Normally closed-type clutch module

Abstract

The invention relates to a normally closed-type clutch module (1) having a first axis of rotation (X) and comprising: - an output disc holder (3) that is rotatable relative to the first axis of rotation (X); - at least one friction disc (6); - a piston (20) comprising an actuating finger (21), the piston being configured such that, when the clutch module is in an engaged position, the actuating finger exerts a positive force on the friction disc, and such that, in a disengaged position, the actuating finger exerts no force on the friction disc; - an elastic device (30) configured to exert an elastic return force on the piston (20) in order to keep it in the engaged position, the elastic device (30) bearing axially against a portion of the output disc holder (3) that is located radially outside with respect to the actuating finger (21).

Description

Description Title of the invention: Normally closed type clutch module [1] The field of the present invention is that of clutch modules of the normally closed type, in particular for vehicles. [2] Transmission systems are known, arranged between the gearbox and the thermal engine, comprising an electric machine and a clutch on the engine side allowing the crankshaft of the thermal engine to be coupled in rotation to the rotor of the electric machine. Thus, it is possible to switch off the thermal engine each time the vehicle stops and to restart it using the electric machine. The electric machine can also constitute an electric brake or provide additional energy to the thermal engine to assist it or prevent it from stalling. The electric machine can also provide the vehicle's drive. When the thermal engine is running, the electric machine acts as an alternator.An actuation system has a rest state and an active state to ensure the control of the clutch between a coupling position of the thermal engine, called the "engaged position", and a decoupling position of the thermal engine, called the "disengaged position". If the active state of the actuation system corresponds to the engaged position, then it is referred to as a clutch of the normally open type. If the active state of the actuation system corresponds to the disengaged position, then it is referred to as a clutch of the normally closed type. Such a transmission assembly is disclosed in particular in patent application EP3532324. In this patent application, the clutch is of the "normally open" type. [3] The present invention aims in particular to further improve torque transmission systems. [4] The invention thus relates to a clutch module of the normally closed type having a first axis of rotation and comprising: - an output disc holder which can rotate relative to the first axis of rotation; - at least one friction disc, in particular a multi-disc assembly; - a piston comprising at least one actuating finger, the piston being configured so that, in an engaged position of the clutch module, the at least one actuating finger exerts a positive force on the at least one friction disc, and so that, in a disengaged position of the clutch module, the at least one actuating finger exerts a zero force on the at least one friction disc; - an elastic device configured to exert an elastic return force on the piston to maintain said piston in the engaged position, the elastic device being axially supported on a portion of the output disc holder located radially to the outside relative to the actuating finger. [5] The invention makes it possible, thanks to the fact that the elastic device is axially supported on a portion of the output disc carrier located radially to the outside relative to the actuating finger, to reduce the axial size of the clutch module. In addition, the elastic device can be of simple design which makes it possible to reduce manufacturing costs without impacting the durability or performance of the clutch module. [6] The "normally closed" type of the clutch module further has the following advantage. In order to transmit the torque of the thermal engine, which is the majority situation of use of the vehicle, it is not necessary to permanently activate the actuation system, therefore the invention allows energy saving. Furthermore, in the event of a system failure, the vehicle still remains functional. [7] According to one aspect of the invention, the elastic device is directly axially supported on a portion of the output disc holder located radially to the outside relative to the actuating finger. Thus, the number of parts is limited, which reduces the costs and complexity of manufacturing the module. [8] According to another aspect of the invention, the elastic device is indirectly axially supported on a portion of the output disc holder located radially to the outside relative to the actuating finger. Thus, an intermediate part ensures the connection between the elastic device and the output disc holder. output. This intermediate piece allows better contact with the elastic device. [9] According to one aspect of the invention, the output disc holder comprises a cylindrical skirt, said skirt being adapted to center the elastic device. Thus, the clutch module is easier to produce and the risks of deterioration of the capacities of the elastic device are reduced.

[0010] According to one aspect of the invention, the skirt is adapted to directly center the elastic device. Thus, the number of parts is limited, which reduces the costs and complexity of manufacturing the module.

[0011] According to another aspect of the invention, the skirt is adapted to indirectly center the elastic device. Thus, an intermediate piece ensures the connection between the elastic device and the skirt.

[0012] Advantageously, the clutch module further comprises a piston actuation system adapted to bring the piston, against the elastic return force of the elastic device, from the engaged position to the disengaged position. The presence of the actuation system allows optimal efficiency of the clutch module.

[0013] According to one aspect of the invention, the piston actuation system is axially supported, on the one hand, on the piston and, on the other hand, on the output disc holder, preferably through a bearing.

[0014] The invention makes it possible, thanks to the fact that the piston actuation system is axially supported, on the one hand, on the piston and, on the other hand, on the output disc holder, to create a force path during the actuation of the piston, a path which passes through the actuation system, the piston and the output disc holder, and advantageously without passing through a casing which surrounds the clutch module.

