• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a clutch support (500) arranged to support at least a first clutch, said support delimiting a duct (700) comprising at least one radial extension portion (720) and having at least one outlet orifice ( 725) allowing a hydraulic fluid to flow from an actuating system to the at least one first clutch.
    公开号:FR3062698A1
    申请号:FR1758050
    申请日:2017-08-31
    公开日:2018-08-10
    发明作者:Arnaud Dole；Francois Thibaut
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    Technical area
    The present invention relates to a clutch support for a removable double-clutch mechanism as used in the automotive field. The invention also relates to a double clutch mechanism and a transmission system incorporating such a support.
    State of the art
    The clutch mechanisms include a large number of elements which must be assembled with care. Recent developments have continued to seek to reduce the dimensions of the clutch mechanisms, always reducing the space available to assemble and mount them on a transmission of a motor vehicle, and more particularly on a casing. gearbox.
    In known manner, the clutch mechanisms generally comprise a first sub-assembly comprising at least one clutch associated with the elements which make it possible to implement it, and a second sub-assembly which comprises at least one actuator making it possible to configure the clutch. in its engaged or disengaged configuration.
    According to a first type of known architecture, the first and second subsets of such clutch mechanisms can be assembled by “internal” fixing means to the clutch mechanisms in order to form a module; and the module thus formed is then mounted on the transmission by "external" fixing means to the clutch mechanisms. This configuration advantageously makes it possible to facilitate maintenance operations on the clutch mechanisms by facilitating their replacement: it suffices to manipulate the "external" fixing means to separate 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.
    In both types of architecture, a disadvantage of known clutch mechanisms is that it is not easy to assemble them. For example, part of the lubricating oil
    -2 used to lubricate the clutch mechanisms can leak out of said clutch mechanisms through the openings rather than migrating towards the clutch (s). In addition, it is not always easy to reach the fixing means with the corresponding tool for mounting and / or dismantling the clutch mechanisms.
    The object of the present invention is to respond at least in large part to the above problems and to also lead to other advantages by proposing a new clutch support for a double clutch mechanism. Another object of the invention is to improve the lubrication of such a double-clutch mechanism, that is to say to facilitate the transport of the cooling flow from the pump into friction.
    io Statement of the invention
    According to a first aspect of the invention, at least one of the abovementioned objectives is achieved with a clutch support arranged to support at least one first clutch, said support delimiting a conduit comprising at least one radial extension part and having at least one outlet opening allowing hydraulic fluid to flow from an actuation system to the clutch (s).
    Preferably, the clutch support is arranged to support a first clutch and a second clutch.
    The duct has in particular at least one inlet for hydraulic fluid, for example several inlet ports.
    The hydraulic fluid is supplied by a hydraulic pump, in particular located on the actuation system side. More precisely, the fluid is supplied from the gearbox side. Said actuation system is in particular arranged to configure the first clutch (s) between a clutch configuration and a clutch configuration
    In particular, the conduit can be included in the clutch support, for example by forming a bore passing through at least part of said clutch support, or by forming at least partly a groove on a face peripheral to the clutch support . In other words, the clutch support duct can be at least partially open laterally. In this case, the conduit can then be delimited jointly by the clutch support and a
    -3 other component part of the clutch mechanism, such as for example the support bearing or the casing of the actuation system.
    By radial extension part is meant in the context of the present invention, a part forming with a direction parallel to the elongation axis of the clutch support a non-zero angle. Said radial extension part may in particular be wholly or partly perpendicular to the elongation axis of the clutch support (90 °).
    Said radial extension part of the duct may comprise, in addition to or alternatively, at least one inclined extension part, that is to say forming with a direction parallel to the elongation axis of the clutch support an angle strictly between 0 and 90 °. In a variant, the duct may also comprise at least one part of axial extension.
    The outlet outlet of the conduit, in particular of the radial extension part or of the axial extension part, takes the form of a through hole situated on an external face of the clutch support, allowing fluid communication between the conduit and a space located radially outside the clutch support, in the clutch module. The hydraulic fluid circulating inside the clutch support duct is thus projected towards the clutch (s) through the outlet orifice in order to lubricate and / or cool in particular the first and second clutches. In the sense of the invention, an outlet orifice is defined as being an opening situated on the external face of the clutch support and which gives in particular access to the radial extension part of the conduit, making it possible to communicate the conduit, 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.
    In the following 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, “the rear” designating the part situated to the right of the figures, on the side of the transmission, and "the front" designating the left part of the figures, on the engine side; and
    -4- "interior / internal" or "exterior / external" with respect to the axis O and in a radial orientation, orthogonal to said axial orientation, "the interior" designating a proximal part of the axis O and "l 'exterior' designating a distal part of the axis O.
    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 can be taken alone or in combination:
    - The conduit has an annular part; this can be located in an axial extension part of the clutch support, according to the variants on the same side or on the side opposite to the fixing member; the annular part of the conduit can be located at an axial end of the clutch support,
    the conduit comprises a plurality of inlet ports and / or a plurality of outlet ports, said inlet ports, respectively outlet ports preferably being angularly regularly distributed around a longitudinal axis of the clutch support, in particular confused with the axis of rotation of the double clutch mechanism;
    - the clutch support is made in one piece;
    - the clutch support is made in at least two parts;
    - the clutch support is made at least in part from a material chosen from:
    steel, aluminum, sintered material, plastic material;
    - the clutch support comprises a support bearing, in particular for radially supporting the clutch (s).
