FR2705417A1 - Torsion damper and locking clutch including such a damper for a hydrokinetic coupling - Google Patents

Abstract

The torsion damper for a hydrokinetic coupling includes a guide washer (40) and a thin section (60) mounted so that they can move with respect to each other circumferentially against the action of elastic members (50). The thin section (60) has a holding portion and bearing portions (365) for respectively internally holding the elastic members (50) and allowing them to bear. The bearing portions (365) are formed by virtue of bearing hollows, of wavy shape, extending from the internal periphery to the external periphery of the holding portion of the thin section (60). The locking clutch includes such a torsion damper. Application to motor vehicles.

Description

 The present invention relates to a torsion damper, for a clean locking clutch & to intervene between the casing and the turbine wheel of a hydrokinetic coupling device, in particular for a motor vehicle.

 It also relates to a locking clutch comprising such a shock absorber, which is described for example in document US-A-5,119,911. In this, the hydrokinetic coupling device comprises, arranged in the same sealed housing forming an oil pan, a torque converter and a locking clutch.

 The torque converter includes a turbine wheel, an impeller wheel and a reactor wheel.

As a reminder, it will be recalled that the turbine wheel is driven by the impeller wheel thanks to the circulation of fluid contained in the housing and that, after starting the vehicle, the locking clutch allows, to avoid the phenomena of sliding between the turbine and impeller wheels, a fastening of the connected driven shaft to the turbine wheel, with the driving shaft connected to the casing of the hydrokinetic device.

 More precisely and as shown in FIG. 1, the casing 2 forms a driving element and is suitable for being linked in rotation to the crankshaft of the engine & internal combustion of the motor vehicle.

 This casing 2, of annular shape, is composed of a first shell 5 and a second shell (visible in document US-A-5,119,911) facing the first shell and shaped so as to define an impeller & blades.

 The two shells are connected, usually by welding, to each other in a sealed manner at their outer periphery.

 The shell 5 has an annular transverse wall centrally forming a centering device. This wall carries & its external periphery threaded parts for its connection in rotation to the crankshaft.

 The locking clutch 4 is mounted in the space delimited by the turbine wheel 10, provided with blades 11, and by said transverse wall of the first shell 5.

 The locking clutch 4 comprises a torsional damper 20, a piston 21 mounted axially movable relative to the hub 18 secured to the turbine wheel 10, and at least one friction lining 24 associated with the piston 21 and suitable for being clamped between said piston 21 and here the transverse wall of the shell 5.

 The hub 18 constitutes a driven element and is integral in rotation with the driven shaft 17 belonging to the transmission of the vehicle.

 The torsion damper is integral in rotation with the hub 18 by a mounting & splines. This hub 18 is therefore stepped and comprises a grooved portion for its connection in rotation with the torsion damper 20, and a smooth portion for centering the piston 21 integral with the torsion damper 20.

 As a reminder, it will be recalled that it is under the effect of the hydraulic control pressure that the piston comes to tighten the friction lining 24 against the shell 5.

 Parts 24, 21 and 5 therefore form a clutch to the piston of which the torsion damper 20 is coupled for better filtration of vibrations.

 In this FIG. 1, the torsion damper 20 is installed at the internal periphery of the turbine wheel 10 attached by riveting to the hub 18.

In document FR 92 11400 filed on 24
September 1992 and not published & to date, a torsional damper has been described for a clean locking clutch to intervene between the casing and the turbine wheel of a hydrokinetic coupling device, of the kind comprising two coaxial parts mounted movable l relative to each other circumferentially against elastic members, namely a first part intended to be connected in rotation to the casing, and a second part intended to be connected in rotation to the turbine wheel.

 The torsion damper therefore intervenes between the casing and the turbine wheel and makes it possible to resiliently couple the casing to the turbine wheel.

 In the aforementioned document, one of the parts constitutes a guide washer, while the other part is called a veil.

 The guide washer comprises a holding portion and support portions for respectively holding the elastic members externally and allowing their support, while the web also comprises a holding portion and support portions for respectively holding the elastic members internally and allow their support.

 The number of parts of the shock absorber is therefore reduced to a minimum, the elastic members, the web and the guide washer being located at the outer periphery of the turbine wheel between the latter and the first shell.

 This arrangement is satisfactory, however, in certain cases it may be desirable to stiffen the veil even more, in particular for transmitting a greater torque.

 In fact, in this document, the support portions of the veil are made by means of lugs produced by cutting and folding the holding portion.

 The object of the present invention is to fulfill this wish and therefore to create, in a simple and economical manner, a new, more robust veil.

 According to the invention a torsion damper of the above-mentioned type is characterized in that the support portions of the web are formed & the favor of support punctures, of sinuous shape, extending from the internal periphery & the periphery external of the veil holding portion.

 According to the invention a locking clutch mounted between the casing and the turbine wheel of the hydrokinetic coupling device is characterized in that it comprises a torsional damper according to the invention.

 Thanks to the invention, the elastic members are allowed to cooperate with the edge of the punctures so that the veil transmits a greater torque and is therefore more resistant. It is also more stable in operation.