[0015] This force path is internal to the clutch module in the sense that the clutch module is self-sufficient, or almost self-sufficient, to allow its actuation. In other words, the clutch module is operational, for example, for a test / trial, without it being necessary to place this clutch module in its final environment. This is made possible by the fact that the force path is internal to the module (this force path does not have need to rely on components that are external to the clutch module). Another advantage is that the clutch module can be manufactured in a factory and then conveniently transported, before being assembled with other components such as an input module with damper.

[0016] According to one aspect of the invention, the at least one actuating finger of the piston passes axially through the elastic device. Thus, the axial size of the clutch module is reduced.

[0017] According to one aspect of the invention, the elastic device comprises a plurality of helical springs connected together by their ends. Thus, the elastic device is simple, inexpensive to produce and effective.

[0018] According to another aspect of the invention, the elastic device comprises at least one elastic washer. Thus, the elastic device is simple, inexpensive to produce and effective.

[0019] Advantageously, the at least one elastic washer can be a Belleville washer. Thus, the elastic device is simple, inexpensive to produce and effective.

[0020] Alternatively, the at least one elastic washer may be a Belleville washer or a wave washer. Thus, the elastic device is simple, inexpensive to produce and effective. The wave washer has, circumferentially, a succession of zones axially offset two by two.

[0021] According to one aspect of the invention, the clutch module further comprises an intermediate element adapted to ensure axial contact between the elastic device and the output disc carrier. Thus, contact between the elements is better achieved.

[0022] Advantageously, the intermediate element is a reed. Thus, the intermediate element is simple and inexpensive to produce and install.

[0023] According to one aspect of the invention, the clutch module further comprises an elastic ring axially secured to the at least one actuating finger and in which a portion of the elastic device, located radially inward relative to the actuating finger, rests on said elastic ring. Thus, the elastic return force of the elastic device is optimally transmitted to the piston.

[0024] Advantageously, the elastic ring is a circlip. Thus, the elastic ring is simple and inexpensive to make and install.

[0025] According to one aspect of the invention, the elastic device extends radially between an inner end and an outer end, the inner end bearing on said circlip.

[0026] According to one aspect of the invention, the clutch module further comprises at least one support piece adapted to ensure axial contact between the elastic ring and the elastic device. The support piece comprises a contact surface, adapted to be in contact with the elastic device, which is flat. Thus, the elastic device is more efficient because it works flat.

[0027] According to one aspect of the invention, the elastic device comprises at least one Belleville washer comprising a main body and at least two tabs extending radially outwardly from the main body, the at least one actuating finger of the piston passing axially through an opening located circumferentially between said at least two tabs. Thus, the Belleville washer has significant stiffness and load and is easy to install. In addition, the exposure fragility of the tabs is reduced.

[0028] According to another aspect of the invention, the elastic device comprises at least one Belleville washer comprising a main body and at least two tabs extending radially inward from the main body, the at least one actuating finger of the piston passing axially through an opening located circumferentially between said at least two tabs. Thus, the Belleville washer has significant stiffness and load and is easy to install. In addition, the size of the clutch module remains optimized.

[0029] According to another aspect of the invention, the elastic device comprises at least one Belleville washer comprising a main body in which at least one recess is made, the at least one actuating finger of the piston passing axially through said at least one recess. Thus, the Belleville washer has a very large solid surface, increasing its stiffness, and is easy to install. In addition, the elastic device offers an optimal load while having an optimized footprint.

[0030] According to another aspect of the invention, the elastic device comprises at least one Belleville washer comprising a main body in which at least one recess is made, the at least one actuating finger of the piston passing axially in said at least one recess, and at least one tab extending radially inwards, or outwards, from said main body. Thus, the Belleville washer has a large solid surface, increasing its stiffness, and is easy to install. In addition, the elastic device offers a suitable load while having an optimized size.

[0031] According to another aspect of the invention, the elastic device comprises two radially superimposed Belleville washers, the at least one actuating finger of the piston passing axially in a space located radially between the two Belleville washers. Thus, the Belleville washers each have a large solid surface, increasing their stiffness, and are easy to install. In addition, the elastic device provides an appropriate load while having an optimized size.

[0032] According to one aspect of the invention, the main body of the at least one Belleville washer extends circumferentially around the axis of rotation. Thus, the Belleville washer is easy to produce. Thus, the Belleville washer has significant stiffness and is easy to install.

[0033] According to one aspect of the invention, the main body of the at least one Belleville washer extends circumferentially continuously around the axis of rotation. Thus, the Belleville washer has a high load resistance.

