rotary parts then being, according to the invention,

  common to at least one elastic element with circumferential action

  tial and at least one friction element.

  The assembly of the assembly is advantageously and

economically simplified.

  The characteristics and advantages of the invention stand out

  will derive from the description which follows, by way of

  example, with reference to the schematic drawings attached on the-

  which: Figure 1 is an axial sectional view of a torsion damping device according to the invention, along the line I-I of Figure 2; Figures 2 and 3 are cross-sectional views of this torsion damping device.

  line II-II, which is broken, and line iII-III, of the fi-

  gure 1; Figure 4 is, along the line IV-IV of Figure 5, a cross-sectional view of the single hub used in this torsion damping device, shown in isolation;

  Figure 5 is an axial sectional view of this hub,

vant line V-V of Figure 4;

  FIG. 6 is a plan view of one of the modular flanges

  laires used in the torsion damping device according to the invention. for the constitution of elastic means with circumferential action, shown in isolation; Figure 7 is an axial sectional view of this modular flange, along the line VIII-VIII of Figure 6;

  Figure 8 is an elevational view of another component.

  killing of the torsion damping device according to the invention, shown in isolation; Figure 9 is an axial sectional view of this component, along the line IX-IX of Figure 8; FIG. 10 is an elevation view of a spring in,

  pin also used in the damping device

  torsion sor according to the invention, shown in isolation.

  In these figures, the torsional damping device to which the invention is applied constitutes, by way of example, a clutch friction with a damping hub for a motor vehicle. Generally speaking, such clutch friction

  has at least two coaxial parts A, B, one exciting

  te, the other excited, rotatably mounted relative to one another, in the lirlites of a determined angular movement,

  and against elastic means capable of acting circumferentially-

  between them, said for convenience elastic means

circumferential action.

  In the embodiment shown, the ro-

  tative A is formed by a simple tubular hub 10, and the part

  rotary tie B is formed by an annular case 11, which is arranged annularly around the hub 10, with interposition of bearings 13a, 13b, and which carries a friction disc 12. In practice, in the embodiment shown ,

  this boot 11 is formed of two annular shells complete

  14a, 14b, which are nested one inside the other by their respective peripheral edges 18a, 18b, and which are

  secured to one another by welding by these perimeter edges

spheres 18a, 18b.

  The most internal shell 14a carries the dis-

  than friction 12, this being for example, as shown

  felt, attached to this shell 14a using rivets 15

  taken from the very mass of it.

  For reasons which will appear below, the peripheral rim 18a of this shell 14a is, in the example of

  achievement represented, allocated, in positions globally

  metrically opposite, of two pairs of punctures 16.16 'at the front

  veur of which are respectively formed legs 17,17 'folded so as to project obliquely in the internal volume of the boot 11, and, for each pair of legs 17,17', the tab 17 extends circumferentially obliquely in a

  first direction while the associated tab 17 'extends circum-

  preferentially obliquely in opposite directions.

  As will appear below, the legs 17 are des-

  keen to intervene for a first direction of rotation of the

  seems, which, indicated by the arrow F in FIGS. 2 and 3, is the one according to which they extend, and the lugs 17 ′ are intended to intervene for the opposite direction of rotation,

  which is also the one according to which they extend.

  In a manner known per se, the rotating part B thus

  is intended to be secured in rotation to a pre-

  mier tree, in practice a driving tree, by tightening the dis-

  that friction 12, between two rotationally integral plates

  of such a tree (not detailed in the figures).

  Similarly, the hub 10 constituting the rotary part A is intended to be secured in rotation to a second shaft, in practice a driven shaft, and, for this purpose, this hub 10 has internally, in the exemplary embodiment. depicted,

splines 21.

  Externally, and for reasons that will appear below

  afterwards, the hub 10 has at. further, according to the invention, to

  its periphery, at least one. axial elongated interlocking means-

  is lying. In the illustrated embodiment, two such interlocking means are provided, in diametrically opposite positions, and these are two grooves 19, which each have a trapezoidal outline in cross section, and which are thus

  each suitable for mounting of the dovetail mounting type.

