CLUTCH MECHANISM, ESPECIALLY FOR A MOTOR VEHICLE

Description

[0001] The present invention relates to a clutch mechanism, particularly for motor vehicles, for example, automobiles, motorcycles, or any other vehicle comprising at least one internal combustion engine. The motor vehicle may be an industrial vehicle, such as a heavy goods vehicle, a public transport vehicle, or an agricultural vehicle.

[0002] More specifically, the invention relates to an improvement to the clutch mechanism typically comprising a cover, a pressure plate, a diaphragm spring mounted, possibly pre-stressed, between the cover and the pressure plate, and means for articulating this diaphragm spring relative to the cover.

[0003] In such a clutch mechanism, when engaged, the diaphragm spring exerts sufficient force on the pressure plate to clamp a clutch disc between the pressure plate and a flywheel, such as a dual-mass flywheel, thus enabling the transmission of engine torque to the gearbox. In a push-type clutch mechanism, disengagement is achieved by a clutch release bearing pressing against the central portion of the diaphragm spring along its axis of rotation. This diaphragm spring then interacts with the articulation means provided between the diaphragm spring and the cover, allowing the radially outer portion of the diaphragm spring to move away from the pressure plate.Under these conditions, the pressure plate moves away from the clutch disc under the effect of elastic return means, thus releasing the disc, which makes it possible to stop transmitting the engine's torque to the gearbox and, if necessary, to make the necessary gear changes.

[0004] Following numerous clutch disengagements, the diaphragm spring's joint relative to the cover tends to wear (this is referred to as wear and / or flattening) due to repeated movements, and play develops between this joint and the diaphragm spring. These flattening and / or wear phenomena are particularly observed in clutch mechanisms used in commercial vehicles or heavy goods vehicles where the forces exerted by the diaphragm spring on the joint can reach 10,000 N. The development of such play reduces the travel of the diaphragm's periphery when it is pushed by the clutch release bearing, and thus reduces the axial displacement of the pressure plate during the transition from the engaged to the disengaged position. In this degraded mode, complete disengagement is no longer possible.Part of the engine's torque continues to be transmitted to this disc, making gear changes difficult, if not impossible. There is a need for a clutch mechanism where the axial movement of the pressure plate remains constant throughout the vehicle's lifespan.

[0005] We are familiar with document FR 2 886 997, which describes a clutch mechanism comprising means for compensating the operating play between the joint and the diaphragm spring. These play compensation means include a ring gear fixed relative to the cover, and a counter-ring gear mounted freely between said ring gear and said diaphragm spring. The ring gear and counter-ring gear are respectively equipped with ramps and counter-ramps. Elastic return means tend to pivot said counter-ring gear relative to said ring gear as soon as wear appears within the joint. In this way, the counter-ring gear remains in contact with the diaphragm spring regardless of the wear inflicted by the diaphragm spring on this counter-ring gear, and allows for complete disengagement of the clutch mechanism.This clutch mechanism, however, has a complex architecture and uses a large number of components that must move around the axis of rotation to prevent play between the joint and the diaphragm spring. Other examples of clutch mechanisms are described in documents WO 2007 / 085766 A1, DE 10 2016 202300 A1, FR 2 456 878 A1, and FR 2 548 301 A1.

[0006] The invention aims to remedy these technical problems by proposing an improved clutch mechanism capable of compensating for wear in the diaphragm spring joint in order to achieve complete disengagement of the clutch mechanism while presenting a simplified architecture compared to known prior art clutch mechanisms.

[0007] The invention also aims to provide a simple, effective and economical solution to these problems.

[0008] To this end, the present invention proposes a clutch mechanism for a motor vehicle, comprising a cover, a pressure plate rotationally fixed to the cover and axially movable relative to it, a diaphragm spring bearing on the cover and the pressure plate, the diaphragm spring being held under axial preload against the cover by means of a support washer having axial protrusions passing through the diaphragm spring and the cover, each axial protrusion having an axial stop capable of transmitting the axial preload force to the cover, and a plurality of elastic segments, distributed angularly around the axis of rotation X of the clutch mechanism, disposed between two adjacent components of the clutch mechanism, namely between the axial stop of the axial protrusions and the cover or between the support washer and the diaphragm spring,which elastic segments exert axial preload on the diaphragm spring.