    According to another aspect, the subject of the invention is an assembly of a clutch support as described and of a fixing member configured to allow the clutch support to be fixed on a casing of the actuation system.
    According to yet another aspect, the subject of the invention is a clutch module comprising:
    - a first clutch rotating around an axis of rotation;
    - a second clutch rotating around the axis of rotation;
    - a clutch support as described above;
    - a clutch module fixing member.
    The fixing member and / or the clutch module may advantageously comprise at least one of the improvements below, the technical characteristics forming these improvements can be taken alone or in combination with them.
    -5 combination Torgane fixation is located radially inside at least one axial bearing separating a first output disc holder coupled to the first clutch of a second output disc holder coupled to the second clutch;
    - the fixing member is located at an axial end of the clutch support in order to facilitate its access during assembly or disassembly operations on the transmission. Preferably, the fixing member is located at the front end of the clutch support. Advantageously also, the access to the fixing member is situated at an axial end of the clutch support, for example at the level of 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 its access during assembly or disassembly operations on the transmission. Advantageously also, the access to the fixing member is located on the side opposite the support bearing with respect to the actuation system;
    - the fixing member bears against a front face of the clutch support in order to facilitate its access during assembly or disassembly operations on the transmission;
    - The clutch module comprises an input web intended to be coupled in rotation to an input shaft of the engine, a first output disk holder coupled in rotation to the first clutch and a second output disk holder coupled in rotation at the second clutch, said inlet web and said first and second outlet disc carriers each comprising at least one axial opening situated opposite the fixing member and forming access to said fixing member. In particular, a radial dimension of the openings may be greater than an outside diameter of the fixing member in order to have easier access to said fixing member;
    - 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 manipulation of the fixing member;
    - The fixing member is configured to achieve an axial locking of the clutch module on the housing of the actuation system, thus making it possible to secure the clutch module in a non-definitive manner on the actuation system. Once assembled, the clutch module forms an easily manipulated module. Said module can then, for example, be more easily assembled on the actuation system and / or more easily mounted on a transmission. In addition, this advantageous configuration makes it possible to be able to quickly disassemble the clutch module in accordance with the first aspect of the invention of the actuation system and / or of the transmission, by limiting the number and the difficulty of the disassembly operations;
    - The fixing member is of the type of an axial locking ring making it possible to axially lock the clutch module on the casing of the actuation system;
    the fixing member is housed in a circular groove, interrupted or not, of the front face of the clutch support in order to facilitate its pre-assembly on the clutch module, and more particularly its centering with respect to the axis of rotation of the clutch module according to the first aspect of the invention;
    - the fixing member is of the type of elastic ring delimited by an internal contour and an external contour, the internal 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 housing of the actuation system in order to establish a mechanical connection between the clutch module and said housing. , preferably via an axial blocking as described above. This advantageous configuration also allows the fixing member to be able to take the second radial configuration in which it is configured so that it no longer collaborates 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 internal contour
    -7and / 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 axial retaining means of the fixing member in order to facilitate its pre-assembly on the clutch support, said axial retaining means defining at least partially the groove, in particular the circular groove;
    - The axial retaining means are made from material with the clutch support. Alternatively, axial retaining means are attached and fixed to the clutch support. In this embodiment, the axial retention means are fixed to the clutch support according to any known means, and in particular by welding and / or by screwing. The axial retaining means can form an overmolding of the fixing member on the clutch support. The axial retaining means are configured to allow, if necessary, the fixing member to be able to take one or other of its configurations in order to be able to link the clutch module to the actuation system or in order to 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 alternative embodiment, the axial retaining means comprise at least two flanges arranged to axially lock the fixing member against the clutch support. Each flange can advantageously take the form of an angular sector at least partially covering the fixing member;
    - According to a second alternative 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 sectoral opening allowing access to the fixing member.
    According to another aspect of the invention, there is proposed a double 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 actuator, 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 part arranged to collaborate with the conduit, in particular with the annular part of the conduit. The casing channel may alternatively cooperate with the axial extension part or the radial extension part of the duct. .
    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 can be taken alone or in combination:
    - The housing of the actuation system comprises an axial elongation range which extends axially in front of the first and second actuators, the axial extension range being arranged to collaborate with the clutch support. The axial extension range of the actuation system extends axially towards the clutch module. More particularly, the axial elongation range extends in the direction of the clutch support in order to collaborate with it. The collaboration between the clutch support and the axial elongation range of the casing can take the form of a radial shoulder in order in particular to achieve centering with respect to the axis of rotation of the double clutch mechanism in accordance with the second aspect of the invention of the clutch module - via the clutch support on the actuation system - via the housing. To this end, an internal cylindrical bearing surface of the clutch support can be in radial abutment against an external face of the axial elongation bearing surface of the casing, said elongating bearing surface
    -9axial being located radially inside said clutch support. Alternatively, an inner face of the axial elongation bearing surface of the casing can be in radial abutment against an outer face of the clutch support, said axial elongation bearing being located radially outside of said clutch support;
    - According to a first alternative embodiment, the axial elongation range of the casing is made in one piece with said casing. According to a second alternative embodiment, the axial elongation range 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 again by snap-fastening. In the first alternative embodiment, the axial elongation range of the casing can 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 housing includes a particularly circumferential groove arranged to be able to house part of the fixing member. The groove of the housing, in particular circumferential, is arranged to be able to participate in the fixing of the clutch module on 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 in order to fix the clutch module in a durable and non-permanent manner on the actuation system;
    the axial elongation range of the casing comprises an end situated on the side opposite to the actuators of the actuation system with respect to the circumferential groove, said end having an external face with a diameter less than or equal to the diameter of the internal contour of the member fixing, advantageously when said fixing member is not configured to fix the clutch module to the actuation system;
    -10- the end of the axial elongation surface 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 interior 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 internal 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 outside diameter of the axial elongation range of the casing, so that said axial elongation range is force fitted into the clutch support ;
    - The double clutch mechanism according to the invention comprises means for coupling the housing in rotation to the clutch support. According to a first alternative embodiment, the means for rotationally coupling comprise first splines located on the axial elongation surface of the casing and collaborating by engagement of complementary shapes with second splines located on the clutch module clutch support . The first grooves can be of the male type and the second grooves can be of the female type, or the first grooves can be of the female type and the second grooves can be of the male type. According to a second alternative embodiment, the rotary coupling means comprise a key located on the housing of the actuation system or on the clutch module clutch support and collaborating with a corresponding housing located respectively on the support clutch or on the crankcase;
    - The double clutch mechanism according to the second aspect of the invention is of the multi-disc type operating in a humid environment.
