FR2919696A1 - Internal combustion engine and gear box coupling device for transmitting torque to e.g. crankshaft, has filler strips deformed along radial direction with axes of driving and driven units and connected to inlet and outlet ring gears - Google Patents

Abstract

The device (10) has an inlet ring gear (12) rotatively connected to a driving unit formed by a shaft or crankshaft of an internal combustion engine, and an outlet ring gear (14) rotatively connected to a driven unit formed by gear box shafts. Oblong shaped flexible filler strips (16) are elastically deformed along orthogonal radial direction with main axes of the driving and driven units, and are rotatively connected to the inlet and outlet ring gears, respectively. A double clutch type mechanism is temporarily coupled to the crankshaft.

Description

The invention relates to a coupling device capable of transmitting a

  torque between a main axis leading member X 'and a main axis driven member X. Coupling devices are known in the art, in particular in the field of vehicle transmissions, generally automobile, intended to mechanically couple in rotation an internal combustion engine and a gearbox.

  In the case of a transmission assembly for a motor vehicle, the driving member is a shaft or crankshaft of the internal combustion engine, and the torque is generally transmitted to a driven member, such as at least one input shaft. of a gearbox, via at least one clutch comprising a torsion damper. The clutch is in particular adapted to selectively transmit a torque between a main axis motor shaft X 'forming the driving member and at least one main axis gearbox shaft X forming the driven member, in particular to allow shifting gears without breaking torque. In the case of a clutch for example, the differences in position between the driving member linked to the motor and the driven member linked to the gearbox due to play or tolerances generally cause on the one hand difficulties during assembly and on the other hand unwanted phenomena in operation. Indeed, the assembly of the clutch can prove difficult in the presence of tolerance deviations, in particular the tolerances in the radial direction which are induced by the coaxiality defects between the respective axes X 'and X of the crankshaft and the (or) shaft (s) of the gearbox. In addition, the recovery of the radial tolerances generates, in particular during operation, additional forces on the engine and gearbox components which cause in particular, in addition to operating noise, premature wear of the members, said wear being able to cause premature rupture of certain mechanical organs.

  When the clutch is a multiple clutch such as that shown in Figure 1 of FR-A-2.893.370, coaxiality defects between the axes are at least partially resumed radially by the flexible plate (referenced 30), ci -after designated as the flexible steering wheel.

  Indeed, the flexible flywheel is respectively fixed at its radial inner periphery to the crankshaft of the engine and at its outer radial periphery to a member of the clutch capable of being temporarily connected to at least one shaft of the gearbox, here two shafts respectively an internal output shaft coaxially mounted to an external output shaft. More specifically, the flexible flywheel is fixed at its outer radial periphery to a portion of the cover which is itself mechanically connected in rotation to a peripheral portion of a reaction plate capable of transmitting the torque of the motor to the inner and outer shafts of the gearbox when the clutch is in said engaged position, as opposed to the disengaged position in which the engine and the gearbox are decoupled. The flexible flywheel has a very high rigidity in the radial direction orthogonal to the X 'and X axes, the radial differences corresponding to the coaxiality defects therefore cause a warping of the flexible flywheel. Thus, the part of the flywheel which extends radially between the fastening members implanted at each of its inner and outer peripheries, tends to be concealed so that the flywheel then transmits to the engine, clutch and gear box members. speeds of additional efforts causing the aforementioned drawbacks.

  The invention therefore aims to solve the aforementioned drawbacks by proposing in particular a solution for transmitting a torque between a driving member and a driven member while compensating for radial tolerances, in particular when their respective axes have a coaxiality defect. For this purpose, the invention proposes a coupling device capable of transmitting a torque between a main axis driving member X 'and a main axis driven member X, characterized in that the coupling device comprises at least an input member adapted to be rotatably connected to the driving member, an output member adapted to be rotatably connected to the driven member and flexible means which, respectively rotatably connected to the input member and to the output element to ensure the transmission of the torque, are able to deform elastically in a radial direction, orthogonal to the X 'and X axes, so as to compensate radially for the tolerances between the driving members and driven axes X' and X. The radially flexible means make it possible in particular to compensate for the differences induced by the coaxiality defects between the X 'and X axes.

  Advantageously, the coupling device according to the invention makes it possible to simply and reliably produce a homokinetic-type link between off-axis driven and driven members. Thanks to the coupling device according to the invention, the assembly of a clutch is likely to be facilitated and dynamic radial movements caused for example, in operation, by phenomena such as unbalance compensated, or at least mitigated by the elastic deformation of the flexible means in the radial direction. According to other characteristics of the invention: the input element is constituted by a so-called input ring having at least one axial portion and the output element by at least one so-called output ring, having at least one axial portion and the output ring is arranged radially inside or outside the inlet ring so that at least a portion of said axial portions are superimposed; - The output element comprises an intermediate ring which, having at least one axial portion, is interposed radially between the input ring and the output ring; - The output element comprises an intermediate ring which, having at least one axial portion, is interposed radially inside the inlet ring and the output ring; each flexible means is arranged in an annular housing delimited respectively, in the radial direction, by an inner annular face of an axial portion and an outer annular face of another axial portion, the axial portions respectively belonging to each of the two rings; among the input, intermediate and output rings which are adjacent to said flexible means; each flexible means is respectively rotatably connected to each of the two rings of the inlet, intermediate and outlet rings which are radially adjacent to said flexible means; - The flexible means are angularly distributed regularly with an angle α on the circumference of the axial portions of the input and output rings or the axial portions of the input and intermediate rings and the intermediate and output rings respectively; the flexible means consist at least of a first pair of flexible means which are diametrically opposed along a main axis of deformation and by a second pair of flexible means which are diametrically opposed along a principal axis of deformation orthogonal to the main axis of deformation the first pair of flexible means; each flexible means is matched to another flexible means which is diametrically opposed to it; each flexible means is respectively fixed by first fixing means on the input element or the intermediate element and by second fixing means on the intermediate element or on the output element; each flexible means is fixed, at one of its ends, by the first fixing means on the input element or the intermediate element and is fixed, at the other of its ends, by the second means of attachment to the intermediate element or the output element; the first fixing means are arranged symmetrically with respect to the second fixing means according to at least one radial axis of deformation of the flexible means; each flexible means is fixed at one and the other of its ends by the first fixing means on the input element or the intermediate element and is fixed by the second fixing means, arranged centrally between said ends, on the output member or the intermediate member; - The first fixing means are arranged symmetrically with respect to a radial axis of deformation of the flexible means and the second fixing means are arranged on said radial axis of deformation of said flexible means; - In a determined direction of rotation - direct or retrograde, the scheduling of the first and second fixing means is determined, for each flexible means, so that the forces applied to the flexible means during the transmission of torque are tensile forces or compression efforts; for a given pair of flexible means constituted by a first flexible means and a second associated flexible means, the scheduling of the first and second fixing means of the first flexible means and the scheduling of the first and second means for fixing the second flexible means are determined so that, for the direction of rotation - direct or retrograde - chosen, the first flexible means works in tension when the second flexible means works in compression and vice versa; whatever the direction of direct or backward rotation, the tensile or compressive forces applied to the flexible means during the torque transmission are balanced when the flexible means is fixed at one and the other of its ends by the second fixing means and is fixed centrally between said ends by the first fixing means; the fixing means of the flexible means are rivets; the flexible means consist of at least one flexible tongue; the flexible means, the fastening means and the axial portions of the crowns are coplanar along a median vertical plane, said torque transmission plane, orthogonal to the X 'and X axes. the coupling device comprises absorption means which , radially interposed between the input element and the output element, are able to deform elastically to absorb vibrations transmitted to the device by the driving member; the elastic vibration absorption means consist of the flexible means; - The elastic absorption means are constituted by means, such as springs, pads of elastomeric material, a ring of elastomeric material, a spring plate or resilient tongues, friction means, which are capable of damping and / or or limit the radial deflections between the input and output elements of the device; - The input element of the coupling device is integral in rotation with a flexible flywheel so as to constitute a unitary module; The invention proposes a transmission assembly, in particular for coupling a motor and a gearbox, comprising at least one coupling device that is associated with a clutch for selectively transmitting the torque between the body main axis X 'formed by a driving shaft and the main axis driven member X formed by at least one gearbox shaft to which is selectively connected at least one member of the clutch, characterized in that associated clutch is a multiple clutch mechanism, such as a dual clutch, having a reaction plate and in that the output member of the coupling device is rotatably connected to said clutch member, such that the reaction plate. The invention also proposes a transmission assembly, in particular for coupling a motor and a gearbox, comprising at least one coupling device which is associated with a clutch for selectively transmitting torque between the clutch and the gearbox. main axis driving member X 'formed by a drive shaft and the main axis driven member X formed by at least one gearbox shaft, characterized in that the associated clutch is a clutch comprising a double damping flywheel which comprises a primary flywheel and a secondary flywheel between which is mounted a torsion damper and in that the output element of the coupling device is rotatably connected to the primary flywheel of the double damping flywheel.