[0009] The clutch mechanism according to the invention is remarkable in that each elastic segment exerts a first action force along a first diameter of force application and a second action force along a second diameter of force application on one of the adjacent components of the clutch mechanism, as well as a reaction force along a third diameter of force application on the other adjacent component of the clutch mechanism, the first, second and third diameters of force application being concentric and radially spaced.

[0010] This clutch mechanism, according to the invention, has the advantage of compensating for wear on the diaphragm spring joint due to the elasticity of the segments along the X axis of rotation. In this way, it will always be possible to achieve complete disengagement of the clutch mechanism throughout the vehicle's lifespan. Thanks to the specific geometry of the elastic segments, the wear compensation capacity is improved by radially offsetting the force application diameters. This offset reduces the stiffness of the elastic segments while still allowing them to withstand the forces exerted by the diaphragm spring on the joint, which can reach, for example, 10,000 N. For instance, the action and reaction forces can be axially oriented.

[0011] Preferably, each elastic segment can extend angularly around the X axis at an angle between 25° and 170°.

[0012] Advantageously, the number of elastic segments can be between 2 and 12, with the elastic segments being regularly distributed angularly around the X axis.

[0013] Preferably, at least one of the first and second action forces can be oriented axially in a direction opposite to the reaction force.

[0014] Advantageously, each elastic segment can include through holes for axial protrusions, with the through holes arranged radially beyond the first force application diameter of the first acting force. In this way, the joint architecture within the clutch mechanism is radially compact.

[0015] Preferably, the lid can support the diaphragm spring by means of stampings formed directly in the lid or of an annular ring fitted into a groove in the lid.

[0016] Advantageously, each elastic segment can include a first application surface for the first action force, a second application surface for the second action force, a third application surface for the reaction force, the third application surface being axially offset with respect to the first and second application surfaces.

[0017] Preferably, the application diameter of force of at least one of the first and second action forces or of the reaction force may be offset radially with respect to the implantation diameter of the axial protrusions.

[0018] According to one embodiment of the invention, the third diameter of application of the reaction force can be arranged radially beyond the first and second diameters of application of the force. This offset of the third diameter of application of the reaction force reduces the stiffness of the elastic segments and increases the wear compensation capacity of the diaphragm spring joint.

[0019] Advantageously, the first action force along a first diameter of force application and the second action force along a second diameter of force application can be oriented axially in opposite directions.

[0020] Preferably, each elastic segment, arranged between the support washer and the diaphragm spring, can include a bearing diameter on the diaphragm spring coinciding with the third force application diameter.

[0021] Advantageously, each elastic segment may include tabs originating from an internal circumferential edge and the support washer may include holes distributed angularly around the X axis, the tabs of the elastic segments being inserted into the holes.

[0022] Preferably, the support washer may include an upper bearing face oriented towards the diaphragm spring and a lower bearing face axially opposite to the upper bearing face, each elastic segment simultaneously pressing on the lower bearing face according to the first action force and on the upper bearing face according to the second action force.

[0023] Advantageously, the legs of each elastic segment can press against the lower bearing face of the support washer.

[0024] Advantageously, each elastic segment can press against an inner periphery of the support washer via each lug which is formed with an angle Δ with respect to the lower bearing face of the support washer.

[0025] Preferably, the second application diameter of the second action force can be substantially coincident with the implantation diameter of the axial protrusions from the support washer.

[0026] Advantageously, the support washer may include at least one centering stud associated with each elastic segment, each centering stud being inserted into a hole provided in the associated elastic segment. The centering stud may be extruded from the annular portion of the support washer.

[0027] Alternatively, each elastic segment may include tabs originating from an internal circumferential edge and the support washer may include notches formed on an internal edge and distributed angularly around the X axis, with the tabs of the elastic segments being inserted into the notches.

[0028] According to another embodiment of the invention, the third diameter of application of the reaction force can be arranged radially between the first and second diameters of application of the force. The offset of the third diameter of application of the reaction force has the effect of reducing the stiffness of the elastic segments and increasing the wear compensation capacity of the diaphragm spring joint.

[0029] Preferably, the through holes for the axial protrusions can be arranged radially between the first force application diameter and the second force application diameter.

[0030] Advantageously, the first action force along a first diameter of force application and the second action force along a second diameter of force application can be oriented axially in the same direction.

[0031] Preferably, the support washer may include an upper bearing face oriented towards the diaphragm spring, each elastic segment simultaneously pressing on the upper bearing face with the first and second acting forces.