    According to a first alternative 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 alternative 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.
    According to another aspect of the invention, there is proposed a transmission system for a motor vehicle comprising a double clutch mechanism as described above and in which:
    - The first clutch is coupled in rotation to a first output shaft of the transmission by means of a first input disc holder;
    - The second clutch is coupled in rotation to a second output shaft of the transmission by means of a second input disc holder;
    - The first and the second clutches are alternately coupled in rotation to an inlet sail, said inlet runner being coupled in rotation to an inlet shaft driven in rotation by at least one crankshaft.
    According to another aspect of the invention, there is also proposed a reversible assembly method for a double 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 with respect 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 axial locking of the clutch module to the actuation system.
    According to another aspect of the invention, a method of non-destructive disassembly of a double clutch mechanism is proposed, 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.
    -12Various embodiments of the invention are provided, integrating according to all of their possible combinations the different optional characteristics set out here.
    Description of the figures
    Other characteristics and advantages of the invention will become apparent from the following description on the one hand, and from several exemplary embodiments given by way of non-limiting indication with reference to the appended schematic drawings on the other hand, in which :
    - FIGURE IA illustrates an axial sectional view of an exemplary embodiment of the double clutch mechanism according to the invention;
    - FIGURE IB illustrates a view in axial section of another exemplary embodiment of a double clutch mechanism according to the invention;
    - FIGURES 2A and 2B illustrate sectional views of a preassembled fixing member on a clutch support according to two alternative embodiments of an assembly according to the invention;
    - FIGURES 3A, 3B and 3C illustrate views of a preassembled fixing member on a clutch support according to the variant of FIGURE 2A;
    - FIGURES 3D to 3F illustrate different views of a variant of the fixing member according to the invention;
    - FIGURES 4A, 4B, 4C, 5A, 5B, 5C and 5D illustrate in profile views various stages of assembly of the double clutch mechanism illustrated in FIGURE 1 A.
    Of course, the characteristics, the variants and the various embodiments of the invention can be associated with one another, according to various combinations, insofar as they are not incompatible or mutually exclusive of each other. One can in particular imagine variants of the invention comprising only a selection of characteristics described below in isolation from the other characteristics described, if this selection of characteristics is sufficient to confer a technical advantage or to differentiate the invention from in the prior art.
    In particular, all the variants and all the embodiments described can be combined with one another if nothing is technically opposed to this combination.
    -13 In the figures, the elements common to several figures keep the same reference.
    Detailed description of the invention
    Referring to FIGURE IA, the illustrated embodiment of a double clutch mechanism 10 according to the invention is preferably of the wet double clutch type, and comprises a first clutch 100 and a second clutch 200. Also preferably, in a so-called radial position, the first clutch 100 is situated outside the second clutch 200. Alternatively, the double clutch mechanism 10 can be in a so-called axial configuration, the first clutch 100 being located in front of the second clutch 200. The double clutch mechanism 10 is intended to be integrated on a transmission chain comprising a transmission coupled in rotation to the double clutch mechanism 10.
    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 flow from an actuation system 300 to the clutches. The conduit 700 comprises at least one radial extension part 720 and has at least one orifice 725 for the outlet of the fluid towards the clutches. The clutch support 500 will be more particularly described later, in particular in connection with a fixing member 600 with which it forms an assembly 900. Different assembly variants 900 are illustrated in FIGURES 2A and 2B and 3A to 3C.
    In general, 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 respectively the first clutch 100 or second clutch 200.
    In the context of the invention, the input shaft is rotated 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 of those fitted to motor vehicles.
    Preferably, the first transmission shaft A1 and the second transmission shaft A2 are coaxial. More particularly, the second transmission shaft A2 takes
    -14 possibly the shape of a hollow cylinder inside which the first drive shaft Al can be inserted.
    As illustrated in FIGURE IA, the first clutch 100 and the second clutch 200 are advantageously of the multi-disc type. Each multi-plate clutch comprises on the one hand a plurality of first friction elements 101, 201, such as for example flanges, connected in rotation with the input shaft, and on the other hand a plurality of second friction elements 102, 202, such as for example friction discs, joined in rotation with at least one of the transmission shafts A1, A2.
    Optionally, the plurality of first friction elements 101, 201 consists of friction discs connected in rotation with the input shaft, and the plurality of second friction elements 102, 202 consists of flanges which are rotationally connected with at least one of the drive shafts A1, A2.
