WO2017174583A1

WO2017174583A1 - Assembly for torque-transmission device, torque-transmission device and methods for assembling same

Info

Publication number: WO2017174583A1
Application number: PCT/EP2017/057994
Authority: WO
Inventors: Laurent Dequesnes
Original assignee: Valeo Embrayages
Priority date: 2016-04-04
Filing date: 2017-04-04
Publication date: 2017-10-12
Also published as: CN109073036A; FR3049671B1; DE112017001837T5; FR3049671A1

Abstract

The invention relates to an assembly for a torque-transmission device of a motor vehicle power transmission chain, in particular for a clutch, said assembly comprising: an element (3) including a hub (5), an annular bearing (6) mounted on the hub (5), in which the hub (5) has: a first axial bearing surface (34), a cylindrical surface (33) which is bordered axially on one side by the first axial bearing surface (34) and on the other side by a groove (29), a second axial bearing surface (36) being formed by a bulge (35) obtained by pushing material of said hub towards the groove (29); the annular bearing (6) being mounted against the cylindrical surface (33) and inserted axially between the two axial bearing surfaces (34, 36) so as to be held axially.

Description

TORQUE TRANSMISSION DEVICE ASSEMBLY, TORQUE TRANSMISSION DEVICE, AND METHODS OF MOUNTING

Technical area

The invention relates to the field of torque transmission devices and, more particularly, torque transmissions in the automotive field.

Technological background

In the field of automotive torque transmissions, it is known torque transmission devices comprising an input member and an output member rotatable about a common axis of rotation and coupled by resilient damping means. These torque transmission devices, also known as torsion dampers, make it possible to transmit a torque from the engine to the wheels of the vehicle while absorbing and damping the vibrations and acyclisms generated by an internal combustion engine.

Such torsion dampers equip including double damping flywheels (DVA), friction clutch, in the case of a manual or robotic transmission, or locking clutches, also called "lock-up" clutches, equipping the devices hydraulic coupling, in the case of an automatic transmission.

The input member and the output member are movably mounted in relative rotation by a bearing such as a rolling bearing. This bearing is interposed between a hub of the input element and a hub of the output element to allow relative movement between these elements. In order to be held in position on the output member, the rolling bearing is locked axially between an inner shoulder of the hub of the output member and an elastic stop ring. This stop ring is mounted by hand in a circular groove of an inner face of the hub of the output member. This circular groove requires precise machining to ensure a stable and reliable retention of the stop ring on the hub of the output member, making it both the realization of the circular groove and the positioning of the stop ring in said circular groove. The mounting of such bearings between the input element and the output element are for example illustrated in the documents EP2886907 A1 or FR301 1602 A1.

Thus, the mounting of the bearings in this type of torsion damper requires a large number of parts. In addition, the steps of mounting the bearing on each element are complex and require a delicate mounting precision.

There is therefore a need for torque transmission devices having a simple structure that are easy and quick to assemble.

Object of the invention

One aspect of the invention is based on the idea of solving the disadvantages of the prior art by proposing a torque transmission device which has a simple structure and which is quick and easy to assemble.

According to one embodiment, the invention provides an assembly for a transmission link torque device of a motor vehicle, in particular for a clutch, said assembly comprising: an element comprising a hub,

an annular bearing mounted on the hub,

wherein the hub has:

a first axial bearing surface,

a cylindrical surface which is axially bordered on the one hand by the first axial bearing surface and on the other hand by a groove,

a second axial bearing surface being formed by a bulge obtained by pushing back material from said hub towards the groove; the annular bearing being mounted against the cylindrical surface and arranged axially between the two axial bearing surfaces so as to be retained axially.

Thus, such an assembly for a torque transmission device has a simple structure. In particular, such an assembly for a torque transmission device does not require additional parts, such as a stop ring, to maintain the bearing in position on at least Γ element. In addition, this set for a torque transmission device is easy and quick to assemble since it requires only a simple deformation of the element to ensure the maintenance of the bearing. The bearing must be interpreted here as a rotational guiding element of the elements of the torque transmission device. The term "bearing" includes both plain bearings, in particular having a single ring, which rolling bearings having an inner ring and an outer ring.