[0032] Advantageously, each elastic segment, arranged between the axial stop of the axial protrusions and the cover, can include a bearing diameter on the axial stops coinciding with the third diameter of force application.

[0033] Preferably, the cover may include an upper support face oriented axially outwards from the clutch mechanism, each elastic segment simultaneously pressing on the upper support face with the first and second acting forces.

[0034] Advantageously, the diaphragm spring can be mounted so as to pivot relative to the lid around articulation means. For example, the articulation means are partly formed as stampings directly into the lid or partly as a ring attached to the lid.

[0035] The invention may exhibit one or more of the features described below, either combined or taken independently of each other: Each elastic segment can be securely fixed to the support washer or the cover using at least one fixing point, for example by riveting, welding or screwing; the fixing points of the elastic segments can be angularly distributed according to the first diameter of force application; the fixing points can be rivets; the fixing points can be weld points; the axial protrusions can be attached to the support washer; the axial protrusions can be spacers crimped onto the support washer; the second diameter of force application of the second action force can substantially coincide with the mounting diameter of the spacers crimped onto the support washer; the support washer can bear directly on the diaphragm spring;The support washer may bear indirectly on the diaphragm spring, notably via elastic segments axially interposed between the two adjacent components; the axial protrusions may be formed from the material of the support washer; the axial protrusions may be bent tabs extending from the inner periphery of the support washer; the axial protrusions may pass through openings made in the bottom of the cover; the tabs of the elastic segments may be angularly offset relative to the holes made to allow the axial protrusions to pass through; the tabs of the elastic segments may be oriented angularly opposite the holes made to allow the axial protrusions to pass through.

[0036] The invention also relates, according to another aspect, to a transmission sub-assembly for a motor vehicle, comprising: a flywheel, a clutch mechanism incorporating all or part of the characteristics mentioned above, fixed to the flywheel, and a clutch disc axially interposed between the flywheel and the pressure plate of the clutch mechanism.

[0037] This transmission sub-assembly, according to this other aspect of the invention, has the advantage of being able to transmit high torques from the internal combustion engine to the gearbox.

[0038] The invention will be better understood upon reading the following description, given solely by way of example and with reference to the accompanying drawings in which: the figure [ Fig. 1 ] is an axial cross-sectional view of a motor vehicle transmission subassembly incorporating a clutch mechanism according to a first embodiment of the invention; the figure [ Fig. 2 ] is an isometric view of the elastic segments of the clutch mechanism according to the first embodiment of the invention of the figure 1 ; the figure [ Fig. 3 ] is another partial isometric view of the clutch mechanism according to the first embodiment of the invention of the figure 1 ; the figure [ Fig. 4 [ ] is an axial cross-sectional view of the clutch mechanism according to the first embodiment of the invention of the figure 1 ; the figure [ Fig. 5 ] is an axial cross-sectional view of a clutch mechanism according to a second embodiment of the invention; the figure [ Fig. 6 ] is a front view of a clutch mechanism according to a third embodiment of the invention; the figure [ Fig. 7 [ ] is an axial cross-sectional view of the clutch mechanism according to the third embodiment of the invention of the figure 6 ; the figure [ Fig. 8 ] is an axial cross-sectional view of a clutch mechanism according to a fourth embodiment of the invention; the figure [ Fig. 9 ] is a front view of a clutch mechanism according to a fifth embodiment of the invention; the figure [ Fig. 10 [ ] is an axial cross-sectional view of the clutch mechanism according to the fifth embodiment of the invention of the figure 9 .

[0039] In the following description and claims, the terms "front" or "rear" will be used, without limitation and to facilitate understanding, according to the direction with respect to an axial orientation determined by the main X axis of rotation of the transmission of the motor vehicle and the terms "inside / internal" or "outside / external" with respect to the X axis and along a radial orientation, orthogonal to said axial orientation.

[0040] THE figures 1 à 4 illustrate a motor vehicle transmission of the industrial vehicle type integrating the clutch mechanism 10 according to a first embodiment of the invention.

[0041] The industrial vehicle includes, in particular, an internal combustion engine, a gearbox, and a transmission sub-assembly 1 interposed between the internal combustion engine and the gearbox. The transmission sub-assembly 1 is kinematically linked to the driven shaft A1 of the gearbox.