  The invention also proposes a transmission assembly, in particular for coupling a motor and a gearbox, comprising at least one coupling device according to any one of the preceding claims which is associated with a clutch for selectively transmitting the torque between the main axis driving member X 'formed by a driving shaft and the main axis driven member X formed by at least one gearbox shaft, characterized in that the associated clutch is a clutch comprising a double damping flywheel which comprises a primary flywheel and a secondary flywheel between which is mounted a torsion damper and in that the input element of the coupling device is connected in rotation to the secondary flywheel of the double flywheel damper and the output member of the coupling device is rotatably connected to at least one member of the clutch. Advantageously, the clutch associated with the coupling device comprises at least one torque limiting device.

  The invention finally proposes a transmission assembly, in particular for coupling a motor and a gearbox, comprising at least one coupling device which is associated with a clutch to selectively transmit the torque between the main axis driving member X 'formed by a driving shaft and the main axis driven member X formed by at least one gearbox shaft to which is selectively connected at least one member of the clutch, characterized in that the associated clutch is a hydrokinetic coupling apparatus having at least one housing and that the output member of the coupling device is rotatably connected to the casing of the hydrokinetic coupling apparatus. Advantageously, the input element of the coupling device is connected to the motor via a flexible flywheel which is respectively rotatably connected to the motor shaft and the input element of the device. coupling or primary flywheel of a double damping flywheel. Other features and advantages will appear on reading the description which follows, for the understanding of which reference will be made to the appended drawings in which: - Figure 1 is a front view which shows a coupling device according to a first embodiment of the invention and which illustrates a unitary module formed by a flexible flywheel and the device comprising two rings respectively forming the input member and the output member rotatably connected by flexible means elastically deformable in the direction radial; - Figures 2, 3 and 4 are respectively views in axial section along the corresponding sections II-II, III-III and IV-IV of the device according to Figure 1; - Figure 5 is a perspective view which shows an exploded second embodiment of the coupling device according to the invention and which illustrates a device comprising an input ring, an intermediate ring and an output ring between which are respectively arranged the flexible means; FIG. 6 is a perspective view showing the unitary module formed by the coupling device according to the second embodiment and a flexible flywheel; FIG. 7 is a cross-sectional view showing the coupling device according to FIGS. 5 and 6 and illustrating a first pair of flexible means connecting in rotation the input and intermediate rings, and a second pair of flexible means. linking the intermediate and output rings in rotation; FIG. 8 is a view in axial section which represents the device according to FIG. 6 according to section VIII-VIII and which illustrates the arrangement of the output ring radially inside the inlet ring so as to form with the flexible flywheel an axially compact unitary module; FIG. 9 is a front view which represents a third embodiment of the coupling device according to the invention and which illustrates, with respect to the second embodiment illustrated in FIGS. 5 to 8, a variant of attachment according to which the means hoses are fixed at three points by the fastening means to balance the tensile and compressive forces applied to the flexible means; FIGS. 10 and 11 are respectively views in axial section along the corresponding sections XII-XII and XIII-XIII of the coupling device according to FIG. 11 forming a unitary module; FIG. 12 is a half-view in axial section showing a transmission assembly comprising a coupling device according to the third embodiment illustrated in FIGS. 9 to 11 and a double clutch and illustrating an example of possible industrial application. of the device according to the invention.

  In the following description and the claims, the terms such as "external" and "internal", "axial" and "radial", "forward" and "backward" etc. will be used without limitation. to designate the elements according to the orientations defined in the description, in particular with respect to the trihedron (L, V, T) shown in the figures. In the description, identical, similar or similar elements will be designated by the same reference numerals. The invention is advantageously, but not exclusively, able to be implemented in a transmission assembly intended to allow the coupling of an engine, such as an internal combustion engine, and a gearbox, such as than a vehicle gearbox, usually automobile. In such an application, the coupling device according to the invention is associated with a clutch, which clutch is known in known manner to selectively transmit torque between a main axis driving member X 'formed by a driving shaft, generally a crankshaft, and a main axis driven member X formed by at least one gearbox shaft to which at least one member of the clutch is capable of being temporarily connected depending on whether the latter is in the engaged or disengaged position. Advantageously, the coupling device according to the invention is indeed able to compensate for the radial tolerances between the driving and driven members of axes X 'and X respectively, in particular the distances induced by the coaxiality defects between these axes X In the remainder of the description, a first, a second and a third exemplary embodiment of the coupling device according to the invention will be described successively before describing an example of application in a transmission assembly, in conjunction with a multiple clutch.

  FIGS. 1 to 4 show a first exemplary embodiment of a coupling device 10 according to the invention which is capable of transmitting a torque between a main axis driving member X 'and a driven axis member. main X (not shown). According to the invention, the coupling device 10 comprises at least one input element 12 adapted to be rotatably connected to the driving member, an output element 14 adapted to be connected in rotation to the driven member and flexible means 16 which, respectively rotatably connected to the input element 12 and to the output element 14 to ensure the transmission of the torque, are able to deform elastically in a radial direction orthogonal to the X 'and X axes leading and led bodies. Advantageously, the coupling device 10 is able to compensate radially for the tolerances between the driving and driven members, in particular the differences induced by the coaxiality defects between the respective axes X 'and X of the driving and driven members.

  In this first embodiment, the coupling device 10 more particularly comprises a first ring forming the input element 12 and a second ring forming the output element 14, said rings being connected in rotation by the flexible means. .

  As can be seen in axial section in Figures 2 to 4, the first ring 12, said input, and the second ring 14, said output respectively have an "L" profile consisting of a bar which s' extends longitudinally and another bar that extends vertically, substantially orthogonal to the longitudinal portion.

  In the remainder of the description, the "axial" direction corresponds to the longitudinal orientation of the trihedron (L, V, T) shown in the figures. The input ring 12 has mainly an axial portion 18 and a vertical portion 20 while the output ring 14 has an axial portion 22 and a vertical portion 24 which form respectively the bars of the "L". Preferably, the output ring 14 is arranged radially inside the inlet ring 12 and at least a portion of said axial portions 18, 22 are superposed vertically. In addition, the output ring 14 is received axially inside the inlet ring 12 in the manner of nesting elements. Advantageously, the coupling device 10 thus has a reduced axial size. Alternatively, the arrangement of the rings 12, 14 is reversed so that the output ring 14 is arranged radially outside the input ring 12. Preferably, the axial portion 18 of the input element 12 and the axial portion 22 of the output member 14 are circumferentially generally continuous so that each forms an annular skirt of axial orientation. Likewise, the vertical portions 20 and 24 of the input 12 and output 14 elements are preferably constituted by an annular skirt of vertical orientation. Alternatively (not shown), the axial portions 18, 22 or vertical 20, 24 of the input elements 12 and output 14 are for example constituted by tabs distributed circumferentially on each of the vertical skirts 20, 24 of the rings 12, 14 .

  When the coupling device 10 is not connected to the driving and driven members as illustrated in FIG. 1, the inlet and outlet crowns 14 are then concentric and are advantageously centered on a point O forming the center of the device. By definition, the term "front" corresponds in the axial direction to an orientation towards the driving shaft, for example to the motor, and the term "rear" to an orientation towards the driven shaft, for example towards the clutch and the gearbox in the case of a transmission assembly. Thus, considering FIGS. 2 to 4, the vertical skirts 20, 24 of each of the rings 12, 14 are connected by bends at the front end of the axial skirts 18, 22 and the "L" -shaped profiles of the rings 12, 14 being arranged in the same direction, the coupling device 10 is axially "open" towards the rear. Advantageously, the flexible means 16 are arranged in an annular housing 26 delimited respectively, in the radial direction, by an inner annular face 28 of the axial skirt 18 of the inlet ring 12 and an outer annular face 30 of the axial portion 22 The radial dimension of the annular housing 26, that is to say the spacing between the inner annular face 28 and the outer annular face 30, determines in combination with the flexible means 16 the ability to travel radial radial between the input ring 12 and the output ring 14. The flexible means 16 are respectively rotatably connected to each of the inlet 12 and output 14 adjacent crowns.

  Advantageously, the flexible means 16 are regularly angularly distributed over all or part of the circumference of the axial skirts 18, 22 of the inlet and outlet crowns 14. Advantageously, each flexible means 16 is matched with another flexible means which it is diametrically opposed. Preferably, the coupling device 10 comprises at least two pairs of flexible means 16, here three pairs of flexible means angularly distributed regularly at 120 °. Preferably, each flexible means 16 is constituted by at least one flexible tongue, generally of oblong shape, having a capacity of elastic deformation in the radial direction. Advantageously, the flexible tongue has contrario a high rigidity in the transverse direction corresponding to its length (largest dimension) and the direction in which the torque is transmitted from the input element 12 to the output element 14 of the coupling device 10.

