FR2816019A1 - HYDROKINETIC COUPLING APPARATUS, PARTICULARLY FOR MOTOR VEHICLE - Google Patents

Abstract

The invention concerns a hydrokinetic coupling apparatus (10) comprising a front crankcase (20) provided with a wall (24), designed to be linked in rotation with a driving shaft, a front turbine wheel (50), designed to be linked in rotation with a driven shaft, including a first part forming a torus (52), and a second part (54) linking the torus in rotation with the driven shaft, a hydraulic circuit formed by a rear impeller wheel (40) and the torus (52), a piston (31), mounted mobile and arranged axially between the crankshaft (20) wall (24) and the turbine wheel (50), and defining with said wall a control chamber (34), radially delimited externally by at least a friction element (33), an inner annular space (100), located radially beneath the hydrodynamic circuit, and at least a vibration damping device (60), interposed between the driven and driving shafts, and housed in the annular space (100) and comprising at least an elastic member (64) adapted to co-operate with input and output elements, and at least an element of the second linking part (92, 93) of the turbine wheel (50) co-operates with at least an elastic member (64) of the damping device (60).

Description

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 The present invention relates to a hydrokinetic coupling device, in particular for a motor vehicle.

 The present invention relates more particularly to a hydrokinetic coupling device of the type shown in document US-A-6. 016. 894.

 This document describes and represents a device of the type comprising a front casing provided with a wall, generally of radial orientation, suitable for being linked in rotation to a driving shaft, a front turbine wheel, suitable for being linked in rotation to a driven shaft, comprising a first radially outer part forming a torus and a second radially inner part for rotationally connecting the torus with the driven shaft, a hydrodynamic circuit formed by at least one rear impeller wheel and the torus of the turbine, a piston, generally of radial orientation, mounted movable and arranged axially between the casing wall and the turbine wheel, and defining with said wall a control chamber, delimited radially externally by at least one friction element, a space inner ring located radially below the hydrodynamic circuit, and at least one vibration damping device, intervening between the driven shafts and leading and which is housed at least partially axially in the annular space and comprising at least one elastic member with circumferential action which is capable of cooperating with input and output elements.

 It is known, for example from document FR-A-2,453. 335, to arrange radially inside, between the piston and the turbine wheel assembly, a torque converter, a vibration damping device, usually called torsion damper. Such an arrangement has the drawback of having a relatively large axial size.

 Document US-A-6. 016. 894 proposes, to reduce the axial size of such an apparatus, to arrange the vibration damping device in an annular space situated radially below the

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 hydrodynamic circuit, which is defined by the turbine and impeller wheels, so that the damping device extends axially under the turbine wheel and at least partially under the impeller wheel.

 To do this, the second radially inner part of the turbine wheel, which extends the first part forming the torus of the turbine wheel, has a recess which delimits, axially towards the rear, the annular space in which the damping device.

 This document describes various embodiments in which, for both double-sided and single-sided devices, the vibration damping device successively comprises, arranged axially from front to rear, a first front guide washer, a median web, a second rear guide washer and the second radially inner part of the turbine wheel. Elastic circumferential members are interposed between the two front and rear guide rings, which are connected to each other axially and in rotation, the guide rings forming the input element of the damping device, and the web forming the outlet member.

 More specifically, the two front and rear guide rings, integral in rotation by means of rivets, are linked by means of rotation-type driving of the teeth type, that is to say the friction disc in the case of a device of the two-sided type, that is to say the piston in the case of a single-sided type device, and they include elements for attacking the elastic members which are attached to the guide washers. The guide washers are here mounted to rotate freely relative to the hub, that is to say relative to the driven shaft.

 These driving elements cooperate and drive in rotation the elastic members arranged in windows of the web which is linked in rotation to the hub of the turbine wheel, as well as the second radially inner part of the turbine wheel, and which constitutes the output element of the damping device.

 As a variant, this document proposes that the second radially inner part of the turbine wheel is connected, by means of rivets, to the second rear guide washer, that is to say to the input element of the device 'amortization.

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 Such a damping device is known per se and it makes it possible in particular to filter vibrations, due to the acyclisms of an internal combustion engine in the case of an application to a motor vehicle, between the driving and driven shafts.

 However, in the various embodiments described in this document, the axial size resulting from the arrangement of the damping device in the annular space is not entirely satisfactory.

 Indeed, such a damping device has a still significant axial size since it comprises, axially from front to rear, at least four parts, that is to say more precisely, two guide washer, a web and the second radially inner part of the turbine wheel.

 Such a device therefore comprises numerous parts for the production of the damping device and this results, in addition to a large axial size, a complex and expensive manufacture, in particular due to the assembly of the different parts.

 In addition, when the second radially inner part of the turbine wheel is linked in rotation to the hub, that is to say to the output element of the damping device, it is necessary to provide an axial space, between this part and the rear guide washer, in order to avoid any direct contact between these parts, which has the effect of increasing the axial size. It is the same when the second radially inner part of the turbine wheel is linked in rotation to the rear guide washer, that is to say to the input element, since these two parts are linked axially to the rear of the elastic members by rivets, which increases the axial size of the entire damping device.

 The present invention aims to provide a hydrokinetic coupling device of the type mentioned above, which overcomes the drawbacks which have just been mentioned.

 To this end, the invention provides a hydrokinetic coupling device, in particular for a motor vehicle, of the type comprising:

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 a front casing provided with a wall, generally of radial orientation, suitable for being linked in rotation to a driving shaft; a front turbine wheel, suitable for being linked in rotation to a driven shaft, comprising a first radially outer part forming a torus, and a second radially inner part for rotating connection of the torus with the driven shaft; a hydrodynamic circuit formed by at least one rear impeller wheel and the torus of the turbine wheel; a piston, generally of radial orientation, mounted movable and arranged axially between the casing wall and the turbine wheel, and defining with said wall a control chamber, delimited radially externally by at least one friction element; an interior annular space, located radially below the hydrodynamic circuit; at least one vibration damping device, intervening between the driven and driving shafts, and housed at least partially axially in the annular space and comprising at least one elastic member with circumferential action which is capable of cooperating with input elements , and outlet, characterized in that at least one element of the second radially inner connecting part of the turbine wheel cooperates with at least one elastic member of the damping device.

 Thus thanks to the invention, on the one hand the axial size of the device, in particular of the vibration damping device, is reduced, and on the other hand the number of parts required, which makes it possible to perform the function of amortization at lower cost.

 Advantageously, the damping device comprises, axially from front to back, less than four coaxial parts forming the input and output elements of said device. In fact, according to the invention, the second radially inner part for rotationally connecting the toroid is integrated into the damping device to constitute one of these elements, that is to say either at least one of the guide washer, or the middle veil of said

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 device, so that the driving element of the second radially inner part cooperates with at least one elastic member.