 In addition, these punctures offer greater reach to the elastic members. By virtue of this arrangement, the elastic members can comprise several stages, some of them being mounted circumferential clearance between two support punctures of the web.

 These punctures also favor the mounting of support cups for the elastic members. As a variant, this arrangement favors the mounting of concentric elastic members.

 It may also be advantageous from the manufacturing point of view to create a captive, manipulable and transportable unitary assembly comprising the torsion damper, the turbine wheel and the associated piston & the torsion damper or a set comprising the damper torsion, the piston and the housing shell & which is then connected the guide washer. As a variant, the sub-assembly may comprise only the torsional damper with its associated piston.

 In general, it is desirable to create a unitary assembly comprising at least the torsional damper.

 Thus, according to a characteristic of the invention, the guide washer is provided at its outer periphery with a plurality of clips or snap-on lugs, for cooperation with the edge of the outer periphery of the web and retained therefrom.

 Thus the veil, after assembly of the elastic members, is assembled by snap-fastening on the guide washer and it is possible to create in a first production unit said sub-assembly and to assemble it in the end thereafter, either to the wheel turbine or & its hub, or to the casing in another production unit.

 Advantageously, the support portion of the web has a rounded zone at its external periphery to facilitate snap-fastening, said roundness constituting a ramp means making it possible to easily deploy the snap-on lugs.

 Taking advantage of these tabs, which have a flange, one can then interpose a friction washer between the web and said flange. Similarly, a friction washer can be interposed between an extension of the web and the piston to create friction in the locking clutch in a simple and economical manner.

 According to another characteristic, the holding portion of the guide washer is provided with at least one bead for holding and positioning the elastic members.

 Thus said elastic members are very well maintained and do not risk being lost during the mounting of the torsion damper within the hydrokinetic coupling device.

 After mounting the torsion damper in said device, the elastic members are well positioned and work in excellent conditions.

 The guide washer can be provided with mortises at its internal periphery, for example in the form of windows, for cooperation with tenons of a disc belonging to the clutch itself.

 Thus it is possible to easily create a two-sided locking clutch and this in a simple manner.

This arrangement opens the way to a large number of applications.

The following description illustrates the invention with reference to the accompanying drawings in which
- Figure 1 is an axial sectional view of a locking clutch of the prior art mounted between the turbine wheel and one of the shells of the casing of the hydrokinetic coupling device;
- Figure 2 is a sectional view along line 2-2 of Figure 5 of the torsional damper according to the invention;
- Figure 3 shows & upper scale the lower part of Figure 2;
- Figure 4 shows the upper part of the upper part of Figure 2;
- Figure 5 is a partially cut view along arrow 5 in Figure 2;
- Figure 6 is a view along arrow 6 of Figure 2;
- Figure 7 is an enlarged view of the insert 7 of Figure 5;
- Figure 8 is a view along arrow 8 of Figure 5;
- Figure 9 is a view similar to Figure 3 for another embodiment;
- Figure 10 is a partial view along the arrow 10 in Figure 9
- Figures 11 and 12 are partial views similar to Figure 4 for other embodiments;
- Figure 13 is a diagram showing the characteristic curve of the torsion damper according to Figures 1 8;
- Figure 14 is a partial sectional view along line 14-14 of Figure 17, for another embodiment;
- Figure 15 is a partial view of the guide washer of the torsion damper of Figure 14;
- Figure 16 is a view along arrow 16 of Figure 15;
- Figure 17 is a partially cut view along arrow 17 in Figure 13;
- Figure 18 is a sectional view along line 14-14 of Figure 17 showing & reduced scale the lower part of this section;
- Figure 19 is an axial sectional view similar to Figure 2 for yet another embodiment;
- Figure 20 is a view along arrow 20 of Figure 19;
- Figure 21 is a view along the arrow 21 in Figure 19 with local cutaway to show the piston;
- Figure 22 is a partial sectional view showing the engagement means & play between the piston and a thrust ring;
- Figure 23 is a partial view similar to Figure 22 for yet another embodiment.

 In the figures illustrated, the torsional damper 20 according to the invention belongs to a locking clutch 4 for a motor vehicle. This clutch is intended to be mounted and to intervene between the turbine wheel 10 and the shell 5 of FIG. 1 and slides by its piston 21, shaped as a hub at its internal periphery for this purpose, on the hub 18, or on a push ring 126 (Figures 19 & 23) mounted on the hub 18.

 The torsion damper 20 comprises an inlet part 40 (FIG. 2) intended to be connected in rotation to the casing 2 and more precisely to the first shell 5 of the latter, an outlet part 60 intended to be connected in rotation & the turbine wheel 10 and elastic members 50 & circumferential action intervening between the two said parts 40.50. The damper 20 therefore intervenes between parts 5 and 10.

 More precisely, the inlet 40 and outlet 60 parts are mounted coaxially while being movable relative to each other circumferentially against the elastic members 50.