    The first transmission shaft A1 is coupled in rotation to the input shaft. The first drive shaft A1 is driven by the rotary input shaft when the first clutch 100 is configured in a so-called engaged position for which the plurality of first friction elements 101 is coupled in rotation to the plurality of second drive elements. friction 102. Alternatively, the first drive shaft A1 is decoupled in rotation 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 decoupled in rotation at the plurality of second friction elements 102.
    Similarly, the second transmission shaft A2 is coupled in rotation to the input shaft. The second transmission shaft A2 is driven by the rotary input shaft when the second clutch 200 is configured in a engaged position for which the plurality of first friction elements 201 is coupled in rotation to the plurality of second friction elements 202. Alternatively, the second transmission shaft A2 is decoupled in rotation 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 decoupled in rotation from the plurality second friction elements 202.
    In the double clutch mechanism 10 illustrated in FIGURE 1A, the first clutch 100 is arranged to engage the odd ratios of the transmission and the second clutch
    -15200 is arranged to engage the even reports and the reverse gear of the transmission. Alternatively, the ratios supported by said first clutch 100 and second clutch 200 can be respectively reversed.
    The first clutch 100 and the second clutch 200 are arranged to alternately transmit a so-called input power - a torque and a speed of rotation - from the input shaft, to one of the two transmission shafts A1, A2, as a function of the respective configuration of each clutch 100 and 200 and by means of an input web 109.
    The first clutch 100 and the second clutch 200 are arranged so as 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.
    The double clutch mechanism 10 comprises an input element which is coupled in rotation on the one hand to the input shaft and on the other hand to the input web 109 in order to transmit the power - the torque and the speed. rotation - generated at the engine at one of the clutches 100, 200 of the double clutch mechanism 10. Preferably, the input element of the double clutch mechanism 10 comprises an input hub 130, preferably in rotation around the longitudinal axis O. The input hub 130 has a first lower elongation which is linked in rotation and / or axially to the input shaft, optionally by means of a damping device, such than a double damping flywheel for example.
    The input hub 130 comprises an external elongation which is coupled to the input veil 109, and more particularly to a lower end 1091 of the input veil 109. The lower end 1091 is located towards the front AV of said veil d 'inlet 109. Preferably, the inlet web 109 and the inlet hub 130 are integral, for example fixed by welding and / or by riveting.
    The entry veil 109 has an upper end 1092 by which the entry veil 109 is linked in rotation 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 produced by the 'through an outer axial elongation span 1061 of an input disc carrier 106, the input disc carrier 106 being linked in rotation to the input web 109,
    preferably by cooperation of shapes, for example by grooves at the front end AV of said outer axial elongation span 1061. Alternatively, the input disc holder 106 and the input web 109 are linked in rotation through any similar connecting means.
    At its inner end 1091, the entry veil comprises a plurality of oblong and through openings 1092 forming 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 external radial dimension of the fixing member 600 in order to facilitate its handling and / or the insertion of a tool to manipulate and / or configure it.
    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 clutch configuration and the disengaged configuration.
    The actuation system 300 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 are housed at least part of the first and second actuators 320, 330.
    Preferably, the first and second actuators 320 and 330 are of the hydraulic cylinder type. The first and second actuators 320, 330 may each include 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 includes a hydraulic fluid supply channel for each actuator 320, 330. Preferably, the hydraulic fluid is a pressurized fluid, for example oil.
    The first actuator 320 is linked to the first clutch 100 by means of a first decoupling bearing 140 on the one hand and a first force transmission member 105 on the other hand. The first decoupling bearing 140 is arranged to transmit axial forces generated by the first actuator 320 to the first force transmission member 105.
    The first force transmission member 105 is arranged to transmit an axial force El, exerted parallel to the longitudinal axis O, to the first clutch 100 via its upper elongation, said upper elongation extending axially forwards AV in order to be able to separate or pressing the first friction elements 101 against the second friction elements 102 on the one hand, and against an external reaction means 103 of the inlet web 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.
    The first force transmission member 105 takes the form of a corrugated sheet metal curved axially towards the front AV at its outer radial end. More particularly, the first force transmission member 105 collaborates with the first clutch 100 by means of a plurality of external axial extension surfaces 1051 which extend parallel to the axis of rotation O and which form fingers upper ones which allow the friction elements 101, 102 of the first clutch 100 to be pushed forward AV under the effect of an axial movement forward AV of the first actuator 320. The axial extension surfaces 1051 of the first member force transmission 105 collaborate with the first clutch 100 through an opening 1064 arranged through the input disc carrier 106.
    The first force transmission member 105 comprises an upper radial extension range 1052 located behind the rear AR axial extension ranges 1051. The upper radial extension span 1052 extends radially from the first clutch 100 to the interior of the second clutch 200.
    An intermediate axial extension span 1053 extends the first upper radial extension span 1052 under the second clutch 200, towards the front AV of the double clutch mechanism 10. The first intermediate axial extension span 1053 is located
    -radially perpendicular to the 1051 external axial extension spans. The intermediate axial extension span 1053 is formed parallel to the longitudinal axis O and parallel to the external axial extension spans 1051.
    Finally, the first force transmission member 105 comprises a plurality of internal radial extension ranges 1055 connected to the intermediate axial extension range 1053 via a curved zone 1054. Rear faces AR of the ranges of internal radial extensions 1055 are in contact with a front face AV of the first decoupling bearing 140 connected to the first actuator 320.
    By way of nonlimiting example, the first force transmission member 105 can be obtained by stamping.