[0034] According to another aspect of the invention, the elastic device comprises a first corrugated washer and a second corrugated washer radially superimposed, the at least one actuating finger of the piston passing axially in a space located radially between the first corrugated washer and the second wave washer. Thus, the wave washers each have a large diameter and a significant quantity of material to increase the stiffness and load of the elastic device. In addition, the size of the clutch module remains optimized.

[0035] According to another aspect of the invention, the elastic device comprises a third corrugated washer in which at least one window is made, the at least one actuating finger of the piston passing axially through said at least one window. Thus, the corrugated washer has a large diameter and a large quantity of material making it possible to increase the stiffness and the load of the elastic device. In addition, it is easy to make and to put in place while having an optimal size.

[0036] According to one aspect of the invention, the window is open. Thus, the elastic washer consumes less material without reducing its efficiency.

[0037] According to another aspect of the invention, the window is closed. Thus, the elastic washer is more resistant.

[0038] According to another aspect of the invention, the elastic device comprises a plurality of helical springs arranged circumferentially on a first circle and a second concentric circle, the first circle being located radially outside the at least one actuating finger of the piston and the second circle being located radially inside the at least one actuating finger. Thus, the elastic device has a high stiffness and load. In addition, it is easy to produce and install while optimizing the size of the clutch module.

[0039] According to one aspect of the invention, the number of springs of the plurality of springs present on the first circle is equal to the number of springs of the plurality of springs present on the second circle.

[0040] According to another aspect of the invention, the number of springs of the plurality of springs present on the first circle is different from the number of springs of the plurality of springs present on the second circle.

[0041] According to one aspect of the invention, the springs of the plurality of springs present on the first circle are identical to the springs of the plurality of springs present on the second circle.

[0042] According to another aspect of the invention, the springs of the plurality of springs present on the first circle are different from the springs of the plurality of springs present on the second circle.

[0043] According to another aspect of the invention, the elastic device comprises a plurality of helical springs arranged circumferentially on a first circle, the first circle being located radially outside the at least one actuating finger of the piston. Thus, the elastic device has a high stiffness and load. In addition, it is easy to produce and install while optimizing the size of the clutch module.

[0044] According to another aspect of the invention, the elastic device comprises a plurality of helical springs arranged circumferentially on a third circle, the third circle being located radially at the level of the at least one actuating finger of the piston, the at least one actuating finger passing between two springs of the plurality of helical springs. Thus, the elastic device has a high stiffness and load. In addition, it is easy to produce and install while optimizing the size of the clutch module.

[0045] Advantageously, the clutch module is configured to be assembled in a torque transmission system, in particular for a vehicle, which further comprises an input module cooperating with the clutch module, the input module being upstream (in the direction of torque passage) of the clutch module.

[0046] According to one aspect of the invention, the clutch module comprises a multi-disc assembly between an input disc carrier and the output disc carrier.

[0047] According to one aspect of the invention, the clutch module is of the wet type. It operates with immersion in a transmission fluid such as oil.

[0048] The invention also relates to a torque transmission system, in particular for a motor vehicle, comprising the clutch module as described above, and an input module assembled together, the input module being upstream (in the direction of torque passage) of the clutch module.

[0049] According to one aspect of the invention, the input module comprises an input disk holder placed opposite the output disk holder.

[0050] According to one aspect of the invention, the input module comprises a damper and an input disc holder.

[0051] According to one aspect of the invention, the input disc carrier is placed opposite, radially and / or axially, the output disc carrier of the clutch module and linked to an output of the damper.

[0052] As is known, the damper serves to filter the torsional oscillations (or acyclisms) of the thermal engine, independently of the engaged / disengaged state of the clutch module.

[0053] According to one aspect of the invention, the clutch module and the damping module are placed in an enclosure formed by a casing.

[0054] According to one aspect of the invention, the bottom of the housing contains the transmission fluid, and the clutch module is immersed in the transmission fluid.

[0055] The torque transmission system is intended in particular for a hybrid vehicle comprising a thermal engine and a rotating electrical machine, the clutch module being intended to couple / decouple the thermal engine from the vehicle's transmission line.

[0056] Other characteristics, details and advantages of the invention will emerge more clearly on reading the description which follows on the one hand, and several examples of embodiment given for informational and non-limiting purposes with reference to the appended schematic drawings on the other hand, in which:

[0057] Figure 1 is a sectional representation of a torque transmission system according to a first embodiment of the invention;

[0058] Figure 2 is a detail view of the system of Figure 1;

[0059] Figure 3 is a sectional representation of a torque transmission system according to Figure 2;

[0060] Figure 4 is a sectional representation of an alternative of the first embodiment of the torque transmission system according to Figure 3;

[0061] Figure 5 is a detailed view of a first variant of the system of Figure 1;

[0062] Figure 6 is a sectional representation, along the section GG shown in Figure 5;

[0063] Figure 7 is a detail view of a second embodiment of the system of Figure 1;