 The inlet part 40 forms in FIGS. 2 & 8 a guide washer 40, while the second part or outlet element 60 will hereinafter be referred to as a sail. These parts 40.60 are metallic.

 The guide washer 40 (FIGS. 2 to 8) has a holding portion 42 and support portions 145 for respectively externally holding the elastic members 50 and allowing them to be supported, while the web 60 also includes a holding portion 361 and support portions 365 for internally holding the elastic members 50 and allowing their support.

 According to the invention a torsion damper of the above-mentioned type is characterized in that the bearing portions 365 of the veil are formed by favoring punctures, of sinuous shape, extending from the internal periphery to the external periphery of the holding portion 361 of the web 60.

 In FIGS. 2 to 8, the guide washer 40 includes a transverse flange 41 attached to the face of the piston 21 facing the web 60, opposite the shell 5. This flange 41 is connected by riveting to the piston 21 here metallic. The piston 21 has extruded portions 170 through which there are openings 47 made in the portion 41.

 Then the head of the portions 170 is crushed, so that the rivets come directly from the piston 21.

The guide washer 40 is therefore disengageably connected to the casing 2 by means of the piston 21, which is here of smooth shape, the shell 5 carrying transversely for fixing at its external periphery an annular friction lining 24 for cooperation with friction with the external periphery of the piston 21, generally of transverse orientation and formation of a clutch, the piston of which is locked in rotation on the hub 18 via the torsion damper 20 as described below.

 The flange 41 is extended at its outer periphery by the annular holding and support portion 42 of the springs.

 This portion (Figure 3) forms a half-shell 42 and externally retains the elastic members 50, in particular against the centrifugal force.

 The portion 42 therefore has a rounded shape in section, which is connected at its internal periphery to the flange 41 and is extended at its external periphery by an annular rim 143 of axial orientation.

 The metallic veil 60 comprises the annular holding and support portion 361, which is extended towards the axis of the assembly & its internal periphery by a flange 162, generally of transverse orientation, provided at its internal periphery with a hub provided with teeth 163 for its rotational connection with the hub 18 with external teeth of FIG. 1.

 The flange 162 therefore extends parallel to the piston 21 and is intended to be connected to the turbine wheel 10 via its hub 18.

 The holding portion 361 also has the shape of a half-shell and internally retains the elastic members 50. The holding portions 42, 361 face each other and therefore have an annular shape. They support the organs 50 both internally and externally.

 The portion 361 is connected at its internal periphery to the flange 162 by a rounded zone and at its external periphery by a peripheral rounded zone 369 to an annular rim 368 of axial orientation.

 The rim 368 stiffens the portion 361 just as the rim 143 stiffens the portion 42. In addition, the rim 143 allows the web 60 to be guided via its rim 368. The rim 368 is locally notched at the latching tabs 243 described. below. There is thus formed a peripheral rim of axial orientation 144 which is shorter than the rim 368. The holding portion 361 therefore has on its external periphery two profiles 144 and 368 directed axially opposite the piston 21.

 The portion 361 is interrupted locally by the continuous support punctures 365 according to the invention and therefore robust. These supports 365 comprise an axial orientation portion extending radially below the rim 143 and connecting to the rim 368 by a rounded zone partly comprising the zone 369.

 Internally the axial orientation portion of the punctured 365 is connected by a rounded inclined portion, itself connected by a rounded & the internal periphery of the portion 361.

 The metal guide washer is also interrupted locally by two series of parallel legs 46, 145 forming supports for the elastic members 50.

 The tabs 145 are formed by deformation of material inwards and extend radially inwards relative to the outer peripheral rim 143, being of axial orientation.

 Thus a part of the rim 143 and of the portion 42 is knocked inwards to form the legs 145 and this with shearing of the sheet (slots of zero width). As a variant, the deformation of the material towards the inside can lead to shearing thereof with the appearance of slots. The legs 145 therefore come from the holding portion 142 and consist of punctures.

 The lugs 46 are produced by cutting and folding the transverse part 41. These lugs 46 extend axially over a short length below the lugs 145 radially in alignment with the latter and with the punctures 365.

 The guide washer 40 therefore has, overall, in section, a U shape at the level of the legs 145, 46, one of which 46 of the branches is shorter than the other, with the formation of a window below the leg 46 (figure 15). The bottom of the U is offset axially towards the turbine wheel 10 relative to the transverse part of the washer 40 (FIG. 16).

 Thus the tabs 145 are connected by a rounded portion to the axial rim 143 of the washer 40. The tabs 145 extend above the axial portion of the punctures 365, parallel to the latter. Thus the supports 365 extend, by their axial part, radially above the axis of axial symmetry of the elastic members 50 and by their inclined part intercept the axis of radial symmetry of said elastic members (Figure 4).

 These inclined parts are therefore oblique with respect to the axis of radial symmetry of the elastic members 50. It is the same in all the figures.

 The inclined parts are tilted in the direction of the flange 41 and of the piston 21 going from the internal periphery of the portion 361 to the axial part of the puncture 365 for increasing the length of the legs 46 and of said axial part of the puncture.