    The external reaction means 103 is integral with the entry veil 109. Preferably, the external reaction means 103 is connected to the entry veil 109 by means of the entry disc port 106; alternatively, the external reaction means 103 is fixed integrally to the entry veil 109 by any fixing means, such as for example by riveting or by welding.
    The external reaction means 103 in particular has external grooves which cooperate with corresponding internal grooves of the input disc holder 106. By way of nonlimiting example, the external reaction means 103 can take the form of a ring with a toothing on the outer periphery and a central support groove which extends axially towards the rear AR. As a non-limiting example, the external reaction means 103 can take the form of a boss of the inlet web 109.
    The external reaction means 103 has a shape complementary to that of the first or second friction elements 101, 102, so as to allow friction coupling of the first and second friction elements 101, 102 when the first actuator 320 exerts the first force axial El forward AV to configure the first clutch 100 in its engaged position. Conversely, when the first force transmission member 105 is pushed backwards AR by elastic return elements which will be described later, then the first friction elements 101 separate from the second friction elements 102, thus making it possible to decouple said friction elements and thus making it possible to configure the first clutch 100 in its disengaged configuration.
    The first clutch 100 is intended to be coupled in rotation to the first transmission shaft A1 by means of a first output disc holder 110 forming an output element of said first clutch 100. More particularly, the first output disc port 110 is rotatably coupled to the second friction elements 102 via an upper end 1101 that the outlet disc holder 110 includes. More particularly still, the first outlet disc holder 110 is coupled in rotation to a first outlet hub 120 by means of an inner end 1102 which the first outlet disc holder 110 comprises.
    The first outlet disc holder 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 holder 110 is thus coupled in rotation by engagement with the second friction elements 102 of the first clutch 100.
    The inner end 1102 of the first outlet disc holder 110 is linked to the first outlet hub 120; they are preferably fixed together by welding, by riveting or the like.
    At its inner end 1102, the first outlet disc holder 110 comprises a plurality of oblong and through openings 1103 forming access T to the fixing member 600 which will be described later. The openings 1103 of the first outlet 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 outlet disc holder 110 is greater than one external radial dimension of the fixing member 600 in order to facilitate its handling and / or the insertion of a tool for handling and / or configuring it. Advantageously, the openings 1103 of the first outlet disc holder 110 are coaxial with the openings 1092 of the entry veil
    109. Also preferably, a radial dimension of the openings 1103 of the first outlet disc carrier 110 is equal to the radial dimension of the openings 1092 of the entry sail
    109.
    -20The first output hub 120 has radially inside the axial grooves arranged to cooperate with complementary grooves located on the first drive shaft Al, so as to achieve a rotation coupling.
    A radial bearing 117 is interposed between the first outlet hub 120 and the inlet hub 130 in order to withstand the radial forces of the inlet hub 130 and / or the inlet web 109 despite the different rotational speeds which can respectively turn the input shaft and the first drive shaft Al.
    Similarly, the second clutch 200 of the double-clutch mechanism 10 is similar in design to that of the first clutch 100.
    The second actuator 330 is linked 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 for transmitting axial forces generated by the second actuator 330 to the second force transmission member 205.
    The second force transmission member 205 is generally located axially between the input disc holder 106 and the first force transmission member 105.
    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 forwards AV in order to be able to separate or pressing 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 spaced 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.
    The second force transmission member 205 takes the form of a corrugated sheet metal curved axially forwards AV at its outer radial end. More particularly, the second force transmission member 205 collaborates with the second clutch 200 by means of a plurality of axial extension surfaces 2051 which make it possible to
    Pushing forward the friction elements 201, 202 of the second clutch 200 under the effect of an axial movement towards the front of the second actuator 330. The axial extension surfaces 2051 of the second transmission member of force 205 collaborate with the second clutch 200 through an opening 1065 arranged through the input disc carrier 106.
    The second force transmission member 205 includes an upper radial extension range 2052 located behind the rear AR axial extension ranges 2051. The upper radial extension range 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 range 1053 of the first force transmission member 105 .
    An intermediate axial extension range 2053 extends the upper radial extension range 2052 under the second clutch 200, towards the front AV of the double clutch mechanism 10. The intermediate axial extension range 2053 is located radially inside of the second clutch 200 and at the level of the upper radial extension range 1052 of the first force transmission member 105.
    Finally, the second force transmission member 205 comprises a plurality of internal radial extension spans 2055 connected to the intermediate axial extension bearing surface 2053 via a curved zone 2054. Rear faces AR of the bearing spans internal radial extensions 2055 are in contact with a front face AV of the second decoupling bearing 240 connected to the second actuator 330.
    By way of nonlimiting example, the second force transmission member 205 can be obtained by stamping.
    The internal reaction means 203 is integral with an interior axial elongation part 1062 facing forward AV and integral with the input disc carrier 106, fixed to the input disc carrier 106 by any means, such as for example by welding or riveting. Alternatively, the internal reaction means 203 and the input disc holder 106 are made from material.
    The external reaction means 203 has a shape complementary to that of the first or second friction elements 201, 202, so as to allow friction coupling of the first and second friction elements 201, 202 when the second actuator 330
    -22 exerts an axial force E2 towards the front AV to configure the second clutch 200 in its engaged position. Conversely, when the second force transmission member 205 is pushed backwards AR by elastic return elements which will be described later, then the first friction elements 201 separate from the second friction elements 202, thus making it possible to decouple said friction elements 201, 202 and thus making it possible to configure the second clutch 200 in its disengaged configuration.
    By way of nonlimiting example, the external reaction means 203 can take the form of a ring with a toothing on the external periphery and a central support groove which extends axially towards the rear AR.
