FR3050497A1 - TORQUE TRANSMISSION DEVICE - Google Patents

Abstract

The invention relates to a torque transmission device comprising a first element (58) and a second element (59) able to pivot relative to each other about an axis, at least one elastic member (50). being disposed between the first and second elements so as to oppose the rotation of the first element (58) relative to the second element (59), stop means capable of limiting the rotation of the first element (58) relative to the second element (59), characterized in that the abutment means comprise at least one deformable pin (36) connected to the first element (58) or the second element (59), able to deform by abutment of the second element (59) or the first member (58) on said pin (36).

Description

Torque transmission device

The present invention relates to a torque transmission device, in particular for a motor vehicle. The invention relates in particular to a hydrodynamic torque converter or a double damping flywheel.

A hydrodynamic torque converter conventionally makes it possible to transmit a torque of an output shaft of an internal combustion engine of a motor vehicle, such as for example a crankshaft, to an input shaft of a gearbox. .

The torque converter conventionally comprises an impeller wheel, capable of hydrokinetically driving a turbine wheel, via a reactor.

The impeller wheel is coupled to the crankshaft and the turbine wheel is coupled to guide washers.

Compression spring type elastic members are mounted between the guide washers and a central hub coupled to the input shaft of the gearbox. The elastic members are arranged in series via a phasing member, so that said elastic members deform in phase with each other, the phasing member being movable relative to the washers. guiding and relative to the hub.

The torque converter further comprises clutch means for transmitting a torque from the crankshaft to the guide washers in a specific operating phase, without involving the impeller wheel and the turbine wheel.

In order to avoid the deterioration of the compression springs, it is important to prevent the turns of said springs from being joined when moving the various moving elements. For this, it is known to provide stops to limit the relative movements of the phasing member, guide washers and / or the web. These abutments are generally abutments, obtained by pressing surfaces or rigid bodies. Such stops have a tendency to generate shocks, vibrations and noises that may be detrimental to the operation of the device and the feeling of the driver.

A dual mass flywheel conventionally comprises a primary flywheel intended to be coupled in rotation to a driving shaft such as a crankshaft of an engine and a secondary flywheel intended to be coupled to a driven shaft such as a input shaft of a gearbox. A torsion damper is generally mounted between the primary and secondary flywheels for transmitting rotational torque between the flywheels by absorbing and damping vibrations and rotational acyclisms generated by the engine.

The patent application EP 2 824 361, in the name of the Applicant, discloses a double damping flywheel in which the torsion damper comprises resilient blades integral in rotation with the primary flywheel and bearing on rollers pivotally mounted on the secondary flywheel. Stops may be provided to limit the angular displacement of the primary flywheel relative to the secondary flywheel, in the forward direction and / or in the retro direction.

The forward direction corresponds to the case of operation in which torque is transmitted from the torque input to the torque output, that is to say from the primary flywheel to the secondary flywheel. In certain phases of operation, for example when the user abruptly removes his foot from the accelerator, a resistive torque is transmitted from the secondary flywheel to the primary flywheel, which may cause a rotation in a reverse direction, called retro direction.

As before, such abutments are abutments, obtained by bearing surfaces or rigid bodies. Such stops therefore also tend to generate shocks, vibrations and noises that can be harmful to the operation of the device and the feeling of the driver. The invention aims in particular to provide a simple, effective and economical solution to this problem. For this purpose, it proposes a torque transmission device comprising a first element and a second element able to pivot relative to each other about an axis, at least one elastic member being disposed between the first and second elements so as to oppose the rotation of the first element relative to the second element, stop means adapted to limit the rotation of the first element relative to the second element, characterized in that the stop means comprise at least one pin deformable connected to the first element or the second element, adapted to deform by abutment of the second element or the first element on said pin.

Thus, the pin makes it possible to limit shocks and noises when the stop means come into contact.

The pin can be housed in a housing of the first element or the second element, at least one stop portion of the pin extending outside said housing.

Preferably, the pin is elastically deformable. The elastic deformable pin makes it possible to damp at least part of the shocks in the event of an abutment, so as to limit damage, vibrations and noise during operation.

The housing may have a cylinder portion shape, especially of revolution.

The pin may have the shape of a cylinder, in particular of revolution, whose axis extends axially inside the housing.

According to one embodiment, the pin is a lamella wound on itself, in particular of the spiral type.