 Thus the punctures 365 have, in relation to their axis of symmetry in section, overall the shape of a V & rounded apex.

 Of course as a variant, it is also possible to tilt the axial parts of the punctures according to the applications. This amounts to more or less opening the V.

 Here the elastic members consist of two series of springs & coil 150,153-151. The springs 150, 153 of the first series are mounted concentrically one inside the other and are supported at each of their circumferential ends on support cups 152 (FIG. 7) having a nose penetrating inside said internal springs 153.

 These cups 152 are able to bear on the edge of the legs 46, 145 and the support punctures 365.

 As will be understood, the sinuous shape of the punctures 365 allows the legs 46 to be given maximum length.

 The cups 152 are therefore supported radially internally by the legs 46 and radially externally by the legs 145 parallel to the legs 46.

 Centrally the cups 152 are supported by the sinuous punctures 365.

 Thus thanks to the invention the veil is robust and the bearing surfaces offered by the legs 46,145 and the punctures 365 to the springs 150,153, via the cups 152, are maximum.

 According to another characteristic, taking advantage of these supports 46, 145 and 365, it becomes possible to mount a floating spring 151 between two series of supports 145, 46, 365 consecutive.

 These springs 151 belong to the aforementioned second series and therefore alternate circumferentially with the springs 150,153. The springs 151 are shorter than the springs 150, 153, being stiffer.

The springs 150, 153-151 are held by the holding portions 42, 361.

 The characteristic curve A of the shock absorber is represented in FIG. 13, (in which the transmitted torque is shown in C and in D the relative angular displacement between the inlet 40 and outlet 60 parts), and has a double slope.

 Thus in a first phase only the springs 150, 153 intervene then in a second phase, after taking up the clearances, the springs 151 make their effects felt and are compressed.

 Advantageously, according to one characteristic, the springs 150, 153 are pre-bent because they have a large circumferential length.

 According to another characteristic, the rim 143 of the retaining portion 42 is locally interrupted in favor of blind slots (FIG. 8), for the formation of latching tabs 243 having a transverse end rim 244 directed towards the axis of the together.

 The legs 243 are here full. As a variant, windows can be provided in these to improve their flexibility.

 The rim 244 is of such dimension that it is able to cooperate, by abutting, with the edge of the peripheral rim 144 of the web 60, in order to create a subassembly a height rod.

 Circumferentially the notched rim 144 has a length such that the tab can be angularly struggled inside this rim during the relative angular movement between the web 60 and the washer 40.

 The tabs 243, thanks to their flange 244, therefore retain the web 60 so that it is possible to create, after mounting the springs 150, 153-151 and the cups 152, by snapping the web 60 into the tabs 243, a sub- captive, manipulable and transportable unit assembly comprising the piston 21 and the torsion damper 20. Finally, this subset is threaded onto the hub 18. It will be appreciated that the mounting of the web 60 with the washer 40 by snap-fastening is facilitated by the fact that this washer 40 is less thick than web 60 so that the tabs 243 are easily raised when the web 60 is snapped on.

 It will be appreciated that the rounded area 369 of the web 60 facilitates the lifting or deployment of the legs 243.

This zone 369 therefore constitutes a ramp making it possible to lift the tabs 243 during the relative approaching of the guide washer 40 relative to the web 60.

 After final assembly of the sub-assembly, a slight clearance exists between the rim 244 and the edge of the rim 144.

The rim 244 also limits the backward movement of the web 60, thus avoiding any interference with the turbine wheel 10.

 It will be noted that the piston 21 has stiffening ribs 55.

 Here six legs 145 and therefore six punctures 365 and six legs 46 are provided, as well as three springs 150 and three springs 151.

 The arrangement is regular as shown in Figures 5 and 6.

 Of course it all depends on the applications.

 Of course we can take advantage of the creation of the latching tabs 243,244 to axially wedge a washer 95 between the flange 244 and the outer periphery of the support portion 361 (Figures 9 and 10).

 In this case the external periphery 461 of the holding or support element 361 is for the most part of transverse orientation at the level of the springs 150, only a small part of the rim 368 is kept in the vicinity of the support punctures.

 The washer 95 carries locally at each tab 243 a friction lining 195 fixed to said washer 95 for example by gluing. The lining 195 is suitable for rubbing against the portion 461.

 The lining 195 is wider circumferentially than the tab 243 for proper application of the lining 195 against the portion 461.

 Of course, it is possible to reverse the structures and glue the lining 195 on the portion 461.

 Similarly, an annular friction lining 295 can be interposed between the flange 162 and the piston 21, preferably at the internal periphery of these (FIG. 9). In this case, the flange 162 constitutes an elastic element with respect to the piston 21 stiffened by the ribs 55. It is thus possible to easily tighten elastically the lining 295 between the piston 21 and the flange 162.

 Thus, during the relative angular movement, between the web 60 and the piston 21 integral with the guide washer 40, friction occurs between the lining 295, secured to one of the elements 162,21, and the other of the elements 21,162 not secured to the lining. Another friction occurs between the linings 195 and the part 461 of the support element 361.