  Alternatively, the flexible means 16 are constituted by any appropriate means such as springs, pads or a ring of elastomeric material, a spring plate or resilient tongues etc., which are able to compensate for the radial tolerances and, advantageously, which are still able to damp and / or limit the radial movements between the input elements 12 and output 14 of the coupling device 10. In this first embodiment, the flexible means - generally designated by the reference 16 - comprise respectively a first pair of flexible tongues 16A and 16'A which are diametrically opposed along a main axis of deformation A, a second pair of flexible tongues 16B, 16'B which are diametrically opposed along a main axis of deformation B and a third pair flexible tongues 16C, 16'C which are diametrically opposed along a main axis of deformation C. The main axes A, B and C extend radially through the center O of the device 10 and define radial deformation axes A, B and C in which the tongues 16 are deformed elastically.

  Advantageously, the tongues 16 are distributed angularly in a regular manner, the intersection of the axes A, B and C determining between each of the tongues of equal angular sectors of angle equal to 600. The tab 16A of the first pair is for example arranged with an angle equal to 60 relative to the tongues which are circumferentially consecutive thereto in a direct direction of rotation D and in a retrograde direction of rotation R, ie the tongue 16B of the second pair and the tongue 16'C of the third pair, as shown in Figure 1.

  Alternatively, the coupling device 10 comprises at least a fourth pair of flexible tongues which are arranged diametrically opposite each other along a main axis D, the tabs 16 are then eight in number and distributed angularly regularly with an angle equal to 45 between each. Each flexible tongue 16 is fixed by first fixing means 32 on the input element 12 and by second fixing means 34 on the output element 14. Advantageously, the first and second fixing means 32, 34 are arranged symmetrically with respect to the radial axis of deformation A, B or C associated with the flexible tongue 16 considered and the radial axis of deformation A, B or C constitutes a radial axis of symmetry for each flexible tongue 16. Advantageously, the first and second fastening means 32, 34 of the flexible tongues 16 are respectively constituted by at least one rivet. In a variant, the means for fixing the flexible tongues 16 are formed by any other suitable fastening means, in particular determined as a function of the type of flexible means chosen, for example by welding, bolting, cooperation of shapes, etc. The first rivet 32 and the second rivet 34 for fixing each tongue 16A, 16'A of the first pair are arranged symmetrically with respect to the radial axis of deformation A, as are the first and second rivets 32, 34 each tongue 16B, 16'B of the second pair with respect to the radial axis B and each tongue 16C, 16'C of the third pair with respect to the radial axis C. Advantageously, each flexible tongue 16 is fixed by the rivets 32, 34 at each of its ends, is fixed to the input ring 12 by a rivet 32 and a rivet 34 to the output ring 14 respectively, so that each tongue 16 here has two attachment points constituted by the two rivets 32 and 34. In a variant, each tongue 16 is fixed to the inlet and outlet crowns 14 by more than two points, for example by at least three attachment points.

  According to this variant, the first fixing means are for example constituted by two rivets 32 which are arranged symmetrically with respect to a radial axis A, B or C at the ends of the flexible tongue 16 in question and the second fixing means are constituted by a rivet 34 which is positioned centrally on the radial axis A, B or C forming the radial axis of symmetry of the flexible tongue 16 considered and two rivets 32. Of course, this variant is not limiting and could still be realized conversely, the fixing of each flexible tongue 16 on the output ring 14 by two rivets 34 arranged at one and the other of its ends and the fixing on the input ring 12 by a rivet 32 positioned centrally, between said transverse ends of the tongue 16. According to a determined direction of rotation - direct D or retrograde R, the scheduling of the first and second fixing means 32, 34 determines, for c each flexible tongue 16, if the forces applied to said tongue during the transmission of torque are tensile forces or compressive forces. For example and as illustrated in Figure 1, when the coupling device 10 is rotated in the forward direction D, the clockwise, the tab 16B which is respectively fixed at one end by a rivet 32 on the crown of 12 and at the other end by a rivet 34 on the output ring 14, then undergoes traction forces.

  Conversely, when the coupling device 10 is rotated in the retrograde direction R, the tongue 16B undergoes, during the transmission of torque between the drive member and the driven member, compressive forces. Advantageously, for a given pair of flexible tongues 16, such as the tongues 16B and 16'B of the second pair, the scheduling of the fastening rivets 32, 34 of the first flexible tongue 16B and the scheduling of the fastening rivets 32 , 34 of the second flexible tongue 16'B are reversed. The rivet 32 of the tongue 16B is therefore symmetrical with the rivet 32 of the other tongue 16'B of the second pair relative to the center O of the device, just as are symmetrical with respect to the center O the rivets 34 of the tongues 16B and 16'B. Alternatively, the rivets 32 and 34 of a tongue 16 of a pair are not diametrically opposed to the rivets 32 and 34 of the other tongue 16 'of the pair so that the rivets 32 and 34 of the tongue 16 are then symmetrical rivets 32 and 34 of the tongue 16 'with respect to an axis passing through O and orthogonal to the deformation axis A, B or C of the pair of tongues considered. The inversion of scheduling between the rivets 32, 34 of a pair of tongues 16 has the consequence that, in one of the directions of rotation, for example the direct direction D, the first flexible tongue 16B works in tension when the second flexible tongue 16'B associated works in compression, and reciprocally, in the other direction of rotation is the retrograde direction R, the first flexible tongue 16B works in compression when the second flexible tab 16'B associated works in tension. As can be seen in FIG. 1, the inversion of the scheduling of the rivets 32, 34 between the tongues 16B and 16'B of the second pair can be illustrated by the fact that, following for example the direct direction D of rotation and considering the axis B as the reference axis, the rivet 32 of the tongue 16B linked to the input ring 12 will be followed by the other rivet 34 connected to the output ring 14, while for the tongue 16 B, it is inversely the rivet 34 linked to the output ring 14 which will be followed by the rivet 32 connected to the input ring 12. Through such scheduling of the rivets 32, 34, when the coupling device 10 is rotated in the direct direction D, the tab 16B then works in tension while the other 16'B diametrically opposite tab works in compression.

  Similarly, when the coupling device 10 is rotated in the retrograde direction R, the tab 16B will then work in compression while the other tab 16'B diametrically opposite will work in tension.

  Of course, the detailed explanations of operation of the tabs 16B, 16'B of the second pair of flexible means are transposable to the first pair of tabs 16A, 16'A as the third pair of tabs 16C, 16'C. On the other hand, for the aforementioned variant with three fixing points of each flexible tongue 16, irrespective of the direction of direct rotation D or retrograde R, the tensile or compressive forces applied to each flexible tongue 16 during transmission of torque. , are balanced. Advantageously, during operation of the transmission of a torque by the coupling device 10, an optimum distribution of the forces applied between each of the tongues 16 of a given pair, namely the tabs 16A and 16'A, 16B, is advantageously obtained. and 16'B, 16C and 16'C of the first, second and third pairs respectively. Advantageously, the compensation of the radial tolerances is effected by a combination of radial translation along the different main deformation axes A, B and C, the inlet and outlet crowns 14 being no longer concentric with respect to the center O Advantageously, the flexible tongues 16A and 16'A, 16B and 16'B, 16C and 16'C, the fastening rivets 32, 34 and the axial skirts 18, 22 of the crowns 12, 14 are generally coplanar in a vertical plane. median, said torque transmission, including orthogonal axes X 'and X leading and driven bodies. Preferably, the flexible tongues 16 each extend circumferentially between the rivets 32 and 34 following the curvature of the axial skirts 18, 22 of the inlet and outlet crowns 14 and 14.

  As a variant, the flexible tongues 16 extend circumferentially tangentially with respect to the curvature of the axial skirts 18, 22 of the inlet and outlet crowns 14. Advantageously, the axial portion 18 of the inlet ring 12 has locally a cutout 36 at least above the rivet 34 for fixing the tongue 16 to the output ring 14 so as to avoid possible shocks between the rivet 34 and the input ring 12 when, in operation, the tab 16 compensates the radial tolerances and / or absorb vibrations especially transmitted by the driving member.

  The cutout 36 is more particularly visible on the upper part of FIG. 4, in which the axial portion 18 of the input ring 12 is reduced axially so as not to come straight above the rivet 34 and to leave the free to move vertically in the radial direction.

  Due to the cutout 36, the radial clearance between the inlet 12 and outlet 14 crowns is no longer necessarily limited by the difference between the inner and outer diameters of the rings 12, 14 respectively, which by default determine the radial dimensions of the annular housing 26 for installing the flexible tongues 16.

  Preferably, the coupling device 10 comprises absorption means which are interposed radially between the input element 12 and the output element 14 and which are able to deform elastically to absorb, in operation, the vibrations transmitted in particular to the device 10 by the driving member.