    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 outlet hub 220 at its lower end.
    The second outlet disc holder 210 has 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 holder 210 is thus coupled in rotation by engagement with the second friction elements 202 of the second clutch 200.
    The inner radial end 2102 of the second outlet disc holder 210 is connected to the second outlet hub 220, preferably fixed together by welding, riveting or the like.
    At its inner end 2102, the second outlet disc holder 210 comprises a plurality of oblong and through openings 2103 forming access T to the fixing member 600 which will be described later. The openings 2103 of the second outlet 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 outlet disc holder 210 is greater than one
    -23 external radial dimension of the fixing member 600 in order to facilitate its manipulation and / or the insertion of a tool for manipulating and / or configuring it. Advantageously, the openings 2103 of the second outlet disc holder 210 are coaxial with the openings 2092 of the inlet web 109 and / or with the openings 1103 of the first outlet disc holder
    110. Also preferably, a radial dimension of the openings 2103 of the second outlet disc holder 210 is equal to the radial dimension of the openings 1092 of the inlet web 109 and / or that of the openings 1103 of the first outlet disc holder 110 .
    The second outlet hub 220 has radially inside the axial grooves arranged to cooperate with complementary grooves located on the second transmission shaft A2, so as to produce a rotation coupling.
    An axial bearing 116 is interposed between the first outlet disc holder 110 and the second outlet disc holder 210 in order to be able to transmit an axial force between the two outlet disc holders 110, 210 which can rotate at different speeds when the first and second clutches 100, 200 are configured in a different configuration.
    The first and second clutches 100, 200 respectively comprise elastic return elements for automatically pushing the first and second actuator 320, 330 backwards. More particularly, the elastic return elements axially stress the first and respectively the second force transmission member 105, 205 rearward AR in order to facilitate the spacing of the first friction elements 101, 201 relative to the second friction elements. 102, 202 of the first and respectively of the second clutch 100, 200 by pushing the first and the second actuator 320, 330 backwards. By way of nonlimiting example, it may for example be Belleville washers.
    The input disc holder 106 further comprises an axial extension surface 1066 which extends axially towards the front AV under the second clutch 200, and an internal 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 is supported on a heel 118 in radial support on a support bearing 113 supported by a clutch support 500 and arranged to support the radial load of the input disc holder 106.
    The clutch support 500 is located in an axial position intermediate between the actuation system 300 and the first and second output hubs 120, 220.
    Axially towards the front AV, the support bearing 113 is in axial abutment against an axial end 510 before AV of the clutch support 500 and forming a bearing heel. Generally, the bearing heel making it possible to axially stop the support bearing 113 is arranged on the side opposite to the axial force El, E2 exerted by the first or second actuator 320, 330.
    The axial end 510 before AV of the clutch support 500 is in axial abutment against the second output disc holder 210 by means of an axial bearing 115 in order to be able to transmit an axial force between the second disc holder of output 210 and the clutch support 500, said clutch support 500 being stationary in rotation while the second output disc holder 210 can be rotated when the second clutch 200 is configured in its engaged configuration .
    The support bearing 113 is here for example a rolling bearing. Advantageously, the support bearing 113 is of the type of a bearing with oblique contacts 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 bearing heel. In fact, when the first or second actuator 320, 330 transmits an axial force El oriented towards the front AV to the first or second force member 105, 205 in order to configure the clutch 100, 200 corresponding in the engaged configuration, l 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 level of the transmission shaft A1, A2, and more particularly at the level of the fixing member 600 All the elements participating in the transmission of the axial force El, E2 during the operation of the double clutch mechanism 10 and situated axially between the fixing member 600 and the first or second actuator 320, 330 are locked axially so as to being able to transmit said axial force El, E2.
    The clutch support 500 will be described more particularly with reference to FIGS. 2A and 2B.
    In order to lubricate and cool the first 100 and second 200 clutches during their operation, the double clutch mechanism 10 includes a conduit and a channel for conveying hydraulic fluid to the first 100 and second 200
    -25 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 for example a radial extension part 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.
    While in the embodiment illustrated in FIGS. 1A and 2A, said conduit 700 comprises an axial extension part 710 and a radial extension part 720, in the embodiment illustrated in FIGS. 1B and 2B, said conduit 700 consists of the radial extension part 720.
    The radial extension part 720 of the conduit 700 is advantageously located near the axial end 510 before AV of the clutch support 500, and more particularly still in an intermediate situation between the clutch support 113 and the output hubs 120, 220.
    The outlet orifice 725 is located radially outside the radial extension part 720 of the conduit 700. The outlet orifice 725 takes the form of a hole opening on the outside of the clutch support 500, and more particularly at an external face of the axial end 510 before AV forming the bearing heel. In other words, the outlet orifice 725 is defined as by an opening situated on the external face of the clutch support 500 and which gives access to the conduit 700, in particular to the radial extension part 720 of the conduit 700 as illustrated in FIGURES 2A, 2B and 3D-F, enabling said conduit, in particular said radial extension part 720, to communicate with the space situated radially outside the clutch support 500, in the module clutch 15.
    Radially, the outlet orifice 725 is situated outside the fixing member 600. More particularly still, the outlet orifice 725 is located radially outside the openings 1103 of the first outlet disc holder 110 and / or openings 2103 of the second outlet disc holder 210 and / or openings 1093 of the inlet web 109. This advantageous configuration allows the hydraulic fluid leaving the duct 700 through the outlet orifice 725 not to be s '' flow out of the double clutch mechanism 10 through the openings 1093, 1103, 2103 forming the access T to the fixing member 600. Subsequently,
    The lubrication and / or cooling of the first 100 and second 200 clutches during their operation is improved.