  According to the invention, and in combination, on the one hand, the elastic means with circumferential action interposed between the rotary parts A, B comprise at least two elastic elements with circumferential action, detailed below, axially staggered, each of which, by a first portion is linked in rotation to a first of said rotary parts A, B, and, in the embodiment shown, it is

  in practice of the rotary part A, and, by a second port-

  tion, is able to be engaged, or to come into engagement, with the second of said rotary parts A, B, and it is therefore,

  in the illustrated embodiment, of the rotatable part

  ve B, and, on the other hand, for its connection in rotation with the par-

  rotary tie A, each of said elastic elements with a circumferential action is, by its said first portion, engaged with the axially elongated interlocking means which for this purpose comprises the hub 10 constituting this rotary part A,

  said first portion comprising for this purpose a means of em-

  limp complementary to the previous one. In practice, in the embodiment shown, some of the elastic elements with circumferential action thus used form modular flanges 20, which extend transversely, and which all have the same

cutting.

  Such a modular flange 20 is shown in isolation on

Figures 6 and 7.

  It comprises, in the embodiment shown, two elastically deformable arms 22, 22 ', which, at one of their ends, are secured to a common support 23, and

  which, from this one, each extend globally

  in opposite directions, on a little less than. Furthermore, in this embodiment, the support 23 comprises on the one hand a washer 24, which is adapted to carry, by its internal periphery, from place to place, on the hub 10, and that a radial clearance separates, at its outer periphery, elastically deformable arms 22, 22 ′, and on the other hand a foot 25, which projects radially at the internal periphery of the washer 24, and which generally has one. trapezoidal contour complementary to that of the axial grooves 19 of the hub of the rotating part B.

  This foot 25 forms the portion. of each of the modular flanges

  laires 20 by which this one is adapted to be engaged with

  the hub 10 of the rotary part B for its rotational connection

tion to it.

  Constituting -n effect one. complementary nesting means

  re that of each of the grooves 19 of the hub 10, it allows free axial engagement of such a modular flange

20 in such a groove.

  In the embodiment shown, there are

  preferentially a shift between, on the one hand, the foot 25 of the support 23 of the elastically deformable arms 22, 22 'which constitutes its anchoring zone on the hub 10, and, on the other hand, the zone of said elastically deformable arms by which

  these are connected to the washer 24 of said support 23.

  At their end opposite to their support 23, the elastically deformable arms 22, 22 'of each modal flange 20 each have respectively a radial extension 28, 28', which is radially directed towards the outside, and which,

  preferably, as shown, is shaped as a hook.

  Radial extensions 28.28! that thus presents each

  that modular flange 20 constitute the portion of this modular flange 20 by which it is able to be engaged, or to come into engagement, with the rotary part B, these radial extensions 28,28 'forming shoulders 27,27' likely, as will appear below, to cooperate with the tabs 17, 17 'of this rotary part B.

  Finally, in the embodiment shown, the sup-

  port 23 that each modular flange 20 has, has, at the level of the corresponding foot 25, a recess 29 intended to

improve elasticity.

  In the embodiment shown, four modular flanges 20 are used, and these are associated in pairs of two modular flanges, which have different thicknesses axially, and which therefore differ one

on the other by their elasticity.

  There is thus a first pair of two modular flanges.