 Advantageously, the damping device comprises only two coaxial parts, respectively forming the input element and the output element of the device, said parts being mounted angularly movable relative to each other against d 'elastic members with circumferential action, and said elastic members then working in shear with the element of the second radially inner connecting part which constitutes one of these two parts.

 Advantageously, the element of the second radially inner connecting part, said element for attacking the elastic members, cooperates directly with at least one elastic member.

 According to other characteristics of the invention: - the second radially inner connecting part comprises portions shaped to accommodate at least partially axially the elastic members; - The second radially inner connecting part extends generally in the mean plane in which the elastic members act; - At least one element of the second radially inner connection part cooperating with the elastic members extends generally tangentially opposite the opposite circumferential ends of the elastic members; - At least one element of the second radially inner connection part cooperating with the elastic members extends generally axially relative to the elastic members; - The element is constituted by at least one boss, in particular by a boss produced by stamping of the second radially inner connection part; - The element is constituted by at least one tab, in particular by a tab produced by cutting and folding of the second radially inner connection part; - The second radially inner connecting part is made in one piece with the torus of the turbine wheel;

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la seconde partie radialement intérieure de liaison et le tore de la roue de turbine sont deux pièces distinctes liées en rotation ; la liaison en rotation de la seconde partie radialement intérieure de liaison et du tore de la roue de turbine est réalisée radialement globalement au-delà des organes élastiques ; la seconde partie radialement intérieure de liaison est liée en rotation avec l'arbre mené par l'intermédiaire d'un moyeu de turbine ; le tore de la roue de turbine comporte des aubes, et en ce que la seconde partie radialement intérieure de liaison est formée en une seule pièce avec les aubes de la roue de turbine ; le dispositif d'amortissement des vibrations comporte, axialement d'avant en arrière pour formation des éléments d'entrée et sortie du dispositif d'amortissement, une première rondelle de guidage avant, un voile et une deuxième rondelle de guidage arrière, et en ce que la seconde partie radialement intérieure de liaison de la roue de turbine constitue l'une au moins des rondelles de guidage ou le voile du dispositif d'amortissement ; - l'appareil comporte un disque de friction interposé axialement entre la paroi de carter et le piston, et en ce que ce disque comporte des moyens d'entraînement en rotation avec un élément d'entrée ou de sortie du dispositif d'amortissement des vibrations ; et - au moins une portion de la seconde partie radialement intérieure de liaison s'étend radialement à l'intérieur de la première partie formant tore de la roue de turbine pour constituer un déflecteur.

the second radially inner connecting part and the torus of the turbine wheel are two separate parts linked in rotation; the rotational connection of the second radially inner connection part and of the torus of the turbine wheel is carried out radially generally beyond the elastic members; the second radially inner connection part is linked in rotation with the driven shaft by means of a turbine hub; the torus of the turbine wheel has blades, and in that the second radially inner connecting part is formed in one piece with the blades of the turbine wheel; the vibration damping device comprises, axially from front to back for forming the input and output elements of the damping device, a first front guide washer, a web and a second rear guide washer, and in this that the second radially inner connecting part of the turbine wheel constitutes at least one of the guide washers or the web of the damping device; - The apparatus comprises a friction disc interposed axially between the casing wall and the piston, and in that this disc comprises means for driving in rotation with an input or output element of the vibration damping device ; and - at least a portion of the second radially inner connection part extends radially inside the first toroid portion of the turbine wheel to form a deflector.

 Other characteristics and advantages of the invention will appear on reading the detailed description which follows for the understanding of which reference will be made to the appended drawings in which: - Figure 1 is a half-view in axial section of a first embodiment of a hydrokinetic coupling device, according to a first example of implementation of the principles of the invention in the case of a device of the two-sided type;

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qui illustrent trois variantes de réalisation de la figure 14 ; la figure 18 est une vue partielle en coupe axiale, d'un appareil bifaces du type de celui illustré à la figure 1, qui illustre un cinquième mode de réalisation dans lequel la seconde partie Figures 2 and 3 are exploded perspective views, respectively front and rear, of an apparatus according to Figure 1; Figure 4 is a partial view in axial section of a two-sided device of the type illustrated in Figure 1, which illustrates a second embodiment in which the damping device comprises two front and rear guide washers, of which at least one is constituted by the second radially inner part for rotationally connecting the torus, a veil and elastic members; Figures 5 to 7 are views similar to that of Figure 4 which illustrate three alternative embodiments of Figure 4; Figure 8 is a partial view in axial section of a two-sided device of the type illustrated in Figure 1, which illustrates a third embodiment in which the elastic members of the damping device work in shear between an element d input and an output element, the second radially inner rotational connection part of the torus constituting one of these two elements; FIG. 8A illustrates an alternative embodiment in which the radially inner end of the second radially inner rotational connection part of the torus constitutes a front flange of one of the needle stops; Figures 9 to 13 are views similar to that of Figure 8 which illustrate three alternative embodiments of Figure 8; FIG. 14 is a partial view in axial section, of a two-sided device of the type illustrated in FIG. 1, which illustrates a fourth embodiment in which the second radially inner connection part and the torus of the turbine wheel are two separate parts linked in rotation; Figures 15 to 17 are views similar to that of Figure 14

which illustrate three alternative embodiments of Figure 14; Figure 18 is a partial view in axial section, of a two-sided device of the type illustrated in Figure 1, which illustrates a fifth embodiment in which the second part

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 radially inner connection in rotation of the torus constitutes the median web of the damping device; - Figures 19 and 20 are partial views in axial section of a sixth embodiment and a variant, according to a second example of implementation of the principles of the invention in the case of an apparatus of the type sided.

 In the description which follows, identical, similar or analogous components will be designated by the same reference numbers.

 According to a known design, for example from document WO-A-94/07058, to which reference may be made for more details, a hydrokinetic coupling device 10 rotatable around an axis of axial symmetry XX, comprises, arranged in a same housing filled with a fluid such as oil and forming a casing 20, a hydrodynamic converter or coupler and a locking clutch 30, usually called lock-up, comprising a vibration damping device 60, also called torsional damper.

 FIG. 1 represents a hydrokinetic coupling apparatus 10 according to a first example of implementation of the principles of the invention to an apparatus of the two-sided type, which will be described below and for the understanding of which reference will be made to FIGS. 2 and 3 on which certain referenced elements will be better visible.

 The casing 20, here metallic, constitutes a driving element and it is capable of being linked in rotation to a driving shaft, namely for example the crankshaft (not shown) of an internal combustion engine in the case of an application to a motor vehicle.

 The casing 20, of generally annular shape, consists of two half-shells, respectively a first front half-shell 21 and a second rear half-shell 22, which face each other and are tightly fixed to their external periphery, usually by a welding operation, the bead of which is visible at 23 in FIG. 1.