The presence of the groove advantageously allows the material discharge of the hub to form the second axial bearing surface without the discharge material does not generate modification of the cylindrical surface. Thus, the material discharge of the hub forming the second axial bearing surface does not generate pressure on the annular bearing.

According to other advantageous embodiments, such an assembly for a torque transmission device may have one or more of the following characteristics:

- The second axial bearing surface projects radially from the groove.

- The annular bearing is mounted against the cylindrical surface and interposed axially between the two axial bearing surfaces so as to be retained axially.

- The annular bearing is mounted against the cylindrical surface and axially interposed without play between the two axial bearing surfaces so as to be axially locked.

- The annular bearing is mounted against the cylindrical surface and arranged axially between the two axial bearing surfaces so as to be retained axially, an axial play being present between the bearing and the second axial bearing surface. Thus, an axial retaining means is provided and the risk of damaging the bearing is further reduced.

the hub and the bearing are coaxial around an axis of rotation X.

the throat is an annular groove.

the groove is an annular groove bordering the cylindrical surface around the axis of rotation.

the groove is local, in other words it extends over a limited angular sector around the axis of rotation X, for example 20 degrees.

the bulge is obtained by a local discharge of material in the direction of the throat. By local displacement is meant a displacement carried out on a limited angular sector around the axis of rotation X, in particular less than 30 degrees, for example 20 degrees.

preferably, the local discharge is carried out on an angular sector less than or equal to 20 degrees, for example 5 or 10 degrees. Thus it is easier to achieve the discharge of material, the appearance of cracks is avoided and the upsets can be made without the need to turn the hub. In particular, the hub can be fixed during the discharge step and the discharge can be carried out for example by an axially displaced punch. The process is simple.

the second axial bearing surface is formed by a plurality of bulges obtained by local delivery of material towards the groove.

the bulges formed by the discharge of material inside the groove are regularly distributed over the circumference of the hub.

the bearing comprises an inner ring and an outer ring radially offset from one another, one of the inner ring and the outer ring being carried by the cylindrical surface and interposed axially between the two axial bearing surfaces, the bearing further comprising rolling bodies housed in a running space, said running space comprising an outer raceway arranged on a inner circumference of the outer ring and an inner raceway formed on the outer periphery of the inner ring.

- The bearing is a plain bearing.

the bulge includes cast iron, especially vermicular or spheroidal cast iron. The cast iron has indeed a good ductility, especially better than steel, which promotes the realization of the bulge. According to one embodiment, the bulge is cast iron, especially vermicular or spheroidal cast iron. According to one embodiment, the hub is cast iron, especially vermicular or spheroidal cast iron.

When the discharge is local, the realization of a local discharge on the cast iron greatly reduces the risk of crack on the hub and avoids deformations of the cylindrical surface. The realization of the bulge is simple and the pressure necessary to achieve the discharge can also be reduced.

According to one embodiment, the invention also provides a torque transmission device for a motor vehicle transmission chain, in particular for a clutch, comprising an assembly such as above and a complementary element mounted to rotate in rotation. relative to the other about an axis of rotation X by means of the annular bearing, the annular bearing being radially interposed between the hub of the element of the assembly and a complementary hub formed on Γ complementary element.

According to other advantageous embodiments, such a torque transmission device may have one or more of the following characteristics:

the other of the inner ring and the outer ring is carried by the complementary hub.

the other inner or outer ring is mounted in force on the corresponding hub.

the inner ring cooperates with the outer ring to guide relative rotation of the element of the assembly and the complementary element. a torque transmission member is arranged between the element of the assembly and the complementary element to transmit a torque between the element of the assembly and the complementary element.

- The transmission member comprises an elastic damping means arranged to deform during the transmission of torque between the element of the assembly and the complementary element.

the hub of the assembly is an outer hub and the complementary hub is an inner hub.

The second axial bearing surface formed by material discharge of the hub of the element of the assembly is axially interposed between the first axial bearing surface and the complementary element.