  Advantageously, the resilient means for absorbing vibrations are constituted by the flexible means 16 for compensating for radial tolerances. Indeed, the tabs 16 are capable of elastically deforming in the radial direction a first time during assembly of the coupling device 10 to compensate for radial tolerances between non-coaxial driving and driving members, and then to deform selectively during operation. that is to say when the coupling device 10 transmits a torque between the input ring 12 and the output ring 14. In operation, the flexible means 16 of the coupling device 10 are in particular capable of absorbing and filtering the vibrations by limiting their transmission of the member leading to the driven member and damping the radial movements due to the dynamic effects, for example unbalance movements in the case of an output element connected to a member driven by a clutch. As a variant, the elastic absorption means consist of means that are distinct from the flexible compensating means 16 and consist, for example, of additional means, such as springs, pads of elastomeric material, a ring of elastomer material, a spring plate or resilient tongues, friction means, or any other similar means which is capable of damping and / or limiting radial deflections between the input elements 12 and output 14 of the coupling device 10. Advantageously, the crown of 12 of the coupling device 10 is integral with a flexible flywheel 38 so as to constitute a unitary module 40.

  In known manner, the flexible flywheel 38 comprises at its outer radial periphery a starter ring 42. In a variant, such a starter ring 42 can be carried by the input ring 12, being for example attached to fixing or made of material on the outer annular face of the axial portion 18 of the ring 12. Preferably, the input ring 12 has in its axial portion an extra thickness for the formation of means 44 connecting such as pads having centrally a tapped hole 46 adapted to permit assembly by screwing with the flexible flywheel 38, here by screws 48 (see FIG. 2) whose heads bear against the vertical front face of the flexible flywheel 38.

  The studs 44 are advantageously distributed circumferentially in a regular manner on the input ring 12, the ring 12 comprising, for example, six studs which are arranged successively between each of the flexible tongues 16.

  Such a unitary module 40 is, in particular adapted to be, in a transmission assembly, interposed axially between a driving member formed by a motor shaft to which is usually connected in rotation the flexible flywheel 38 and a member of a clutch to which is connected in rotating the output element 14.

  In known manner, such a clutch is able to selectively transmit the torque between the drive member and a main axis driven member X formed by at least one gearbox shaft to which said clutch member is selectively connected. As a variant, the vertical part 20 of the input element 12 extends radially toward the center of the device 10 so as to form a web that can be directly connected to the driven member, such as the crankshaft of the engine, the flexible flywheel 38 then being advantageously removed. Advantageously, the output ring 14 comprises lugs 50 capable of allowing the output ring 14 of the coupling device 10 to be connected in rotation with a driven member, in particular for its attachment to at least one clutch member, such as a pressure plate, which is selectively connected to said driven member. The tabs 50 extend here vertically and are integral with the rear axial end of the portion 22 of the output ring 14 with which the tabs 50 are advantageously made of material. The output ring 14 comprises, for example, three lugs 50 which are distributed angularly in a regular manner, each of the lugs 50 advantageously comprising at least one hole 52 intended to allow the passage of fastening means, such as rivets or balusters, suitable for connect in rotation the output ring 14 to the driven member.

  A second embodiment of the coupling device 10 according to the invention which is illustrated in FIGS. 5 to 8 will now be described by comparison with the first embodiment. According to the invention, the coupling device 10 comprises at least one input element 12 formed by a ring which is adapted to be rotatably connected to the drive member of axis X 'and an outlet member 14 formed by a ring adapted to be rotatably connected to the member X-axis driven, and comprises flexible means 16 which are elastically deformable in a radial direction to at least radially compensate the tolerances between the driving and driven members of X 'and X axes. The flexible means 16 are rotatably connected respectively to the input element 12 and the output element 14 to ensure the transmission of the torque while compensating in particular the coaxiality defects between the axes X 'and X. The input ring 12 comprises a part a xiale 18 and a vertical portion 20 which respectively form the bars of an "L" corresponding to its profile in axial section. In this second embodiment of the invention, the input ring 12 is not connected directly by the only flexible means 16 to the output ring 14. Advantageously, the output element comprises an intermediate ring 54 which is interspersed kinematically between the input ring 12 and the output ring 14, which output ring 14 25 is intended to be connected to the driven member. In this second mode, the output ring 14 is arranged radially inside the inlet ring 12 and outside the intermediate ring 54, that is to say that the axial portion 22 of the crown 14 is interposed radially between those of the input rings 12 and intermediate 54. Unlike the first embodiment, the output ring 14 is open axially forward and not backward, its vertical portion 24 It is therefore adjacent to that of the input ring 12 so as to fit axially in the manner of nesting elements. However, the input ring 12 and the output ring 14 interpenetrate axially for the most part so that the device 10 has a reduced axial size. The intermediate ring 54 has a generally L-shaped axial section whose bars are respectively formed by an axial portion 56 and a vertical portion 58. Advantageously, the axial portions 18, 22 and 56 of the inlet crowns 12, 14 and intermediate 54 are at least partly superposed radially relative to each other so that the coupling device 10 has a small axial size. The flexible means - generally designated by the reference 16 - are advantageously constituted by tabs or strips of tongues having radially elastic deformation capacity to introduce a freedom of movement in the radial direction, between the input elements 12 and output 14 of the coupling device 10, and thus compensate radial tolerances and more particularly the coaxiality defects and dampen the radial deflections between the elements 12 and 14. The device 10 comprises a first group I of flexible tongues, here a pair 16A, 16'A, which are respectively arranged in a first annular housing 25 delimited, in the radial direction, by an inner annular face 28 of the axial portion 18 of the inlet ring 12 and by an outer annular face 60 of the axial part 56 of the intermediate ring 54. The device 10 comprises a second group II of flexible tongues, here a pair 16B, 16'B, arranged in a second annular housing 27 which, offset angularly with respect to the first housing 25, is delimited as the latter in the radial direction by an inner annular face 28 of the axial portion 18 of the input ring 12 and an outer annular face 60 of the axial portion 56 of the intermediate ring 54 when the axial portion 22 of the output ring 14 is interposed radially between those 18 and 56 of the inlet rings 12 and intermediate 54 respectively.

  The tabs 16A and 16'A of the first group I are each respectively connected in rotation to the input ring 12 and the intermediate ring 54 while the tongues 16B, 16'B are each respectively connected in rotation to the intermediate ring 54 and to the output ring 14.

  In the coupling device 10, the torque is thus transmitted from the input ring 12 to the output ring 14 through the intermediate ring gear 54. Advantageously, the flexible tabs 16A and 16'A forming the first group I constitute a first pair of flexible means 16 which are arranged diametrically opposite each other along a main axis of deformation A. In the same way, the flexible tongues 16B and 16'B forming the second group II constitute a second pair of flexible means 16 which are arranged diametrically opposite each other along a main axis of deformation B. The deformation axes A and B extend radially through the center O of the device 10 (in unassembled position) and the tabs 16 being distributed angularly in a regular manner. The radial axes of deformation A and B being orthogonal, their intersection determines angular sectors with an angle equal to 90 corresponding to a cardinal or "cross" positioning of the four tabs 16A, 16'a, 16B and 16'B. Advantageously, each flexible tongue 16A, 16B is matched to another flexible tongue 16'A, 16'B which is diametrically opposed to it.

  Advantageously, the degree of freedom of movement of a coupling device 10 according to this second embodiment is greater than that of the first mode. Indeed, the freedom of radial movement is "double" because it consists, on the one hand, of a first radial clearance between the input ring 12 and the intermediate ring 54 along the deformation axis A which is authorized by the first group of tongues 16A, 16'A and, secondly, a second radial clearance between the intermediate ring 54 and the output ring 14 along a deformation axis B which is authorized by the second group of tabs 16B, 16'B. Alternatively, the coupling device 10 comprises another intermediate ring interspersed kinematically between the input ring 12 and output 14, and a third group of flexible tongues so as to advantageously obtain a third radial clearance corresponding to an axis deformation C by analogy with the first embodiment. Alternatively, the first group of flexible means 16 comprises at least two pairs of tongues arranged between the input ring 12 and the intermediate ring 54, the tabs of each pair being arranged diametrically opposite one another along a given axis of deformation and the deformation axes of said pairs being for example orthogonal to each other. In the same way, the second group of flexible means 16 arranged between the intermediate ring 54 and the output ring 14 may comprise more than one pair of tongues, for example two pairs arranged along orthogonal deformation axes with respect to each other. to the other and advantageously offset angularly with respect to the deformation axes of the pairs of tongues of the first group. Each flexible tongue 16A, 16'A of the first group I is fixed by first fixing means 32 on the input ring 12 and is fixed by second fixing means 34 on the intermediate ring 54.

  In the same way, each flexible tongue 16B, 16'B is fixed by first fixing means 32 on the intermediate ring 54 forming the inlet and is fixed by second fastening means 34 on the output ring 14.