 As illustrated in FIG. 1, the first front half-shell 21 is capable of being linked in rotation to the driving shaft and it is essentially constituted by an annular wall 24 which is generally of transverse orientation, that is to say which extends in a radial plane perpendicular to

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 the axis XX of the device, and which is extended on the one hand, at its external periphery by a first cylindrical wall in the form of an annular skirt 25, generally of axial orientation towards the rear, and on the other hand to its internal periphery by a second cylindrical wall in the form of an annular skirt 26, generally of axial orientation towards the front.

 The annular wall 24 comprises means 200, for example of the screw-nut type, for its connection with a flywheel (not shown) integral with the driving shaft, and is advantageously, at its outer periphery, axially offset rearward for integrate these means 200 into the general axial size of the device.

de la partie la plus en avant de la paroi annulaire 24, en sorte que le volant puisse être agencé axialement au plus prêt de ladite paroi 24. Les moyens 200 sont ici constitués d'une part, par une partie formant écrou 201 et apte à recevoir des moyens de fixation tels que des vis, et d'autre part une plaque de support 202, dont est solidaire la partie formant écrou, qui est rapportée par soudage sur la paroi annulaire 24. Preferably, these means 200 do not extend axially beyond

of the most forward part of the annular wall 24, so that the flywheel can be arranged axially as close as possible to said wall 24. The means 200 here consist on the one hand, by a part forming a nut 201 and capable of receiving fixing means such as screws, and on the other hand a support plate 202, of which the nut part is integral, which is attached by welding to the annular wall 24.

 The second rear half-shell 22 is suitable for being linked in rotation to a driven shaft and it is constituted by an annular wall 27 which is generally of transverse orientation and which is extended, on the one hand at its external periphery by a first wall in the form of an annular skirt 28, generally oriented axially forwards and connected by welding at 23 to the annular skirt 25 of the first half-shell 21, and on the other hand to its internal periphery 29 by a hub d impeller 90 on which the internal periphery 29 is attached, here by welding.

 The impeller hub 90 has, at its inner radial periphery, a guide ring 91 for the hub 90 relative to the driven shaft.

 The radially outer periphery of the wall 27 is shaped so as to define a rear impeller wheel 40 of which vanes 41 are arranged on the side of its internal face 42.

 These blades 41 face the blades 51 of a front turbine wheel 50.

Thus, when the vehicle starts, the impeller wheel 40 drives the turbine wheel 50 by virtue of the circulation of oil between the vanes 41, 51 of the impeller wheel 40 and of the turbine wheel 50 respectively.

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 During this phase, the locking clutch 30 is released, so that the torque is transmitted from the driving shaft (crankshaft) to the first front half-shell 21 then to the hub 70 and to the shaft driven via the hydrokinetic coupler , alternatively a converter.

 Then, to avoid any sliding between the turbine 50 and impeller 40 wheels, the locking clutch 30 is engaged (bridged), so that the torque is transmitted from the shaft leading to the driven shaft via the locking clutch 30 and the torsional vibration damping device 60 which it comprises for damping the vibrations generated by the engine.

 To do this, the locking clutch 30 comprises, according to a known design, a hydrokinetic device of the two-sided type corresponding to the first example of implementation according to the invention, a piston 31 which delimits with a central ring 80, the transverse wall 24 of the first front half-shell 21 and with an annular disc 32, a control chamber 34 with variable volume, fed through the driven shaft.

 The driven shaft is hollowed out internally to form at least one supply channel allowing pressurized oil to pass through the shaft.

 The piston 31, generally of transverse orientation, is mounted axially movable in leaktight fashion along a guide surface 81 of axial orientation of the central ring 80.

 The piston 31 here comprises, at its internal radial periphery on the side of its rear face, a chamfered portion 132 which cooperates with a first external radial extension 85 of the front flange 86 of a first needle stop 87 interposed axially between the ring 80 and the turbine hub 70, the extension 85 here being inclined towards the rear and substantially parallel to the chamfered portion 132 of the piston 31. The extension 85 acts as a rear stop for the piston 31 in order to avoid any direct contact between the piston 31 and the element located axially towards the rear opposite it, such as the hub 70 or else a guide washer attached to said hub.

 The first needle stopper 87 is linked in rotation to the central ring 80 by means of a second internal radial extension

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 88 which cooperates with the ring 80. The first stop 87 is centered, here by means of a second rear flange, on the front lateral face of the hub 70, radially above the passages 170.

 As a variant, the second rear flange can be omitted and the front lateral face of the hub 70 constitutes a rolling surface for the first stop 87.

 The passages 170 connect the second chamber, opposite to the control chamber 34 and which is delimited axially forwards by the rear lateral face of the piston 31, with a supply channel for the driven shaft.

 The passages 170 and 180 respectively of the hub 70 and of the central ring 80 may consist of grooves, alternatively in through holes.

face latérale arrière du moyeu 70 et la face latérale avant de la périphérie radiale intérieure 29 de la deuxième demi-coquille arrière 22. A second needle stopper is interposed axially between the

rear side face of the hub 70 and the front side face of the inner radial periphery 29 of the second rear half-shell 22.

Advantageously, the hub 70 has on its rear lateral face a recess so that the second stop 89 is centered on the latter and that it is at least partially housed axially in this recess in order to reduce the axial bulk.

 A groove 82 is produced in the central ring 80 at the level of the guide surface 81 and is intended to receive sealing means 83, such as a segment or a seal, which cooperate with the inner radial periphery of the piston 31 to seal the control chamber 34.

 The piston 31 is linked to the annular wall 24 of the first front half-shell 21, here by elastic tongues 38 of tangential orientation, which are preferably distributed regularly circumferentially. The tongues 38 extend in the volume of the control chamber 34, radially below the friction disc 32.

 As illustrated in FIGS. 2 and 3, the elastic tongues 38 are here coupled at the front to the annular wall 24 by means of first extruded rivets 39a in said wall 24 and at the rear to the piston 31 by second rivets 39b .

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 Alternatively, the elastic tongues 38 are linked in rotation to the annular wall 24 by means of an additional part which is attached to the latter, for example by welding.

 To allow, during assembly, the riveting operation of the subassembly, formed by the piston 31 and the elastic tabs 38, with the annular wall 24 which includes the first extruded rivets 39a, the piston 31 has through holes 131 in alignment axial with the rivets 39a which allow the passage of a tool for riveting the subassembly 31-38 with the annular wall 24. The passage holes 131 of the piston are then closed in leaktight manner, here by plugs 231.

 Thus, thanks to the elastic tongues 38, the piston 31 is linked and mounted movable axially relative to the annular wall 24.

 The central ring 80 is linked in rotation to the first front half-shell 21, the ring 80 is here force-fitted on the second cylindrical wall in the form of an annular skirt 26 of generally axial orientation towards the front. The central ring 80 has at its external and internal peripheries, on the side of its front lateral face, passages 180 for the communication of the feed channel of the driven shaft with the control chamber 34.