According to one embodiment, the invention also provides a vibration damper for a transmission chain of a vehicle comprising a torque transmission device as above.

According to one embodiment, the invention also provides a double damping flywheel comprising a vibration damper as above, characterized in that the element of the assembly is one of the primary and secondary flywheels of the double damping flywheel and in that the complementary element is the other primary and secondary flywheels of said double damping flywheel. In a preferred embodiment, the element of the assembly is the secondary flywheel of the double damping flywheel and the complementary element is the primary flywheel of the double damping flywheel.

According to one embodiment, the invention also provides a method of mounting an assembly for a torque transmission device comprising the following steps:

providing an element having a hub, the hub having a first axial bearing surface and a cylindrical surface axially bordered by firstly the first axial bearing surface and, on the other hand, a groove,

- provide a landing,

- Mount the bearing on the hub bearing axially against said first axial bearing surface, the bearing being disposed axially between the first axial bearing surface and an axial end of the groove opposite the first axial bearing surface,

deforming the hub so as to form, by material discharge of said hub, a bulge projecting radially from the groove, said bulge forming a second axial bearing surface and the bearing being interposed axially between the two axial bearing surfaces,

According to other advantageous embodiments, such a method of mounting an assembly for a torque transmission device may have one or more of the following characteristics:

- The other axial end of the groove, located on the side of the first axial bearing surface, is located radially facing the bearing.

the hub comprises a zone to be deformed delimited axially by, on the one hand, a striking surface and, on the other hand, the groove, the step of forming the bulge being made by striking the striking surface by means of a tool such as a punch in the direction of the throat.

- The striking surface is arranged after the deformation step, in the vicinity of the groove, in particular at an axial distance from the groove of between 1 and 5 mm.

- In a plane passing through the axis of rotation and the bulge, the height (H) of the striking surface is greater than the height (h) of the groove.

the striking surface is, before the deformation step, at an axial distance from the groove less than twice the width of the groove.

- The step of mounting the bearing on the element comprises a step of positioning the bearing vis-à-vis the radial groove.

- The step of mounting the bearing on the element comprises a step of positioning the end of the bearing closest to the groove radially opposite the groove.

the step of forming the bulge is carried out locally on a plurality of deformation zones so as to obtain a plurality of local deformations distributed circumferentially so as to forming a plurality of deformed material bulges, said deformed material bulges protruding radially from the groove so as to jointly form the axial bearing surface.

According to one embodiment, the invention also provides a method of mounting a torque transmission device comprising:

mounting an assembly for a torque transmission device according to the method as above,

provide a complementary element comprising a complementary hub,

- Mount the hub of the element of the assembly and the complementary hub one on the other radially on either side of the bearing so that the element of the assembly and the complementary element are movable in rotation relative to each other about the axis of rotation X. Certain aspects of the invention depart from the idea of providing an assembly for a torque transmission device having a simple structure. Certain aspects of the invention start from the idea of providing a torque transmission device having a simple structure. Certain aspects of the invention start from the idea of providing a set for and / or an easy torque transmission device and quick to assemble. Some aspects of the invention start from the idea of providing an assembly for and / or a transmission device in which the maintenance of the bearing does not require a large number of parts. Some aspects of the invention start from the idea of not degrading the bearing when it is mounted on one of the elements. Some aspects of the invention start from the idea of providing reliable bearing fixation, including in the case of hub made of cast iron.