According to another embodiment, the pin can be hollow and split, the slot of the pin extending axially.

In this case, the slot is located inside said housing.

The abutment portion is intended to come into contact with a part of the opposite element, so as to provide the stop function. The fact that the slot is housed entirely inside the housing prevents the edge of the slot comes to lock and then prevent the deformation of the pin.

The abutment means may comprise at least a first and a second abutment zone, at least one of said zones being equipped with a deformable pin, the first element being able to be simultaneously abutting on the second element, on the first and second areas. The use of a deformable pin thus makes it possible to compensate for any dimensional tolerances. It is then guaranteed to provide the stop function at each of the first and second stop zones.

If desired, each stop zone is equipped with a deformable pin. Thus, the forces are distributed over the different pins and on all the abutment zones.

According to one embodiment, the deformable pin is plastically deformable. This may be in particular a solid pin, made for example of untreated steel.

This plain pin can have the shape of a cylinder of revolution.

According to one embodiment of the invention, the device may comprise at least two elastic members arranged in series between a torque input element and a torque output element, via a phasing member, first stop means being arranged between the torque input member and the phasing member, second stop means being arranged between the phasing member and the torque output member, the first and second means for stop comprising respectively at least a first and a second deformable pins.

According to this embodiment, one of the first and second members is formed by the phasing member and the other of the first and second members is formed by one of the torque input and torque output members.

According to another embodiment of the invention, the elastic member may comprise at least one resilient blade secured to the first element or the second element, a support element being connected to the second element or the first element respectively, the blade being resiliently supported on said support member, said resilient blade being adapted to flex upon rotation of the first member relative to the second member.

In this case, the support element may comprise at least one rolling body, such as for example a rolling roller.

Furthermore, the elastic blade can be designed so that, in a relative angular position of the first element relative to the second element, different from a rest position, the support element exerts a bending force on the elastic blade producing an opposite reaction force of the elastic blade on the support element, this reaction force having a circumferential component tending to return the first and second elements to said relative position of rest.

In addition, the elastic blade can be designed so that, in a relative angular position of the first element relative to the second element, different from a rest position, the support element exerts a bending force on the an elastic blade producing an opposite reaction force of the elastic blade on the support element, this reaction force having a radial component tending to maintain the elastic blade in contact with the support element.

The elastic blade may comprise a fastening portion integral with the first element, or respectively the second element, and an elastic portion having a radially inner strand, a radially outer strand and an arcuate or bent portion connecting the inner strand and the outer strand.

The device may comprise at least two elastic blades, each elastic blade being integral with the first element, or respectively the second element, each blade being associated with a bearing element connected to the second element, or respectively to the first element, each blade being maintained. resiliently bearing on said corresponding bearing member, each resilient blade being adapted to bend upon rotation of the first member relative to the second member. The invention will be better understood and other details, characteristics and advantages of the invention will become apparent on reading the following description given by way of non-limiting example with reference to the accompanying drawings, in which: FIGS. 1 to 7 illustrate a torque converter type torque transmission device, in particular, - Figure 1 is a schematic representation of a torque converter, - Figure 2 is a front view of the torque converter, - Figure 3 is a axial sectional view of the torque converter; FIG. 4 is a perspective view of a portion of the torque converter; FIG. 5 is a perspective view of the phasing member; FIG. in perspective of a guide ring, - Figures 7 and 8 illustrate two stop positions of a phasing member with respect to an annular web coupled to a hub, - Figures 9 to 15 illustrate a device tr In particular, FIG. 9 is a perspective view of the double damping flywheel, FIG. 10 is a view in axial section of the double damping flywheel, FIG. 11 is a view illustrating the positioning the resilient blades and the support members in a rest position of the double damping flywheel, - Figures 12 and 13 are views corresponding to Figure 11, illustrating two different stop positions, - Figure 14 is a view Figure 15 is a perspective view of said spring pin. FIG. 16 is a perspective view of a deformable pin according to a second embodiment; FIG. 17 is a perspective view of a deformable pin according to a third embodiment;

Figures 1 to 7 illustrate a torque transmission device type hydrodynamic torque converter. This converter makes it possible to transmit a torque of an output shaft of an internal combustion engine of a motor vehicle, such as for example a crankshaft 1, to an input shaft 2 of a gearbox.

The torque converter conventionally comprises an impeller impeller 3 capable of hydrokinetically driving a turbine blade wheel 4 via a reactor 5.