 It will be noted that here the friction lining 24 is integral with the piston 21. Of course it depends on the applications.

 It will also be noted that the latching tabs 243 make it possible to block the washer 95 in rotation. In fact, this washer has, projecting outwards, radial tabs for supporting the linings 195 (FIG. 10). These tabs are overhung by the tabs 243, so that by cooperation of shapes a rotation blocking of the washer 95 is obtained, which is also blocked axially between the flange 244 and the part 461 of the support element 361.

 It will be noted (FIG. 10) that the washer 95 passes below the flange 368. In this embodiment (FIG. 10) the flange 244 is notched, here in two places referenced in 196, in order to be able to lift the legs 243 using a tool to allow the snap-fit mounting of the web and the washer 95 with the guide washer 40 fitted with the springs 150 and the piston 21.

 Of course, the present invention is not limited to the embodiment described. In particular, the veil 60 can be simplified and its flange removed.

 Thus in FIG. 11, the generally transverse part 241 of the guide washer 40, attached to the piston 221, is fixed by rivets 270 to the piston 221 carrying the friction lining 24. This piston has at its external periphery an annular rim of axial orientation in contact with which comes the holding portion 242 of the washer 40.

 The piston 221 belongs to the locking clutch and is capable of tightening the friction lining 24 between the latter and the shell 5 of the casing 2.

 This portion 242 is stamped at 343 for holding and positioning the springs 50 according to a characteristic of the invention. The springs 50 are locked axially in one direction by the zone of connection of the holding portion 242 to the internal part 241 of the guide washer 40, here its transverse part 241, and in the other direction by the deep-drawn 343 , in the form of a rounded bead, described below.

 This bead 343 is formed at the connection of the annular holding portion 242 with an annular peripheral rim of axial orientation 348 for stiffening extending said portion.

 Here the web 60 is fixed by welding at 563 directly to the turbine wheel 10. The support portions 565 of the springs 50 having a sinuous shape analogous to that of FIG. 1, these portions 565 are connected by a rounded shape & the portion of attachment and support 562 of the web 60 to the turbine wheel.

 The portion 562 follows the shape of the turbine wheel 10.

 In FIG. 12, the web 60 is also fixed directly by welding at 663 to the turbine wheel 10.

This welding is carried out at the connection rounding, which has the holding part 661.

 As in FIGS. 1 to 8, the guide washer 40 has clip tabs 243 for their retention relative to the web 60 and more particularly for cooperation of the transverse rim 244 of the tabs 243 with the edge of the outer periphery of the web 60.

 This veil 60 has at its internal and external periphery an axial orientation portion. These axial portions are successively connected to each other by a first rounded support zone, a transverse portion and a second rounded portion 662. It is this peripheral portion of revolution 662 which will facilitate the snap-on mounting of the washer. guide 40 previously equipped with springs 50 on the web.

 The portion 662 therefore allows the legs 243 to be raised and is therefore connected to an annular peripheral rim of axial orientation of the web 60.

 In this figure it is the web 60 which carries the guide washer unlike the embodiments of Figures 2 & 10.

 The sinuous support punctures 665 extend between the two said axial portions.

 Here the transverse part 341 of the guide washer 40 is extended at its internal periphery by an axial orientation rim 342 perforated for the formation of mortises 380 and mounting of a disc 62 bearing & securing on each of its faces friction linings 24 clean & be clamped between the shell 5 and the piston 321 to form a clutch. The washer 40 is therefore disengageably connected, via the piston 321, & the shell 5.

 The guide washer 40 is therefore connected to the input part of a clutch proper, said input part consisting of a disc provided at its external periphery with pins 167 meshing with the openings 380, here closed, (visible at Figure 20 described below).

 The piston 321 is locked in rotation on the shell 5 as described below.

 Thus the torsion damper is mounted in series with the clutch itself.

 It is therefore created a two-sided locking clutch for transmitting a large torque and compact axially because the piston 321 extends in the middle part of the turbine wheel 10, while the torsion damper is located at the periphery external of said turbine wheel 10.

 Of course (FIG. 14), the guide washer 40 can be fixed directly to the shell 5, which has for this purpose extruded rivets 70 passing through the openings 47 of the guide washer 40.

 In this case the disc 62 (FIG. 17) meshes with these tenons 167 with rounded slots 480 provided in the holding portion 761. These slots 480, in the form of mortises, are more numerous than the slots 764 associated with the portions of support 765, of sinuous shape according to the invention.

 As in FIG. 12, the tabs 243 cooperate with the edge of the outer peripheral edge 368 of the web 60 to retain the latter and form a sub-assembly comprising the torsional damper 20 and the shell 5.

In this case, the peripheral rim 368 is not notched unlike the embodiment of Figure 2 because there is axially enough space.

 In FIG. 14, it is the guide washer 40 which retains the veil and carries it, while in FIG. 12 it is the reverse.

 It will be noted that the guide washer has tongues 148 for fixing it to the shell 5 and tongues 149 in which the lugs 46 and 145 are formed, with the formation of a stamping, the lugs 46, 145 being offset axially towards the wheel 10.