[0064] Figure 8 is a detailed view of a first variant of the system of Figure 7;

[0065] Figure 9 is a detailed view of a second variant of the system of Figure 7;

[0066] Figure 10 is a detail view of a third embodiment of the system of Figure 1;

[0067] Figure 11 is a sectional representation of a first variant of the system of Figure 10;

[0068] Figure 12 is a sectional representation of a second variant of the system of Figure 10;

[0069] The features, variants and different embodiments of the invention may be combined with each other in various combinations, provided that they are not incompatible or mutually exclusive. In particular, variants of the invention may be conceived comprising only a selection of features described below in isolation from the other features described, if this selection of features is sufficient to confer a technical advantage and / or to differentiate the invention from the prior art.

[0070] In the description and the claims, the terms "exterior" and "interior" as well as the orientations "axial" and "radial" will be used to designate, according to the definitions given in the description, of the elements of the damping device. The axis of rotation X determines the "axial" orientation. The "radial" orientation is directed orthogonally to the axis of rotation X. The "circumferential" orientation and / or the "tangential" contact are directed orthogonally to the axis of rotation X and orthogonally to the radial direction. The terms "outer" and "inner" are used to define the relative position of one component with respect to another, with reference to the axis of rotation X, a component close to said axis is thus qualified as internal as opposed to an external component located radially on the periphery. Furthermore, the angles and angular sectors expressed are defined in relation to the axis of rotation X.

[0071] By "vehicle" is meant motor vehicles, which include not only passenger vehicles but also industrial vehicles, which include in particular heavy goods vehicles, public transport vehicles or agricultural vehicles, but also any transport machine allowing a living being and / or an object to move from one point to another.

[0072] Ordinal numeral adjectives are used to differentiate characteristics. They do not define the position of a characteristic. Therefore, for example, a third characteristic of a product does not mean that the product has a first and / or second characteristic.

[0073] Figure 1 shows a cross-section of a torque transmission system 100 according to one embodiment of the invention.

[0074] The torque transmission system 100 is part of a drive train of a transmission line of a motor vehicle. The torque transmission system 100 is part of a drive train of a transmission line of a vehicle. The drive train may comprise a rotating electrical machine 200 provided with a stator and a rotor. The vehicle may be propelled, depending on requirements, by an internal combustion engine or by the rotating electrical machine 200.

[0075] As illustrated in particular in FIG. 1, the torque transmission system 100 has a first axis of rotation X. The torque transmission system 100 may comprise a torsional oscillation damper 300. The torsional oscillation damper 300 may comprise a support primary 301 pivoting about the first axis of rotation X and capable of being connected in rotation to a crankshaft of an internal combustion engine. The torque transmission system 100 may further comprise a secondary support 310 and elastic members 304 elastically coupling in rotation the primary support 301 to the secondary support 310. In a known manner, the torsional oscillation damper 300 serves to filter the torsional oscillations (or acyclisms) of the internal combustion engine. In the embodiment of FIG. 1, the elastic members 304 are curved helical springs. There may be four of them.

[0076] The torque transmission system 100 may further comprise an additional inertial mass 311 fixedly attached to the torsional oscillation damper 300. The additional inertial mass 311 may be in the form of an attached annular ring welded to the primary support 301. The additional inertial mass 311 has a second thickness equal to its largest axial dimension, preferably between 8 and 30 mm.

[0077] The torque transmission system 100 may further comprise a torque output element 302, here in the form of a hub. The torque output element 302 may comprise an internal spline. The torque output element 302 may pivot about the first axis of rotation X and is capable of being rotationally connected, directly or indirectly, to at least one input element, for example a splined shaft, of a gearbox BV.

[0078] The torque transmission system 100 may further comprise a transmission ring 80 rotationally connected to the torque output element 302 and configured to cooperate rotationally, directly or indirectly, with a rotor shaft 210 of the rotating electrical machine 200.

[0079] The elastic members 304, the additional inertia mass 311 and the transmission ring 80 are arranged axially opposite each other. The elastic members 304 can be axially positioned between the additional inertia mass 311 and the transmission ring 80. The elastic members 304 can be positioned radially outside the clutch module 1.

[0080] “Axially opposite” means that the elastic members 304, the additional inertia mass 311 and the transmission ring 80 are all crossed by the same right circular cylindrical surface having as its axis of revolution the first axis of rotation X and offset from each other parallel to this first axis of rotation X.

[0081] The primary support 301 may be driven by a crankshaft hub 306 via, for example, rivets 318. The crankshaft hub 306 may extend towards the center by an axial extension portion 307. The axial extension portion 307 may cooperate with a casing 70, for example by means of a needle centering bearing 308. The needle centering bearing 308 makes it possible to ensure the centering of the primary support 301. An axial bearing 90, formed by an axial needle thrust bearing or a plain axial bearing, may be interposed axially between the crankshaft hub 306 and the casing 70.