[0042] Transmission subset 1 comprises: a flywheel 2 linked in rotation with the output shaft of the internal combustion engine, a clutch mechanism 10 fixed on the flywheel, and a clutch disc 3 interposed axially between the flywheel and a pressure plate 12 of the clutch mechanism.

[0043] The clutch disc 3 comprises a torque transmission disc 4 of annular shape around an axis of rotation X, guide elements 5 and helical compression springs 6. The two guide elements 5, also called guide washers, are arranged on either side of the torque transmission disc 4, trapping the helical compression springs 6 in intermediate housings. This clutch disc 3 architecture is said to be "symmetrical" because the engine torque enters first through the friction linings fixed to the torque transmission disc 4, then the engine torque is transmitted to the driven shaft A1 via a hub 7 which is rotationally fixed to the two guide elements 5.

[0044] As illustrated on the figure 1 The clutch mechanism 10 includes a cover 11 connected by suitable fastening means to the flywheel 2. Between the cover 11 and the flywheel 2 are arranged a diaphragm spring 13, the pressure plate 12, and the clutch disc 3. Optionally, a wear compensation device for the friction linings of the clutch disc may be arranged between the diaphragm spring and the pressure plate. The diaphragm spring 13 is arranged axially between the cover 11 and the pressure plate 12. This diaphragm spring 13 has, on the one hand, a peripheral portion 13a and, on the other hand, fingers 13b that extend radially inward from the peripheral portion 13a towards the diaphragm 13.

[0045] The diaphragm spring 13 is mounted so as to be able to pivot relative to the cover 11 around articulation means, which are here partly formed as stampings 18 directly in the cover. During a disengagement phase, the diaphragm spring 13 is actuated by a clutch stop 8. The clutch stop 8 exerts an axial thrust force F (see figure 1 ) on the free ends of the fingers 13b of the diaphragm spring 13. In doing so, the peripheral part 13a of the diaphragm spring 13 bears against the articulation means and in this way a lever effect is obtained by which the outer edge of the diaphragm approaches the cover 11. The pressure plate 12 then moves away from the friction linings, the transmission of torque is interrupted so that it is possible to change gear ratios.

[0046] With a conventional clutch mechanism, wear of the articulation means such as the cover stampings and the contact areas of the diaphragm spring would result in the appearance of operating play between the cover and the diaphragm spring.

[0047] The main object of the invention is therefore to provide an improved clutch mechanism 10 capable of compensating for wear of the diaphragm spring joint so as to achieve complete disengagement of the clutch mechanism throughout the life of the motor vehicle.

[0048] We will now describe in more detail the arrangement of the clutch mechanism 10, according to one of the preferred embodiments of the invention, with reference to figures 1 à 4 .

[0049] Within the clutch mechanism 10, the diaphragm spring 13 is held under axial preload against the cover 11 by means of a support washer 14 having axial protrusions 15 passing through the diaphragm spring and the cover and a plurality of elastic segments 20, distributed angularly around the axis of rotation X of the clutch mechanism, arranged between two adjacent components of the clutch mechanism, namely the support washer 14 and the diaphragm spring 13. The support washer 14 is therefore indirectly supported on the diaphragm spring in particular by means of the elastic segments interposed axially between the two adjacent components, which elastic segments 20 exert the axial preload on the diaphragm spring.

[0050] Each elastic segment 20 extends angularly around the X-axis at an angle between 25° and 170°, and the number of elastic segments can be between 2 and 12, with the elastic segments being regularly distributed angularly around the X-axis. As illustrated in the figure 2 , the clutch mechanism includes, as an example, six elastic segments 20 which each extend angularly around the X axis at an angle of approximately 55°.

[0051] In order to improve these elastic properties, the elastic segment 20 is preferably made of chrome-vanadium steel (for example, 50CV4 type steel) or high carbon steel with a carbon content between 0.55% and 0.95%.

[0052] Also, each elastic segment 20 exerts a first action force along a first application diameter D1 and a second action force along a second application diameter D2 on one of the adjacent components of the clutch mechanism, in this example the support washer 14, as well as a reaction force along a third application diameter D3 on the other adjacent component of the clutch mechanism, in this example the diaphragm spring 13. As illustrated in the figure 4 The first, second, and third force application diameters, D1, D2, and D3, are concentric and radially spaced. The offset of the force application diameters reduces the stiffness of the elastic segments. Action force and reaction force refer to the preload forces that each elastic segment exerts on adjacent components when the clutch mechanism is assembled. These forces are measurable in Newtons. For example, the action forces F1 and F2 and the reaction force F3 are axially oriented.

