CLUTCH SUPPORT

Description

Technical field

[0001] The present invention relates to a clutch support for a removable dual clutch mechanism as used in the automotive field. The invention also relates to a dual clutch mechanism and a transmission system incorporating such a support. State of the prior art

[0002] Clutch mechanisms comprise a large number of components that must be assembled with care. Recent developments have continually sought to reduce the dimensions of clutch mechanisms, further reducing the space available for their assembly and mounting on a motor vehicle transmission, and more specifically on a gearbox housing.

[0003] In a known manner, clutch mechanisms generally comprise a first subassembly comprising at least one clutch associated with the elements which enable it to be implemented, and a second subassembly which comprises at least one actuator enabling the clutch to be configured in its engaged or disengaged configuration. Document DE102011014778A1 thus describes the assembly of an actuation module with a dual clutch device.

[0004] According to a first type of known architecture, the first and second subsets of such clutch mechanisms can be assembled by means of fastening “internal” to the clutch mechanisms in order to form a module; and the module thus formed is then mounted on the transmission by means of fastening “external” to the clutch mechanisms. This configuration advantageously makes it possible to facilitate maintenance operations on the clutch mechanisms by facilitating their replacement: it is sufficient to manipulate the “external” fastening means to detach the clutch mechanism from the transmission on which it was mounted. According to a second type of known architecture, the first and second subsets of such clutch mechanisms can be assembled and mounted one after the other on the transmission, without prior assembly.

[0005] In both types of architecture, a disadvantage of the known clutch mechanisms is that they are not easy to assemble. For example, some of the lubricating oil used to lubricate the clutch mechanisms may leak out of the clutch mechanisms through the openings rather than migrating towards the clutch(es). In addition, it is not always easy to reach the fastening means with the corresponding tool for mounting and / or dismounting the clutch mechanisms.

[0006] The present invention aims to address at least a large part of the above problems and also to lead to other advantages by proposing a new clutch support for a dual clutch mechanism. Another aim of the invention is to improve the lubrication of such a dual clutch mechanism, i.e. to facilitate the transport of the cooling flow from the pump to the frictions. Statement of the invention

[0007] According to a first aspect of the invention, at least one of the aforementioned objectives is achieved with a clutch support according to claim 1.

[0008] Preferably, the clutch carrier is arranged to support a first clutch and a second clutch.

[0009] The conduit has in particular at least one inlet orifice for the hydraulic fluid, for example several inlet orifices.

[0010] The hydraulic fluid is supplied by a hydraulic pump, particularly located on the actuation system side. More precisely, the fluid is supplied from the gearbox side. Said actuation system is particularly designed to configure the first clutch(es) between an engaged configuration and a disengaged configuration.

[0011] In particular, the duct may be included in the clutch support, for example by forming a bore passing through at least a portion of said clutch support, or by forming at least in part a groove on a peripheral face of the clutch support. In other words, the duct of the clutch support may be at least in part laterally open. In this case, the duct may then be jointly delimited by the clutch support and another component part of the clutch mechanism, such as for example the support bearing or the casing of the actuation system.

[0012] The radial part of the duct may in particular be open laterally. Alternatively or additionally, the annular part may be open, in particular open inwards, i.e. towards a longitudinal axis of the clutch support.

[0013] The annular portion of the duct may be located in an axial extension portion of the clutch support, depending on the variants on the same side or on the opposite side to the fixing member. The annular portion of the duct is for example located radially inside the axial portion of the clutch support.

[0014] The annular portion of the duct may be located at an axial end of the clutch carrier.

[0015] The duct may comprise at least one axial extension portion and at least one radial extension portion. By radial extension portion, in the context of the present invention, is meant a portion forming with a direction parallel to the axis of elongation of the clutch support a non-zero angle. Said radial extension portion may in particular be wholly or partly perpendicular to the axis of elongation of the clutch support (90°).

[0016] Said radial extension part of the duct may additionally or alternatively comprise at least one inclined extension part, i.e. forming with a direction parallel to the axis of elongation of the clutch support an angle strictly between 0 and 90°.

[0017] The outlet orifice of the duct, in particular of the radial extension portion of the duct or of the axial extension portion of the duct, takes the form of a through hole located on an outer face of the clutch support, allowing fluid communication between the duct and a space located radially outside the clutch support, in the clutch module. The hydraulic fluid circulating inside the duct of the clutch support is thus projected towards the clutch(es) through the outlet orifice in order to lubricate and / or cool in particular the first and second clutches.For the purposes of the invention, an outlet orifice is defined as being an opening located on the outer face of the clutch support and which in particular gives access to the radial extension part of the duct, making it possible to communicate the duct, for example said radial extension part or said axial extension part, respectively said inclined extension part, with the space located radially outside the clutch support, in the clutch module.

[0018] In the remainder of the description and in the claims, the following terms will be used, without limitation and in order to facilitate understanding: “front” or “rear” depending on the direction relative to an axial orientation determined by the main axis O of rotation of the clutch module, “rear” designating the part located to the right of the figures, on the transmission side, and “front” designating the left part of the figures, on the engine side; and “inner / inner” or “outer / outer” relative to the axis O and following a radial orientation, orthogonal to said axial orientation, “inner” designating a proximal part of the axis O and “outer” designating a distal part of the axis O.

[0019] The clutch support according to the first aspect of the invention may advantageously comprise at least one of the improvements below, the technical characteristics forming these improvements being able to be taken alone or in combination: the conduit comprises a plurality of inlet orifices and / or a plurality of outlet orifices, said inlet orifices, respectively outlet orifices being preferably angularly regularly distributed around a longitudinal axis of the clutch support, in particular coincident with the axis of rotation of the double clutch mechanism; the clutch support is made in a single piece; the clutch support is made in at least two parts; the clutch support is made at least in part of a material chosen from: steel, aluminum, a sintered material, a plastic material; the clutch support comprises a support bearing, in particular for radially supporting the clutch(es).

[0020] According to another aspect, the invention relates to an assembly of a clutch support as described and a fixing member configured to allow the clutch support to be fixed to a casing of the actuation system.

[0021] According to yet another aspect, the invention relates to a clutch module comprising: a first clutch rotating about an axis of rotation; a second clutch rotating about the axis of rotation; a clutch support as described previously; a clutch module fixing member. The fastening member is configured to allow the clutch module to be fastened to the housing of the actuation system. The actuation system is notably arranged to configure the first and second clutches between an engaged configuration and a disengaged configuration.