 The central ring 80 comprises, like the impeller hub 90, a guide ring 181 with the driven shaft.

 Thus, by varying the pressure on either side of the piston 31, for example by varying the pressure in the control chamber 34, the piston 31 is allowed to move axially relative to the annular wall 24 of the first front half-shell 21, to bring, in a first case the piston 31 in the bridged state, that is to say the state in which the piston 31 and the wall are connected in friction rotation, directly or indirectly 24, and in a second case the piston 31 in the disassembled state in which they are no longer linked.

 In the case of a device 10 of the two-sided type, the piston 31 moves axially forwards, the locking clutch 30 is then in the bridged position and the piston then comes to clamp an intermediate element, usually a friction disc 32 , interposed between the front side face of the outer radial periphery of the piston 31 and the side face

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 rear of the annular wall 24, here generally opposite the connection means 200 to the drive shaft.

 The disc 32 here comprises on each of its lateral faces, respectively opposite the front and rear lateral faces of the piston 31 and of the annular wall 24, friction linings 33 which are attached by any means to the friction disc, here by collage.

 As a variant, the friction linings are integral with the piston 31 and the annular wall 24.

 The disc 32 has, at its external radial periphery, radially beyond the piston 31, an inclined part which extends generally towards the rear and which comprises first rotational drive means 35, such as tabs, which cooperate with second means 36, such as notches, which the input element of the damping device 60 comprises, in order to link in rotation the disc 32 and the input element by a link, for example of the tenon type -mortaises, allowing axial movement of the disc 32.

 Thanks to this possibility of axial movement, the friction disc 32 can be tightened by the piston 31 during bridging, the torque then being transmitted to the input element of the damping device 60.

 The turbine wheel 50 and the impeller wheel 40 constitute a hydrodynamic circuit and more particularly here form a hydrodynamic coupler. As a variant, the coupler can be replaced by a converter, which, as is known, differs therefrom by the addition of a central reactor.

 The hydrodynamic circuit delimits, radially outward, an interior annular space 100, which is thus located radially below the circuit.

 The vibration damping device 60 is thus housed, in favor of said interior annular space 100, at least partially axially in this space so that the axial size of the assembly is reduced.

 The damping device or damper 60 comprises two coaxial elements mounted movable angularly with respect to each other against at least one elastic member with circumferential action 64

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 which is capable of cooperating with these elements forming the input elements, and the output of the damper 60.

 The turbine wheel 50 is suitable for being linked to a driven shaft and has a first radially outer part forming a torus 52 which contains the blades 51, and a second radially inner part 54 for rotationally connecting the torus 52 with the driven shaft , by means of the damping device 60, the outlet element of which is connected to the hub 70 provided internally with splines 71 for its connection in rotation with said driven shaft.

 As visible in FIG. 1, the input element of the damping device 60 is constituted by a flange 65 comprising a first radially outer part 66, linked in rotation to the torus 52 of the turbine wheel 50, here by welding, and which is extended by a second radially inner part which constitutes a first front guide washer 67 of the damping device.

The internal radial periphery of the front guide washer 67 is folded to extend axially towards the front, substantially forming an L which cooperates with a shoulder 75, formed in the front lateral face of the hub 70, on which said front washer 67 is centered radially
This second radially inner part of the flange 65 is shaped to at least partially house the elastic members 64 and it comprises at least one driving element 93 which cooperates, preferably directly, with at least one elastic member 64.

 The flange 65 has at its outer radial periphery the second rotation drive means 36, here lugs delimiting notches, which cooperate with the first means 35 located at the outer radial periphery of the friction disc 32. The torque is then transmitted during bridging, that is to say when the friction disc 32 is clamped by the piston 31 against the annular wall 24, thanks to the first and second drive means 35,36 which cooperate to form for example a connection of the tenon type -mortaises. The connection is obtained here in that at least one leg of the first means 35 extends radially rearward in a notch formed by two successive legs of the second means 36 and vice versa at least one leg of the second

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 means 36 extend radially forward in a niche formed by two successive lugs of the first means 35.

 The damper 60 is thus constituted, axially from front to rear, of a first front guide washer 67, of a median web 61 and of a second rear guide washer 68 integral with the first, the two washers of guide 67,68 forming the input element of the device and the web 61 forming the output element.

 The second rear guide washer 68 is here formed by the second radially inner part 54 for rotationally connecting the torus 52 with the driven shaft, which is here produced in one piece with the torus 52 of the turbine wheel 50.

 The second radially inner part 54 has for this purpose a portion shaped to at least partially house the elastic members, and comprises at least one driving element 92 which cooperates with an elastic member 64.

 The two guide rings 67, 68 are connected at their inner periphery by connection means, here spacers 63 which pass through the web 61 through oblong holes 69, having substantially the shape of a bean, and thus allow angular movement, during which the elastic members are urged to transmit the torque from the input element to the output element, that is to say washers 67,68 to the web 61.

The openings or holes 69 have of course a radial width greater than the diameter of the spacers to allow the circumferential movement.

rondelle de guidage avant et arrière 67, 68), aux organes élastiques 64 par l'intermédiaire des éléments d'attaque 92, 93 des deux rondelle de guidage 67,68, et enfin au voile 61 dans lequel sont agencés les organes élastiques 64, voile qui constitue l'élément de sortie et qui est lié au moyeu 70. The torque is thus transmitted through the damper 60, from the input element, formed by the drive means 36 (integral with the two

front and rear guide washer 67, 68), to the elastic members 64 via the drive elements 92, 93 of the two guide rings 67, 68, and finally to the web 61 in which the elastic members 64 are arranged, web which constitutes the outlet element and which is linked to the hub 70.

 The median web 61 forming the outlet element is here in one piece with the hub 70 above which it extends generally transversely. The web is therefore integral with the hub 70, as a variant, the web 61 is attached and linked in rotation to the hub 70.

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 The middle veil 61 has windows 164, better visible in FIGS. 2 and 3, in which the elastic members 64 are received axially. In the embodiment illustrated in FIG. 1, the outer radial periphery of the veil 61 forms a continuous crown which is deformed axially forward, in order to avoid any contact with the toroid 52 of the turbine wheel. Such a crown makes it possible in particular to stiffen the web 61 and therefore to obtain better general mechanical strength.

 Alternatively, as shown in Figures 2 and 3, the windows 164 are open to the outside so that the outer radial periphery of the web 61 forms a discontinuous ring. Advantageously, the torus 52 of the turbine wheel 50 is treated in order to prevent the risks of wear by friction during contact with the elastic members 64, in particular under the effect of centrifugal force.

 The drive elements 92 belonging to the second radially inner part 54 forming the second rear guide washer 68 and the drive 93 belonging to the second radially inner part of the flange 65 forming the first front guide washer 67, here cooperate directly with at least one elastic member 64. These elements consist of bosses 92, 93 produced by stamping in the front and rear guide washers 67, 68.