  As for the first mode, the fastening means 32, 34 of the flexible tongues 16 are preferably constituted by rivets, alternatively by any appropriate means. In this second mode as in the first, the first and second rivets 32, 34 for fixing the first pair of flexible tongues 16A, 16'A are arranged symmetrically with respect to the main axis of deformation A and the first and second rivets 32, 34 for fixing the second pair of flexible tongues 16B, 16'B are arranged symmetrically with respect to the main deformation axis B. In a variant, the first rivets 32 are arranged symmetrically with respect to a deformation axis A, B and the second rivets 34 are arranged on this radial axis of deformation of the flexible tongue. Advantageously, the deformation axes A and B constitute axes of symmetry of each flexible tongue 16. As can be seen in FIG. 6 or 7, each flexible tongue 16 is fixed at one of its circumferential ends to the input ring 12 or intermediate ring 54 by at least one rivet 32 and, at the other of its circumferential ends, on the intermediate ring 54 or on the output ring 14 by at least one rivet 34. As explained above, according to a determined direction of rotation - direct D or retrograde R, the scheduling of the first rivets 32 and the second rivets 34 determines, for each flexible tongue 16, whether the forces applied to said flexible tongue 16 during the transmission of torque are pulling forces or compressive forces.

  Preferably, for example for the first group I, the scheduling of the first and second rivets 32, 34 for fixing the first flexible tongue 16A and the scheduling of the first and second rivets 32, 34 for fixing the second flexible tongue 16 A are opposed so that, for a given direction of direct rotation D or retrograde R, the first tongue 16A works in tension when the second flexible tongue 16'A works in compression and vice versa. Advantageously, the orders of the rivets 32, 34 of the tabs 16B and 16'B of the second group II are determined in an analogous manner so that the efforts are balanced between the paired tabs of the same group.

  Advantageously, the flexible tongues 16A, 16'A, 16B, 16'B, the rivets 32, 34 for fixing said tongues and the axial portions 18, 22, 56 of the crowns 12, 54, 14 are generally coplanar in a median vertical plane. , said torque transmission, which is orthogonal to the axes X 'and X of the leading and driven bodies.

  Preferably, the coupling device 10 comprises absorption means which can be interposed radially between the input ring 12 and the intermediate ring 54 and / or between the intermediate ring 54 and the output ring 14. Advantageously, the absorption means are able to deform elastically to absorb or filter the vibrations transmitted to the device 10 by the driving member. The absorption means are preferably constituted by the flexible tongues which are on the one hand able to compensate for the radial tolerances and which, on the other hand, are still able to damp and / or limit radial deflections between the elements of input 12 and output 14 of the coupling device 10. Alternatively, the absorption means are constituted by additional means which are capable of damping and / or limiting the radial movements between the input elements 12 and output 14 of the coupling device 10. Advantageously, such absorption means are capable of forming stop means capable of preventing shocks between the rings 12, 14 and 54 of the device in the event of significant radial deflection. The elastic absorption means may be made in the form of many means, such as springs, pads of elastomeric material, a ring of elastomeric material, a spring plate or resilient tongues, friction means, etc. . Advantageously, the input ring 12 of the coupling device 10 is integral in rotation with a flexible flywheel 38 by means of assembly means 62, such as screws, so as to constitute a unitary module 40 illustrated in FIG. Figures 9 to 11. Advantageously, the output ring 14 has notches 64, respectively notches 64A and 64B associated with the flexible tongues of the first and second groups I and II which are in particular intended to allow greater radial deflection, especially without possible shocks between the rings 12, 54, 14 of the device 10 in the vicinity of the flexible tongues 16. Advantageously, the input ring 12 has holes 66 and the intermediate ring 54 of the holes 67 which, like the cuts 36 in the first mode , are also intended to allow a radial clearance without shocks between the heads of the rivets 32, 34 for fastening the tabs 16 and the parts facing each other. 12 and 54 of the device 10. This avoids in a simple way the risk of shocks between the rivets 32, 34 and crowns 12, 54, 14 which could cause unwanted noise. Preferably, the rings 12, 54 and 14 have, in their axial part 18, 56 and 22 respectively, stamped sections to form flats 68, 70 and 72 arranged here radially so that the flexible tongues 16A, 16'A, 16B and 16'B extend circumferentially rectilinear, that is to say generally tangentially to the adjacent portions of the rings 12, 54 and 14.

  Advantageously, the output ring 14 further comprises studs 74 which, similar to the tabs 50 of the first embodiment, are for example intended to allow its attachment with a member of a clutch selectively connected to the driven member, such as a shaft gearbox. We will now describe, in comparison with the first and more particularly the second mode, a third embodiment of a coupling device 10 according to the invention illustrated in FIGS. 9 to 11. As in the second embodiment, the coupling device 10 comprises respectively, in addition to the flexible means 16, an input ring 12, an output ring 14 and an intermediate ring 54 interspersedecinematically between the input ring 12 and the output ring 14. However, the radial arrangement of the rings 12, 54 and 14 differs.

  As can be seen in Figures 9 to 11, the output ring 14 is arranged radially inside the intermediate ring 54 which is itself arranged radially inside the inlet ring 12. Advantageously, the rings 12, 54 and 14 are nesting, that is to say that they fit axially globally into each other so that, their axial portions 18, 56 and 22 being radially superposed, the device Coupling 10 has a reduced axial size. Preferably, the flexible means - generally designated by the reference 16 - are constituted by tongues having an elastic deformation capacity in the radial direction so as to introduce a freedom of movement in the radial direction, between the input elements 12 and output device 14 of the coupling device 10. The device 10 comprises a first group I of flexible tongues constituted by a pair of tabs 16A, 16'A, which are respectively arranged in a first annular housing 25 delimited, in the radial direction, by a portion of the inner annular face 28 of the axial portion 18 of the input ring 12 and a portion of the outer annular face 60 of the axial portion 56 of the intermediate ring 54. The device 10 comprises a second group II of flexible tongues constituted by a pair of tongues 16B, 16'B which are respectively arranged in a second annular housing 27 which is delimited, in the radial direction, by a portion of the inner annular face 76 of the axial portion 56 of the intermediate ring 54 and by a portion of the outer annular face 30 of the axial portion 20 of the output ring 14 The tongues 16A and 16'A of the first group I are respectively each connected in rotation to the input ring 12 and the intermediate ring 54 while the tongues 16B, 16'B are respectively each connected in rotation to the intermediate ring. 54 and the output ring 14. As for the second mode, the flexible tongues 16A and 16'A forming the first group I constitute a first pair of flexible means 16 which are arranged diametrically opposite one of the another along a main axis of deformation A and the flexible tongues 16B and 16'B forming the second group II constitute a second pair of flexible means 16 which are arranged diametrically opposite one the other along a main axis of deformation B. The main deformation axes A and B extend radially through the center O of the device 10 (in unassembled position) and the tongues 16 are distributed angularly in a regular manner, the axes A, B being orthogonal, their intersection determines angular sectors of angle equal to 90 corresponding to a cardinal positioning of the four tabs 16A, 16'A, 16B and 16'B. Advantageously, each flexible tongue 16A, 16B is matched to another flexible tongue 16'A, 16'B which is diametrically opposite.

  Advantageously, the degree of freedom of movement in such a coupling device 10 according to the third mode, as for the second mode, is greater than that of the first embodiment. Thanks to the intermediate ring 54, the radial freedom of movement is "double" because it consists, on the one hand, of a first radial clearance between the input ring 12 and the intermediate ring 54 along the axis of deformation To which is allowed by the first group of tabs 16A, 16'A and, secondly, a second radial clearance between the intermediate ring 54 and the output ring 14 along a deformation axis B which is authorized by the second group of tabs 16B, 16'B. The coupling device 10 comprises first fixing means 32 and second fastening means 34 intended to fix each flexible tongue 16A, 16'A of the first group I respectively on the input ring 12 and the intermediate ring 54 and each flexible tongue 16B, 16'B of the second group II on the intermediate ring 54 and on the output ring 14. Preferably, the fastening means 32, 34 of the flexible tongues 16 are constituted by rivets.