[0022] The fixing member and / or the clutch module may advantageously comprise at least one of the improvements below, the technical characteristics forming these improvements being able to be taken alone or in combination: the fixing member is located radially inside at least one axial bearing separating a first output disc carrier coupled to the first clutch from a second output disc carrier coupled to the second clutch; the fixing member is located at an axial end of the clutch support in order to facilitate access to it during assembly or disassembly operations on the transmission. Preferably, the fixing member is located at the front end of the clutch support. Advantageously, access to the fixing member is located at an axial end of the clutch support, for example at the front end of the clutch support; the fixing member is located on the side opposite the support bearing relative to the actuation system in order to facilitate access to it during assembly or disassembly operations on the transmission. Advantageously,access to the fixing member is located on the side opposite the support bearing relative to the actuation system; the fixing member bears against a front face of the clutch support in order to facilitate access to it during assembly or disassembly operations on the transmission; the clutch module comprises an input disc intended to be coupled in rotation to an input shaft of the engine, a first output disc carrier coupled in rotation to the first clutch and a second output disc carrier coupled in rotation to the second clutch, said input disc and said first and second output disc carriers each comprising at least one axial opening located opposite the fixing member and forming access to said fixing member. In particular,a radial dimension of the openings may be greater than an outer diameter of the fixing member in order to be able to access said fixing member more easily; a diameter of an outer face of each axial opening is greater than an outer diameter of the fixing member in order to facilitate access and / or handling of the fixing member; the axial openings make it possible to configure the fixing member in a first configuration in which said fixing member establishes a mechanical connection with the actuation system and a second configuration in which it is possible to release the clutch module from the actuation system; the axial openings are located opposite an actuation zone of the fixing member in order to facilitate access and / or handling of the fixing member; the fixing member is configured to perform axial locking of the clutch module on the casing of the actuation system,thus enabling the clutch module to be secured non-permanently to the actuation system. Once thus assembled, the clutch module forms an easily handled module. Said module can then, for example, be assembled more easily on the actuation system and / or mounted more easily on a transmission. In addition, this advantageous configuration makes it possible to quickly disassemble the clutch module according to the first aspect of the invention from the actuation system and / or the transmission, limiting the number and difficulty of the disassembly operations; the fixing member is of the type of an axial locking ring enabling axial locking of the clutch module on the casing of the actuation system; the fixing member is housed in a circular groove, interrupted or not, in the front face of the clutch support in order to facilitate its pre-assembly on the clutch module,and more particularly its centering relative to the axis of rotation of the clutch module according to the first aspect of the invention; the fixing member is of the elastic ring type delimited by an inner contour and an outer contour, the inner diameter being able to be deformed radially. This advantageous configuration thus allows the fixing member to be able to take the first radial configuration in which it is configured to be able to collaborate with the casing of the actuation system in order to establish a mechanical connection between the clutch module and said casing, preferably via an axial locking as described previously. This advantageous configuration also allows the fixing member to be able to take the second radial configuration in which it is configured to no longer collaborate with the casing of the actuation system in order to release the clutch module from said casing. Advantageously,the first configuration and / or the second configuration of the fixing member corresponds to a radial deformation of said fixing member, in which the inner contour and / or the outer contour are deformed in order to collaborate simultaneously with the clutch module on the one hand - and preferably the clutch support - and the actuation system on the other hand; the clutch support comprises means for axially retaining the fixing member in order to facilitate its pre-assembly on the clutch support, said axial retaining means at least partly delimiting the groove, in particular the circular groove; the axial retaining means are made in one piece with the clutch support. Alternatively, axial retaining means are added and fixed to the clutch support. In this embodiment, the axial retaining means are fixed to the clutch support by any known means,and in particular by welding and / or by screwing. The axial retaining means may form an overmolding of the fixing member on the clutch support. The axial retaining means are configured to allow, where appropriate, the fixing member to be able to take one or other of its configurations in order to be able to connect the clutch module to the actuation system or in order to be able to release them; the axial retaining means are angularly regularly distributed around the axis of rotation in order to make the pre-assembly of the fixing member on the clutch support more stable; according to a first variant embodiment, the axial retaining means comprise at least two flanges arranged to axially block the fixing member against the clutch support. Each flange may advantageously take the form of an angular sector at least partially covering the fixing member; according to a second variant embodiment,the axial retaining means take the form of an annular plate arranged to form, in collaboration with the front face of the clutch support, a housing for the fixing member, said fixing member being taken axially between the annular plate and the front face of the clutch support, the annular plate comprising at least one sectorial opening allowing access to the fixing member.

[0023] According to another aspect of the invention, there is provided a dual clutch mechanism comprising a clutch module such as one described above and an actuation system comprising: a first actuator arranged to move axially in order to engage or disengage the first clutch; a second actuator arranged to move axially in order to engage or disengage the second clutch; a casing housing the first and second actuators, said casing comprising a channel allowing a hydraulic fluid to circulate, said channel being arranged to collaborate with the conduit in order to allow fluid circulation of the hydraulic fluid between the conduit and the channel. The channel comprises for example an axial extension portion arranged to collaborate with the conduit, in particular with the annular portion of the conduit. The channel of the casing may alternatively cooperate with the axial extension portion or the radial extension portion of the conduit.

[0024] Advantageously, the double clutch mechanism according to the invention can advantageously comprise at least one of the improvements below, the technical characteristics forming these improvements being able to be taken alone or in combination: the casing of the actuation system comprises an axial elongation range which extends axially in front of the first and second actuators, the axial elongation range being arranged to collaborate with the clutch support. The axial elongation range of the actuation system extends axially towards the clutch module. More particularly, the axial elongation range extends towards the clutch support in order to collaborate with it. The collaboration between the clutch support and the axial elongation range of the casing may take the form of a radial shoulder in order in particular to achieve centering relative to the axis of rotation of the dual clutch mechanism according to the second aspect of the invention of the clutch module - via the clutch support - on the actuation system - via the casing. For this purpose,an inner cylindrical bearing surface of the clutch support may be in radial abutment against an outer face of the axial elongation surface of the casing, said axial elongation surface being located radially inside said clutch support. Alternatively, an inner face of the axial elongation surface of the casing may be in radial abutment against an outer face of the clutch support, said axial elongation surface being located radially outside said clutch support; according to a first embodiment variant, the axial elongation surface of the casing is made in one piece with said casing. According to a second embodiment variant, the axial elongation surface of the casing is attached to said casing and fixed integrally to the casing by any known fixing means, such as for example by welding, by pinning, by fitting, preferably by force, or by snap-fastening. In the first embodiment variant,the axial elongation range of the casing may be formed from the same material as said casing or from a different material. In particular, the axial elongation range of the casing is advantageously formed from steel or an alloy comprising steel; the axial elongation range of the casing comprises a groove, in particular a circumferential groove, arranged to be able to partially accommodate the fixing member. The groove of the casing, in particular a circumferential groove, is arranged to be able to participate in the fixing of the clutch module to the actuation system, in collaboration with the fixing member; an inner face of the circumferential groove has a diameter greater than or equal to the diameter of the inner contour of the fixing member,advantageously when said fixing member is configured to fix the clutch module to the actuation system. This advantageous configuration allows the fixing member to be inserted radially into the circumferential groove and to remain there to fix the clutch module to the actuation system in a durable and non-definitive manner; the axial elongation range of the casing comprises an end located on the side opposite the actuators of the actuation system relative to the circumferential groove, said end having an outer face of diameter less than or equal to the diameter of the inner contour of the fixing member,advantageously when said fixing member is not configured to fix the clutch module to the actuation system; the end of the axial elongation range takes the form of a conical surface whose diameter decreases away from the circumferential groove in order to generate a radial deformation of the fixing member, and more particularly a radial deformation of the inner contour of said fixing member; at a distal end of the circumferential groove, the diameter of the conical face is less than the diameter of the inner contour of the fixing member in order to facilitate the assembly of the clutch module on the actuation system; a diameter of an inner face of the clutch support is greater than or equal to an outer diameter of the axial elongation range of the casing,so that said axial elongation surface is force-fitted into the clutch support; the dual clutch mechanism according to the invention comprises means for rotationally coupling the housing to the clutch support. According to a first alternative embodiment, the rotational coupling means comprise first splines located on the axial elongation surface of the housing and collaborating by engagement of complementary shapes with second splines located on the clutch support of the clutch module. The first splines may be of the male type and the second splines may be of the female type, or the first splines may be of the female type and the second splines may be of the male type. According to a second alternative embodiment,the rotational coupling means comprise a key located on the casing of the actuation system or on the clutch support of the clutch module and collaborating with a corresponding housing located respectively on the clutch support or on the casing; the double clutch mechanism according to the second aspect of the invention is of the multi-disc type operating in a humid environment.