* res 20, one relatively thin, the other relatively thick, whose support leg 25 is engaged in a first of the axial grooves 19 of the hub 10, and whose deformable elastic arms 22, 22 'are intended to cooperate with those of the legs 17, 17 ′ of the rotary part B which, directed in the same direction as them, extend in the direction of the shoulder 27, 27 ′ of their radial extensions 28, 28 ′, FIGS. 1 and 3, and

  there is a second pair of annular flanges 20, one re-

  laterally thin, the other relatively thick, whose support leg 25 is engaged in the other of the axial grooves 19 of the hub 10, and whose elastically deformable arms 22, 22 'are, like the preceding ones, intended to cooperate with those legs 17, 17 ′ of the rotary part B which, directed in the same direction as them, extend in the direction of the shoulder

  27.27 'of their radial extensions 28.28', Figures 1 and 2.

he

  In practice, for the rest configuration of the set-

  ble, as shown, the modular flanges 20 are all free from any permanent connection with the rotating part B in the embodiment shown, the radial extensions 28,28 'of their elastically deformable arms 22,22'

  being circumferentially at a distance from the legs 17.17 ′ cor-

  of this rotating part B, in. so that when

  of the assembly of the assembly, their setting. place results from the sim-

  full axial engagement of their support leg 25 on the hub 10 of the rotary part A. In other words, there is circumferentially, in this embodiment, an initial clearance between the shoulders 27, 27 ′ of the elastically deformable arms 22 , 22 'and the legs 17,17' of the rotating part B. Being of similar superposable configurations, the

  modular flanges 20 thus implemented can advantageously

  be cut using the same tool.

  It was assumed above that they were four in number. But, in reality, according to the global characteristics

  elasticity to be obtained, an appropriate number of modular flanges

  laires 20 is used, these being chosen in con.sec-

  quence, like the weights of a box of weights, among a

  plurality of modular flanges available with axial thicknesses

  different, and therefore different elasticities.

  It is also possible to consider the implementation

  modular flanges of different configurations, including

  lying in. regarding the configuration of their elastic arms

  only deformable and / or their support.

  In the embodiment shown, two other elastic elements with circumferential action are also

  provided between the rotating parts A, B.

  These are pin springs 30, one of which is shown

felt in isolation in Figure 10.

  Such a pin spring 30 has one of its ends shaped as a foot 31 complementary to the axial grooves 19 of the

  hub 10, for free axial engagement in such a groove

  re, like the modular flanges 20; the other of its extremi-

  tees is shaped as a hook 32, and between said ends

it extends circumferentially.

  As before, the foot 31 of a hairpin spring therefore constitutes a first portion of such a spring by which it is able to be engaged with the hub 10 of the rotary part A for connection. in rotation thereto, and the hook 32 of such a spring constitutes a second portion by which the latter is able to be engaged with the part

  rotary B, as specified below.

  According to diametrically opposite arrangements relative to each other, as pDur the modular flanges 20, the pin springs 30 are, in fact, by their foot 31, engaged in the axial grooves 19 of the hub 10, one in one of these grooves, the other in the other of these, and, by their hook 32, they are each respectively coupled,

  one at the lug 17 of the shell 14a of the case 10 circumferen-

  essentially farthest from the axial groove 19 in

  which is engaged its foot 31, the other to the leg 17 'cor-

  corresponding to said shell 14a, extending circumferentially-

  tially in opposite directions to each other.

  Thus, the pin springs 30 are, each respectively, axially staggered with one or the other of the pairs of modular flanges 20 used in the

  shown embodiment.

  Of course, according to provisions similar to those

  described above, and for an adjustment of the elasticity

  corresponding, two or more pin springs 30 different

  each other by their elasticity can if desired

be associated.

  In all cases, the springs in. pin 30 used

  vre are preferably of similar configurations superimposed

  bles, and are therefore advantageously likely to be

  made using the same tool.

  Between the rotating parts A, B also intervene friction means and, these, in the form of realization

  sation.representée, comprise two friction pads 34 linked in rotation to one of the rotary parts A, B and able to cooperate in friction with an axial bearing linked in rotation

to the other of these.

  In the embodiment shown, these pads

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  friction 34, which are arranged in diametrically opposite positions with respect to each other, are linked in rotation

  with the hub 10 constituting the rotary part A, and the port

  axial tee with which they cooperate, which is rotatably linked

  tion with the rotary part A, is formed by the inner surface 37 of the peripheral rim 18a of the shell 14a of the

bootmaker 11.