  Advantageously, each tongue 16 is fixed to each of two rings among the input rings 12, intermediate 54 and output 14 which are adjacent by three attachment points and no longer two. As illustrated in FIG. 9, the first attachment means consist of two rivets 32 while the second fixing means consist of a rivet 34. In a variant, the device 10 comprises first fastening means formed by a rivet 32 and second fixing means formed by two rivets 34. Advantageously, the first fastening rivets 32 of the first pair of flexible tongues 16A, 16'A are arranged symmetrically with respect to the main axis of deformation A and the first rivets 32 of fixing the second pair of flexible tabs 16B, 16'B are arranged symmetrically with respect to the main axis of deformation B. Advantageously, the second rivets 34 for fixing the first pair of flexible tabs 16A, 16'A are arranged on the main axis of deformation A and the second rivets 34 for fixing the second pair of flexible tongues are arranged on the main axis of deformation B. Thanks to such an arrangement of the rivets 32, 34 to achieve the fixing of each flexible tongue 16 at three points, regardless of the direct direction of rotation D or retrograde R, the tensile or compressive forces applied to each flexible tongue 16 during torque transmission, are balanced. The duplication of one 32 of the fastening means 32, 34 or the other 34 to obtain the third point of attachment has no impact on this result since their implantations respect the aforementioned symmetries, it is no longer necessary to pay attention to the scheduling of the rivets 32, 34. Advantageously, the coupling device 10 comprises elastic vibration absorption means which are constituted by the flexible means 16 for compensating the radial tolerances. Advantageously, the input ring 12 of the coupling device 10 is integral with a flexible flywheel 38 so as to constitute a unitary module 40. In a variant, the output element 14 of the coupling device 10 according to the invention is integral with the driven member, or a member connected to said driven member, with which the coupling device 10 then forms a unitary module. As in the first embodiment, the input ring 12 has in its axial portion 18 an extra thickness for the formation of means 44 connecting, such as pads, having centrally a threaded hole 46 adapted to allow a screw connection with the flexible flywheel 38, here by screws 48 whose heads bear against the vertical front face of the flexible flywheel 38 as is more particularly visible on the lower part of FIG. 11. The studs 44 are advantageously split and the pairs of studs 44 distributed circumferentially evenly on the input ring 12, successively between each of the flexible tongues 16. As in the first embodiment, the output ring 14 has tabs 50 capable of allowing the ring of output 14 of the coupling device 10 with a driven member, in particular for its attachment to at least one clutch member, such as a flat reaction water, which is selectively connected to said driven member. The tabs 50 extend here vertically and are integral with the rear axial end of the portion 22 of the output ring 14 with which the tabs 50 are advantageously made of material. As illustrated in FIG. 9, the output ring 14 comprises, for example, three tabs 50 which are distributed angularly in a regular manner, each of the tabs 50 comprising here two holes 52 intended to allow the passage of fastening means, such as rivets or Columns, able to connect in rotation the output ring 14 to the driven member. Such a unitary module 40 is, in particular adapted to be, in a transmission assembly, interposed axially between a driving member formed by a motor shaft to which is usually connected in rotation the flexible flywheel 38 and a member of a clutch to which is connected in rotation of the output element 14. In known manner, such a clutch is able to selectively transmit the torque between the drive member of axis X 'and a main axis driven member X formed by at least one box shaft. speeds at which said clutch member is selectively connected. Advantageously, the input element 12 of the coupling device 10 is then linked to the motor via the flexible flywheel 38 which is respectively rotatably connected to the motor shaft at its radial inner periphery and the element input 12 of the coupling device 10 at its outer radial periphery. Document FR-A-2,890,716 describes an exemplary embodiment of a flexible flywheel according to the state of the art. The invention is therefore advantageously adapted to be implemented in a transmission assembly, in particular a transmission assembly for coupling an internal combustion engine and a motor vehicle gearbox.

  In such a transmission assembly, the coupling device 10 according to the invention is associated with a multiple clutch mechanism, such as a double clutch, comprising a reaction plate to which the output element 14 of the device coupling is for example linked in rotation.

  Such a multiple clutch mechanism is for example described in the document FR-A-2,893,370 of the state of the art which will be referred to advantageously for further details. Advantageously, the clutch associated with the coupling device 10 according to the invention is a multiple clutch comprising a double damping flywheel which comprises a primary flywheel and a secondary flywheel between which is mounted a torsion damper, the output element 14 of the device being for example linked in rotation to said primary flywheel of the double damping flywheel. As a variant, such a double damping flywheel is still likely to be associated with a single or single clutch. Alternatively, the coupling device 10 according to the invention is interposed axially between a double damping flywheel and a single or multiple clutch mechanism so that the input element 12 of the device 10 is connected in rotation to the secondary flywheel the double damping flywheel and that the output member 14 is rotatably connected to a member of the clutch, such as the reaction plate.

  Advantageously, the primary flywheel of the double damping flywheel is then connected in rotation to the crankshaft directly or via a flexible flywheel. Preferably, the clutch associated with the coupling device 10 comprises at least one torque limiting device, such as the device incorporated in a double damping flywheel which is for example described in the document FR-A-2,825,129 to which we refer. postpone for further details. According to another example of possible application, the clutch associated with the coupling device 10 is a hydrokinetic coupling device of the type comprising at least one casing to which is connected in rotation the output element 14 of the coupling device 10 As will be understood, the coupling device 10 according to the invention is capable of being applied industrially in the field of transmissions, in particular for a motor vehicle. An example of a preferred application of the coupling device 10 according to the invention will now be described in detail to a transmission assembly 1, in particular for a motor vehicle, in which the device 10 is associated with a multiple clutch 100, more particularly a mechanism double clutch type. In the following description, the elements relating to the double clutch 100 will be designated by reference numerals in hundred, 102, 104 etc. while the same reference numerals will be used for the coupling device 10 according to the invention.

  The coupling device 10 is similar to that of the third embodiment according to the invention shown in FIGS. 9 to 11 and previously described by comparison, a description to which reference will be made advantageously. FIG. 12 shows the upper half of a double friction clutch 100 which has a shape of revolution about an axis X rotation.

  The clutch 100 is intended to temporarily couple a motor shaft 102 which is arranged axially forward and a rear end of which is shown on the left in FIG. 12, with at least one driven shaft 104.

  The drive shaft 102 is rotatable about an axis of rotation X 'and is usually constituted by the crankshaft which is rotated by a motor (not shown) of the motor vehicle. The double clutch 100 comprises two concentric driven shafts 104A, 104B which are rotatably mounted coaxially with the drive shaft 102. The first driven shaft 104A forms an axial tube inside which the second driven shaft 104B is arranged. A free leading end portion 106 of the second driven shaft 104B protrudes axially from the forward end of the first tubular driven shaft 104A. Each of the driven shafts 104A, 104B is rotatable independently of the other. The drive shaft 102 constitutes the X axis driving member and the driven shafts 104A, 104B connected to a gearbox the driven member of axis X 'whose coupling device 10 according to the invention is advantageously suitable. to compensate for the radial tolerances, in particular the deviations caused by the coaxiality defects between X 'and X. The driven shafts 104A, 104B are connected to a gearbox (not shown) arranged rearward, to the right in FIG. 12 More particularly, the first driven shaft 104A corresponds to certain gear ratios of the gearbox, for example the even gear ratios, while the second driven shaft 104B corresponds to the other gear ratios, for example odd gear ratios. . The double clutch 100 comprises first temporary coupling means of the first driven shaft 104A with the drive shaft 102. In known manner, the double clutch 100 comprises a circular radial reaction plate 108 which is rotatably mounted about the axis of rotation X, through a bearing, constituted in this example by a ball bearing 110. The ball bearing 110 is here interposed radially between the inner cylindrical face 112 of a central orifice of the reaction plate 108 and a leading end portion 114 of the first tubular driven shaft 104A. The inner cylindrical face 112 of the reaction plate 108 has a radial rear end shoulder face 116 against which an outer ring of the ball bearing 110 is intended to be axially supported. The front end portion 114 of the first driven shaft 104A also has a radial rear end shoulder face 118 against which an inner ring of the ball bearing 110 is to be axially supported rearwardly. An elastic ring 120 of the "circlip" type is arranged in a groove of the first driven shaft 104A axially in front of the ball bearing 110. Thus, the inner ring of the ball bearing 110 is axially locked in both directions. In this configuration, the inner ring of the ball bearing 110 is rotated by the first driven shaft 104A, while the outer ring of the ball bearing 110 is rotated by the reaction plate 108. The reaction plate 108 is thus rotatably connected to the first driven shaft 104A and is immobilized axially, particularly with respect to the gearbox.

  Furthermore, the reaction plate 108 is at its outer radial periphery integral in rotation with the drive shaft 102 by means of the coupling device 10. Indeed, the input ring 12 of the device 10 is rotatably connected. to the motor shaft 102, directly or via a flexible flywheel 38, while the output ring 14 is connected to a member of the clutch 100, here the reaction plate 108 which is itself suitable to be selectively connected to one and / or the other of the trees 104A, 104B.

  Preferably, the clutch 100 here comprises a flexible flywheel 38 so that the input ring 12 of the coupling device 10 is for example linked in rotation to the flexible flywheel 38 with which the device 10 advantageously forms a unitary module 40.