[0025] According to a first embodiment, the first clutch and the second clutch are arranged in a radial configuration, the first clutch being located radially outside the second clutch. According to a second embodiment, the first clutch and the second clutch are arranged in an axial configuration, the first clutch being located radially in front of the second clutch.

[0026] According to another aspect of the invention, there is provided a transmission system for a motor vehicle comprising a dual clutch mechanism as described above and in which: the first clutch is rotationally coupled to a first output shaft of the transmission via a first input disc carrier; the second clutch is rotationally coupled to a second output shaft of the transmission via a second input disc carrier; the first and second clutches are alternately rotationally coupled to an input disc, said input disc being rotationally coupled to an input shaft driven in rotation by at least one crankshaft.

[0027] According to another aspect of the invention, there is also provided a method of reversibly assembling a dual clutch mechanism, said assembly method comprising the following steps: a step of mounting the fixing member on the clutch support; a step of assembling the clutch module; a step of centering the clutch module on the casing of the actuation system relative to the axis of rotation; a step of relative translation of the clutch module relative to the actuation system in order to bring said clutch module closer to said actuation system; a step of axially locking the clutch module to the actuation system.

[0028] According to another aspect of the invention, there is provided a method for non-destructive disassembly of a dual clutch mechanism, said disassembly method comprising the following steps: a step of configuring the fixing member so as to be able to release the clutch module from the actuation system; a step of separating the clutch module and the actuation system.

[0029] Various embodiments of the invention are provided, incorporating, in all their possible combinations, the various optional features set out herein. Description of figures

[0030] Other characteristics and advantages of the invention will become apparent from the following description on the one hand, and from several examples of embodiment given for informational and non-limiting purposes with reference to the attached schematic drawings on the other hand, in which: there FIGURE 1A illustrates an axial sectional view of an exemplary embodiment of the double clutch mechanism according to the invention; FIGURE 1B illustrates an axial sectional view of another exemplary embodiment of a dual clutch mechanism not forming part of the invention; the FIGURES 2A And 2Billustrate sectional views of a fixing member preassembled on a clutch support according to two alternative embodiments of an assembly according to the invention; the FIGURES 3A , 3B And 3C illustrate views of a pre-assembled fixing member on a clutch support according to the variant of the FIGURE 2A ; THE FIGURES 3D à 3F illustrate different views of a variant of the fixing member according to the invention; the FIGURES 4A , 4B , 4C , 5A , 5B , 5C And 5D illustrate in profile views various stages of assembly of the double clutch mechanism illustrated in the FIGURE 1A .

[0031] Of course, 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 imagined 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 or to differentiate the invention from the prior art.

[0032] In particular, all the variants and embodiments described can be combined with each other if there is no technical obstacle to this combination.

[0033] In the figures, elements common to several figures retain the same reference. Detailed description of the invention

[0034] In reference to the FIGURE 1A , the illustrated embodiment of a dual clutch mechanism 10 according to the invention is preferably of the wet dual clutch type, and comprises a first clutch 100 and a second clutch 200. Preferably again, in a so-called radial position, the first clutch 100 is located outside the second clutch 200. Alternatively, the dual clutch mechanism 10 may be in a so-called axial configuration, the first clutch 100 being located in front of the second clutch 200. The dual clutch mechanism 10 is intended to be integrated into a transmission chain comprising a transmission coupled in rotation to the dual clutch mechanism 10.

[0035] According to the invention, the first clutch 100 and the second clutch 200 are supported by a clutch support 500 delimiting a conduit 700 allowing a hydraulic fluid to circulate from an actuation system 300 to the clutches. The conduit 700 comprises at least one radial extension portion 720 and has at least one outlet orifice 725 for the fluid to flow to the clutches. The clutch support 500 will be described more particularly later, in particular in connection with a fixing member 600 with which it forms an assembly 900. Different assembly variants 900 are illustrated in the FIGURES 2A And 2B And 3A à 3C .

[0036] Generally speaking, the double clutch mechanism 10 is arranged to be able to couple in rotation an input shaft, not shown, to a first transmission shaft A1 or alternatively to a second transmission shaft A2 via the first clutch 100 or the second clutch 200 respectively.

[0037] In the context of the invention, the input shaft is driven in rotation by at least one crankshaft of an engine, for example a heat engine; and the first and second transmission shafts A1, A2 are intended to be coupled in rotation to the transmission, such as for example a gearbox of the type fitted to motor vehicles.

[0038] Preferably, the first transmission shaft A1 and the second transmission shaft A2 are coaxial. More particularly, the second transmission shaft A2 optionally takes the form of a hollow cylinder inside which the first transmission shaft A1 can be inserted.

[0039] As illustrated in the FIGURE 1A , the first clutch 100 and the second clutch 200 are advantageously of the multi-disc type. Each multi-disc clutch comprises on the one hand a plurality of first friction elements 101, 201, such as for example flanges, connected in rotation to the input shaft, and on the other hand a plurality of second friction elements 102, 202, such as for example friction discs, connected in rotation to at least one of the transmission shafts A1, A2.

[0040] Optionally, the plurality of first friction elements 101, 201 consists of friction discs connected in rotation to the input shaft, and the plurality of second friction elements 102, 202 consists of flanges connected in rotation to at least one of the transmission shafts A1, A2.

[0041] The first transmission shaft A1 is rotationally coupled to the input shaft. The first transmission shaft A1 is driven by the input shaft in rotation when the first clutch 100 is configured in a so-called engaged position for which the plurality of first friction elements 101 is rotationally coupled to the plurality of second friction elements 102. Alternatively, the first transmission shaft A1 is rotationally decoupled from the input shaft when the first clutch 100 is configured in a so-called disengaged position for which the plurality of first friction elements 101 is rotationally decoupled from the plurality of second friction elements 102.