 A bead 343, here split, is also provided in the guide washer 40, as in FIGS. 11 and 12, to hold and position the springs 50.

 As best seen in FIG. 16, the beads 343 extend for the most part circumferentially on either side of the legs 145 and have a circumferential length such that it takes account of the relative angular movement between the web 60 and the washer 40 .

 In all cases, the length of the beads is such that the relevant circumferential end of the spring 150 always remains in contact with this bead 343.

 Of course the position of this bead 343 takes account of the dimension of the springs 150.

 Here the beads 343 do not affect the support and central parts of the legs 145.

 Here the elastic members 50 consist solely of coil springs 150,153 mounted concentrically and extending between two consecutive punctures 765. These springs are supported on the cups 152.

 As in FIG. 5, these springs 150, 153 are supported by the holding portions 242 of the guide washer 40 and 761 of the web 60.

 It will be noted that the disc 62 with its linings 24 is intended to be clamped between the piston and a counter piston 31 as in the aforementioned document FR 92 11400.

 A two-sided locking clutch is thus created as in FIG. 12, the web 60 being locked in rotation on the hub 18 in a disengageable manner thanks to the counter-piston 31 secured to the hub 18 and to the turbine wheel 10.

 Of course, various combinations are possible.

 Thus in FIG. 19, the web 60 has a configuration similar to that of FIG. 2, while the guide washer 40 has a configuration similar to that of FIG. 12 and the elastic members a configuration of that of FIG. 17.

 Of course, a single spring 150 can be provided between two consecutive punctures 365.

 A flange 262 extends parallel to the piston 321 and extends inwards the holding portion 361 in which the punctures are made 365. The flange 262 is directly fixed by riveting to the hub 18 of the turbine wheel 10.

 The disc 62 therefore has tenons 167 which mesh with the openings 380 affecting the internal periphery of the transverse part 341, as well as the rim of axial orientation referenced at 342 & FIG. 12.

 The friction linings 24 of the disc 62 are adapted to be clamped between the piston 321 and a clean reaction part 322 & to be fixed by riveting to the shell 5. All these parts belong to the locking clutch.

 Of course we can reverse the structures, that is to say that the linings 24 may be integral with the piston 321 and the part 322, the disc 62 being devoid of linings. It is the same in all the variants where two linings 24 are arranged on either side of the disc 62. These linings can be integral with the parts between which the disc 62 and linings 24 assembly is clamped.

 The part 322 avoids precisely machining the shell 5.

 Thus, this part 322 has openings 47, for passage of rivets coming from the shell 5. This part 322 has, at its internal periphery, tabs 324 which mesh with notches 325 (FIG. 20) formed in favor of grooves 27, which have a bi-material thrust ring 126 mounted on the hub 17. This ring is thus connected in rotation to the casing 2 and to the shell 5 via the part 322.

 As is known, the grooves 27 are intended to pressurize and depressurize the chamber 23 delimited by the piston 321 and the part 322. Another chamber 23 being delimited by the web 60 and the piston 321.

 Thus by variation of the pressures in the chambers 22 and 23, the piston 321 is moved in one direction or the other to tighten or loosen the linings 24.

 Axially the ring 126 is interposed between the flange, which has in one piece the turbine hub 18, and the shell 5.

 The piston 321 slides along this ring 126 and is linked in rotation to the part 322 by means of pins 323 which it has at its internal periphery, said pins 323 penetrating into complementary openings made in part 322 offering a face friction At its outer periphery for the friction linings of the disc 62, more precisely for tightening the linings 22 integral with the disc 62 between the piston 321 and the part 322.

 The piston 321 is therefore locked in rotation on the shell 5 and slides axially along the ring 126.

 The guide washer 40 has latching tabs 243 as mentioned above.

 Of course it is possible to remove the part 322 and in this case the friction linings of the disc 62 are suitable for being clamped between the piston 421, locked in rotation on the shell 5 via the welded ring 126, and the shell 5 of the 'proper clutch (Figure 22).

 To do this, the piston 421 is mounted axially movable on the ring 126 while being linked to the latter by means of meshing with play 423.

 These meshing means are formed by means of a part 422 fixed by welding to the piston 421.

 In this case, the ring 126 is fixed by welding to the shell 5.

 More specifically, the part 422 is provided at its internal periphery with grooves capable of coming into engagement with grooves formed at the external periphery of a radial flange 424, which for this purpose has the ring 126.

 There is thus engagement of the part 422 with the flange 424. The part 422 is fixed by welding to the face of the piston 421, turned away from the shell 5.

 Of course, the part 422 can be fixed by riveting on the piston 421.

 Of course (FIG. 23) the structures can be reversed, the part 422 then being placed on the face of the piston 421 facing the shell 5.

 It will be appreciated that the embodiments of Figures 22 and 23 are suitable for connecting the piston 321 of Figure 12 in rotation with the shell 5 and it is for this reason that in Figure 23, there is shown schematically, the disc 62 adapted to mesh with the closed openings, in the form of mortises 380, of FIG. 12.