  The flexible flywheel 38 is arranged in front of the clutch 100 and has at its inner radial periphery holes 122 for the fastener passage 124 intended to conventionally secure its attachment, coaxially to the X-axis drive shaft 102. The flexible flywheel 38 is again connected in rotation to its outer radial periphery to the input ring 12 of the device 10, for example by means of screws 48 (not shown in the section of FIG. 12), each of which heads is in abutment against the vertical front face of the flexible flywheel 38 and whose threaded rods are each received in the threaded hole 46 complementary to one of the studs 44 that comprises the input ring 12 in its axial portion 18 of greater thickness . The output ring 14 comprises lugs 50 to enable the output ring 14 of the coupling device 10 to be rotatably connected to a driven member, more precisely here its attachment to the reaction plate 108 which is able to be connected selectively to at least one of the X-axis shafts 104A, 104B forming said driven member in the sense of the present invention. The tabs 50 extend here vertically and are integral with the rear axial end of the portion 22 of the output ring 14 with which the tabs 50 are advantageously made of material. As illustrated in FIG. 9, the output ring 14 may comprise, for example, three tabs 50 which are distributed angularly in a regular manner, each of the tabs 50 comprising at least one hole 52 (not shown) intended to allow the passage of fastening means. 126. Advantageously, the fastening means 126 are constituted by columns which ensure, on the one hand, the rotational connection of the output ring 14 of the coupling device 10 with the pressure plate 108 of the clutch 100 and, d secondly, the rotational connection of a radially inner cover 128 of the clutch 100. In known manner, the flexible flywheel 38 comprises at its periphery a start ring 42. The clutch 100 comprises a first annular pressure plate 130 which is mounted integral in rotation with the reaction plate 108 about the axis of rotation X. The first pressure plate 130 is more particularly arranged axially in relation to a rear face 132 of the reaction plate 108. When assembling the clutch 100 mounted on the shafts 104A, 104B with the drive shaft 102, the coupling device 10 which is interposed axially is, thanks to the radial elastic deformation of the flexible tongues 16, to compensate for the coaxial defects between the X 'and X axes. Indeed, the input ring 12 is rotatably connected by the flexible flywheel 38 to the motor shaft 102 of 'X axis' while the output ring 14 is rotatably connected to the pressure plate 108 of the clutch 100 which is mounted on one of the X axis output shafts 104. Advantageously, the flexible tongues 16 are still which can absorb in operation, in particular when a torque is transmitted from the drive shaft 102 to the output shafts 104A, 104B via the device 10 and the associated clutch 100, the radial movements, such as those caused by the unbalance phenomenon of the clutch ge. In known manner, the unbalance phenomenon corresponds in particular to the vibrations occurring during the rotation of an object having an imbalance generally caused by an unequal distribution of the mass on a volume of revolution, here that of the clutch 100.

  The main components of such a double clutch 100 will now be described for the purpose of memory by which the torque supplied by the drive shaft 102 is selectively transmitted to the reaction plate 108 and finally to the shafts 104A and / or 104B, having of course crossed previously the coupling device 10 according to the invention. The first pressure plate 130 is slidably mounted axially relative to the reaction plate 108. The clutch 100 comprises a first coaxial friction disk 134 which is interposed axially between the reaction plate 108 and the first pressure plate 130. friction disc 134 has on both sides an annular friction lining 136 which is arranged axially opposite the first pressure plate 130. The first friction disc 134 is intended to be clamped against the rear face 132 of the plate by the first pressure plate 130 for temporarily coupling the first driven shaft 104A with the motor shaft 102. For this purpose, the first friction disc 134 is mounted to rotate with the first driven shaft 104A, and is mounted sliding axially on the first tubular driven shaft 104A between a tight front position against the rear face 132 of the reaction plate 108 and a rear position re free towards which it is elastically returned and in which the first friction disc 134 is moved away from the rear face 132 of the reaction plate 108.

  The axial clearance existing between the first friction disc 134 in its free rear position and the rear face 132 of the reaction plate 108 is very small and, by convention, it has not been shown in FIG. 12. The clutch 100 comprises a first coaxial annular diaphragm 138 for actuating the first pressure plate 130.

  In known manner, the first diaphragm 138 comprises a radially outer ring and resilient fingers extending radially towards the axis of rotation X from the ring to a free inner end. More particularly, the first pressure plate 130 is interposed between the reaction plate 108 and the first diaphragm 138.

  The first diaphragm 138 is supported on the first radially inner annular cover 128 which is fixed to the reaction plate 108. In the extreme forward clutching position, the first driven shaft 104A is temporarily coupled to the drive shaft 102, and in the extreme position the first friction disc 134 is moved away from the reaction plate 108 and the first pressure plate 130 so that the first driven shaft 104A is decoupled from the drive shaft 102. The double clutch 100 also comprises second means coupling means for the temporary coupling of the second driven shaft 104B with the motor shaft 102. These second coupling means comprise a second pressure plate 140 and a second friction disk 142 for the temporary coupling of the second driven shaft 104B with the motor shaft 102. The functions of the second pressure plate 140 and the second friction disk 142 are respectively similar those of the first pressure plate 130 and the first friction disk 134. The second pressure plate 140 is mounted axially opposite the front face 144 of the reaction plate 108.

  The second pressure plate 140 is rotatably connected to the reaction plate 108 via a second cover 146 which notably comprises a cylindrical axial skirt which extends forwardly, surrounding the first cover 128, up to to the second pressure plate 140 to which it is attached.

  The second pressure plate 140 is slidably mounted axially with respect to the reaction plate 108.

  The second coaxial friction disk 142 is interposed axially between the reaction plate 108 and the second pressure plate 140. It also comprises on its two faces an annular friction lining 148 which is interposed axially between the front face 144 of the reaction plate. 108 and the second pressure plate 140. The second friction disc 142 is intended to be clamped against the front face 144 of the reaction plate 108 by the second pressure plate 140 to temporarily couple the second driven shaft 104B with the motor shaft 102.

  For this purpose, the second friction disc 142 is rotatably mounted to the second driven shaft 104B, and is axially slidably mounted on the front end portion 106 of the second driven shaft 104B between a rear position pressed against the front face 144 of the reaction plate 108 and a free front position to which it is resiliently biased and wherein the second friction disc 142 is moved away from the front face 144 of the reaction plate 108. The clutch 100 further comprises a second annular diaphragm 150 annular coaxial for the actuation of the second pressure plate 140. The second diaphragm 150 has a conventional structure, similar to that of the first diaphragm 138. The fingers of the second diaphragm 150 are elastically flexible between: an extreme front clutch position in which the second diaphragm 150 biases axially towards the rear the second pressure plate 140 to the first friction disc 142 against the reaction plate 108, through the second sliding rear cover 146, and a rearward disengaging extreme position towards which the fingers are elastically biased and in which the second pressure plate 140 is more axially biased so that the second friction disc 142 is in its free forward position, as shown in FIG.

  Thus, in the extreme forward clutching position, the second driven shaft 104B is coupled to the drive shaft 102, and in the rearmost disengaging position, the second driven shaft 104B is decoupled from the drive shaft 102.

  In known manner, the clutch 100 further comprises means 152 able to independently control the first diaphragm 138 and the second diaphragm 150 to selectively transmit to one and / or the other gearbox shafts 104A, 104B. torque transmitted by the coupling device 10 according to the invention of the drive shaft 102 to the reaction plate 108. Advantageously, the clutch 100 shown in Figure 12 comprises conventional damping means which are integrated friction discs 134 and 142. In variant not shown, the damping means belong to a double damping flywheel interposed axially between the engine and the coupling device 10 or between the coupling device 10 and the clutch 100. As we As will be understood, the coupling device 10 according to the invention firstly makes it possible, during assembly, to facilitate the coupling between the crankshaft 102 of the engine and the assembly formed by the embra 100 and the gearboxes 104A, 104B. Indeed, the flexible means 16 of the coupling device 10 according to the invention are then capable of elastically deforming along one or more deformation axes A, B or C to compensate for the aforementioned radial tolerances, in particular induced by a defect of coaxiality between the axes X 'and X. When the parts 102, 38, 12, 14, 100-108 and 104 of the transmission assembly 1 are coupled, the radial tolerances are compensated by the tongues which have elastically deformed according to the radial direction in order to allow relative movement between the input element 12 connected to the drive member of axis X 'and the output element 14 connected to the driven member of axis X.

  As explained above, the rings 12 and 14, or even 54 of the device 10 are no longer concentric with respect to the center O, the relative displacement of each of them being a function of the radial tolerances compensated by the flexible tongues 16.

  Advantageously, the arrangement of the tongues 16 is thus determined so as to offer a radial displacement capacity between the rings 12, 14 and 54 sufficient to compensate for all or part of the radial tolerances, for example by deforming along at least a first axis of deformation A and / or along a second deformation axis B, orthogonal to the first axis A. The coupling device 10 according to the invention, by compensating the radial tolerances, makes it possible to guarantee optimum transmission of the torque between the drive shaft 102 and the shafts 104A, 104B advantageously limiting the transmission of additional forces that may cause premature wear, or even breakage of certain mechanical members. In addition, the flexible means 16 of the coupling device 10 according to the invention are also capable of deforming elastically in the radial direction when, in operation, a torque received by the input element 12 of a driving member is transmitted to the output element 14 to a driven member. Indeed, the tabs 16 are, parallel to the torque transmission, capable of elastically deforming permanently to dampen or absorb vibrations, such as vibrations transmitted to the device by the motor shaft 102 or the vibrations produced by the movements dynamic radial caused in particular by the presence of an unbalance in the clutch 100.