Brief description of the figures

The invention will be better understood, and other objects, details, characteristics and advantages thereof will appear more clearly in the course of the following description of several particular embodiments of the invention, given solely for illustrative and non-limiting purposes. with reference to the accompanying drawings. - Figure 1 shows a sectional view of a torque transmission device comprising a first element and a second element mounted in relative rotation by a bearing type bearing;

FIG. 2 represents a detail sectional view illustrating the rolling bearing between the first element and the second element of the torque transmission device of FIG. 1;

FIG. 3 shows a detail sectional view of a step of mounting a torque transmission device according to the invention after positioning of the bearing on the hub of the output element and before deformation of the hub of the an output member for axially holding the bearing on the output member;

FIG. 4 shows a detailed sectional view of the transmission device of FIG. 3 after deformation of the hub of the output element in order to keep the bearing axially on the output element;

FIG. 5 represents a detail sectional view of a mounting step of a torque transmission device according to a second embodiment after positioning of a sliding bearing on the hub of the input element and before deforming the hub of the input member to axially maintain the bearing on the input member;

- Figure 6 shows a detail sectional view of the transmission device of Figure 5 after deformation of the hub of the input member for axially maintaining the bearing on the input member.

- Figure 7 shows a schematic front view of an embodiment having four circular local bulges.

Detailed description of embodiments

In the description and the claims, the terms "external" and "internal" as well as the "axial" and "radial" orientations will be used to designate, according to the definitions given in the description, elements of the torque transmission device. By convention, the "radial" orientation is directed orthogonally to the axis (X) of rotation of the elements of the torque transmission device determining the "axial" orientation and, from the inside to the outside away from said axis, the "circumferential" orientation is directed orthogonal to the axis of the torque transmission device and orthogonal to the radial direction. Thus, an element described as circumferentially developing is an element whose component develops in a circumferential direction. The terms "external" and "internal" are used to define the relative position of one element relative to another, with reference to the axis of rotation of the torque transmission device, an element close to the axis is thus described as internal as opposed to an external element located radially periphery. Finally, the terms "rear" (AR) and "front" (AV) are used to define the relative position of one element relative to another along the axial orientation, an element located near the engine being described as front relative to an element further from the engine along the axial orientation, the latter being referred to as rear.

The remainder of the description is made with reference to the figures in the context of a torque transmission device of the double damping flywheel type. This description is not limiting and the invention is applicable by analogy to any type of torsion damper and any type of torque transmission device generally provided that two elements of the torque transmission device is rotatably mounted. one on the other in favor of a landing. The double flywheel illustrated in Figure 1 is intended to be integrated in a transmission chain of a motor vehicle.

The torsion damper 1 comprises an input element 2 and an output element 3 which are arranged in the transmission chain respectively on the internal combustion engine side and the gearbox side. By way of example, in the embodiment shown in FIG. 1, the torsion damper 1 is a double damping flywheel, the input element 2 being constituted by a first flywheel intended to be fixed to the end of a driving shaft, such as the crankshaft of an internal combustion engine, while the output element 3 is constituted by a second flywheel forming, in general, reaction plate of a coupling clutch to a driven shaft, such as the input shaft of a gearbox.

The input 2 and output 3 elements are rotatable about a common axis of rotation X. Input 2 and output 3 elements have a hub respectively internal 4 and external 5. The input 2 and output 3 elements are guided in rotation relative to each other by means of a bearing 6. The bearing 6 is interposed radially between the inner hub 4 and the outer hub 5 as described below. The input element 2 comprises an annular portion 7 developing radially outwardly from the inner hub 4. This annular portion 7 comprises fastening means to the driving shaft, for example in the form of orifices intended for the fixing screw passage on the driving shaft. In addition, an outer periphery of the annular portion 7 comprises a ring gear 8 for rotating the input element 2 with a starter. A skirt 9 protrudes radially rearwards from the radially outer periphery of the annular portion 7. A cover 10 mounted on a rear end of the skirt 9 forms together with the annular portion 7 an annular housing 1 1 in which are housed resilient members 12, such as coil springs.