The impeller wheel 3 is coupled to the crankshaft 1 and the turbine wheel 4 is coupled to a turbine hub 6 (Figure 2), itself coupled to two guide washers 7, referenced 7a and 7b.

As best seen in FIG. 3, the guide ring 7b and the turbine hub 6 are rotatably mounted around a splined central hub 8, intended to be coupled to the input shaft 2 of the gearbox. .

The guide washer 7a is mounted around the turbine hub 6 and fixed thereto. The two guide rings 7a, 7b extend radially and delimit between them an internal space 9 (serving in particular for the housing of first elastic members 10a and second elastic members 10b, which are for example helical compression springs.

The guide ring 7b has a cylindrical rim 11 at its radially outer periphery, extending towards the guide ring 7a and fixed thereto. The free end of the cylindrical flange 11 comprises tabs 13 extending axially through orifices 14 of the washer 7a. These tongues 13 are riveted on the outer periphery of the guide washer 7a and can be welded to the latter, so as to ensure the attachment of the two guide rings 7a, 7b.

The guide washers 7a, 7b conventionally comprise windows 15 for accommodating the elastic members 10a, 10b.

Furthermore, the guide ring 7b has three openings or housings 16 in the form of a circular arc (Figure 6).

A splined hub 18 (FIG. 2) is also fixed by riveting on the rear face of the guide washer 7b. This corrugated hub 18 has a radial portion 19 fixed on said rear face of the guide washer 7b, and a corrugated cylindrical flange 20 extending rearwardly from the radially outer periphery of the radial portion 19.

A clutch 21 (FIG. 1) makes it possible to transmit a torque from the crankshaft 1 to the guide washers 7, in a determined operating phase, without involving the impeller wheel 3 and the turbine wheel 4. This clutch 21 comprises an element 22 coupled to the crankshaft 1 and an output member including the splined hub 18.

A radially extending annular web 24 is mounted in the inner space and is fixed to the central hub 8, via rivets, or formed integrally with the central hub 8, as is the case in the embodiment represented.

As best seen in Figures 4, 7 and 8, the annular web 24 has a radially inner annular portion 25, here formed of material with the hub 8, from which tabs 26, for example three in number, 'extend radially outwards. Each lug 26 has two opposite faces 27 serving to support the elastic members 10a, 10b, inclined with respect to each other and with respect to the radial direction. Two abutment studs 28 extend circumferentially on either side of each tab 26, at its outer periphery.

The elastic members 10a, 10b are mounted circumferentially between the annular web 24 and the guide washers 7a, 7b.

More particularly, the elastic members 10a, 10b are arranged in pairs. The elastic members of the same pair are arranged in series via a common phasing member 29, so that the elastic members 10a, 10b deform in phase with each other. In the embodiment shown in the figures, the torque converter comprises three pairs of elastic members 10a, 10b.

Thus, for each pair of elastic members 10a, 10b, depending on the direction of rotation of the guide washers 7a, 7b with respect to the annular web 24, one of the elastic members (for example 10a) is intended to bear, on the one hand, on the corresponding end of the windows 15 of the guide washers 7a, 7b and, on the other hand, on the phasing member 29. The other elastic member (for example 10b) is then intended to take support, on the one hand, on the phasing member 29 and, on the other hand, on one of the faces 27 of the corresponding tab 26 of the annular web 24. The phasing member 29 has an outer annular portion 30 from which tabs 31, here three in number, extend radially inwardly. Each lug 31 has two opposite faces 32 serving to support the resilient members 10a, 10b, inclined relative to each other and relative to the radial direction. Two abutment zones 33, forming shoulders, extend circumferentially on either side of each tab 31.

Each abutment zone 33 comprises a housing 34 in the form of a cylinder portion, opening circumferentially on the corresponding shoulder face 35. A resiliently deformable pin 36, such as for example a split hollow pin for example, is mounted in the housing , a part of the pin 36, said abutment portion, extending outside the housing 34. The slot 37 (best seen in Figures 14 and 15) of the pin 36 extends axially and is located entirely in the housing. Inside the housing 34. The pin 36 is prestressedly mounted in the housing 34 to prevent it from pivoting within said housing 34.

The abutment studs 28 of the tabs 26 of the annular web 24 are able to bear respectively on the abutment zones 33 of the bearing portions 31 of the phasing member 29, in particular on the abutment portions of the pins 36.