  Each friction pad 34 has a lining of

  curved friction 38 and a support 35 starting therefrom.

  In the embodiment shown, this support 35

  is formed by a flange, which extends transversely relative

  port to the axis of the assembly, and which, at its end opposite to the friction lining 38, forms a foot 36 of trapezoidal contour complementary to that of the axial grooves 19 of the

hub 10.

  In addition, in this embodiment, such a support comprises, on its radial edges, alternating notches

  41 locally giving it an S shape, for the constitution

  tion of elastic means with radial action suitable for keeping the associated friction lining 38 permanently applied

  against the axial bearing 37 with which it cooperates.

  As will be understood, the friction pads 34 thus used in the embodiment shown

  are sensitive to centrifugal force.

  For their rotational connection to the hub 10, the friction pads 34 are simply axially engaged, by the foot 36 of their support 35, including the elongated interlocking means

  axially constituted by both of the ax grooves: ia-

  those of this hub 10, said foot 36 of their support 35 forming

  indeed a means of nesting complementary to the previous one.

  Thus, according to the invention, the same groove 19 of the hub is common, on the one hand to at least one elastic element with circumferential action, constituted by a modular flange

  or a hairpin spring 30, and therefore, in practice, more

  sieurs such elastic elements with circumferential action,

  and, on the other hand, to at least one friction element, constituted

  killed in practice by a friction shoe 34.

  All the elements thus engaged with a groove 19 of the hub 10 are advantageously freely axially engaged

in this one.

  As described above, the mounting of the shock absorbing device

  torsion weaver according to the invention is therefore advantageously

  by simply stacking its various components axially

  killing on the hub 10, the shells 14a, 14b being, at the end of this stacking, secured one to the other, by soXure

  in the embodiment shown.

  When the rotary part B is driven in rotation along for example the direction of rotation indicated by the arrow F in FIG. 2, and when, according to a "pull" operation

  of the whole, the torque to be transmitted from this rotating part

  ve B at the rotating part A increases, the rotating part

  tive B rotates the rotating part A through the

  median of the elastic means acting circumferentially between it and said rotary part A.

  First of all, only the thorny springs intervene.

  gle 30 which is coupled to the lug 17 of the housing 11 directed cir-

  in the direction of rotation concerned, then when this lug 17 and the other lug 17 engage

  with the elastically deformable arms 22 of the modular flanges

  laires 20, after absorption of the corresponding initial circumferential play, these modular flanges 20 intervene in their turn, adding their effects to that of the pin spring

previous.

  Together, the friction pads 34 deploy

their effects.

  In practice, the angular movement between the parts

  rotary A, B is limited by the arms elastically de-

  fornables 22, the stiffness of which increases with said flow; angularly, depending in particular on a radial support of these arms on the edge of the washer 24 of the support 23 Corresponding

  following an arc which increases with this angular deflection

  laire, by progressive absorption of the corresponding radial clearance.

  For a decreasing evolution of the torque to be transmitted from the rotary part B to the rotary part A corresponding to

  "retro" operation of the assembly, the travel

  gular between said rotating parts reverses, and urnpro-

  cessus analogous to that described above develops, being

  understood that intervene then, by the legs 17 'of the co-

  keel l4a of shoemaker 11, first the other of the springs in.

  pin 30, then the elastically deformable arms 22 'of

modular flanges 20.

  Of course, the present invention is not limited to the embodiments described and shown, but also

globe any variant of execution.

  In particular, the axially elongated interlocking means

  Lement that includes the hub 10 of the rotary part A, instead of being formed of grooves, could be formed of ribs, the elements to be engaged on such a hub then being shaped accordingly, and / or, instead of being provided on the hub 10 of the rotary part A, such embolism means could be provided on the rotary part B.