The output element 3 comprises an annular portion 13 developing radially outwardly from the outer hub 5. In the context of a double damping flywheel, this annular portion 13 forms, on a face opposite to the element of inlet 2, a bearing surface 14 for a friction lining of a clutch disc (not shown). The output element 3 then has, near its outer edge, orifices 15 and pads 16 for mounting a clutch cover. A web 17 is fixed on a front face of the annular portion 13 by means of rivets. This web 17 has a plurality of tabs 18 protruding radially outwardly. The input element 2 and the output element 3 are coupled in rotation by the elastic members 12. To this end, each elastic member 12 is circumferentially disposed between two lugs 18 of the veil 17 and between two bearing seats carried. by the input element. Each support seat carried by the input element 2 is for example constituted by a boss (not shown) formed in the annular portion 7 of the input element 2 and by a boss (not shown) formed in the cover 10. The elastic members 12 are thus able to transmit a driving torque from the input element 2 to the output element 3 (forward direction) and a resisting torque of the output element 3 to the input element 2 (retro sense). On the other hand, the resilient members 12 develop an elastic return torque tending to return the input member 2 and the output member 3 in a relative angular position of rest. The document EP2886907 describes the general operation of such a double damping flywheel.

According to other embodiments, the elastic members 12 of torque transmission are not coil springs but elastic blades, as described for example in the document FR3008152.

FIG. 2 illustrates the rotational mounting of the input element 2 and of the output element 3 of FIG. 1 by means of the rolling bearing 6.

The rolling bearing 6 comprises an inner ring 19 and an outer ring 20. The inner ring 19 and the outer ring 20 each form an inner and outer race 21 and outer race 22. These bearing tracks 21, 22 define a running space. in which are housed balls 23 allowing the relative rotation between the inner ring 19 and the outer ring 20.

The inner ring 19 is carried by the input member 2. The inner hub 4 has a flange 24 forming a bearing surface facing rearwardly. This flange 24 defines axially an outer surface 25 of the inner hub 4 of circular cylindrical shape. The inner ring 19 is mounted on the inner hub 4 of the input element 2 on the one hand axially against the flange 24 and on the other hand in radial contact with the outer surface 25 of the inner hub 4. The inner ring is for example mounted in force on the inner hub 4. A rear end 26 of the outer hub 5 has a shoulder 27.

A front end 28 of the outer hub 5 has a groove 29. The groove 29 has a rear side wall 30, a bottom 31 and a front side wall 32. The bottom 31 here has a cylindrical shape of revolution and develops axially parallel to the X-axis. The rear and front-side walls 30 face each other axially and develop parallel to each other in the radial direction. The outer hub 5 further comprises an inner surface 33 of cylindrical shape of revolution. This inner surface 33 is bordered at the rear by the shoulder 27 and, at the front, by the groove 29. The rear lateral wall 30 of the groove 29 is contiguous with the inner surface 33 and the bottom 31. The inner surface 33 has a diameter for adjusting the outer ring 20. In another embodiment, the outer ring 20 is force-fitted on the outer hub 5 with interference with the inner surface 33.

The shoulder 27 forms a first axial bearing surface 34 facing forward. The front end 28 of the hub has a bulge 35. This bulge 35 projects radially inwards from the groove 29. This bulge 35 forms a second axial bearing surface 36 facing rearwardly. The outer ring 20 is mounted on the outer hub 5 of the output member 3 interposed axially between the first axial bearing surface 34 and the second axial bearing surface 36. Thus, the outer ring 20 is locked in axial displacement. by the first axial bearing surface 34 and the second axial bearing surface 36. In addition, the outer ring 20 is in radial contact with the inner surface 33.

Figures 3 and 4 illustrate two steps of mounting the bearing on the output member according to the invention.

FIG. 3 illustrates a detail sectional view of a step of mounting a torsion damper 1 according to the invention after positioning of the bearing 6 on the outer hub 5 of the output element 3 and before deformation of the hub 5 external to axially hold the bearing 6 on the output member 3.

As illustrated in FIG. 3, the front end 28 of the outer hub 5 has, before deformation, a diameter greater than the external diameter of the outer ring 20. Thus, the outer ring 20 can be introduced on the outer hub 5 by sliding from the front end 28 of the outer hub 5. The outer ring 20 is introduced on the outer hub 5 until a rear end of the outer ring 20 is positioned in axial abutment against the first axial bearing surface 34. As illustrated in FIG. 3, when the outer ring 20 is mounted in axial abutment against the first axial bearing surface 34, an axial end of the outer ring 20 located on the side of the bulge to be formed, here the front end 39 of the outer ring 20 is radially opposite the groove 29. More particularly, the rear side wall 30 of the groove 29 is axially interposed between the front end 39 of the outer ring 20 and the first axial bearing surface 34. The front end 39 of the outer ring 20 is further axially interposed between the rear side wall 30 of the groove 29 and the side wall before 32 of the groove 29. Typically, the front end 39 of the ring is in radial vis-à-vis of the groove 29.