The pads 28, the zones 33 and the pins 36 are positioned and dimensioned so as to limit the compression of the elastic members 10a, 10b and avoid, when it comes to helical springs, that the turns of the springs are joined during their compression, both in the direction of rotation said direct direction in the opposite direction of rotation, said retro direction. The direct direction corresponds to the case of operation in which torque is transmitted from the guide washers 7a, 7b to the hub 8. In certain operating phases, for example when the user abruptly removes his foot from the accelerator, a resistant torque is transmitted from the hub 8 to the guide washers 7a, 7b, which can cause a rotation of the phasing member 29 in the retro direction.

Furthermore, each lug 31 of the phasing member 29 comprises at its base an elastically deformable pin 38 (FIG. 5), such as for example an axially extending split hollow pin, engaged at one end in a housing of the phasing member 29 and engaged at the other end in one of the openings 16 in an arc of the guide ring 7b.

The device further comprises pendular masses 39 movably mounted at the radially outer periphery of an annular support 40, the radially inner periphery of said support 40 being rotatably coupled with the tabs 31 by means of flat connecting struts 41 (Figure 2).

The pendular masses 39 are movably mounted on the support 40 by means of spacers and rollers for example, as is known per se, these masses 39 being intended to improve the filtration of vibrations and rotational acyclisms.

In operation, the guide washers 7a, 7b and the hub 8 pivot relatively relative to the web 24 and the hub 8 (in the forward direction or in the retro direction), so as to cause the rotation of the phasing member 29 relative to the guide washers 7a, 7b, on either side of a so-called rest position in which no torque is transmitted.

If the clearance is very important, the pads 28 of the web 26 abut on the abutment portions of the pins 36 which can then elastically deform by crushing, so as to dampen shocks and noises.

Furthermore, if the pivoting between the phasing member 29 and the guide washer 7b is important, the pins 38 bear against the circumferential ends 41 of the openings 16, said pins 38 then being able to deform so as to dampen the shocks and noises. The use of such deformable pins 36, 38 also makes it possible to compensate for any dimensional tolerances by ensuring that the pins 36, 38 may be simultaneously abutting on the corresponding pads 28 or on the corresponding circumferential ends 41.

Figures 9 to 15 illustrate a torque transmission device of the double damping flywheel type. It comprises a primary mass of inertia 42 (or primary flywheel), intended to be coupled in rotation to a driving shaft such as a crankshaft of a motor.

A starter ring 43 is mounted at the radially outer periphery of said primary mass of inertia 42, which also carries two diametrically opposed shafts 44 and fixed, for example by screwing, at the radially outer periphery of said primary mass of inertia 42 Two rollers 45 are pivotally mounted about the shafts 44 via bearings such as needle bearings 46.

A cylindrical portion 47 also extends axially, at the radially inner periphery of the primary mass of inertia 42.

A secondary mass of inertia 48 (or secondary flywheel) is pivotally mounted around the cylindrical portion 47 of the primary mass of inertia 42, via a bearing 49 such as for example a bearing. balls. The secondary mass of inertia 48 is intended to be coupled to a driven shaft such as an input shaft of a gearbox. A torsion damper is mounted between the primary 42 and secondary 48 masses to transmit rotational torque between said masses by absorbing and damping vibrations and rotational acyclisms generated by the motor. The torsion damper comprises, in addition to the aforementioned rollers 45, two elastically deformable blades 50 mounted axially between radial portions of the masses of inertia 42, 48. As can be seen more clearly in FIGS. 11 to 13, each elastic blade 50 comprises a fastening portion 51 fixed at the radially inner periphery of the secondary mass of inertia 48 by means of the rivets 52, here three in number, and an elastic portion having a radially inner strand 53, a radially outer strand 54 and a arcuate or bent portion 55 connecting the inner strand 53 and the outer strand 54. The arcuate or bent portion 55 has an angle of about 180 °. In other words, the elastically deformable portion of the elastic blade 50 comprises two radially offset regions of one another and separated by a radial gap.

The outer strand 54 develops circumferentially at an angle of between 120 ° and 180 °.

The radially outer strand 54 has a radially outer surface 56 forming a rolling track abutting on the corresponding roller roller 45, said roller roller 45 being situated radially outside the outer strand 54 of the elastic blade 50. bearing 56 has a generally convex shape. The rolling track 56 may be formed directly by a zone of the outer strand 44 or by a piece which is attached to said outer strand 54.