    The casing 307 of the actuation system 300 comprises a channel 800 allowing a hydraulic fluid to circulate. In the example illustrated, said channel 800 comprises an axial extension part 810 and a radial extension part 820 located at the front axial end AV of the axial extension part 810. The channel 800 is arranged to collaborate on conduit 700 in order to allow fluid circulation of the hydraulic fluid between the conduit 700 and the channel 800. More particularly, in the example illustrated FIGURE IA an outer radial end of the radial extension part 820 of the channel 800 collaborates with an axial end rear 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 part 750 of the conduit 700 in order to facilitate the angular positioning of the clutch support 500 without require angular indexing.
    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.
    The casing 307 of the actuation system 300 comprises an axial elongation range 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 range 3071 of the casing 307 is arranged to collaborate with the clutch support 500 in order to achieve centering and / or rotation coupling. Centering and / or coupling in rotation is carried out by fitting, preferably by force, a radial diameter of an outer face of the axial elongation span 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 grooves located on the axial elongation surface 3071 and collaborating with second grooves located on the clutch support 500.
    A terminal end 3072 before AV of the axial extension range 3071 is arranged to collaborate with the fixing member 600 during 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 of which
    -27 a diameter decreases 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 span 3071 of the casing 307 will be described in more detail with reference to FIGURES 2A and 2B.
    The axial elongation range 3071 of the casing 307 also includes 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 achieve 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.
    Finally, the double-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 FIGURES 4A to 4C.
    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 includes all the elements which make it possible to establish a coupling in rotation 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 web 109, the input disk carrier 106, the first 110 and second 210 output disk 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.
    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.
    The fastener 600 will now be described more precisely with reference to FIGS. 2A and 2B and 3A to 3C describing various embodiments of such a fastener 600 preassembled on the clutch support 500.
    As shown in FIGURES 2A and 2B, in the corresponding variant embodiments, the clutch support 500 includes an axial extension part 530 configured to be placed 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 seat so as to be able to accommodate the transmission shafts A1, A2, not visible in FIGURES 2A and 2B. The clutch support 500 also comprises the axial end 510 which extends radially outside the axial extension part 530 of the clutch support 500. In general, the axial end 510 before the clutch support 500 extends substantially perpendicular to the axial extension part 530 of said clutch support 500.
    As illustrated in section 2A, in this example, the axial extension part 530 of the clutch support 500 houses the axial extension part 710 of the conduit 700 described above; and the axial end 510 before the front of the clutch support 500 houses the radial extension part 720 of the conduit 700. The clutch support 500 here comprises several radial extension parts 720 of the conduit 700 which are angularly regularly distributed around of the axis O and are in fluid communication via the axial extension parts 710 with the annular part 750. The latter is here located at an axial end of the clutch support 500, the fixing member 600.
    In the example illustrated in section 2B, the axial extension part 530 of the clutch support 500 houses the radial extension part 720 of the conduit 700 as well as the annular part 750. In this example in particular the conduit 700 consists of several radial extension parts 720 extending between an outlet orifice 725 and the annular part 750 of the conduit 700. The outlet orifices 725 and the radial extension parts 720 are angularly regularly distributed around the axis O. The annular part 750 of the conduit 700 is here located in the axial extension part 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 end axial 510 before AV of the clutch support 500, the fixing member 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 the interior of the oblong openings 1093, 1103, 2103 of the inlet web 109 and the outlet disc carriers 110, 210 forming the access T in order to
    -29facilitating the mounting and dismounting of the fixing member 600. In the first embodiment illustrated in FIGURES 2A-2B, the axial retaining means 500 of the fixing member 600 take the form of several flanges 550a, 550b, 550c forming each of the angular sectors and making it possible to achieve axial locking, possibly with a non-zero axial clearance - of the fixing member against the front face.
    The flanges 550a-550c advantageously come from one piece with the clutch support 500. Optionally they can be attached 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 inlet web 109 and the outlet disc holders 110, 210 forming the access T in order to facilitate mounting and disassembly of the fixing member 600.
    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.
    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.
    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 member. fixing 600 by off-center with respect 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.
    In the illustrated exemplary embodiments, the fixing member 600 takes the form of an radially deformable axial locking ring: the internal contour 610 and / or the external contour 620 of the fixing member 600 are radially deformable in order to allow to dislodge or house said fixing member 600 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 internal contour 610
    -30and / or its external contour 620 and, consequently, allow its internal diameter and / or its external diameter to be modified in order to configure it in a first configuration in which the fixing member 600 establishes a mechanical connection between the module d clutch 15 and the actuation system 300, and a second configuration in which the fastening member 600 no longer cooperates with the actuation system 300, thus making it possible to release the clutch module 15 from said actuation system 300 .
    FIGURE 3C illustrates a second 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 a closure plate annular collaborating with the front face 515 of the clutch support 500. In a manner comparable to the flanges 550a-550c of FIGURES 3A-3C, the closure plate illustrated in FIGURE 3 forms a groove located between said closure 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 fastener 600, it is deformed radially so as to pass it through the center of the annular closure plate. In order to facilitate the handling of the fastening member 600, openings 540a-540c are provided on the closure 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 disassembly to be assembled. The openings 540a-540c of the closure plate are advantageously located radially inside the oblong openings 1093, 1103, 2103 of the inlet web 109 and the outlet disc carriers 110, 210 forming the access T in order to facilitate mounting and dismounting the fastening member 600.