[0053] In this example, each elastic segment 20, located between the support washer and the diaphragm spring, has a bearing diameter D5 on the diaphragm spring 13 that coincides with the third force application diameter D3. The third force application diameter D3 of the reaction force is positioned radially beyond the first and second force application diameters D1 and D2. This offset of the third force application diameter reduces the stiffness of the elastic segments and increases the wear compensation capacity of the diaphragm spring joint. To maintain the diaphragm spring under axial preload against the cover 11, the reaction force along the third force application diameter D3 must be greater than the axial thrust force F exerted by the clutch stop 8.

[0054] On the figure 3 The clutch mechanism 10 is shown in a substantially new condition. The operation of this clutch mechanism 10 according to the invention, particularly during the disengagement and engagement phases, is similar to the operation of a conventional clutch mechanism, except that here, each elastic segment 20 deforms elastically during these different phases so that the elastic segments 20 are always in contact with both the diaphragm spring 13 and the support washer 14. Thus, advantageously, permanent contact of the articulation means with the diaphragm spring 13 and the cover 11 is ensured.

[0055] In this example, the first action force along a first diameter of application of force D1 and the second action force along a second diameter of application of force D2 are oriented axially in opposite directions. Similarly, the second action force is oriented axially in a direction opposite to the reaction force.

[0056] The support washer 14 is made in the form of a rigid annular component fixed to the cover 11 by means of axial protrusions 15. Each axial protrusion 15 has an axial stop 16 capable of transmitting the axial preload force to the cover. More precisely, the axial protrusions 15 are spacers crimped onto the support washer. The axial stop 16 corresponds to an enlarged spacer head resting on an upper bearing surface of the cover. The second force application diameter D2 of the second action force is essentially the same as the mounting diameter D4 of the spacers crimped onto the support washer 14.

[0057] Each elastic segment 20 includes through holes 21 for axial protrusions 15, the through holes 21 being arranged radially beyond the first force application diameter D1 of the first action force.

[0058] Finally, each elastic segment 20 includes tabs 23 extending from an internal circumferential edge 24, and the support washer 14 includes orifices 14a distributed angularly around the X-axis, the tabs 23 of the elastic segments being inserted into the orifices 14a. The tabs 23 are oriented angularly opposite the through holes 21 provided to allow passage of the axial protrusions 15.

[0059] As illustrated on the figure 4 The support washer 14 comprises an upper bearing face 141 oriented towards the diaphragm spring 13 and a lower bearing face 142 axially opposite to the upper bearing face 141. Each elastic segment 20 simultaneously bears against the lower bearing face 142 according to the first acting force and against the upper bearing face 141 according to the second acting force. In this example, the tabs 23 of each elastic segment bear against the lower bearing face 142 of the support washer 14.

[0060] We will now describe, with reference to the figure 5 , a clutch mechanism 10 according to a second embodiment of the invention substantially similar to the previous one. This second embodiment of the invention is distinguished by the fact that each elastic segment 20 is securely fixed to the support washer 14 by means of at least one fixing point 25, for example by riveting, welding or screwing.

[0061] In this example, each elastic segment 20 comprises tabs 23 extending from an internal circumferential edge 24, and the support washer 14 comprises holes 14a distributed angularly around the X-axis, with the tabs 23 of the elastic segments being inserted into the holes 14a. The attachment points 25 are arranged on the tabs 23.

[0062] The attachment points 25 of the elastic segments 20 are distributed angularly along the first diameter of force application D1. The attachment points 25 are rivets. Alternatively, the attachment points may be weld points.

[0063] We will now describe with reference to figures 6 And 7 , a clutch mechanism 10 according to a third embodiment of the invention substantially similar to the first embodiment. This third embodiment of the invention is distinguished by the fact that the support washer 14 comprises centering studs 30 associated with each elastic segment 20.

[0064] Each of the centering studs 30 is inserted into a hole 26 provided in the associated elastic segment 20 in order to hold the elastic segments in position. For example, the centering studs 30 are extruded from the annular portion of the support washer 14.

[0065] In this example, each elastic segment 20 comprises tabs 23 extending from an internal circumferential edge 24, and the support washer 14 comprises holes 14a distributed angularly around the X-axis, the tabs 23 of the elastic segments being inserted into the holes 14a. The tabs 23 are angularly offset relative to the through holes 21 provided to allow passage of the axial protrusions 15.