[0042] Similarly, the second transmission shaft A2 is rotationally coupled to the input shaft. The second transmission shaft A2 is driven by the input shaft in rotation when the second clutch 200 is configured in an engaged position for which the plurality of first friction elements 201 is rotationally coupled to the plurality of second friction elements 202. Alternatively, the second transmission shaft A2 is rotationally decoupled from the input shaft when the second clutch 200 is configured in a so-called disengaged position for which the plurality of first friction elements 201 is rotationally decoupled from the plurality of second friction elements 202.

[0043] In the dual clutch mechanism 10 illustrated in the FIGURE 1A , the first clutch 100 is arranged to engage the odd gears of the transmission and the second clutch 200 is arranged to engage the even gears and reverse gear of the transmission. Alternatively, the gears supported by said first clutch 100 and second clutch 200 may be respectively reversed.

[0044] The first clutch 100 and the second clutch 200 are arranged to alternately transmit a so-called input power - a torque and a rotational speed - from the input shaft, to one of the two transmission shafts A1, A2, depending on the respective configuration of each clutch 100 and 200 and by means of an input disc 109.

[0045] The first clutch 100 and the second clutch 200 are arranged not to be simultaneously in the same engaged configuration. On the other hand, the first clutch 100 and the second clutch 200 can simultaneously be configured in their disengaged position.

[0046] The dual clutch mechanism 10 comprises an input element which is rotationally coupled on the one hand to the input shaft and on the other hand to the input disc 109 in order to transmit the power - the torque and the rotational speed - generated at the engine to one of the clutches 100, 200 of the dual clutch mechanism 10. Preferably, the input element of the dual clutch mechanism 10 comprises an input hub 130, preferably rotating about the longitudinal axis O. The input hub 130 comprises a first lower elongation which is rotationally and / or axially connected to the input shaft, possibly via a damping device, such as a double damping flywheel for example.

[0047] The inlet hub 130 comprises an external elongation which is coupled to the inlet web 109, and more particularly to a lower end 1091 of the inlet web 109. The lower end 1091 is located towards the front AV of said inlet web 109. Preferably, the inlet web 109 and the inlet hub 130 are integral, for example fixed by welding and / or by riveting.

[0048] The input web 109 comprises an upper end 1092 by which the input web 109 is rotationally connected to the first clutch 100, and more particularly at the level of the first friction elements 101 of the first clutch 100. This connection is made by means of an external axial elongation surface 1061 of an input disc carrier 106, the input disc carrier 106 being rotationally connected to the input web 109, preferably by cooperation of shapes, for example by grooves at the level of the front end AV of said external axial elongation surface 1061. Alternatively, the input disc carrier 106 and the input web 109 are rotationally connected by means of any similar connection means.

[0049] At its inner end 1091, the entry web comprises a plurality of oblong and through openings 1092 forming the access T to the fixing member 600 which will be described later. The openings 1092 are preferably angularly regularly distributed around the axis of rotation O of the double clutch mechanism 10. A radial dimension of each opening 1092 is greater than an outer radial dimension of the fixing member 600 in order to facilitate its handling and / or the insertion of a tool to handle and / or configure it.

[0050] The first and second clutches 100 and 200 are controlled by the actuation system 300 which is arranged to be able to configure them in any configuration between the engaged configuration and the disengaged configuration.

[0051] The 300 actuation system includes: a first actuator 320 arranged to configure the first clutch 100 in a configuration between the engaged configuration and the disengaged configuration; a second actuator 330 arranged to configure the second clutch 200 in a configuration between the engaged configuration and the disengaged configuration; a casing 307 in which at least a portion of the first and second actuators 320, 330 are housed.

[0052] Preferably, the first and second actuators 320 and 330 are of the hydraulic cylinder type. The first and second actuators 320, 330 may each comprise an annular piston, each annular piston being coaxial with the axis O and developing an axial movement to configure the corresponding clutch. In this case, the actuation system 300 also comprises a hydraulic fluid supply channel for each actuator 320, 330. Preferably, the hydraulic fluid is a pressurized fluid, for example oil.

[0053] The first actuator 320 is connected to the first clutch 100 via, on the one hand, a first decoupling bearing 140 and, on the other hand, a first force transmission member 105. The first decoupling bearing 140 is arranged to transmit axial forces generated by the first actuator 320 to the first force transmission member 105.

[0054] The first force transmission member 105 is arranged to transmit an axial force E1, exerted parallel to the longitudinal axis O, to the first clutch 100 via its upper elongation, said upper elongation extending axially forward AV to be able to separate or press the first friction elements 101 against the second friction elements 102 on the one hand, and against an external reaction means 103 of the input disc 109 on the other hand. When the first friction elements 101 are separated from the second friction elements 102, then the first clutch 100 is configured in its disengaged configuration. On the other hand, when the first friction elements 101 are pressed against the second friction elements 102, then the first clutch 100 is configured in its engaged configuration.

[0055] The first force transmission member 105 takes the form of a corrugated sheet metal curved axially forward AV at its outer radial end. More particularly, the first force transmission member 105 collaborates with the first clutch 100 via a plurality of outer axial extension surfaces 1051 which extend parallel to the axis of rotation O and which form upper fingers which make it possible to push the friction elements 101, 102 of the first clutch 100 forward AV under the effect of an axial movement forward AV of the first actuator 320. The axial extension surfaces 1051 of the first force transmission member 105 collaborate with the first clutch 100 through an opening 1064 arranged through the input disc carrier 106.

[0056] The first force transmission member 105 comprises an upper radial extension bearing surface 1052 located behind AR of the outer axial extension bearing surfaces 1051. The upper radial extension bearing surface 1052 extends radially from the first clutch 100 to the inside of the second clutch 200.

[0057] An intermediate axial extension surface 1053 extends the first upper radial extension surface 1052 under the second clutch 200, towards the front AV of the double clutch mechanism 10. The first intermediate axial extension surface 1053 is located radially in line with the outer axial extension surfaces 1051. The intermediate axial extension surface 1053 is arranged parallel to the longitudinal axis O and parallel to the outer axial extension surfaces 1051.

[0058] Finally, the first force transmission member 105 comprises a plurality of inner radial extension bearing surfaces 1055 connected to the intermediate axial extension bearing surface 1053 via a curved zone 1054. Rear faces AR of the inner radial extension bearing surfaces 1055 are in contact with a front face AV of the first decoupling bearing 140 connected to the first actuator 320.

[0059] By way of non-limiting example, the first force transmission member 105 can be obtained by stamping.

[0060] The external reaction means 103 is integral with the inlet web 109. Preferably, the external reaction means 103 is connected to the inlet web 109 via the inlet disc holder 106; alternatively, the external reaction means 103 is fixed integrally to the inlet web 109 by any fixing means, such as for example by riveting or by welding.

[0061] The external reaction means 103 has in particular external grooves which cooperate with corresponding internal grooves of the input disc holder 106. By way of non-limiting example, the external reaction means 103 may take the form of a ring with teeth on the external periphery and a central support groove which extends axially towards the rear AR. By way of further non-limiting example, the external reaction means 103 may take the form of a boss of the input disc 109.