 The bosses 92, 93 generally extend each end of the elastic member 64 which transmits the torque, by filtering the vibrations, to the hub 70 by means of the web 61 and this in proportion to the angular movement allowed.

21, le disque de friction 32, le piston 31, la bague centrale 80, la première butée à aiguilles 87, le flasque 65, le voile 61 en une pièce avec le moyeu 70 et les organes élastiques 64, la roue de turbine 50, la seconde butée à aiguilles 89 et la deuxième demi-coquille arrière 22 formant la roue d'impulseur 40. Figures 2 and 3 are exploded perspective views of a hydrokinetic apparatus similar to that of Figure 1. We can thus see from left to right, ie from front to back, the first half - front shell

21, the friction disc 32, the piston 31, the central ring 80, the first needle stop 87, the flange 65, the web 61 in one piece with the hub 70 and the elastic members 64, the turbine wheel 50, the second needle stopper 89 and the second rear half-shell 22 forming the impeller wheel 40.

 According to the principles of the invention and as will have been understood after the description of the first embodiment, apart from the elastic members, the damper 60 does not comprise, axially from front to back,

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 that three parts arranged successively, at least one of which is constituted by the second inner radial part 54 for rotationally connecting the torus 52, so that the axial size of such a damper is reduced.

 The description of the figures which will follow will be made by comparison first with respect to FIG. 1, and then between the different figures illustrating different embodiments according to the invention.

 Figures 4 to 7 illustrate a second embodiment according to the invention in which the damper 60 consists of an input element and an output element of the device, said elements being mounted angularly movable one by relation to the other against the elastic members with circumferential action 64.

 The damper input element is further constituted by a flange 65 linked to the torus 52 and two front and rear guide washers 67, 68, the front guide washers 67 being able to be in one piece, or separate, of the flange 65. The rear guide washer 68 is formed by the inner radial rotation connection portion 54 of the torus 52, being in this embodiment, a separate part from the torus 52.

 In FIGS. 4 and 5, the flange 65 constitutes the input element of the damper 60. The flange 65 consists of a first radially outer part 66, linked in rotation to the torus 52 of the turbine wheel 50, here by welding, and which is extended by a second radially inner part which constitutes the first front guide washer 67 of the damping device. The second radially inner part forming the front guide washer 67 comprises at least one cutout 300 from which comes at least one tab 301 which extends generally axially towards the rear and the end of which is free.

 These tabs 301, which constitute the outer radial periphery of the guide washer 67, extend radially below the inner periphery of the torus 52 and substantially parallel thereto.

 The guide washer 67 is thus formed consecutively from the outside to the inside, of a first part formed by the tab 301, of a second part or portion 302, of section generally in an arc of a circle, shaped to form a housing in which the elastic members 64 at least partially penetrate axially, and a third

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 part 303, generally transverse and substantially parallel to the front lateral face of the web 61-hub 70 assembly made in one piece. The part 303 is crossed by spacers 63 and is thus linked in rotation to the second rear guide washer 68 which is similarly arranged on the rear lateral face of the sail assembly 61 hub 70.

 The two guide washers 67, 68 are centered at their inner radial periphery around the shoulders 75 of the hub 70 and comprise attack elements 92, 93 formed by bosses produced by stamping. The attack elements 92, 93 are interposed between two consecutive elastic members 64.

 The second radially inner connection part 54 constituting the second rear guide washer 68 and the torus 52 of the turbine wheel 50 are two separate parts linked in rotation. The connection between these two parts is carried out radially generally beyond the elastic members 64 by means 310, here by crimping the inner periphery of the torus 52 on the guide washer 68.

auquel sont liées les rondelles, respectivement par soudage de la partie radialement extérieure 66 du flasque 65 pour la rondelle de guidage avant 67 et par sertissage pour la rondelle de guidage arrière 68. The two guide washers 67, 68 are thus linked to one another by means of the spacers 63 on the one hand and the torus 52 on the other hand.

to which the washers are linked, respectively by welding the radially outer part 66 of the flange 65 for the front guide washer 67 and by crimping for the rear guide washer 68.

 The windows 164 of the web 61 in which the elastic members 64 are arranged are here open and delimited radially outwards by the tabs 301 which prevent any direct contact between the elastic members 64 and the torus 52, in particular under the action of the centrifugal force.

 FIG. 5 illustrates a variant of the second embodiment, according to FIG. 4 in which the end of the tab 301 of the first front guide washer 67 is not axially free but is linked in rotation by means 310, here by crimping, to the second rear guide washer 68. As a variant, the crimps can for example be replaced by welding operations and vice versa.

 The external radial periphery of the second guide washer 68 extends freely beyond the means 310 and it is not linked to the torus 52 of the turbine wheel 50, so that the guide washers 67, 68 do not

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 are linked in rotation to the torus 52 only by welding the outer radial part 66 of the flange 65, and are linked together by crimping.

 In a variant not shown, the welding between the outer radial part 66 of the flange 65 and the torus 52 is replaced by a crimping of at least one lug belonging to at least one blade 51 of the turbine wheel 50.

 FIG. 6 illustrates a variant of the second embodiment, according to FIG. 4, in which the flange 65 only has an external radial part 66 and does not extend radially inwards to form the first front guide washer 67. The first front guide washer 67 is constituted by a separate part from the flange 65, the outer periphery of which is free.

 As in FIG. 4, the second radially inner connection part 54 constituting the second rear guide washer 68 and the torus 52 of the turbine wheel 50, are two separate parts linked in rotation. The connection between these two parts is carried out radially generally beyond the elastic members 64 by means 310, here by crimping the inner periphery of the torus 52 on the guide washer 68.

 Thus the connecting means 310 of the second radially inner part 54 intervene either with the toroid 52, or with the first front guide washer 67.

 FIG. 7 illustrates a variant of the second embodiment, according to FIG. 4 in which connection means 310 intervene on the one hand and the torus 52 and on the other hand, between the second radially inner part 54 and the outer periphery of the first front guide washer 67. The connection means 310 here consisting of offset crimps, that is to say a first crimping between the washer 68 and the torus 52 and a second crimping, offset radially with respect to the first, between the two guide rings 67,68.

 FIGS. 8 to 13 illustrate a third embodiment according to the invention and its variants, in which the damper 60 is constituted by two coaxial parts movable angularly with respect to one another against elastic members with circumferential action 64, these parts forming the input and output elements of the shock absorber 60. There is no longer any web 61, the output element consists of the guide washer 67,

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 while the washer 68 constitutes, with the torus 52 and the flange 65, the input element.