[0066] Each elastic segment 20, positioned between the support washer and the diaphragm spring, has a bearing diameter D5 on the diaphragm spring 13 that coincides with the third force application diameter D3. The third force application diameter D3 of the reaction force F3 is positioned radially beyond the first and second force application diameters D1, D2 of the first and second action forces F1, F2. The first force application diameter D1 of the first action force F1 is offset radially along the X-axis to reduce the stiffness of the elastic segments and increase the wear compensation capacity of the diaphragm spring joint. To achieve this, each elastic segment 20 bears against an inner periphery of the support washer 14 via each tab 23, which is formed at an angle Δ to the lower bearing face 142 of the support washer.

[0067] Each elastic segment 20 comprises a first application surface 201 of the first action force F1, a second application surface 202 of the second action force F2, a third application surface 203 of the reaction force F3, the third application surface 203 being axially offset with respect to the first and second application surfaces 201, 202.

[0068] The second force application diameter D2 of the second action force F2 is substantially coincident with the mounting diameter of the spacers 15 crimped onto the support washer. According to the invention, the term "substantially coincident" means that the diameters are equal or of similar dimensions.

[0069] In this example, the first action force F1 along the first diameter of force application D1 and the second action force F2 along the second diameter of force application D2 are oriented axially in opposite directions. Similarly, the second action force F2 is oriented axially in a direction opposite to the reaction force F3.

[0070] From the figure 7 It is understood that, in order to maintain the diaphragm spring 13 under axial preload against the cover 11, the reaction force F3 along the third diameter of force application D3 must be greater than the axial thrust force F exerted by the clutch stop 8. Each elastic segment 20 is elastically deformed to ensure permanent contact between the articulation means and the diaphragm spring 13 and the cover 11. To prevent excessive deformation of the elastic segments 20, the support washer 14 includes on its outer periphery an annular support rim 14b which limits the axial deformation of said elastic segments. In the engaged position of the clutch mechanism 10, an axial gap exists between this rim 14b and the outer radial end of each elastic segment.Beyond a certain effort, the external radial end can come to rest on the annular support rim 14b and thus prevent cracking or breakage of the elastic segments.

[0071] We will now describe, with reference to the figure 8 , a clutch mechanism 10 according to a fourth embodiment of the invention in which the third force application diameter D3 of the reaction force is arranged radially between the first and second force application diameters D1, D2. The offset of the third force application diameter of the reaction force has the effect of reducing the stiffness of the elastic segments and increasing the wear compensation capacity of the diaphragm spring joint.

[0072] In this example, each elastic segment 20, positioned between the support washer 14 and the diaphragm spring 13, has a bearing diameter D5 on the diaphragm spring 13 that coincides with the third force application diameter D3. Advantageously, the first acting force along a first force application diameter D1 and the second acting force along a second force application diameter D2 are oriented axially in the same direction. Thus, the support washer 14 has an upper bearing face 141 oriented towards the diaphragm spring 13, with each elastic segment 20 simultaneously bearing on the upper bearing face 141 with the first and second acting forces.

[0073] Each elastic segment 20 comprises a first application surface 201 for the first action force, a second application surface 202 for the second action force, and a third application surface 203 for the reaction force. The third application surface 203 is axially offset from the first and second application surfaces 201 and 202. The first application surface 201 is located on the first application diameter D1, the second application surface 202 is located on the second application diameter D2, and the third application surface 203 is located on the third application diameter D3. The axial offset of the application surfaces for the action and reaction forces reduces the stiffness of the elastic segments.

[0074] In this fourth embodiment of the invention, each elastic segment 20 includes through holes 21 for axial protrusions 15, the through holes 21 being arranged radially beyond the first force application diameter D1 of the first action force. More specifically, the axial protrusions 15 are spacers crimped onto the support washer. The axial stop 16 corresponds to an enlarged spacer head resting on an upper bearing surface of the cover. The through holes 21 for the crimped spacers 15 are arranged radially between the first force application diameter D1 and the second force application diameter D2.

[0075] In this embodiment, the diaphragm spring 13 is mounted so as to be able to pivot relative to the cover 11 around articulation means, here partly implemented in the form of a ring 19 attached to the cover. The attached ring 19 is, for example, an open or closed ring.