 The piston 421 is therefore in FIGS. 22 to 23 suitable for tightening the friction linings 24 of the disc 62 between the latter and the shell 5, belonging to the locking clutch.

 As a variant, the connection can be made by tangential tongues or by cooperation of shapes.

 In all cases, the torsion damper comprises only two metal parts, easily achievable with the press, for the maintenance of the elastic members, the holding portions of said parts being opposite one another with an axis of symmetry inclined with respect to the radial axis of symmetry of the elastic members 50.

Claims (37)

 1- Torsional damper for a clean locking clutch (4) & working between the turbine wheel (10) and the casing (2) of a hydrokinetic coupling device (1), of the type comprising two coaxial parts (40, 50) mounted movable with respect to each other circumferentially & against elastic members (50), namely a first part forming a guide washer (40), and a second part (60), called a veil, wherein the guide washer has a holding portion (42,242) and support portions (145) for respectively externally holding the elastic members (50) and allowing their support, while the web (60) also includes a portion of holding (361,461,561,661,761) and support portions (365,565,665,765) to respectively maintain internally the elastic members (50) and allow their support, characterized in that the support portions (365,565,665,765) of the web (60) are formed in favor punctured s support, sinuous in shape, extending from the internal periphery to the external periphery of the holding portion (361,461,561,661,761) of the web (60).  2- shock absorber according to claim 1, characterized in that said punctures generally have a V shape.  3- shock absorber according to claim 1 or 2, characterized in that said support punctures comprise a portion of axial orientation connected by a rounded zone (369,662) to a peripheral annular rim (144,368) of axial orientation, which has said holding portion, and in that said axial orientation portion of the support puncture (365,565,665,765) is connected by a rounded & an inclined portion, itself connected to a rounded internal periphery of said holding portion.  4- shock absorber according to claim 3, characterized in that said portion of axial orientation of the support puncture (365,565,665,765) extends above the axis of axial symmetry of the elastic members (50) and in that said inclined portion of said puncture is oblique to the axis of radial symmetry of said elastic members (50) and intercepts said axis of radial symmetry.  5- shock absorber according to any one of claims 1 to 4, wherein the guide washer (40) is interrupted locally by two series of legs (46,145) forming supports for said elastic members, the legs (46) of the second series extending axially below the legs (145) of the first series from the holding portion (42,242) of the guide washer (40), characterized in that the legs (145) of the first series are formed by material deformation inward, and in that said tabs (145) extend axially above the axially oriented portions of the support punctures (365,565 ...) of the web (60).  6- shock absorber according to claim 5, characterized in that the guide washer (40) has generally, in section, a U-shape, one of the branches of which is shorter than the other, with the formation of a window below a leg (46) of the second series of legs (145,46).  7- Shock absorber according to any one of claims 1 to 6, in which the elastic members (50) consist of coil springs, characterized in that at least some of said springs & coil (150,153) bear at their circumferential ends on the support punctures (365,565 ...) by means of support cups (152).  8- Shock absorber according to claim 7, characterized in that some of the coil springs (151) are mounted floating between two series of support punctures (365,565 ...) while being retained by the holding portions (42,242-361, ...) of the guide washer (40) and of the web (60).  9- Shock absorber according to claim 7 or 8, characterized in that the coil springs (150,153) are pre-bent.  10- Shock absorber according to any one of claims 1 to 9, characterized in that the holding portion (242) of the guide washer (40) is stamped for holding and positioning of the elastic members (150,153).  11- Shock absorber according to claim 10, characterized in that the elastic members (50) are locked axially in one direction by the connection zone of the holding portion (42,242) & the internal part (242,341) of the guide washer ( 40) and in the other direction by the stamp (343).  12- Shock absorber according to claim 11, wherein the holding portion (242) is extended by an annular peripheral rim of axial orientation (348), characterized in that the stamping (343) is formed at the connection of the holding portion (342) with said flange (348).  13- Shock absorber according to claim 5 or 12, characterized in that two beads (343) extend circumferentially for the most part on either side of a tab (145) of the first series.  14- Shock absorber according to claim 13, characterized in that the beads (343) do not affect the support parts and the central part of said legs of the first series.  15- Damper according to any one of claims 1 to 14, wherein the guide washer has at its outer periphery an annular flange (143,348) of axial orientation, characterized in that said flange (143,348) is interrupted locally for formation of latching tabs (243) having a transverse flange (244) directed towards the axis of the assembly, and in that said flange (244) is clean & cooperating with the edge of said peripheral flange (143,348) of the web ( 60) for the formation of a unitary unit which can be handled and transported.  16- Shock absorber according to claim 15, characterized in that said peripheral flange (348) of the web (60) is notched at the level of the latching tabs (243), so that a peripheral flange of axial orientation is formed (144) shorter than said flange (348).  17- Shock absorber according to claim 15 or 16, characterized in that the support punctures are connected to said peripheral flange (144,348) by a rounded zone (369,662) and in that the flange (244) of the latching tabs (243 ) is capable of cooperating with said rounded zone during the snap-fitting assembly of the guide washer (40) with the web (60).  