 The flange 65 has a radial part linked to the torus 52 of the turbine wheel 50 by welding, the flange not extending radially inwards to form the first front guide washer 67. The first front guide washer 67 is in fact constituted here by a separate part which is linked in rotation to the hub 70 and clamped axially against its front lateral face by means 63, such as rivets or spacers.

ainsi à la périphérie extérieure le logement annulaire des organes élastiques 64, d'une seconde partie 302 constitué par une portion globalement de section en arc de cercle conformée pour former un logement dans lequel pénètre au moins partiellement axialement les organes élastiques 64, et d'une troisième partie 303 globalement transversale et sensiblement parallèle à la face latérale avant du moyeu 70 contre laquelle elle est serrée axialement et auquel elle est donc liée en rotation par des moyens 63, tels que des rivets ou des entretoises. The front guide washer 67 here consists consecutively from the outside to the inside, of a first transverse part 301 open towards the front and which follows the shape of the torus 52 in opposite by closing

thus at the outer periphery the annular housing of the elastic members 64, of a second part 302 constituted by a portion generally of section in an arc of a circle shaped to form a housing in which the elastic members 64 penetrate at least partially axially. a third part 303 generally transverse and substantially parallel to the front lateral face of the hub 70 against which it is clamped axially and to which it is therefore linked in rotation by means 63, such as rivets or spacers.

 The guide washer 67 is centered radially, at the inner periphery of its part 303, around a shoulder 75 of the hub 70.

 The portion 302 of the washer 67 comprises at least one attack element 92 formed by a boss produced by stamping. Likewise, the washer 68 comprises at least one attack element 93 generally facing the attack element 92, said elements 92, 93 being interposed between two consecutive elastic members 64.

 The driving elements formed by the bosses 92, 93 extend generally tangentially opposite the opposite circumferential ends of the elastic members 64. Advantageously, the bosses 92, 93 are produced by stamping the two guide washers 67, 68.

 The second radially inner part 54 of the turbine wheel 50 is in one piece with the torus 52 and it constitutes the second rear guide washer 68. The internal periphery of the washer 68 is centered on a shoulder 175 of the hub 70 and it is linked in rotation to the hub 70

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 with the possibility of angular movement through the spacers 63 which pass through oblong holes 369.

 The two guide washers 67, 68 can thus, by virtue of the angular play of the rear end of each spacer in its oblong hole, have an angular clearance relative to one another.

 FIG. 8A illustrates an alternative embodiment in which the radially inner end of the second radially inner part 54 for rotationally connecting the torus 52 constitutes a front flange of one of the needle stops, here the second needle stop 89.

 FIG. 9 illustrates an alternative embodiment of the third mode according to FIG. 8, in which the shock absorber 60 comprises an input element constituted by the flange 65-torus 52-rear guide washer 68, and an output element consisting of the front guide washer 67.

 The rear guide washer 68 is formed by the second radially inner part 54 for connecting the torus 52, with which it constitutes a single piece.

 The guide washer 68 comprises at least one driving element 92 of the elastic members 64, here bosses 92 produced by stamping the second radially inner part 54 and the torus 52, the bosses extending here generally axially with respect to the members elastic 64.

 The front guide washer 67 comprises at least one element for attacking the elastic members 64, here a lug 93 obtained by cutting and folding the washer 67, the lug 93 extending generally axially relative to the elastic members 64, between the bosses 92 of the washer 68. The cutting and folding in order to constitute the tab 93 can be carried out on the outer or inner radial periphery.

 The angular clearance between the two guide washers 67, 68 is obtained in the same way as above, but the two radially inner portions of the washers are here adjacent and arranged on the same side of the hub 70, in this case along the face. front side of the hub 70 which has a single shoulder 75 obtained by countersinking or annular dressing of greater axial depth between the second radially inner part 54 for centering the two washers.

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 FIG. 10 illustrates an alternative embodiment of the third mode according to FIG. 8. This variant is similar to that illustrated in FIG. 9 from which it differs only by the inversion of certain elements, in particular in that the second radially inner part 54 of connection of the toroid 52 forms the front guide washer 67, and no longer the rear washer 68 as in FIG. 9.

 Thus, the shock absorber 60 comprises an input element constituted by the flange 65-torus 52-front guide washer 67, and an output element constituted by the rear guide washer 68.

 The front guide washer 67 is formed by the second radially inner part 54 for connecting the torus 52, with which it constitutes a single piece.

 The front guide washer 67 comprises at least one element for attacking the elastic members 64, here bosses 93 produced by stamping the second radially inner part 54, the bosses extending here generally axially with respect to the elastic members 64.

 The rear guide washer 68 comprises at least one element 92 for attacking the elastic members 64, here a tab 92 obtained by cutting and folding the washer 68, the tab 92 extending generally axially relative to the elastic members 64, between the bosses 93 of the washer 67. The cutting and folding in order to constitute the legs 92 can be carried out on the outer or inner radial periphery.

The angular clearance between the two guide washers 67, 68 is obtained in the same way as above, but the two radially inner portions of the washers are here adjacent and arranged on the same side of the hub 70, in this case along the face. rear side of the hub 70 which has a single shoulder 75 obtained by countersinking or annular dressing of greater axial depth between the second radially inner part 54 for centering the two washers.

FIG. 11 illustrates an alternative embodiment of the third mode according to FIG. 8. This variant is similar to that illustrated in FIG. 9 from which it differs in particular in that the driving elements 92 of the elastic members 64 of the rear guide washer 68 are constituted

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 by lugs 92 obtained by cutting and folding the washer 68, the lugs 92 extending generally axially relative to the elastic members 64.

 The driving element 93 of the front guide washer 67 is constituted by a lug 93 obtained by cutting and bending the outer or inner radial periphery of the washer 67, the lugs 93 extending generally axially with respect to the elastic members and between the legs 92 of the guide washer 68.

 FIG. 12 illustrates an alternative embodiment of the third mode according to FIG. 8. This variant is similar to that illustrated in FIG. 11 from which it differs only by an inversion, like FIG. 10 relative to FIG. 9.

 Thus, the second radially inner portion 54 of connection of the torus 52 forms the front guide washer 67 and not the rear washer 68 as in FIG. 11. As in FIG. 11, the front and rear guide washers 67, 68 have respectively attack elements 93, 92 consisting of at least one lug extending generally axially with respect to the elastic members 64.

 FIG. 13 illustrates an alternative embodiment of the third mode according to FIG. 8.

 The damper 60 comprises an input element constituted by the flange 65 forming a front guide washer 67, and an output element constituted by the rear guide washer 68.

 The flange 65 comprises a first radially outer part 66 provided at its periphery with rotation drive means 36 with the friction disc 32 and which is not linked in rotation to the torus 52, the first part 66 extending by a second radially inner part which constitutes the first front guide washer 67 of the damping device 60.

 The rear guide washer 68 is formed by the second radially inner part 54 for connecting the torus 52, with which it constitutes a single piece.

 The front and rear guide washers 67,68 respectively comprise attack elements 93,92 constituted by at least one

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 tab extending generally axially relative to the elastic members 64.