[0062] The external reaction means 103 has a shape complementary to that of the first or second friction elements 101, 102, so as to allow frictional coupling of the first and second friction elements 101, 102 when the first actuator 320 exerts the first axial force E1 forward AV to configure the first clutch 100 in its engaged position. Conversely, when the first force transmission member 105 is pushed back AR by elastic return elements which will be described later, then the first friction elements 101 separate from the second friction elements 102, then allowing said friction elements to be decoupled and thus allowing the first clutch 100 to be configured in its disengaged configuration.

[0063] The first clutch 100 is intended to be rotationally coupled to the first transmission shaft A1 via a first output disc carrier 110 forming an output element of said first clutch 100. More particularly, the first output disc carrier 110 is rotationally coupled to the second friction elements 102 via an upper end 1101 that the output disc carrier 110 comprises. Even more particularly, the first output disc carrier 110 is rotationally coupled to a first output hub 120 via an inner end 1102 that the first output disc carrier 110 comprises.

[0064] The first output disc carrier 110 comprises on its outer radial periphery a first axial elongation 107 which is provided with a toothing intended to cooperate with a complementary toothing on each second friction element 102, and more particularly at the inner radial periphery of each second friction element 102 of the first clutch 100. The first output disc carrier 110 is thus coupled in rotation by meshing with the second friction elements 102 of the first clutch 100.

[0065] The inner end 1102 of the first output disc carrier 110 is connected to the first output hub 120; they are preferably fixed together by welding, riveting or the like.

[0066] At its inner end 1102, the first output disc holder 110 comprises a plurality of oblong and through openings 1103 forming the access T to the fixing member 600 which will be described later. The openings 1103 of the first output disc holder 110 are preferably angularly regularly distributed around the axis of rotation O of the double clutch mechanism 10. A radial dimension of each opening 1103 of the first output disc holder 110 is greater than an outer radial dimension of the fixing member 600 in order to facilitate its handling and / or the insertion of a tool to handle and / or configure it. Advantageously, the openings 1103 of the first output disc holder 110 are coaxial with the openings 1092 of the inlet web 109.Preferably again, a radial dimension of the openings 1103 of the first output disc holder 110 is equal to the radial dimension of the openings 1092 of the input web 109.

[0067] The first output hub 120 comprises radially inside axial splines arranged to cooperate with complementary splines located on the first transmission shaft A1, so as to provide a rotational coupling.

[0068] A radial bearing 117 is interposed between the first output hub 120 and the input hub 130 in order to support the radial forces of the input hub 130 and / or the input web 109 despite the different rotational speeds at which the input shaft and the first transmission shaft A1 can respectively rotate.

[0069] Similarly, the second clutch 200 of the dual clutch mechanism 10 is of a similar design to that of the first clutch 100.

[0070] The second actuator 330 is connected to the second clutch 200 via, on the one hand, a second decoupling bearing 240 and, on the other hand, a second force transmission member 205. The second decoupling bearing 240 is arranged to transmit axial forces generated by the second actuator 330 to the second force transmission member 205.

[0071] The second force transmission member 205 is generally located axially between the input disc carrier 106 and the first force transmission member 105.

[0072] The second force transmission member 205 is arranged to transmit an axial force E2, exerted parallel to the longitudinal axis O, to the second clutch 200 via its upper elongation, said upper elongation extending axially forward AV to be able to separate or press the first friction elements 201 against the second friction elements 202 on the one hand, and against an internal reaction means 203 on the other hand. When the first friction elements 201 are separated from the second friction elements 202, then the second clutch 200 is configured in its disengaged configuration. On the other hand, when the first friction elements 201 are pressed against the second friction elements 202, then the second clutch 200 is configured in its engaged configuration.

[0073] The second force transmission member 205 takes the form of a corrugated sheet metal curved axially forward AV at its outer radial end. More particularly, the second force transmission member 205 collaborates with the second clutch 200 via a plurality of axial extension surfaces 2051 which make it possible to push the friction elements 201, 202 of the second clutch 200 forward AV under the effect of an axial movement forward AV of the second actuator 330. The axial extension surfaces 2051 of the second force transmission member 205 collaborate with the second clutch 200 through an opening 1065 arranged through the input disc carrier 106.

[0074] The second force transmission member 205 comprises an upper radial extension surface 2052 located to the rear AR of the outer axial extension surfaces 2051. The upper radial extension surface 2052 extends radially from the second clutch 200 to the inside of the second clutch 200, and more particularly at the level of the intermediate axial extension surface 1053 of the first force transmission member 105.

[0075] An intermediate axial extension surface 2053 extends the upper radial extension surface 2052 under the second clutch 200, towards the front AV of the double clutch mechanism 10. The intermediate axial extension surface 2053 is located radially inside the second clutch 200 and at the level of the upper radial extension surface 1052 of the first force transmission member 105.

[0076] Finally, the second force transmission member 205 comprises a plurality of inner radial extension bearing surfaces 2055 connected to the intermediate axial extension bearing surface 2053 via a curved zone 2054. Rear faces AR of the inner radial extension bearing surfaces 2055 are in contact with a front face AV of the second decoupling bearing 240 connected to the second actuator 330.

[0077] By way of non-limiting example, the second force transmission member 205 can be obtained by stamping.

[0078] The internal reaction means 203 is integral with an internal axial elongation portion 1062 oriented towards the front AV and integral with the input disc holder 106, fixed to the input disc holder 106 by any means, such as for example by welding or by riveting. Alternatively, the internal reaction means 203 and the input disc holder 106 are made of one material.

[0079] The external reaction means 203 has a shape complementary to that of the first or second friction elements 201, 202, so as to allow frictional coupling of the first and second friction elements 201, 202 when the second actuator 330 exerts an axial force E2 forward AV to configure the second clutch 200 in its engaged position. Conversely, when the second force transmission member 205 is pushed back AR by elastic return elements which will be described later, then the first friction elements 201 separate from the second friction elements 202, then allowing said friction elements 201, 202 to be decoupled and thus allowing the second clutch 200 to be configured in its disengaged configuration.

[0080] By way of non-limiting example, the external reaction means 203 may take the form of a ring with teeth on the external periphery and a central support groove which extends axially towards the rear AR.

[0081] The second clutch 200 is intended to be coupled in rotation to the second transmission shaft A2 via a second output disc carrier 210 forming an output element of said second clutch 200. More particularly, the second output disc carrier 210 is coupled in rotation to the second friction elements 202 at its upper end on the one hand, and on the other hand to a second output hub 220 at its lower end.

[0082] The second output disc carrier 210 comprises on its inner radial periphery an axial elongation 207 which is provided with a toothing intended to cooperate with a complementary toothing on each second friction element 202, and more particularly at the inner radial periphery of each second friction element 202 of the second clutch 200. The second output disc carrier 210 is thus coupled in rotation by meshing with the second friction elements 202 of the second clutch 200.