Since the outer ring 20 is mounted on the outer hub 5 bearing axially against the first axial bearing surface 34 and in radial contact against the inner surface 33 of the outer hub 5 as shown in Figure 3, it is necessary to axially locking the outer ring 20 on the outer hub 5. For this, a pressure is exerted locally by means of a press and a tool such as a punch on a striking surface 40 formed here on the front end 28 of the outer hub 5 to deform the deformation zone 41 located axially between the striking surface 40 and the groove 29.

As seen in FIG. 4, the material of the deformation zone 41 of the front end 28 of the outer hub 5 is deformed by the pressure and is forced radially inwards and axially towards the rear.

The material of the deformation zone 41 is discharged axially towards the rear and is partially pushed back into the groove 29. Thus, the front lateral wall 32 of the groove 29 is thus displaced axially rearwardly as illustrated in FIG. 4.

On the other hand, the material of the deformation zone is forced radially inwards and forms the bulge 35 protruding inwardly beyond the inner surface 33 of the outer hub 5.

Thus, the material of the front end 28 of the outer hub 5 pushed by the pressure forms a bulge 35 of material that develops from the bottom 31 of the groove 29 and projects radially inwardly from the groove 29. This bulge 35 of discharge material forms both the front side wall 32 of the groove 29 and the second axial bearing surface 36. The formation of the bulge 35 by the pressure on the front end 28 of the outer hub makes it possible to axially lock the ring 20 between the first axial bearing surface 34 formed by the shoulder 27 and the second axial bearing surface 36 formed by the bulge 35, thus locking axially in position the outer ring 20 on the outer hub 5.

The presence of the groove 29 advantageously allows the discharge of material from the front end 28 of the outer hub 5 rearwardly without the discharge material generates a modification of the inner surface 33 against which the outer ring 20 rests. , the material of the deformation zone 41 of the external hub 5 pushed back by the pressure is partially housed in the groove 29 and, therefore, does not generate deformation at the inner surface 33. Thus, the material discharge of the front end 28 of the outer hub 5 does not generate radial pressure on the outer ring 20.

The pressure is preferably exerted on the striking surface 40 of the front end 28 of the outer hub 5 so that the material discharge causes the bulge 35 in contact with the front end 39 of the outer ring 20 without exerting deformante pressure on the outer ring 20. The groove 29 can be achieved simply by machining without requiring precise dimensioning, this groove 29 must simply have sufficient dimensions to accommodate a portion of the repressed material .. In addition, to ensure a good stability of the outer ring 20 and to facilitate the deformation operation it is preferable to make several local pressures distributed circumferentially on the front end 28 of the outer hub 5. Such local pressures generate a plurality of material discharges thus forming a plurality of bulges 35 distributed circumferentially on the outer hub 5. These bulges 35 f together, the second axial bearing surface 36. In a variant, it is also possible to deform the front end 28 of the outer hub 5 over the entire circular periphery of the front end 28 of the outer hub 5 in such a way that to form a single bulge 35 over the entire inner circular periphery of the outer hub 5.

The outer hub 5 is preferably made of vermicular or lamellar cast iron. In particular, a vermicular cast has a very good resistance to deformation and does not tend to fray when it is deformed. Figures 5 and 6 show a second embodiment respectively before and after the deformation step 141.

Elements identical or similar to the elements of the first embodiment illustrated in FIGS. 1 to 4, that is to say fulfilling the same function, carry the same reference numeral increased by 100.

The bearing 106 is here a plain bearing. In other words, it comprises only a ring interposed radially between an inner hub 104 of a first element 102 and an outer hub 105 of a second element 103.