[0082] A friction washer 317 can be interposed between the primary support 301 and the secondary support 310 in order to axially position these two parts between them and to take up the axial forces passing through the transmission system 100.

[0083] The torque transmission system 100 further comprises a clutch module 1 selectively coupling the secondary support 310 of the torsional oscillation damper 300 with the torque output element 302.

[0084] The clutch module 1 may comprise several friction discs 6. The friction discs 6 may form a multi-disc assembly. The friction discs 6 may be arranged between an input disc carrier 2 and an output disc carrier 3. The input disc carrier 2 may be rotatably connected to the secondary support 310. The output disc carrier 3 may be rotatably connected to the torque output element 302. The input disc carrier 2 and the output disc carrier 3 may overlap axially.

[0085] The output disc holder 3 may comprise internal teeth arranged radially outside the friction discs 6 and linked in rotation with the friction discs 6. The transmission crown 80 can be fixed securely to the output disc holder 3.

[0086] The torque transmission system 100 may further comprise an input module 350. The input module 350 may comprise the damper 300 and the input disc carrier 2 which is placed opposite the output disc carrier 3 of the clutch module 1 and linked to an output of the damper 300.

[0087] The multi-disc assembly of the clutch 1 may comprise several friction discs 6 integral in rotation with the input disc carrier 2, several plates 7 arranged on either side of each friction disc 6, integral in rotation with the output disc carrier 3 and friction linings arranged between the plates 7 and the friction discs 6. The friction linings may be fixed, in particular glued or riveted, on the friction discs 6. Two friction linings may be fixed axially on either side of a friction disc 6.

[0088] In another embodiment not shown, a single friction lining can be fixed on a single axial side of a friction disc 6.

[0089] In another embodiment not shown, a single friction lining can be fixed axially on a single axial side of a friction disc 6 and another friction lining can be fixed on a single axial side of a plate 7.

[0090] The clutch module 1 can take a disengaged position and an engaged position. In the engaged position, the plates 7 and the friction discs 6 pinch the friction linings so as to transmit a torque between the input disc carrier 2 and the output disc carrier 3. The output disc carrier 3 can carry, fixed axially, a reaction element against which the multi-disc assembly is clamped in the engaged position. The plates 7 and the friction discs 6 can be radially between a cylindrical skirt 12 of the output disc carrier 3 and a cylindrical skirt 14 of the input disc carrier 2. The cylindrical skirt 14 can carry radially external teeth which cooperate in rotation with the friction discs 6. The clutch module 1 can comprise between 2 and 7 friction discs, for example 2 friction discs.

[0091] Of course, other arrangements of friction discs 6 and plates 7 can be envisaged.

[0092] The clutch module 1 may further comprise a piston 20. The piston 20 may comprise at least one actuating finger 21 adapted to, in the engaged position, exert a positive force on the multi-disc assembly in order to tighten the latter. The at least one actuating finger 21 is further adapted to, in the disengaged position, exert a zero force on the multi-disc assembly in order to loosen the latter. The at least one actuating finger 21 may press on a counter-disc 29 to tighten the multi-disc assembly. The counter-disc 29 may be connected in rotation to the output disc carrier 3, with the possibility of axial movement.

[0093] The piston 20 may comprise a plurality of actuating fingers 21.

[0094] The clutch module 1 may further comprise an elastic device 30.

[0095] The elastic device 30 is adapted to exert an elastic return force on the piston 20 to maintain said piston 20 in the engaged position. Such a clutch module 1 is said to be of the normally closed type.

[0096] The elastic device 30 may bear axially on the at least one actuating finger 21 of the piston 20. Alternatively, said axial bearing may be achieved via an elastic ring, for example a circlip 49. The circlip 49 may be axially secured to the at least one actuating finger 21. The circlip 49 may be circular. The circlip 49 may be continuous.

[0097] A support piece 34 may further be added axially between the circlip 49 and the elastic device 30. The support piece 34 is adapted to ensure axial contact between the two elements. The support piece 34 comprises a flat contact surface. Said contact surface is adapted to be in contact with the elastic device 30.

[0098] The elastic device 30 may furthermore be axially supported on a portion of the output disc holder 3. This portion of the output disc holder 3 may be located radially to the outside relative to the actuating finger 21. Alternatively, said axial support may be achieved via an intermediate element, for example a snap ring 33. The snap ring 33 may be circular. The snap ring 33 may be continuous.

[0099] The elastic device 30 may extend between an inner end 31 and an outer end 32. More particularly, the inner end 31 may bear axially, directly or via the elastic ring, on the at least one actuating finger 21 of the piston 20. More particularly, the outer end 32 may bear axially, directly or indirectly, on the portion of the output disc holder 3.