[0083] The inner radial end 2102 of the second output disc carrier 210 is connected to the second output hub 220, preferably fixed together by welding, riveting or the like.

[0084] At its inner end 2102, the second output disc holder 210 comprises a plurality of oblong and through openings 2103 forming the access T to the fixing member 600 which will be described later. The openings 2103 of the second output disc holder 210 are preferably angularly regularly distributed around the axis of rotation O of the double clutch mechanism 10. A radial dimension of each opening 2103 of the second output disc holder 210 is greater than an outer radial dimension of the fixing member 600 in order to facilitate its handling and / or the insertion of a tool to handle and / or configure it. Advantageously, the openings 2103 of the second output disc holder 210 are coaxial with the openings 2092 of the input web 109 and / or with the openings 1103 of the first output disc holder 110.Preferably again, a radial dimension of the openings 2103 of the second output disc holder 210 is equal to the radial dimension of the openings 1092 of the inlet web 109 and / or to that of the openings 1103 of the first output disc holder 110.

[0085] The second output hub 220 comprises radially inside axial splines arranged to cooperate with complementary splines located on the second transmission shaft A2, so as to provide a rotational coupling.

[0086] An axial bearing 116 is interposed between the first output disc carrier 110 and the second output disc carrier 210 in order to be able to transmit an axial force between the two output disc carriers 110, 210 which can rotate at different speeds when the first and second clutches 100, 200 are configured in a different configuration.

[0087] The first and second clutches 100, 200 respectively comprise elastic return elements for automatically pushing the first and second actuators 320, 330 rearward. More particularly, the elastic return elements axially bias the first and respectively the second force transmission member 105, 205 rearward AR in order to facilitate the separation of the first friction elements 101, 201 relative to the second friction elements 102, 202 of the first and respectively the second clutch 100, 200 by pushing the first and second actuators 320, 330 rearward. By way of non-limiting example, these may for example be Belleville washers.

[0088] The input disc carrier 106 further comprises an axial extension surface 1066 which extends axially forward AV under the second clutch 200, and an inner segment 1067 which extends radially, substantially perpendicular to the axis of rotation O of the double clutch mechanism 10. At its inner end, the inner segment 1067 of the input disc carrier 106 bears on a heel 118 bearing radially on a support bearing 113 supported by a clutch support 500 and arranged to support the radial load of the input disc carrier 106.

[0089] The clutch support 500 is located in an intermediate axial position between the actuation system 300 and the first and second output hubs 120, 220.

[0090] Axially forward AV, the support bearing 113 is axially supported against an axial end 510 front AV of the clutch support 500 and forming a support heel. Generally, the support heel making it possible to axially stop the support bearing 113 is arranged on the side opposite the axial force E1, E2 exerted by the first or second actuator 320, 330.

[0091] The front axial end 510 AV of the clutch support 500 bears axially against the second output disc carrier 210 via an axial bearing 115 in order to be able to transmit an axial force between the second output disc carrier 210 and the clutch support 500, said clutch support 500 being immobile in rotation while the second output disc carrier 210 can be driven by a rotational movement when the second clutch 200 is configured in its engaged configuration.

[0092] The support bearing 113 is here for example a rolling bearing. Advantageously, the support bearing 113 is of the angular contact bearing type in order to be able to transmit both an axial force and a radial force. This axial force is, at the rolling bearing 113, taken up by the clutch support 500 at the support heel. Indeed, when the first or second actuator 320, 330 transmits an axial force E1 oriented towards the front AV to the first or second force member 105, 205 in order to configure the corresponding clutch 100, 200 in the engaged configuration, the axial force E1, E2 is transmitted between a first end comprising said first or second actuator 320, 330 and a second end located at the transmission shaft A1, A2, and more particularly at the fixing member 600.All the elements participating in the transmission of the axial force E1, E2 during operation of the double clutch mechanism 10 and located axially between the fixing member 600 and the first or second actuator 320, 330 are axially blocked so as to be able to transmit said axial force E1, E2.

[0093] The clutch support 500 will be described more particularly with reference to the figures 2A And 2B .

[0094] In order to lubricate and cool the first 100 and second 200 clutches during their operation, the dual clutch mechanism 10 comprises a conduit and a channel for conveying a hydraulic fluid to the first 100 and second 200 clutches. More particularly, the clutch support 500 comprises a conduit 700 opening out of the clutch support 500 via an outlet orifice 725. The conduit 700 comprises a radial extension portion 720 located in the examples illustrated at the support bearing 113, said radial extension portion 720 opening out of the clutch support 500 via the outlet orifice 725.

[0095] While in the embodiment illustrated in the figures 1A And 2A , said conduit 700 comprises an axial extension portion 710 and a radial extension portion 720, in the embodiment illustrated in the figures 1B et 2B , said conduit 700 consists of the radial extension part 720.

[0096] The radial extension portion 720 of the duct 700 is advantageously located close to the front axial end 510 AV of the clutch support 500, and more particularly still in an intermediate situation between the support bearing 113 and the output hubs 120, 220.

[0097] The outlet orifice 725 is located radially outside the radial extension portion 720 of the duct 700. The outlet orifice 725 takes the form of a hole opening onto the outer face of the clutch support 500, and more particularly at an outer face of the front axial end 510 AV forming the support heel. In other words, the outlet orifice 725 is defined as an opening located on the outer face of the clutch support 500 and which gives access to the duct 700, in particular to the radial extension portion 720 of the duct 700 as illustrated in the FIGURES 2A , 2B And 3D-F , allowing said conduit, in particular said radial extension part 720, to communicate with the space located radially outside the clutch support 500, in the clutch module 15.

[0098] Radially, the outlet orifice 725 is located outside the fixing member 600. More particularly still, the outlet orifice 725 is located radially outside the openings 1103 of the first output disc carrier 110 and / or the openings 2103 of the second output disc carrier 210 and / or the openings 1093 of the inlet web 109. This advantageous configuration allows the hydraulic fluid exiting the conduit 700 through the outlet orifice 725 not to flow out of the double clutch mechanism 10 through the openings 1093, 1103, 2103 forming the access T to the fixing member 600. Consequently, the lubrication and / or the cooling of the first 100 and second 200 clutches during their operation is improved.

[0099] The casing 307 of the actuation system 300 comprises a channel 800 allowing a hydraulic fluid to circulate. In the illustrated example, said channel 800 comprises an axial extension portion 810 and a radial extension portion 820 located at the front axial end AV of the axial extension portion 810. The channel 800 is arranged to collaborate with the conduit 700 in order to allow fluid circulation of the hydraulic fluid between the conduit 700 and the channel 800. More particularly, in the illustrated example FIGURE 1A an outer radial end of the radial extension portion 820 of the channel 800 collaborates with a rear axial end of the conduit 700 in order to allow fluid communication between the conduit 700 and the channel 800. Advantageously, the channel 800 is in particular in fluid communication with the annular portion 750 of the conduit 700 in order to facilitate the angular positioning of the clutch support 500 without requiring angular indexing.