Between each elastic blade 50 and the corresponding roller roller 45, the torque transmitted between the two masses of inertia 42, 48 is decomposed into radial forces and circumferential forces. The radial forces allow to bend the corresponding blade 50 and the circumferential forces allow the corresponding roller roller 45 to move on the raceway 56 of the blade 50 and transmit the torque.

When the torque transmitted between the masses of inertia 42, 48 varies, the radial forces exerted between the elastic blade 50 and the roller roller 45 vary and the bending of the elastic blade 50 is changed. The modification of the bending of the blade 50 is accompanied by a displacement of the roller roller 45 along the corresponding raceway 56 under the action of the circumferential forces.

The rolling tracks 56 have profiles arranged in such a way that, when the transmitted torque increases, the rollers 45 each exert a bending force on the corresponding elastic blade 50 causing a closer to the free distal end of the elastic blade 50 in the direction of the X axis and a relative rotation between the first mass of inertia 42 and the second mass of inertia 48 as they deviate from their relative position of rest, illustrated in Figure 11. It defines by rest position the relative position of the first mass of inertia 42 relative to the second mass of inertia 48 in which no torque is transmitted between them.

The profiles of the raceways 56 are such that the rollers 45 exert on the elastic blades 50 bending forces having radial components and circumferential components.

The elastic blades 50 exert on the rollers 45 a restoring force having a circumferential component which tends to turn the rollers 45 in an opposite direction of rotation and thus to recall the primary mass of inertia 42 and the mass of inertia secondary 48 towards their relative rest position, and an outwardly directed radial component tending to maintain the running track 56 bearing on the corresponding roller wheel 45.

Preferably, when said masses of inertia 42, 48 are in their rest position, the elastic blades 50 are prestressed radially towards the axis X so as to exert a reaction force, directed radially outwards, so as to keep the blades 50 resting on the rollers 45.

The profiles of the raceways 56 can be arranged in such a way that the characteristic curve of transmission of the torque as a function of the angular displacement is symmetrical or not with respect to the rest position. According to an advantageous embodiment, the angular displacement can be greater in a direction of rotation said direct, than in a direction of rotation opposite, said retro direction.

The angular displacement of the primary mass of inertia 42 with respect to the secondary mass of inertia 48 may be greater than 20 °, preferably greater than 40 °.

The elastic blades 50 are regularly distributed around the X axis and are symmetrical with respect to the X axis so as to ensure the balance of the torque converter.

The torque converter may also comprise friction means 57 (FIG. 10) arranged to exert a resisting torque between the primary inertia mass 42 and the secondary inertia mass 48 during their relative deflection so as to dissipate the energy accumulated in the elastic blades 50.

According to the invention, the primary 42 and secondary 48 inertia masses respectively comprise axially extending studs 58 and 59. Preferably, each mass of inertia 42, 48 comprises two pads 58, 59 diametrically opposed. The rollers 45 are housed, at least in part, in recesses 60 of complementary shapes formed in the studs 58 of the primary mass of inertia 42. The recesses 60 open out at the radially inner periphery of the studs 58 and the radially inner parts of the rollers 45 protrude radially inwards relative to the pads 58 so that the blades 50 can bear on said rollers 45.

The studs 58 of the primary mass of inertia 42 are circumferentially offset relative to the studs 59 of the secondary mass of inertia 48.

The pads 58 of primary mass of inertia 42 each comprise two circumferential ends 61 having housings 62 in the form of a cylinder portion, opening circumferentially at the corresponding end. A pin 36 resiliently deformable, such as for example a split hollow pin for example, is mounted in each housing 62, a portion of the pin 36, said abutment portion, extending outside the housing 62. The slot 37 (FIGS. 14, 15) of the pin 36 extends axially and is located entirely inside the housing 62. Each pin 36 is prestressedly mounted in the housing 62 to prevent it from pivoting within said housing 62.

The studs 59 of the secondary inertia mass 48 are able to bear respectively on the abutment portions of the pins 36.

In a variant, the pins 36 can equip the studs 49 with the secondary inertia mass 48 and not the studs 58 with the primary inertia mass 42.

The pads 58, 59 and the pins 36 are positioned and dimensioned so as to limit the compression of the resilient blades 50 and prevent their degradation in the case of transmission of an over-torque through the double damping flywheel resulting from limiting operating conditions or a malfunction.