 More particularly here, the rear guide washer 68 has a lug 92 which extends generally axially between two lugs 93 constituting the attack elements of the guide washer 67.

 Figures 14 to 16 illustrate a fourth embodiment according to the invention and its variants, similar to the third embodiment of Figure 13, but in which the second radially inner connection part 54 and the torus 52 of the turbine wheel 50 are two separate parts linked in rotation.

 The second radially inner part 54 forming the rear guide washer 68 is linked to the torus 52 by means 310, such as crimping. For more detail, reference may be made to the second embodiment according to the invention.

 The connection means 310 are here advantageously produced radially generally beyond the elastic members 64 to reduce the axial size.

 FIG. 15 illustrates an alternative embodiment of the fourth embodiment according to FIG. 14, in which at least a portion of the second radially inner connecting part 54 extends radially inside the first part forming the torus 52 of the turbine wheel 50 to constitute a deflector 320.

 The second radially inner part 54 forming the rear guide washer 68 is linked to the torus 52 by means 310, such as a crimping of the periphery of the torus 52 on the part 54.

 As is known, such a deflector 320 makes it possible to reduce the absorption torque of the impeller, and therefore to reduce the drag torque when the internal combustion engine is idling. Thanks to the deflector 320, the engine rotation speed is increased, particularly at the setting point.

réalisation selon la figure 14, semblable à la figure 15 en ce qu'elle comporte un déflecteur 320 réalisé en une seule pièce avec la seconde partie 54. FIG. 16 illustrates an alternative embodiment of the fourth embodiment

embodiment according to FIG. 14, similar to FIG. 15 in that it comprises a deflector 320 produced in one piece with the second part 54.

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 The second radially inner part 54, forming the rear guide washer 68, is linked in rotation to the torus 52, by means of the deflector 320 and the vanes 51 of the torus 52, which are linked by means 310. These means 310 consist here in lugs 311, coming from the blades 51, which are crimped on the deflector 320 to ensure the connection in rotation between the two parts 54 and 52.

 The connection means 310 are here advantageously produced radially generally beyond the elastic members 64, which makes it possible to reduce the axial size of the damper 60.

 According to the principles of the invention and as will have been clearly understood after the description of the third embodiment, apart from the elastic members, the damper 60 comprises, axially from front to rear, only two parts arranged successively, the l 'One is formed by the second inner radial part 54 for rotationally connecting the torus 52, so that the axial size of such a damper is very small.

réalisation selon la figure 14, dans laquelle la seconde partie radialement intérieure 54 de liaison en rotation du tore 52 formant la rondelle de guidage arrière 68 est réalisée en une seule pièce avec les aubes 51 de la roue de turbine 50. FIG. 17 illustrates an alternative embodiment of the fourth embodiment

embodiment according to FIG. 14, in which the second radially inner part 54 for rotationally connecting the torus 52 forming the rear guide washer 68 is produced in one piece with the blades 51 of the turbine wheel 50.

 The embodiment of FIG. 17 is similar to FIG. 14, and differs in that the front and rear guide washers 67, 68 respectively comprise attack elements 93, 92 constituted by at least one boss extending generally tangentially in look at the opposite circumferential ends of the elastic members 64.

 FIG. 18 illustrates a fifth embodiment according to the invention, in which the second radially inner part 54 for rotationally connecting the torus 52 constitutes the median web 61 of the damping device 60.

 The damper 60 comprises an input element constituted by the flange 65 attached by welding to the torus 52 of the turbine wheel, the second radial part 54 of which forms the median web 61, and an output element constituted by the two washer front and rear guide 67.68 mounted coaxially, angularly movable relative to one another, against the elastic members 64.

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 The two front and rear guide washers 67, 68 extend on either side of the hub 70, respectively along the front and rear lateral faces of the hub, hub 70 on which the washers are axially clamped by spacers 63 and radially centered by means of shoulders 75.

 The two guide washers 67, 68 has a portion 502 of generally circular arc section shaped to constitute a housing in which the elastic members 64 and at least partially penetrates axially 92.93 etching elements formed by bosses, produced by stamping, and which extend generally tangentially opposite the opposite circumferential ends of the elastic members 64.

voile, pour augmenter la surface de contact entre le voile 61 et les organes élastiques 64. Advantageously, the median web 61 comprises on the lateral edges of the windows 164 which cooperate with the elastic members 64, an enlarged portion 561 formed in favor of the web 61, here by folding the material of the

web, to increase the contact surface between the web 61 and the elastic members 64.

 The median web 61 is therefore here a separate part from the hub 70, the inner radial periphery of the veil being centered on the one hand radially on the external periphery of the hub 70 and, on the other hand, axially by the two guide washers 67, 68.

 Figures 19 and 20 illustrate a sixth embodiment and a variant, according to a second example of implementation of the principles of the invention in the case of a device of the single-sided type.

 As is well known, a device of the single-sided type differs from a device of the two-sided type, in that it does not include a friction disc 32. The friction lining 33 is here attached to the front side face to the outer periphery of the piston 31 by gluing.

 As a variant, the friction lining 33 is attached to the annular wall 24 of the first front half-shell 21.

The operation and the various elements of a single-sided device are for the rest similar to those of a two-sided and have already been described previously.

The damper 60 comprises an input element constituted here by the piston 31 and an output element constituted by a guide washer

<Desc / Clms Page number 27>

 rear 68 formed by the second inner radial part 54 for rotationally connecting the torus 52, the input and output elements being mounted angularly movable relative to one another, against the elastic members 64.

 The second inner radial part 54 is here produced in one piece with the torus 52 and comprises on the one hand a shaped portion to accommodate at least partially axially the elastic members 64 and, on the other hand, at least one attack element 92 of the elastic organs.

 The driving elements 92 here consist of bosses 92, produced by stamping, which extend generally tangentially opposite the opposite circumferential ends of the elastic members 64.

 The inner radial periphery of the second part 54 is fixed axially and linked in rotation to the hub 70, here by rivets 63 on the rear lateral face of the hub. Advantageously, the hub 70 comprises a shoulder 75 on which the second part 54 is centered radially.

 As a variant, the inner radial periphery of the second part 54 extends inwards to form the front flange 73 of the second needle stopper 89, interposed axially between the hub 70 and the internal periphery 29 of the second rear half-shell 22.

 The piston 31 comprises at least one driving element 93 of the elastic members 64, here constituted by bosses 93, formed directly in the piston 31, and which extend generally tangentially opposite the opposite circumferential ends of the elastic members 64.

 As a variant, the driving elements 92, 93 consist of lugs produced by cutting and folding the piston 31 and the second radial part 54 of the torus 52, respectively, and which extend generally axially with respect to the elastic members 64.

 FIG. 20 illustrates a variant of the sixth embodiment according to FIG. 19, in which the driving element 93 belongs to a front guide washer 67 attached, here by welding, to the rear lateral face of the piston 31.