Claims (30)

  Coupling device (10) capable of transmitting a torque between a main axis driving member X 'and a main axis driven member X, characterized in that the coupling device (10) comprises at least one input member (12) adapted to be rotatably connected to the driving member, an output member (14) adapted to be rotatably connected to the driven member and flexible means (16) which, respectively rotatably connected to the input element (12) and the output element (14) to ensure the transmission of the torque, are able to deform elastically in a radial direction, orthogonal to the X 'and X axes, so as to compensate radially the tolerances between the driving and driven members of axes X 'and X.   2. Coupling device (10) according to claim 1, characterized in that the input element (12) is constituted by a ring, said input, comprising at least one axial portion (18) and the output member (14) is constituted by at least one so-called output ring having at least one axial portion (22) and in that the output ring (14) is arranged radially inside or outside the inlet ring (12) so that at least a portion of said axial portions (18, 22) are superposed.   3. Coupling device (10) according to claim 2, characterized in that the output element (14) comprises an intermediate ring (54) which, having at least one axial portion (56), is interposed radially between the input ring (12) and the output ring (14).   4. coupling device (10) according to claim 2, characterized in that the output member (14) comprises an intermediate ring (54) which, having at least one axial portion (56), is interposed radially to the interior of the input ring (12) and the output ring (14).   5. Coupling device (10) according to any one of claims 2 to 4, characterized in that each flexible means (16) is arranged in an annular housing (25, 26, 27) delimited respectively, in the radial direction by an inner annular face (28, 76) of an axial portion (18, 56) and an outer annular face (30, 60) of another axial portion (22, 56), the axial portions belonging respectively to each two rings among the input (12), intermediate (54) and output (14) rings which are adjacent to said flexible means (16).   6. A coupling device (10) according to any one of claims 2 to 5, characterized in that each flexible means (16) is respectively rotatably connected to each of the two rings among the input rings (12), intermediate (54) and outlet (14) which are radially adjacent to said flexible means.   Coupling device (10) according to one of Claims 2 to 6, characterized in that the flexible means (16) are regularly angularly distributed at an angle (a) on the circumference of the axial parts (18). , 22) inlet (12) and outlet (14) rings or axial portions (18, 56, 22) of the inlet (12) and intermediate (54) and intermediate (54) crowns and output (14) respectively.   8. Coupling device (10) according to any one of claims 2 to 7, characterized in that the flexible means (16) are constituted at least by a first pair (I) of flexible means (16A, 16'A ) which are diametrically opposed along a main axis of deformation (A) and by a second pair (II) of flexible means (16B, 16'B) which are diametrically opposed along a main axis of deformation (B) orthogonal to the axis main deformation (A) of the first pair (I) of flexible means (16A, 16'A).   9. Coupling device (10) according to any one of the preceding claims, characterized in that eachflexible means (16A, 16B, 16C) is matched to another flexible means (16'A, 16'B, 16'C ) which is diametrically opposed to it.   Coupling device (10) according to one of the preceding claims, characterized in that each flexible means (16) is fixed respectively by first fixing means (32) on the input element (12). or the intermediate element (54) and second fixing means (34) on the intermediate element (54) or on the output element (14).   11. Coupling device (10) according to any one of the preceding claims, characterized in that each flexible means (16) is fixed at one of its ends, by the first fastening means (32) on the the input member (12) or the intermediate member (54) and is attached at the other end thereof by the second fastening means (34) to the intermediate member (54) or the member output (14).   12. Coupling device (10) according to any one of the preceding claims, characterized in that the first fastening means (32) are arranged symmetrically with respect to the second fastening means (32, 34) in at least one axis radial deformation (A) and / or (B) and / or (C) of the flexible means (16).   Coupling device (10) according to claim 10, characterized in that each flexible means (16) is fixed at one and the other of its ends by the first fastening means (32) on the input member (12) or the intermediate member (54) and is fixed by the second fastening means (34), arranged centrally between said ends, on the output member (14) or the intermediate member (54). ).   14. A coupling device according to claim 13, characterized in that the first fastening means (32) are arranged symmetrically with respect to a radial axis of deformation (A, B, C) of the flexible means (16) and in that that the second fastening means (34) are arranged on said radial deformation axis (A, B, C) of said flexible means (16).   Coupling device according to any one of Claims 10 to 12, characterized in that, in a determined direction of rotation -direct (D) or retrograde (R), the scheduling of the first (32) and second ( 34) fixing means is determined for each flexible means (16) so that the forces applied to the flexible means during the transmission of torque are tensile forces or compressive forces.   16. Coupling device according to any one of claims 9 to 12, characterized in that for a given pair of flexible means (16) consisting of a first flexible means (16A, 16B) and a second flexible means (16'A, 16'B), the scheduling of the first and second means (32, 34) for fixing the first flexible means (16A, 16B) and the scheduling of the first and second means (32, 34) of fixing the second flexible means (16'A, 16'B) are determined so that, for the direction of rotation - direct (D) or retrograde (R) - chosen, the first flexible means (16A, 16B) works in traction when the second flexible means (16'A, 16'B) works in compression and vice versa.   17. Coupling device (10) according to one of claims 13 or 14, characterized in that, regardless of the direct direction of rotation (D) or retrograde (R), the tensile or compressive forces applied to the flexible means (16) during the torque transmission are balanced when the flexible means (16) is fixed at one and the other of its ends by the second fastening means (34) and is fixed centrally between said ends by the first fastening means (32).   18. Coupling device (10) according to any one of claims 9 to 17, characterized in that the fastening means (32, 34) of the flexible means (16) are rivets.   19. Coupling device (10) according to any one of the preceding claims, characterized in that the flexible means (16) consist of at least one flexible tongue.   Coupling device (10) according to one of Claims 2 to 19 taken in combination with Claim 10, characterized in that the flexible means (16), the fastening means (32, 34) and the parts axial (18, 56, 22) crowns (12, 54, 14) are coplanar in a median vertical plane, said torque transmission, orthogonal axes X 'and X.   21. Coupling device (10) according to any one of the preceding claims, characterized in that the coupling device (10) comprises absorption means which, radially interposed between the input element and the output element, are able to deform elastically to absorb vibrations transmitted to the device by the driving member.   22. Coupling device (10) according to claim 21, characterized in that the resilient means of vibration absorption are constituted by the flexible means (16).   23. Coupling device (10) according to one of claims 21 or 22, characterized in that the elastic absorption means are constituted by means, such as springs, pads of elastomeric material, a ring of material elastomer, a spring plate or resilient tongues, friction means, which are capable of damping and / or limiting the radial movements between the input (12) and output (14) of the device.   24. Coupling device (10) according to any one of the preceding claims, characterized in that the input element (12) of the coupling device (10) is integral in rotation with a flexible flywheel (38). ) so as to form a unitary module (40).   Transmission assembly (1), in particular for coupling a motor and a gearbox, comprising at least one coupling device (10) according to any one of the preceding claims which is associated with a clutch (100) for selectively transmitting the torque between the main axis driving member X 'formed by a drive shaft (102) and the main axis driven member Xformed by at least one gearbox shaft (104A , 104B) to which is selectively connected at least one member (108) of the clutch, characterized in that the associated clutch is a multiple clutch mechanism, such as a dual clutch, having a reaction plate (108) and in that the output member (14) of the coupling device (10) is rotatably connected to said member of the clutch (100), such as the reaction plate (108).   26. Transmission assembly (1), in particular for coupling a motor and a gearbox, comprising at least one coupling device (10) according to any one of the preceding claims which is associated with a clutch (100) for selectively transmitting the torque between the main axis driving member X 'formed by a driving shaft (102) and the main axis driven member X formed by at least one transmission shaft ( 104A, 104B), characterized in that the associated clutch (100) is a clutch comprising a double damping flywheel which comprises a primary flywheel and a secondary flywheel between which is mounted a torsion damper and in that the output element (14) of the coupling device (10) is rotatably connected to the primary flywheel of the double damping flywheel.   27. Transmission assembly (1), in particular for coupling a motor and a gearbox, comprising at least one coupling device (10) according to any one of the preceding claims which is associated with a clutch (100) for selectively transmitting the torque between the main axis driving member X 'formed by a driving shaft (102) and the main axis driven member X formed by at least one transmission shaft ( 104A, 104B), characterized in that the associated clutch (100) is a clutch comprising a double damping flywheel which comprises a primary flywheel and a secondary flywheel between which is mounted a torsion damper and in that the element of input (12) of the coupling device (10) is rotatably connected to the secondary flywheel of the double damping flywheel and the output element (14) of the coupling device (10) is rotatably connected to at least one member of the clutch (100).   28. Transmission assembly (1) according to any one of claims 25 to 27, characterized in that the clutch (100) associated with the coupling device (10) comprises at least one torque limiting device.   Transmission assembly (1), in particular for coupling a motor and a gearbox, comprising at least one coupling device (10) according to any one of the preceding claims which is associated with a clutch (100) for selectively transmitting the torque between the main axis driving member X 'formed by a driving shaft and the main axis driven member X formed by at least one gearbox shaft to which is selectively connected at least one member of the clutch (100), characterized in that the associated clutch (100) is a hydrokinetic coupling apparatus having at least one housing and that the output member (14) of the coupling (10) is rotatably connected to the casing of the hydrokinetic coupling apparatus.   Transmission assembly (1) according to one of claims 25 to 29, characterized in that the input element (12) of the coupling device (10) is connected to the motor via a flexible flywheel (38) which is respectively rotatably connected to the motor shaft and the input element (12) of the coupling device (10) or the primary flywheel of a double damping flywheel.