As before, the use of deformable pins 36 makes it possible to dampen shocks and noises in the event of an abutment. The use of such deformable pins 36 also makes it possible to compensate for any dimensional tolerances by ensuring that the pins 36 concerned can simultaneously be in abutment with the corresponding studs 59.

In each of the aforementioned embodiments, the pins 36 may have the structure shown in Figures 14 and 15. In this case, each pin 36 may comprise a circumferentially median portion 63 having a first outer diameter, extended by end portions 64 next to each other and defining the edges of the slot 37. The end portions 64 extend towards the axis of the pin 36 relative to the extension of the first diameter. The end portions 64 extend for example to a second diameter, smaller than the first diameter, or are curved or straight portions inclined towards the axis of the pin 36.

In this way, it prevents that the edges of the slot 37, which form protruding corners, catch on the material defined by the edge of the housing 62, thereby preventing the deformation of the pin 36 and causing damage.

As a variant, the edges of the medial portion 63 comprise chamfers or radially outer fillets delimiting the edges of the slot 37.

This pin 36 is preferably metallic.

FIG. 16 shows a second embodiment of the invention that is alternative to that presented in FIG. 4, in which the elastic pin is a coil-wound lamella of the spiral type. With reference to FIG. 16, elements identical or similar to the elements of FIG. 4, that is to say fulfilling the same function, bear the same reference numeral increased by 100.

Each abutment zone 133 has a housing 134 in the form of a cylinder portion. The pin 136, which is elastically deformable, is mounted in the housing 134, a portion of the pin 136, said abutment portion, extending outside the housing 134.

The pin 136 is a lamella wound on itself, like a spiral. Here, the pin has between two and three lamella thicknesses according to the angular sector. The axis around which the lamella is wound is located entirely inside the housing 134. It is substantially parallel to the axis of rotation of the damper. This pin is metallic.

The spiral pin 136 has, around its axis, an internal free space allowing a deformation of the pin.

This spiral-shaped pin shape allows the different lamella thicknesses to rub against each other when abutting. This makes it possible to obtain a limit hysteresis.

The pin 136 may be prestressedly mounted in the housing 134 to prevent it from pivoting within said housing 134.

The abutment studs 128 of the tabs of the annular web are able to bear respectively on the abutment zones 133 of the bearing portions 131 of the phasing member 129, in particular on the abutment portions of the pins 136.

The pads 128, the zones 133 and the pins 136 are positioned and dimensioned so as to limit the compression of the main elastic members of the damper and avoid, when it comes to coil springs, that the turns of the springs are contiguous when compression, both in the direction of rotation said direct direction in the opposite direction of rotation, said retro direction.

This type of elastically deformable pin can also be used for a double damping flywheel, as shown in FIGS. 9 to 13, in place of the hollow split pins.

Figure 17 shows a third embodiment of the invention alternative to that shown in Figure 4, wherein the pin is plastically deformable. With reference to FIG. 17, elements identical or similar to the elements of FIG. 4 bear the same reference numeral increased by 200.

Each abutment zone 233 comprises a housing 234 in the form of a cylinder portion. The pin 236, which is plastically deformable, is mounted in the housing 234, a portion of the pin 236, said abutment portion, extending outside the housing 234.

The pin 236 has the shape of a cylinder of revolution.

This type of pin can for example be formed for example in untreated steel.

Each pin 236 can be hooped in the housing 234 of the stop zone 233. According to an alternative method, the pins can be glued.

The abutment studs 228 of the tabs of the annular web are able to bear respectively on the abutment zones 233 of the bearing portions 231 of the phasing member 229, in particular on the abutment portions of the pins 236 so as to plastically deform them.

The matting of the abutment portions of the pins thus makes it possible to distribute the contacts on the various abutment areas during the abutment.

The pins have a low hardness, especially between 80 and 300 HV to allow matting.

This type of plastically deformable pin can also be used for a double damping flywheel, as illustrated in FIGS. 9 to 13, in place of the hollow split pins.

Whatever the pin used, plastically deformable or elastically deformable, the pins can be held axially by a creep made at the edge of the housing, on the phasing washer, for a torque converter, or on one of the primary and secondary flywheels for a double damping flywheel.

In FIG. 17, it can be seen that this creep can be effected for example with 3 stamped zones 265 locally so as to form axial retaining surfaces for the pin.