 The front guide washer 67 comprises on the one hand a portion shaped to at least partially house the members axially.

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 elastic 64 and, on the other hand, at least one drive element 93 of the elastic members.

 The driving elements 92 here consist of a tab 93, produced by cutting and folding the portion of the front guide washer 67, which extends generally axially relative to the elastic members 64.

 The second inner radial part 54 is here produced in one piece with the torus 52 and comprises on the one hand a shaped portion to accommodate at least partially axially the elastic members 64 and, on the other hand, at least one attack element 92 of the elastic organs.

 The driving elements 92 are here constituted by lugs 92, produced by stamping, which extend generally tangentially opposite the opposite circumferential ends of the elastic members 64.

 The legs 93 of the first front guide washer 67 acting axially between the legs 92 of the second inner radial part 54 forming the second rear guide washer 68 of the damper 60.

 In all the embodiments described above, it will be noted that the elastic members 64 may consist of coil springs, as a variant in an assembly with two concentric springs of a first spring arranged in the internal diameter of a second spring of larger diameter. Thanks to the invention, the axial size of the damper is reduced, which can also allow the use of elastic members of larger diameter to obtain in certain applications better filtration of vibrations.

 As a variant, the elastic members 64 are constituted by shock-absorbing blocks made of synthetic material or else by long curved springs which may or may not be pre-bent before their mounting.

 The elements, called attack elements 92, 93, cooperate, that is to say act, preferably, directly on the last turns at the ends of the elastic members 64.

 Alternatively, the driving elements 92, 93 act by means of at least one additional piece interposed between said elements and the elastic members 64 at the ends of said members.

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 Thus, without departing from the scope of the invention, the additional parts can consist of cups, which advantageously penetrate into the interior of the first turns of the springs in order to guide and center these springs 64.

 If the elastic members consist of curved springs of great length, it is then possible to have at least one guide shoe between the two ends of the spring and this in order to better guide them while avoiding the significant friction which can occur with the parts surrounding the springs, in particular under the action of centrifugal force.

 As a variant, the elements 92, 93 may include a portion such as a tab which penetrates into the springs 64 to center the latter.

 As a variant, the elements 92, 93 are constituted by the edges of windows provided, for example in the guide washer 67, 68, and which cooperates with the elastic members 64 as is the case with the web 61 when the damper 60 has one.

 Of course, the description of the various embodiments is in no way limiting and it is possible, without departing from the scope of the invention, to combine the characteristics of each of these modes.

Claims (15)

 CLAIMS 1. Hydrokinetic coupling device (10), in particular for a motor vehicle, of the type comprising: a front casing (20) provided with a wall (24), generally of radial orientation, suitable for being linked in rotation to a leading tree; a front turbine wheel (50) capable of being linked in rotation to a driven shaft, comprising a first radially external part forming a torus (52), and a second radially internal part (54) for connecting the torus in rotation (52 ) with the driven shaft; a hydrodynamic circuit formed by at least one rear impeller wheel (40) and the torus (52) of the turbine wheel (50); a piston (31), generally of radial orientation, mounted movable and arranged axially between the wall (24) of the casing (20) and the turbine wheel (50), and defining with said wall a control chamber (34), delimited radially externally by at least one friction element (33); an interior annular space (100), located radially below the hydrodynamic circuit; at least one vibration damping device (60), intervening between the driven and driving shafts, and housed at least partially axially in the annular space (100) and comprising at least one elastic member (64) with circumferential action which is capable of cooperating with input and output elements, characterized in that at least one element (92, 93) of the second radially inner part (54) for connecting the turbine wheel (50) cooperates with at at least one elastic member (64) of the damping device (60).  2. hydrokinetic coupling device according to claim 1, characterized in that the second radially inner connecting part (54) comprises portions (302,502) <Desc / Clms Page number 31>  shaped to accommodate at least partially axially the elastic members (64).  3. hydrokinetic coupling apparatus according to claim 1, characterized in that the second radially inner connecting part (54) extends generally in the mean plane in which the elastic members act (64).  4. hydrokinetic coupling apparatus according to claim 1 or 2, characterized in that at least one element (92, 93) of the second radially inner connecting part (54) cooperating with the elastic members (64) extends generally tangentially opposite the opposite circumferential ends of the elastic members (64).  5. hydrokinetic coupling apparatus according to claim 1 or 2, characterized in that at least one element (92, 93) of the second radially inner part (54) of connection cooperating with the elastic members (64) extends generally axially with respect to the elastic members (64).  6. hydrokinetic coupling apparatus according to claim 4 or 5, characterized in that said element (92,93) is constituted by at least one boss (92,93), in particular by a boss produced by stamping the second part radially inner (54) connection.  7. hydrokinetic coupling apparatus according to claim 4 or 5, characterized in that said element (92,93) is constituted by at least one tab (92,93), in particular by a tab produced by cutting and folding the second radially inner connecting part (54).  8. hydrokinetic coupling apparatus according to any one of the preceding claims, characterized in that the second radially inner part (54) of connection is made in one piece with the torus (52) of the turbine wheel (50) .  9. hydrokinetic coupling device according to one of claims 1 to 7, characterized in that the second radially inner part (54) of connection and the torus (52) of the turbine wheel (50) are two separate linked parts in rotation. <Desc / Clms Page number 32>  10. hydrokinetic coupling apparatus according to claim 9, characterized in that the rotational connection of the second radially inner part (54) of connection and of the torus (52) of the turbine wheel (50) is carried out radially generally beyond elastic members (64).  11. hydrokinetic coupling apparatus according to any one of the preceding claims, characterized in that the second radially inner connecting part (54) is linked in rotation with the driven shaft by means of a turbine hub ( 70).  12. Hydrokinetic coupling apparatus according to any one of the preceding claims, characterized in that the torus (52) of the turbine wheel (50) comprises blades (51), and in that the second radially inner part ( 54) of connection is formed in one piece with the blades (51) of the turbine wheel (50).  13. hydrokinetic coupling apparatus according to any one of the preceding claims, characterized in that the vibration damping device (60) comprises, axially from front to back for formation of the input and output elements of the device d damping, a first front guide washer (67), a web (61) and a second rear guide washer (68), and in that the second radially inner part (54) for connecting the turbine wheel (50 ) constitutes at least one of the guide rings (67, 68) or the web (61) of the damping device (60).  14. hydrokinetic coupling device according to any one of the preceding claims, characterized in that it comprises a friction disc (32) interposed axially between the wall (24) of the casing and the piston (31), and in that that this disc (32) comprises drive means (35) in rotation with an input or output element of the vibration damping device (60).  15. hydrokinetic coupling apparatus according to any one of the preceding claims, characterized in <Desc / Clms Page number 33>  that at least a portion of the second radially inner connection part (54) extends radially inside the first toroid part (52) of the turbine wheel (50) to constitute a deflector (320).