[0100] Each actuating finger 21 of the piston 20 can pass axially through the elastic device 30.

[0101] The elastic device 30 may comprise an elastic washer 36.

[0102] According to a first embodiment of the elastic device 30, the elastic washer 36 may be at least one Belleville type washer 50. The Belleville washer 50 may comprise a body 52. The body 52 may be continuous. The body 52 may extend circumferentially around the axis of rotation X. The inner end 31 of the elastic device 30 may be comprised by the body 52. The body 52 may be in contact with the circlip 49. The Belleville washer 50 may further comprise at least two tabs 51. The Belleville washer 50 may comprise a plurality of tabs 51. Each of the tabs 51 extends radially outward. Each of the tabs 51 extends radially between a first end, integral with the body 52, and a second free end. The free end can be confused with the outer end 32 of the elastic device 30. The free end can be in contact with the output disc holder 3.An opening 55 may be formed between two circumferentially adjacent tabs 51. The opening 55 may extend circumferentially between two tabs 51. The at least one actuating finger 21 of the piston 20 may pass axially through the opening 55.

[0103] Alternatively, as seen in Figure 4, each of the tabs 51 extends radially inward. The free end of the tab 51 may be coincident with the inner end 31 of the elastic device 30. The free end may be in contact with the circlip 49. The outer end 32 of the elastic device 30 may be comprised by the body 52. The body 52 may be in contact with the output disc holder 3.

[0104] According to a first variant of the first embodiment of the elastic device 30, as visible in Figures 5 and 6, the body 52 may comprise at least one recess 53. The at least one actuating finger 21 of the piston 20 may pass axially into said at least one recess 53. The outer end 32 and the inner end 31 of the elastic device 30 may be comprised by the body 52. The body 52 may be in contact with the output disc holder 3 and with the circlip 49.

[0105] According to a second variant of the first embodiment of the elastic device 30, the body 52 may comprise at least one recess 53 and tabs 51 extending radially inwards from said body 52. The actuating finger 21 of the piston 20 may pass axially into the recess 53. The free end of the tab 51 may merge with the inner end 31 of the elastic device 30 and be in contact with the circlip 49.

[0106] Alternatively, tabs 51 extend radially outwards from the body 52 and the actuating finger 21 of the piston 20 can pass axially into the recess 53. The free end of the tab 51 can be merged with the outer end 32 of the elastic device 30 and be in contact with the output disc holder 3.

[0107] According to a third variant of the first embodiment of the elastic device 30, the elastic washer 36 may comprise two Belleville type washers 50. The two Belleville washers 50 may be radially superimposed. The two Belleville washers 50 may be identical. The two Belleville washers 50 may be different. A space may be formed radially between the two Belleville washers 50. The at least one actuating finger 21 of the piston 20 may pass axially into said space. The Belleville washer 50 located radially outward may comprise the outer end 32 of the elastic device and the Belleville washer located radially inward may comprise the inner end 31 of the elastic device 30.

[0108] According to a second embodiment of the elastic device 30, the elastic washer 36 may be at least one wave washer 60. The wave washer 60 may comprise a body 64. The body 64 may be continuous. The body 64 may extend circumferentially around the axis of rotation X. The body 64 may have, circumferentially, a succession of zones axially offset two by two. The body 64 may comprise at least one window 65. The at least one actuating finger 21 of the piston 20 may pass axially through said at least one window 65. The window 65 may be closed. The window 65 may comprise a continuous internal contour. The outer end 32 and the inner end 31 of the elastic device 30 may be comprised by the body 64. The body 64 may be in contact with the output disc holder 3 and with the support piece 34.

[0109] According to a first variant of the second embodiment of the elastic device 30, shown in Figure 8, the body 64 of the corrugated washer 60 (also called third corrugated washer 63) may have at least one open window 65. The at least one actuating finger 21 of the piston 20 may pass axially through said at least one window 65. The window 65 may comprise a discontinuous inner contour. The outer end 32 of the elastic device 30 may be comprised by the body 64. The body 64 may be in contact with the output disc holder 3.

[0110] According to a second variant of the second embodiment of the elastic device 30, the elastic washer 36 may comprise two corrugated washers 60, for example a first corrugated washer 61 and a second corrugated washer 62. The first corrugated washer 61 may be identical to the second corrugated washer 62. The first corrugated washer 61 may be different from the second corrugated washer 62. A space 66 may be formed radially between the first corrugated washer 61 and the second corrugated washer 62. The at least one actuating finger 21 of the piston 20 may pass axially into said space 66. The first corrugated washer 61 located radially outward may comprise the outer end 32 of the elastic device 30 and the second corrugated washer 62 located radially inward may comprise the inner end 31 of the elastic device 30.