[0100] The channel 800 is advantageously located on a radially inner part of the casing 307, preferably still located inside the first 320 and second 330 actuators.

[0101] The casing 307 of the actuation system 300 comprises an axial elongation surface 3071 which is located radially inside the first 320 and second 330 actuators and which extends axially forward AV relative to said first 320 and second 330 actuators, in the direction of the input web 109. The axial elongation surface 3071 of the casing 307 is arranged to collaborate with the clutch support 500 in order to achieve centering and / or rotational coupling. The centering and / or the rotational coupling are achieved by fitting, preferably by force, a radial diameter of an outer face of the axial elongation surface 3071 of the casing 307 being less than or equal to a radial diameter of an inner face of the clutch support 500. Optionally, the rotational coupling can be achieved using first splines located on the axial elongation surface 3071 and collaborating with second splines located on the clutch support 500.

[0102] A front terminal end 3072 AV of the axial extension surface 3071 is arranged to collaborate with the fixing member 600 during the assembly of the actuation system 300 on the clutch support 500, and more particularly in order to facilitate the fitting of the casing 307 into the clutch support 500. In particular, the terminal end 3072 of the axial extension surface 3071 of the casing 307 takes the form of a conical surface 3073 whose diameter decreases as it moves away from the first 320 and second 330 actuators. This advantageous configuration makes it easier to open the fixing member 600 by forcing it to deform radially. The interaction between the fixing member 600 and the axial elongation range 3071 of the casing 307 will be described in more detail with reference to FIGURES 2A And 2B .

[0103] The axial elongation range 3071 of the casing 307 also comprises a circumferential groove 3074 intended to collaborate with the fixing member 600. The circumferential groove 3074 is located axially between the conical surface 3073 and the first 320 and second 330 actuators. An axial dimension of the circumferential groove 3074 is such that the fixing member 600 can engage at least partially in said circumferential groove 3074 in order to provide an axial stop. In other words, the axial dimension of the circumferential groove 3074 is greater than or equal to an axial thickness of the fixing member 600.

[0104] Finally, the dual clutch mechanism is formed by a clutch module 15 assembled on the actuation system 300 in particular according to a reversible assembly method illustrated by the FIGURES 4A à 4C .

[0105] The clutch module 15 comprises the first clutch 100 and the second clutch 200 supported by the clutch support 500. More generally, the clutch module 15 comprises all the elements which make it possible to establish a rotational coupling of the first 100 and second 200 clutches with the input shaft and the transmission shafts A1, A2. In particular, the clutch module 15 comprises the input disc 109, the input disc carrier 106, the first 110 and second 210 output disc carriers, the first 105 and second 205 force transmission members, the external reaction means 103 and the internal reaction means 203, the axial bearings 115, 116, 117.

[0106] The clutch module 15 is assembled on the casing 307 of the actuation system 300 by means of the fixing member 600, thus forming the double clutch mechanism 10 according to the second aspect of the invention.

[0107] The fixing member 600 will now be described more precisely with reference to the FIGURES 2A And 2B And 3A à 3C describing various examples of embodiments of such a fixing member 600 pre-assembled on the clutch support 500.

[0108] As visible on the FIGURES 2A And 2B , in the corresponding embodiments the clutch support 500 comprises an axial extension part 530 configured to be arranged under the clutches 100, 200 and to support - via the support bearing 113 - said clutches 100, 200. The axial extension part 530 of the clutch support 500 takes the form of a hollow cylindrical bearing surface in order to be able to house the transmission shafts A1, A2, not visible on the FIGURES 2A And 2B. The clutch support 500 also comprises the front axial end 510 which extends radially outside the axial extension portion 530 of the clutch support 500. Generally, the front axial end 510 AV of the clutch support 500 extends substantially perpendicular to the axial extension portion 530 of said clutch support 500.

[0109] As illustrated in section 2A, in this example, the axial extension portion 530 of the clutch support 500 houses the axial extension portion 710 of the conduit 700 described previously; and the front axial end 510 AV of the clutch support 500 houses the radial extension portion 720 of the duct 700. The clutch support 500 here comprises several radial extension portions 720 of the duct 700 which are angularly regularly distributed around the axis O and are in fluid communication via the axial extension portions 710 with the annular portion 750. The latter is here located at an axial end of the clutch support 500, on the side opposite the fixing member 600. The annular portion 750 is for example open towards the inside of the clutch support 500. In the example illustrated here the radial extension portions 720 of the duct 700 are located at the rear of the radial extension portion 510 of the support 500. They are open laterally.The axial extension parts 710 of the conduit 700 are here also laterally open, more particularly open towards the inside of the support 500.

[0110] In the example illustrated in section 2B, the axial extension portion 530 of the clutch support 500 houses the radial extension portion 720 of the duct 700 as well as the annular portion 750. In particular, in this example, the duct 700 is made up of several radial extension portions 720 extending between an outlet orifice 725 and the annular portion 750 of the duct 700. The outlet orifices 725 and the radial extension portions 720 are angularly regularly distributed around the axis O. The annular portion 750 of the duct 700 is here located in the axial extension portion 530 of the clutch support 500, in particular on the side of the fixing member 600. At the level of the front face 515 of the front axial end 510 AV of the clutch support 500, the member fixing 600 is housed in a removable manner.In particular, the fixing member 600 is pressed against the front face 515 of the clutch support 500 and held in this position in a non-definitive manner by axial retaining means 550. The axial retaining means 550 are advantageously located radially inside the oblong openings 1093, 1103, 2103 of the input web 109 and the output disc carriers 110, 210 forming the access T in order to facilitate the mounting and dismounting of the fixing member 600.

[0111] In the first example of realization illustrated on the FIGURES 2A-2B , the axial retaining means 500 of the fixing member 600 take the form of several flanges 550a, 550b, 550c each forming angular sectors and making it possible to achieve axial locking, possibly with non-zero axial play - of the fixing member against the front face.

[0112] The flanges 550a-550c are advantageously made of the same material as the clutch support 500. Optionally, they can be added and fixed to the clutch support 500 by any fixing means. Radially, the flanges 550a-550c are advantageously located radially inside the oblong openings 1093, 1103, 2103 of the input web 109 and the output disc carriers 110, 210 forming the access T in order to facilitate the assembly and disassembly of the fixing member 600.

[0113] The flanges 550a-550c are advantageously angularly regularly distributed around the axis O in order to improve the axial retention of the fixing member 600 against the clutch support 500.

[0114] Each flange 550a-550c thus forms a groove 520 inside which the fixing member 600 can be housed and held axially. More particularly, the axial dimensions of the groove 520 are greater than or equal to the axial thickness of the fixing member 600, taken at least in its radially outer part.

[0115] Advantageously, the radial dimensions of the groove are such that there is a non-zero radial clearance between the outer contour 620 of the fixing member 600 and the outer contour 521 of the groove 520 in order to allow disassembly of said fixing member 600 by off-centering relative to the axis of rotation O of the clutch support 500. Of course, when the fixing member 600 is radially deformable, the radial clearance described above is not essential.