[0076] The invention is not limited to the examples of implementation of the invention that have just been described. figures 9 And 10 illustrate a fifth embodiment of the invention in which the elastic segments 20 are arranged between the end of the axial protrusions 15 and the cover 11. In other words, the elastic segments 20 are arranged outside the cover contrary to the embodiments previously described.

[0077] Within this clutch mechanism 10, the diaphragm spring 13 is held under axial preload against the cover 11 by means of a support washer 14 having axial protrusions 15 passing through the diaphragm spring and the cover, each axial protrusion 15 having an axial stop 16 capable of transmitting the axial preload force to the cover, and a plurality of elastic segments 20, distributed angularly around the axis of rotation X of the clutch mechanism, arranged between two adjacent components of the clutch mechanism, namely the axial stop 16 of the axial protrusions 15 and the cover 11. The support washer 14 is therefore in direct contact with the diaphragm spring 13 according to a bearing diameter D5.

[0078] As illustrated on the figure 9 , the clutch mechanism 10 includes, by way of example, six elastic segments 20 which each extend angularly around the X axis at an angle of approximately 40°.

[0079] Each elastic segment 20 exerts a first action force along a first application diameter D1 and a second action force along a second application diameter D2 on one of the adjacent components of the clutch mechanism, in this example the support washer 14, as well as a reaction force along a third application diameter D3 on the other adjacent component of the clutch mechanism, in this example the diaphragm spring 13. As illustrated in the figure 10 The first, second, and third force application diameters D1, D2, and D3 are concentric and radially spaced. The offset of the force application diameters reduces the stiffness of the elastic segments.

[0080] In this example, each elastic segment 20 comprises a first application surface 201 for the first action force, a second application surface 202 for the second action force, and a third application surface 203 for the reaction force. The third application surface 203 is axially offset from the first and second application surfaces 201 and 202. The first application surface 201 is located on the first application diameter D1, the second application surface 202 is located on the second application diameter D2, and the third application surface 203 is located on the third application diameter D3. The axial offset of the application surfaces for the action and reaction forces reduces the stiffness of the elastic segments.

[0081] The support washer 14 is made in the form of a rigid annular component. The support washer 14 is fixed to the cover 11 by means of axial protrusions 15, each axial protrusion 15 having an axial stop 16 capable of transmitting the axial preload force to the cover. In this example, the axial protrusions 15 are formed from the same material as the support washer. More precisely, the axial protrusions 15 are bent tabs extending from the inner periphery of the support washer 14. The bent end of the tab 15 constitutes the axial stop 16. Thus, each elastic segment 20 has a bearing diameter D4 on the axial stops 16 coinciding with the third force application diameter D3.

[0082] The elastic segments 20 include through holes 21 for the axial protrusions 15, the through holes 21 being arranged radially beyond the first force application diameter D1 of the first action force. The through holes 21 for the tabs 15 are arranged radially between the first force application diameter D1 and the second force application diameter D2.

[0083] In this fifth embodiment of the invention, the cover 11 comprises an upper support face oriented axially outwards from the clutch mechanism, each elastic segment 20 simultaneously pressing on the upper support face with the first and second action forces. In order to maintain the diaphragm spring 13 under axial preload against the cover 11, the reaction force along the third application diameter of force D3 must be greater than the axial thrust force F exerted by the clutch stop 8.

[0084] According to another embodiment of the invention in which the diaphragm spring 13 is held in axial preload against the cover 11 by means of a support washer 14 and in which a plurality of elastic segments 20 is disposed between two adjacent components of the clutch mechanism, namely the axial stop 16 of the axial protrusions 15 and the cover 11, the third force application diameter D3 of the reaction force can be disposed radially inside the first and second force application diameters D1, D2.

[0085] In this alternative embodiment, each elastic segment can be securely attached to the lid using at least one fixing point, for example by riveting, welding, or screwing. The lid can also include centering studs associated with each elastic segment, the centering studs being extruded from the bottom of the lid.

[0086] The invention is not limited to its use in an industrial vehicle transmission as described above. The clutch mechanism 10 can also be integrated into a so-called "hybrid" motor vehicle transmission comprising a rotating electric machine that can be coupled to the power transmission from the internal combustion engine.