In this second embodiment, the first axial bearing surface 134, the inner surface 133 and the groove 129 are carried by the inner hub 104. In a first step, the sliding bearing 106 is mounted on the inner hub 104 in support axial to the first axial bearing surface 134 and in radial contact against the inner surface 133 of the inner hub 104. To axially lock the sliding bearing 106 on the inner hub 104, a pressure is exerted locally by means of a press and a tool such as a punch on the striking surface 140 provided here on the rear end of the inner hub 104 to deform the deformation zone 141 located axially between the striking surface 140 and the groove 129.

As seen in Figure 6, the material of the deformation zone 141 is deformed by the pressure and is forced radially outward and axially forward.

Thus, the material of the rear end of the internal hub 104 pushed back by the pressure forms a bulge of material which develops from the bottom of the groove 129 and projects radially outwardly from the groove 129. This bulge of repressed material forms both the rear side wall of the groove 129 and the second axial bearing surface 136. The formation of the bulge by the pressure on the rear end of the inner hub 104 makes it possible to axially lock the sliding bearing 106 between the first surface axial bearing 134 formed here by a shoulder on the inner hub 104 and the second axial bearing surface 136 formed by the bulge, thus locking axially in position the smooth bearing 106 on the inner hub 104. The outer hub 105 of the second element can then be mounted around the plain bearing 106.

Figure 7 is a schematic front view showing four circular local bulges. The shape of the punch used may for example be circular, elliptical or rectangular.

Although the invention has been described in connection with several particular embodiments, it is obvious that it is not limited thereto and that it comprises all the technical equivalents of the means described and their combinations if they are within the scope of the invention.

The use of the verb "to include", "to understand" or "to include" and its conjugated forms does not exclude the presence of other elements or steps other than those set out in a claim.

In the claims, any reference sign in parentheses can not be interpreted as a limitation of the claim.

Claims

1 assembly for a transmission link torque device of a motor vehicle, in particular for a clutch, said assembly comprising:

an element (3) comprising a hub (5, 104),

an annular bearing (6, 106) mounted on the hub (5, 104),

wherein the hub (5, 104) has:

a first axial bearing surface (34, 134),

a cylindrical surface (33, 133) which is axially bordered by on the one hand the first axial bearing surface (34, 134) and on the other hand a groove (29, 129),

- a second axial bearing surface (36, 136) being formed by a bulge (35, 135) obtained by discharging material from said hub in the direction of the groove (29, 129);

the annular bearing (6, 106) being mounted against the cylindrical surface (33, 133) and arranged axially between the two axial bearing surfaces (34, 36, 134, 136) so as to be axially retained.

The assembly of claim 1, wherein the second axial bearing surface (36, 136) projects radially from the groove.

3 An assembly according to one of the preceding claims, wherein the annular bearing (6, 106) is mounted against the cylindrical surface (33, 133) and interposed axially between the two axial bearing surfaces (34, 36, 134, 136 ) so as to be retained axially.

4 assembly according to one of the preceding claims, wherein the groove is an annular groove (29, 129).

Assembly according to one of the preceding claims, wherein the bulge (35, 135) is obtained by a local discharge of material towards the groove (29, 129).

Assembly according to one of the preceding claims, wherein the second axial bearing surface (36, 136) is formed by a plurality of bulges (35, 135) obtained by local discharge of material towards the groove (29, 129).

7 assembly according to one of the preceding claims, wherein the bearing (6) comprises an inner ring (19) and an outer ring (20) radially offset from one another, one from the inner ring (19). ) and the outer ring (20) being carried by the cylindrical surface (33) and interposed axially between the two axial bearing surfaces (34, 36), the bearing (6) further comprising rolling bodies (21) housed in a running space, said running space comprising an outer race (22) formed on an inner periphery of the outer race (20) and an inner race (21) formed on the outer periphery of the inner race (19). ).

8 assembly according to one of claims 1 to 7, wherein the bearing (106) is a plain bearing.

9 assembly according to one of the preceding claims, wherein the bulge (35, 135) comprises cast iron, including vermicular cast iron.