[0116] In the illustrated embodiments, the fixing member 600 takes the form of a radially deformable axial locking ring: the inner contour 610 and / or the outer contour 620 of the fixing member 600 are radially deformable in order to allow said fixing member 600 to be dislodged or housed in the groove 520 of the clutch support 500.By deformable, it is understood that the fixing member 600 can undergo a radial elastic deformation making it possible to modify the radial dimensions of its inner contour 610 and / or its outer contour 620 and, consequently, to make it possible to modify its inner diameter and / or its outer diameter in order to configure it in a first configuration in which the fixing member 600 establishes a mechanical connection between the clutch module 15 and the actuation system 300, and a second configuration in which the fixing member 600 no longer cooperates with the actuation system 300, then making it possible to release the clutch module 15 from said actuation system 300.

[0117] There FIGURE 3C illustrates a second example of embodiment of the axial retaining means 550 of the fixing member 600 on the clutch support 500. More particularly, the axial retaining means here take the form of an annular-shaped closing plate collaborating with the front face 515 of the clutch support 500. In a manner comparable to the flanges 550a-550c of the FIGURES 3A-3C , the closing plate illustrated on the FIGURE 3 forms a groove located between said closing plate and the front face 515 of the clutch support, inside which the fixing member 600 can be housed, possibly without axial play. To remove the fixing member 600, the latter is deformed radially in order to make it pass through the center of the annular closing plate. In order to facilitate the handling of the fixing member 600, openings 540a-540c are provided on the closing plate. The openings 540a-540c take the form of oblong holes of sectoral shape, angularly regularly distributed around the axis of rotation O. The openings 540 form the access T to the fixing member 600 in order to allow its assembly and disassembly.The openings 540a-540c of the closing plate are advantageously located radially inside the oblong openings 1093, 1103, 2103 of the inlet web 109 and the outlet disc holders 110, 210 forming the access T in order to facilitate the assembly and disassembly of the fixing member 600.

[0118] THE FIGURES 4A , 4B And 4C illustrate a method of assembling the dual clutch mechanism 10 described previously.

[0119] For example, the method of assembling the dual clutch mechanism 10 comprises the following steps: a step of mounting the fixing member 600 on the clutch support 500; and / or a step of assembling the clutch module 15; and / or a step of centering the clutch module 15 on the casing 307 of the actuation system 300; and / or a step of relative translation of the clutch module 15 with respect to the actuation system 300 in order to bring said clutch module 15 closer to said actuation system 300; and / or a step of axially locking the clutch module 15 to the actuation system 300.

[0120] Cleverly, this is a reversible assembly method, with the dual clutch mechanism 10 being able to be disassembled non-destructively.

[0121] The clutch module 15 and the actuation system 300 are aligned, preferably coaxially with respect to the axis O.

[0122] As visible on the FIGURE 4B , the axial elongation surface 3071 of the casing 307 is fitted into the axial elongation surface 530 of the clutch support 500, the outer face of the axial elongation surface 3071 of the casing 307 collaborating with the inner face of the axial elongation surface 530 of the clutch support 500.

[0123] There FIGURE 4C illustrates the double clutch mechanism 10 in which the fixing member 600 is engaged in the circumferential groove 3074, thus providing axial coupling of the clutch module 15 with the actuation system 300, and more particularly an axial stop. In this configuration, the fixing member 600 makes it possible to secure the clutch module 15 to the actuation system 300 in a non-definitive manner.

[0124] THE FIGURES 5A , 5B , 5C And 5D illustrate a method of disassembling the dual clutch mechanism 10 described previously.

[0125] For example, the method of disassembling the dual clutch mechanism 10 comprises the following steps: a step of configuring the fixing member 600 so as to no longer collaborate with the actuation system 300; a step of separating the clutch module 15 and the actuation system 300.

[0126] Cleverly, this is a non-destructive disassembly process for the various elements of the dual clutch mechanism 10, the latter being able to be reassembled later.

[0127] Of course, the invention is not limited to the examples which have just been described and numerous adjustments can be made to these examples without departing from the scope of the invention. In particular, the different characteristics, forms, variants and embodiments of the invention can be associated with each other in various combinations insofar as they are not incompatible or mutually exclusive. In particular, all the variants and embodiments described above can be combined with each other.

Claims

1. Clutch support (500) designed to support at least one first clutch (100, 200), said support delimiting a duct (700) having at least one outlet orifice (725) allowing a hydraulic fluid to circulate from an actuating system (300) towards the at least one first clutch and comprising at least one radial-extension part (720), characterized in that the duct (700) further comprises an annular part (750), the actuating system (300) comprising a passage (800) designed to cooperate with the duct (700) in order to allow fluidic circulation of the hydraulic fluid between the duct (700) and the passage (800).

2. Clutch support (500) according to Claim 1, the duct comprising a plurality of inlet orifices (723) and / or a plurality of outlet orifices (725), said inlet orifices (723), or respectively outlet orifices (723), preferably being uniformly angularly distributed about a longitudinal axis O of the clutch support.

3. Clutch support (500) according to Claim 1 or 2, the duct being at least partially open laterally.

4. Clutch support (500) according to the preceding claim, at least one radial-extension part (720) of the duct being open laterally.

5. Clutch support (500) according to any one of the preceding claims, the annular part being open towards the inside of the clutch support (500), namely towards a longitudinal axis of the clutch support.

6. Clutch support (500) according to any one of the preceding claims, the annular part of the duct being situated in an axial-extension part of the clutch support.

7. Clutch support (500) according to any one of the preceding claims, being produced at least in part from a material chosen from: steel, aluminium, a sintered material, a plastics material.

8. Clutch support (500) according to any one of the preceding claims, being produced in a single piece.

9. Clutch support (500) according to any one of Claims 1 to 7, being produced in at least two parts.

10. Clutch support (500) according to the preceding claim, comprising a support bearing (113) in particular for radially supporting the first (100) and second (200) clutches.

11. Clutch support according to the preceding claim, the support bearing (113) being of the angular contact bearing type.

12. Assembly (900) of a support according to any one of the preceding claims and of a fixing member (600).

13. Clutch module (10) comprising: - a first clutch (100) rotating about the axis (O); - a second clutch (200) rotating about the axis (O); - a clutch support (500) according to any one of Claims 1 to 9; - a fixing member (600) for fixing the clutch module.

14. Dual-clutch mechanism comprising a clutch module according to the preceding claim and an actuating system comprising: - a first actuator designed to move axially in order to engage or disengage the first clutch; - a second actuator designed to move axially in order to engage or disengage the second clutch; - a casing (307) housing the first and second actuators, said casing comprising a passage (800) allowing a hydraulic fluid to circulate, said passage (800) being designed to cooperate with the duct (700) in order to allow fluidic circulation of the hydraulic fluid between the duct (700) and the passage (800).

15. Dual-clutch mechanism according to the preceding claim, the passage (800) comprising an axial-extension part (810) designed to cooperate with the duct (700).