[0111] According to a third embodiment of the elastic device 30, the latter may comprise a plurality of springs 35. The plurality of springs 35 may be helical. The plurality of helical springs 35 may be connected together by their ends, for example by a plate 41 and preferably by two plates 41. This is then referred to as a “Spring Pack” in English. As seen in Figure 10, the plurality of springs 35 may be arranged circumferentially on a first circle. The first circle may be located radially outside the at least one actuating finger 21 of the piston 20. The plates 41 may respectively comprise the inner end 31 and the outer end 32 of the elastic device 30. The plurality of springs 35 may be entirely arranged radially outside the at least one actuating finger 21 of the piston 20. The springs of the plurality of springs 35 may be located circumferentially between and radially outside two adjacent actuating fingers 21.Alternatively, the plurality of springs 35 may be radially aligned with each actuating finger 21.

[0112] According to a first variant of the third embodiment of the elastic device 30, as visible in FIG. 11, the plurality of springs 35 can be arranged circumferentially on a first concentric circle and a second circle. The second circle can be located radially inside the at least one actuating finger 21 of the piston 20. Thus there are two levels of springs and the at least one actuating finger 21 can be located radially between the first and second circles.

[0113] The number of springs of the plurality of springs 35 located on the first concentric circle may be equal to the number of springs of the plurality of springs located on the second concentric circle. Alternatively, the number of springs of the plurality of springs 35 located on the first concentric circle may be greater than the number of springs of the plurality of springs 35 located on the second concentric circle. Alternatively, the number of springs of the plurality of springs 35 located on the first concentric circle may be less than the number of springs of the plurality of springs 35 located on the second concentric circle.

[0114] The springs of the plurality of springs 35 located on the first concentric circle may be identical to the springs of the plurality of springs 35 located on the second concentric circle. Alternatively, the springs of the plurality of springs located on the first concentric circle may be different from the springs of the plurality of springs located on the second concentric circle.

[0115] The springs of the plurality of springs 35 located on the first concentric circle may be radially aligned with the springs of the plurality of springs 35 located on the second concentric circle. Alternatively, the springs of the plurality of springs 35 located on the first concentric circle may be radially offset with the springs of the plurality of springs 35 located on the second concentric circle.

[0116] According to a second variant of the third embodiment of the elastic device 30, as visible in FIG. 12, the plurality of springs 35 may be arranged circumferentially on a third circle. The third circle may be located radially at the level of the at least one actuating finger 21 of the piston 20. Thus, at least one spring of the plurality of springs 35 is circumferentially adjacent to the at least one actuating finger 21. The springs of the plurality of springs 35 located on the third concentric circle may be circumferentially offset and radially aligned with the actuating fingers 21.

[0117] The transmission system 100 may further comprise an actuation system 40 for the clutch module 1. The actuation system 40 is configured to axially move, against the elastic return force of the elastic device 30, the piston 20 from the engaged position to the disengaged position. The actuation system 40 may be axially supported on the one hand on the piston 20 via a bearing 48 and, on the other hand, on the output disc carrier 3. The actuation system 40 may be of the mechanical, electromechanical, electromagnetic, or hydraulic type.

[0118] The actuation system 40 may be formed by a ball ramp 42 which comprises a first ramp and a second ramp. The first ramp is in the form of a crown which bears on the axial bearing. This first ramp is connected in rotation, for example via grooves or via welding, to an actuation lever. This lever actuating mechanism is formed by a wheel which is toothed internally to mesh with the second ramp and toothed externally to mesh, directly or indirectly, with a pinion which comes out of an actuator motor (not shown).

[0119] The input 2 and output 3 disc holders may comprise, approaching the first axis of rotation X, respectively a first radial zone 16 and a second radial zone 15 opposite each other. A first axial bearing 47, formed by an axial needle thrust bearing or a plain axial bearing, may be interposed between the first radial zone 16 and the second radial zone 15. A second axial bearing 46, formed by an axial needle thrust bearing or a plain axial bearing, may be interposed between the actuating system 40 of the piston 20 and the second radial zone 15 of the output disc holder 3. The piston 20 cooperates with the bearing 48 mounted on the actuating system 40 so as to cause the actuating system 40 to cooperate with the piston 20 with freedom of rotation about the first axis of rotation X, of the piston 20 relative to the actuating system 40.The first axial bearing, the second axial bearing, the bearing 48 mounted on the actuation system 40 and the actuation system 40 are arranged in an axial stack, namely that they are all crossed by the same right circular cylindrical surface having as its axis of revolution the first axis of rotation X and offset relative to each other parallel to this first axis of rotation X.

[0120] The transmission system 100 may further comprise a speed reducer assembly 220 capable of kinematically cooperating in rotation the transmission ring gear 80 with the rotor shaft 210 of the rotating electrical machine 200. The rotor shaft 210 rotates about a second axis of rotation XM. The speed reducer assembly 220 may be configured to allow several speed ratios. The transmission ring gear 80 is for example welded to the output disc holder 3.