Claims

1. A clutch mechanism (10) for a motorized vehicle, comprising a cover (11), a pressure plate (12) coupled in rotation with the cover and movable axially relative thereto, and a diaphragm spring (13) bearing against the cover and the pressure plate, the diaphragm spring being held in axial preload against the cover by a support washer (14) provided with axial protuberances (15) passing through the diaphragm spring and the cover, each axial protuberance (15) having an axial stop (16) able to transmit the axial preload force to the cover, and a plurality of elastic segments (20), distributed angularly about the axis of rotation (X) of the clutch mechanism, these segments being arranged between two adjacent components of the clutch mechanism (10), namely between the axial stop (16) of the axial protuberances (15) and the cover (11) or between the support washer (14) and the diaphragm spring (13), which elastic segments (20) exert the axial preload on the diaphragm spring, characterized in that each elastic segment (20) exerts a first action force over a first force-application diameter (D1) and a second action force over a second force-application diameter (D2) on one of the adjacent components of the clutch mechanism, as well as a reaction force over a third force-application diameter (D3) on the other adjacent component of the clutch mechanism, the first, second and third force-application diameters (D1, D2, D3) being concentric and radially spaced.

2. The clutch mechanism (10) as claimed in claim 1, characterized in that at least one of the first and second action forces is oriented axially in an opposite direction to the reaction force.

3. The clutch mechanism (10) as claimed in one of the preceding claims, characterized in that each elastic segment (20) comprises a first application surface (201) for the first action force, a second application surface (202) for the second action force, a third application surface (203) for the reaction force, the third application surface (203) being offset axially with respect to the first and second application surfaces (201, 202).

4. The clutch mechanism (10) as claimed in one of the preceding claims, characterized in that the force-application diameter (D1, D2, D3) for at least one of the first and second action forces or the reaction force is offset radially with respect to the implantation diameter (D4) at which the axial protuberances (15) are implanted.

5. The clutch mechanism (10) as claimed in one of the preceding claims, characterized in that each elastic segment (20) comprises through-holes (21) for the axial protuberances (15), the through-holes (21) being arranged radially beyond the first force-application diameter (D1) for the first action force.

6. The clutch mechanism (10) as claimed in one of claims 1 to 5, characterized in that the third force-application diameter (D3) for the reaction force is arranged radially beyond the first and second force-application diameters (D1, D2).

7. The clutch mechanism (10) as claimed in the preceding claim, characterized in that the first action force over a first force-application diameter (D1) and the second action force over a second force-application diameter (D2) are oriented axially in opposite directions.

8. The clutch mechanism (10) as claimed in one of claims 6 or 7, characterized in that each elastic segment (20), arranged between the support washer (14) and the diaphragm spring (13), comprises a pressing diameter (D5) for pressing on the diaphragm spring that coincides with the third force-application diameter (D3).

9. The clutch mechanism (10) as claimed in one of claims 6 to 8, characterized in that each elastic segment (20) comprises tabs (23) originating from an internal circumferential edge (24), and the support washer (14) comprises orifices (14a) distributed angularly about the axis (X), the tabs (23) of the elastic segments being inserted in the orifices (14a).

10. The clutch mechanism (10) as claimed in the preceding claim, characterized in that the support washer (14) comprises an upper pressure face (141) oriented toward the diaphragm spring and a lower pressure face (142), axially opposite to the upper pressure face, each elastic segment (20) pressing simultaneously on the lower pressure face (142) with the first action force, and on the upper pressure face (141) with the second action force.

11. The clutch mechanism (10) as claimed in the preceding claim, characterized in that each elastic segment (20) presses on an internal periphery of the support washer (14) via each tab (23) which is formed at an angle (Δ) with respect to the lower pressing pressure face (142) of the support washer.

12. The clutch mechanism (10) as claimed in one of claims 6 to 10, characterized in that each elastic segment (20) is fixed solidly to the support washer (14) using at least one fixing point (25), for example using riveting, welding or screw fastening.

13. The clutch mechanism (10) as claimed in one of claims 1 to 5, characterized in that the third force-application diameter (D3) for the reaction force is arranged radially between the first and second force-application diameters (D1, D2).

14. The clutch mechanism (10) as claimed in the preceding claim, characterized in that the first action force over a first force-application diameter (D1) and the second action force over a second force-application diameter (D2) are oriented axially in the same direction.

15. The clutch mechanism (10) as claimed in claim 13 or 14, characterized in that the through-holes (21) for the axial protuberances (15) are arranged radially between the first force-application diameter (D1) and the second force-application diameter (D2).