Claims (15)

1. Torque transmission device comprising a first element (7a, 7b, 42) and a second element (29, 48) able to pivot relative to each other about an axis, at least one elastic member (10a, 10b, 50) being arranged between the first and second elements so as to oppose the rotation of the first element (7a, 7b, 42) relative to the second element (29, 48), suitable stop means to limit the rotation of the first element (7a, 7b, 42) with respect to the second element (29, 48), characterized in that the stop means comprise at least one deformable pin (36, 38, 136, 236) connected to the first element (7a, 7b, 42) or to the second element (29, 48), able to deform by abutment of the second element (7a, 7b, 42) or of the first element (29, 48) on said pin (36, 38, 136, 236). 2. Device according to claim 1, characterized in that the pin (36, 38, 136, 236) is housed in a housing (34, 62) of the first element (7a, 7b, 42) or the second element (29, 48), at least one abutment portion of the pin (36, 38, 136, 236) extending outwardly of said housing (34, 62, 134, 234). 3. Device according to claim 1 or 2, characterized in that the pin (36, 38) is elastically deformable. 4. Device according to one of claims 1 to 3, characterized in that the pin (36, 38) is hollow and slotted, the slot (37) of the pin (36, 38) extending axially. 5. Device according to claim 4 combined with claim 2, characterized in that the slot (37) is located inside said housing (34, 62). 6. Device according to one of claims 1 to 5, characterized in that the abutment means comprise at least a first and a second abutment zones, at least one of said zones being equipped with a deformable pin (36, 38, 136, 236), the first element (7a, 7b, 42) being able to be simultaneously abutted on the second element (29, 48), on the first and second zones. 7. Device according to one of claims 1 to 6, characterized in that it comprises at least two resilient members (10a, 10b) arranged in series between a torque input member (7a, 7b) and an element of torque output (24, 8) through a phasing member (29), first stop means (38, 16, 41) being arranged between the torque input member (7a, 7b) ) and the phasing member (29), second stop means (36, 28) being arranged between the phasing member (29) and the torque output member (24, 8), the first and second stop means respectively comprising at least first and second deformable pins (38, 36, 136, 236). 8. Device according to one of claims 1 to 6, characterized in that the elastic member comprises at least one elastic blade (50) integral with the first element (42) or the second element (48), a support element (45) being connected to the second element (48) or respectively to the first element (42), the blade (50) being elastically supported on said support element (45), said elastic blade (50) being able to flex during rotation of the first member (42) relative to the second member (48). 9. Device according to claim 8, characterized in that the support element comprises at least one rolling body (45). 10. Device according to claim 8 or 9, characterized in that the elastic blade (50) is designed so that, in a relative angular position of the first element (42) relative to the second element (48), different from a rest position, the support member (45) exerts a bending force on the resilient blade (50) producing a counteracting force of the resilient blade (50) on the support member (45) said reaction force having a circumferential component tending to bias the first and second members (42, 48) toward said relative rest position. 11. Device according to one of claims 8 to 10, characterized in that the elastic blade (50) is designed so that, in a relative angular position of the first element (42) relative to the second element (48) , different from a resting position, the support element (45) exerts a bending force on the elastic blade (50) producing a counteracting force of the elastic blade (50) on the support element (45), this reaction force having a radial component tending to maintain the resilient blade (50) in contact with the support member (45). 12. Device according to one of claims 8 to 11, characterized in that the elastic blade (50) comprises a fixing portion (51) integral with the first element (42), or respectively the second element (48), and a elastic portion having a radially inner strand (53), a radially outer strand (54) and an arcuate or bent portion (55) connecting the inner strand (53) and the outer strand (54). 13. Device according to one of claims 8 to 12, characterized in that it comprises at least two resilient blades (50), each resilient blade (50) being integral with the first element (42), or respectively the second element ( 48), each blade (50) being associated with a bearing element (45) connected to the second element (48), or respectively to the first element (42), each blade (50) being elastically supported on said element corresponding support (45), each resilient blade (50) being adapted to flex upon rotation of the first member (42) relative to the second member (48). 14. Device according to one of claims 1 to 3 or 6 to 12 wherein the deformable pin (136) is a strip wound on itself, for example spiral type. 15. Device according to one of claims 1 or 6 to 13 wherein the deformable pin is a plastically deformable pin (236).