[0121] The transmission system 100 may be housed in the housing 70 to form a transmission module. The housing 70 may be formed by two assembled half-shells 72. A predetermined quantity of fluid transmission may be contained in the housing 70, the transmission fluid being for example an oil.

[0122] The transmission system 100 is said to be “wet”, that is to say that the components housed in the casing 70 are in an oil mist or partially submerged. Annular seals may be provided to seal the casing 70.

Claims

Claims

1. Clutch module (1) of the normally closed type having a first axis of rotation (X) and comprising: - an output disc holder (3) which can rotate relative to the first axis of rotation (X); - at least one friction disc (6), in particular a multi-disc assembly (5); - a piston (20) comprising at least one actuating finger (21), the piston being configured so that, in an engaged position of the clutch module, the at least one actuating finger exerts a positive force on the at least one friction disc, and so that, in a disengaged position of the clutch module, the at least one actuating finger exerts a zero force on the at least one friction disc; - an elastic device (30) configured to exert an elastic return force on the piston (20) to maintain said piston (20) in the engaged position, the elastic device (30) being axially supported on a portion of the output disc holder (3) located radially outside relative to the actuating finger (21).

2. Clutch module (1) according to the preceding claim, further comprising an actuation system (40) for the piston (20) adapted to bring the piston (20), against the elastic return force of the elastic device (30), from the engaged position to the disengaged position.

3. Clutch module (1) according to any one of the preceding claims, wherein the at least one actuating finger (21) of the piston (20) passes axially through the elastic device (30).

4. Clutch module (1) according to any one of the preceding claims, wherein the elastic device (30) comprises a plurality of helical springs (35) linked together by their ends or at least one elastic washer (36), in particular a Belleville washer (50) or a wave washer (60).

5. Clutch module (1) according to any one of the preceding claims, further comprising an intermediate element (33) adapted to ensure axial contact between the elastic device (30) and the output disc carrier (3).

6. Clutch module (1) according to any one of the preceding claims, further comprising an elastic ring, in particular a circlip (49), axially secured to the at least one actuating finger (21) and in which a portion of the elastic device (30), located radially inside relative to the actuating finger (21), bears on said elastic ring.

7. Clutch module (1) according to the preceding claim, further comprising at least one support piece (34) adapted to ensure axial contact between the elastic ring and the elastic device (30).

8. Clutch module (1) according to any one of the preceding claims, wherein the elastic device (30) comprises at least one Belleville washer (50) comprising a main body (52) and at least two tabs (51) extending radially outwards, or inwards, from the main body, the at least one actuating finger (21) of the piston (20) passing axially in an opening (55) situated circumferentially between said at least two tabs.

9. Clutch module (1) according to any one of claims 1 to 7, wherein the elastic device (30) comprises at least one Belleville washer (50) comprising a main body (52) in which at least one recess (53) is made, the at least one actuating finger (21) of the piston (20) passing axially in said at least one recess.

10. Clutch module (1) according to any one of claims 1 to 7, wherein the elastic device (30) comprises a first corrugated washer (61) and a second corrugated washer (62) radially superimposed, the at least one actuating finger (21) of the piston (20) passing axially in a space (66) located radially between the first washer corrugated (61) and the second corrugated washer (62).

11. Clutch module (1) according to any one of claims 1 to 7, wherein the elastic device (30) comprises a third corrugated washer (63) in which at least one window (65) is made, the at least one actuating finger (21) of the piston (20) passing axially in said at least one window.

12. Clutch module (1) according to any one of claims 1 to 7, wherein the elastic device (30) comprises a plurality of helical springs (35) arranged circumferentially on a first circle and a second concentric circle, the first circle being located radially outside the at least one actuating finger (21) of the piston (20) and the second circle being located radially inside the at least one actuating finger (21).

13. Clutch module (1) according to any one of claims 1 to 7, wherein the elastic device (30) comprises a plurality of helical springs (35) arranged circumferentially on a first circle, the first circle being located radially outside the at least one actuating finger (21) of the piston (20).

14. Clutch module (1) according to any one of claims 1 to 7, wherein the elastic device (30) comprises a plurality of helical springs (35) arranged circumferentially on a third circle, the third circle being located radially at the level of the at least one actuating finger (21) of the piston (20), the at least one actuating finger (21) passing between two springs of the plurality of helical springs.

15. Torque transmission system (100), in particular for a vehicle, comprising a clutch module according to one of the preceding claims, and an input module (350) assembled together, the input module (350) being located upstream of the clutch module and comprising a damper and an input disc carrier (2), the input module and the module clutch being in particular placed in a casing (70), the clutch module (1) being in particular linked to an electric machine.

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