Torque transmission device for a motor vehicle transmission chain, in particular for a clutch, comprising an assembly according to one of claims 1 to 9 and a complementary element (2) mounted for rotation in rotation relative to one another. other around an axis of rotation X by means of the annular bearing (6, 106), the annular bearing (6, 106) being radially interposed between the hub (5, 104) of the element of the assembly and a complementary hub (4, 105) provided on the complementary element (2).

1 1 torque transmission device according to the preceding claim in combination with claim 7, wherein the other of the inner ring (19) and the outer ring (20) is carried by the complementary hub (4, 105).

Torque transmission device according to one of Claims 10 to 11, in which a torque transmission member (12) is arranged between the element (3) of the assembly and the complementary element (2) for transmitting a torque between the element (3) of the assembly and the complementary element (2).

Torque transmission device according to the preceding claim, characterized in that the transmission member (12) comprises a elastic damping means arranged to deform during the transmission of torque between the element (3) of the assembly and the complementary element (2).

14 Vibration damper for a transmission chain of a vehicle comprising a torque transmission device according to the preceding claim.

Double damping flywheel comprising a vibration damper according to the preceding claim, characterized in that the element of the assembly is one of the primary and secondary flywheels of the double damping flywheel and in that the complementary element is the other flywheels of primary and secondary inertia of said double damping flywheel.

A method of mounting an assembly for a torque transmission device comprising the steps of:

providing an element (3) having a hub (5, 104), the hub (5, 104) having a first axial bearing surface (34, 134) and a cylindrical surface (33, 133) axially bordered by a part of the first axial bearing surface (34, 134) and, on the other hand, a groove (29, 129),

provide a bearing (6, 106),

mounting the bearing (6, 106) on the hub (5, 104) bearing axially against said first axial bearing surface (34, 134), the bearing (6, 106) being disposed axially between the first bearing surface axial (34, 134) and an axial end of the groove (29, 129) opposite to the first axial bearing surface (34, 134),

deforming the hub (5, 104) so as to form, by material discharge of said hub (5, 104), a bulge (35, 135) protruding radially from the groove (29, 129), said bulge (35, 135 ) forming a second axial bearing surface (36, 136) and the bearing (6, 106) being interposed axially between the two axial bearing surfaces (34, 36, 134, 136),

17 mounting method according to the preceding claim, wherein the hub (5, 104) comprises an area to be deformed (41) defined axially by, on the one hand, a striking surface (40) and on the other hand, the throat (29, 129), the step forming the bulge being made by striking the striking surface (40) by means of a tool such as a punch in the direction of the groove (29, 129).

18 mounting method according to one of claims 16 to 17, wherein the striking surface is arranged, after the deformation step, in the vicinity of the groove, in particular at an axial distance of the groove between 1 and 5 mm .

19 mounting method according to one of claims 16 to 18, wherein the step of mounting the bearing (6, 106) on the element (3) comprises a step of positioning the bearing (6, 106) vis-a-vis radial to the throat (29, 129)

Mounting method according to one of claims 16 to 19, wherein the step of forming the bulge is performed locally on a plurality of deformation zones so as to obtain a plurality of local deformations distributed circumferentially so as to form a plurality deformed material bulges, said deformed material bulges protruding radially from the groove so as to jointly form the axial bearing surface.

21 mounting method according to one of claims 16 to 20, wherein the other axial end of the groove, located on the side of the first axial bearing surface, is located radially facing the bearing.

22 mounting method according to one of claims 16 to 21, wherein the hub (5, 104) is fixed during the deformation step.

23 Method for mounting a torque transmission device comprising:

mounting an assembly for a torque transmission device by a method of mounting an assembly according to one of claims 14 to 18,

providing a complementary element (2) having a complementary hub (4, 105), mounting the hub of the element (3) of the assembly and the complementary hub (4, 105) one on the other radially on either side of the bearing (6, 106) so that the element of the assembly (3) and the complementary element (2) are rotatably mounted relative to one another about the axis of rotation X.