18- Shock absorber according to claim 15 or 16, characterized the rim (244) of the latching tabs (243) is notched in order to be able to lift the tabs using a tool.  19- Shock absorber according to any one of claims 15 to 18, characterized in that a plain washer (95), associated with at least one friction lining (195) is interposed between the flange (244) of the latching tabs and the outer periphery of the holding portion (361).  20- Shock absorber according to claim 19, characterized in that the external periphery (461) of said holding portion (361) is partly transverse orientation for cooperation with the said friction lining (s) (195).  21- Shock absorber according to any one of the preceding claims, in which the guide washer (40) has a transverse part (341), characterized in that said transverse part (341) is extended at its internal periphery by a flange of axial orientation (342) perforated for forming mortises (380) and mounting a disc (62) endowed with its external periphery with pins (167) meshing with said openings (380).  22- Shock absorber according to any one of claims 1 & 20, characterized in that the holding portion (361) of the web (60) has mortises (380) for mounting a disc (62) endowed with its external device studs (167) meshing with said mortises.  23- Clean locking clutch & intervene between the casing (2) and the turbine wheel (10) of a hydrokinetic coupling device, in particular for a motor vehicle, of the type comprising a piston (21) generally of transverse orientation, characterized in that it comprises a torsion damper according to any one of claims 1 & 20, and in that the guide washer (40) is fixed to said clean piston (21) & tighten a friction lining (24) between the latter and a shell (5) belonging to the casing (2) of the hydrokinetic coupling device.  24- Locking clutch according to claim 23, characterized in that the holding portion (361) of the web (60) is extended towards the axis of the assembly by a flange (162) generally of transverse orientation, in that that a friction lining (295) is interposed between said piston (21) and said flange (162), and in that said flange is adapted to be locked in rotation on a hub (18) integral with the turbine wheel ( 10).  25- Locking clutch mounted between the casing (2) and the turbine wheel (10) of a hydrokinetic coupling device, in particular for a motor vehicle, of the type comprising a piston (21) generally of transverse orientation, characterized in that it comprises a torsional damper according to claim 22, in that the guide washer (40) is fixed to a shell (5) of the casing (2) of the hydrokinetic coupling device, and in that the web (60) is set in disengageable rotation on a hub (18) integral with the turbine wheel (10) by means of a counter-piston (31) integral with the hub (18) and tightening of linings friction, integral with the disc (62), between the piston (21) and the counter-piston (31).  26- Locking clutch mounted between the casing (2) and the turbine wheel (10) of a hydrokinetic coupling device, in particular for a motor vehicle, characterized in that it comprises a torsion damper according to claim 21.  27- Clutch according to claim 26, characterized in that the web (60) is fixed by welding (563,663) to the turbine wheel (10).  28- A clutch according to claim 26, characterized in that the holding portion (361) of the web (60) is extended towards the axis of the assembly by a flange (262) generally of transverse orientation suitable for being connected & a hub (18) integral with the turbine wheel (10).  29- A clutch according to claim 28, characterized in that the hub (18) carries a push ring (126), and in that a piston (321,421) is slidably mounted on said push ring (126).  30- Clutch according to claim 29, characterized in that the piston (321) has at its internal periphery studs (323) penetrating into complementary openings formed in a part (322) offering a friction face at its external periphery for the tightening the friction linings (24) integral with the disc (62) between said part (322) and said piston (321).  31- Clutch according to claim 30, characterized in that the part (322) is secured to a shell (5) of the housing (2) and has & its internal periphery of the legs (324) which mesh with notches (325) formed through grooves (27), which has the push ring (126).  32- Clutch according to claim 29, characterized in that the thrust ring (126) is secured by welding & the shell (5) of the housing (2), in that a single piece (422) is fixed on the piston ( 421), and in that play engagement means (423) intervene between said part (422) and the thrust ring (126).  33- clutch according to claim 32, characterized in that the part (422), integral with the piston (421), has & its internal periphery of the splines clean to come into engagement with splines formed at the external periphery of the thrust ring (126).  34- Clutch according to claim 33, characterized in that said part (422) is arranged on the face of the piston (421) facing the shell (5).  35- Clutch according to any one of claims 32 to 34, characterized in that the piston (421) is adapted to come to clamp friction linings integral with the disc (62) between the latter and the shell (5) of the housing (2).  36- Locking clutch mounted between the casing (2) and the turbine wheel (10) of a hydrokinetic coupling device, in particular for a motor vehicle, characterized in that it comprises a torsion damper according to any one claims 1 & 20, in that the web (60) is fixed by welding (563) to the turbine wheel (10), and in that the guide washer is fixed & a piston (221) suitable for clamping a friction lining (24) between the latter and a shell (5) of the casing (2).  37- Clutch according to claim 36, characterized in that the support punctures (565) are connected by a rounded shape & a fixing and support portion (562) of the web (60) to the turbine wheel (10), and in that said portion (562) follows the shape of the turbine wheel (10).