  In. in addition to the modular flanges 20 used does not include

  not necessarily carry two elastically deformable arms,

  one for operation in. the other for a function

retro operation.

  On the contrary, and in particular when different stiffnesses

  annuities must intervene in drawdown and retro, modular flanges to one. single elastically deformable arm can

  be implemented, some for such operation in ti-

  rage, the others for one. such operation in. retro.

  Alternatively, the cutting of the two elastically deflected arms

  formable that such a modular flange possibly presents

  may be different for one. and for the other of his arms.

  In other words, when. modular flange 20 has

  two elastically deformable arms, these were not born

  ceaselessly symmetrical to each other with respect to one. plan

  axial of this flange, and / or the modular flanges used

  are not necessarily of similar configurations

  stackable, even when there are only two.

  Finally, such modular flanges 20 are however

  preferably associated in pairs, and arranged in diamond-

  trally opposite, as described above, to avoid the production of a radial elastic component, except when, for special reasons, such an elastic component

  radial is systematically sought.

  moreover, the field of application of the invention is not limited to the case where the torsion damping device concerned comprises only two rotary parts, but extends

  on the contrary in the case where it comprises a higher number of par-

  coaxial links rotatably mounted. two to two.

  In addition, its field of application. is also not limited to that of clutch friction for motor vehicles, but extends more generally to that of

  any torsion damping device.

Claims (4)

  1. Torsion damping device, in particular fric-   clutch, of the kind comprising at least two coaxial parts mounted to rotate relative to one another, within the limits of a determined angular clearance, and elastic means interposed circumferentially between said rotary parts, said ci afterwards, for convenience, elastic means with circumferential action, characterized in that, in combination, on the one hand, said elastic means with circumferential action comprise at least two elastic elements with circumferential action (20) staggered axially, each of which by a first portion (25), is linked in rotation to   a first (A) of said rotary parts, and, by a two-   th portion (27), is able to be engaged, or to come in.   taken, with the second (B) of these, and, on the other hand,   for its connection in. rotation with said first part rota-   tive, each of said elastic elements with circumferential action   tielle is, by its so-called first portion, engaged with a   interlocking means (19) axially elongated that comprises the ladi-   te first rotating part, said first portion comprises   both for this purpose a means of complementary fitting of the pre- yield.   2. Torsion damping device according to reven.dica-   tion 1, characterized in that, of similar configurations   stackable, the two elastic elements with circumferential action   differ from each other in their elasticity.   3. Torsion damping device according to the claim   tion 2, in which the elastic elements with circumferential action   in the form of flanges, which extend transversely, and which have the same cutout, characterized in that   that the flanges (20) thus forming the two elastic elements   that with circumferential action have different thicknesses your.   4. Torsion damping device according to the claim   tion 3, characterized in that the flanges (20) forming the elastic elements with circumferential action are free from any permanent connection with the second rotary part (u) so that their installation in the device results from a simple axial engagement on the first rotary part (AL) Torsion damping device according to one which   conch of claims 1 to 4, wherein means for   friction also occurs between the two rotary parts concerned, the friction means comprising at least one friction element (34), which, to be linked in rotation to a first of said rotary parts, is in   taken with an axially elongated interlocking means which   carries said first rotary part, said friction element   tement comprising for this purpose a means of interlocking   element (36) of the previous one, characterized in that the axially elongated interlocking means (19) which comprises the first   rotary part (A) is common to at least one elastic element   with circumferential action and with at least one friction element.   6) Torsion damping device according to any one   as in claims 1 to 5, characterized in that an element   (20,34), in engagement with an elongated fitting means (19)   axially which the first rotary part comprises is free   ment axially engaged on or in said fitting means.   7) Torsion damping device according to any one   as in claims 1 to 6, characterized in that the cross-section   transverse of the fitting means (19) that comprises the first   the rotating part (A) has a trapezoid profile.