    FIGURES 4A, 4B and 4C illustrate a method of assembling the double clutch mechanism 10 described above.
    For example, the method of assembling the double 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 relative to the actuation system 300 in order to bring said clutch module 15 closer to said actuation system 300; and or
    - A step of axial locking of the clutch module 15 to the actuation system 300.
    Cleverly, it is a reversible assembly process, the double clutch mechanism 10 can be disassembled in a non-destructive manner.
    The clutch module 15 and the actuation system 300 are aligned, preferably coaxially with respect to the axis O.
    As shown in FIGURE 4B, the axial extension range 3071 of the casing 307 is fitted into the axial extension range 530 of the clutch support 500, the outer face of the axial extension range 3071 of the housing 307 collaborating with the inner face of the axial extension range 530 of the clutch support 500.
    FIGURE 4C illustrates the double-clutch mechanism 10 in which the fixing member 600 is engaged in the circumferential groove 3074, thus achieving an axial coupling of the clutch module 15 with the actuation system 300, and more particularly a stop axial. In this configuration, the fixing member 600 enables the clutch module 15 to be secured in a non-definitive manner to the actuation system 300.
    FIGURES 5A, 5B, 5C and 5D illustrate a method of disassembly of the double clutch mechanism 10 described above.
    For example, the method for disassembling the double 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.
    -32In a clever way, it is a non-destructive disassembly process for the different elements of the double clutch mechanism 10, the latter being able to be reassembled later.
    Of course, the invention is not limited to the examples which have just been described and numerous modifications 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 as long as they are not incompatible or mutually exclusive. In particular, all the variants and embodiments described above can be combined with one another.
    权利要求:
    Claims (11)
    [1" id="c-fr-0001]
    Claims
    1. Clutch support (500) arranged to support at least a first clutch (100, 200), said support delimiting a conduit (700) comprising at least one radial extension part (720) and having at least one orifice of outlet (725) allowing hydraulic fluid to flow from an actuation system (300) to the at least one first clutch.
    [2" id="c-fr-0002]
    2. Clutch support (500) according to claim 1, the conduit (700) comprising an annular part (750).
    [3" id="c-fr-0003]
    3. Clutch support (500) according to claim 1 or 2, the conduit comprising a plurality of inlet ports (723) and / or a plurality of outlet ports (725), said inlet ports ( 723), respectively outlet orifices (723) being preferably angularly regularly distributed around a longitudinal axis O of the clutch support.
    [4" id="c-fr-0004]
    4. Clutch support (500) according to any one of the preceding claims being made in at least two parts.
    [5" id="c-fr-0005]
    5. Clutch support (500) according to any one of the preceding claims, being made at least in part from a material chosen from: 1 ’steel, 1’ aluminum, a sintered material, a plastic material.
    [6" id="c-fr-0006]
    6. Clutch support (500) according to any one of the preceding claims, being made in one piece.
    [7" id="c-fr-0007]
    7. Clutch support (500) according to any one of claims 1 to 6 being made in at least two parts.
    [8" id="c-fr-0008]
    8. 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.
    [9" id="c-fr-0009]
    9. Clutch support according to the preceding claim, the support bearing (113) being of the type of a bearing with oblique contacts.
    [10" id="c-fr-0010]
    10. Assembly (900) of a support according to any one of the preceding claims and of a fixing member (600).
    [11" id="c-fr-0011]
    11. Clutch module (10) comprising:
    - a first clutch (100) rotating around the axis (O);
    A second clutch (200) rotating around the axis (O);
    a clutch carrier (500) according to any one of claims 1 to 9; a fastening member (600) of the clutch module.
    1/13
    600 3074 3071
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    同族专利:
    公开号 | 公开日
    FR3062698B1|2020-06-26|
    EP3580468B1|2021-03-03|
    EP3580468A1|2019-12-18|
    CN110382899B|2021-08-24|
    WO2018146019A1|2018-08-16|
    FR3062699A1|2018-08-10|
    FR3062695A1|2018-08-10|
    FR3062697B1|2019-03-22|
    CN110382899A|2019-10-25|
    WO2018146087A1|2018-08-16|
    FR3062697A1|2018-08-10|
    CN110268178A|2019-09-20|
    EP3580469A1|2019-12-18|
    FR3062695B1|2019-03-22|
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    US9562572B2|2008-02-18|2017-02-07|Borgwarner Inc.|Clutch device with a flex plate|
    DE102009000474A1|2008-09-09|2010-03-11|Zf Friedrichshafen Ag|Multiple coupling device, in particular double clutch device, with actuatable by means of a disk carrier slat clutch assembly|
    CN108916262B|2010-03-25|2021-05-04|博格华纳公司|Concentric dual clutch device|
    WO2014178350A1|2013-04-30|2014-11-06|アイシン・エィ・ダブリュ株式会社|Transmission device|
    FR3024508B1|2014-08-01|2016-07-22|Valeo Embrayages|CLUTCH DEVICE FOR A MOTOR VEHICLE|FR3082572B1|2018-06-14|2021-01-15|Valeo Embrayages|AXIAL STOP BETWEEN TWO PIECES|
    FR3097603B1|2019-06-18|2021-07-02|Valeo Embrayages|WET DOUBLE CLUTCH MECHANISM AND TORQUE TRANSMISSION MODULE INCLUDING SUCH A MECHANISM|
    法律状态:
    2018-08-10| PLSC| Search report ready|Effective date: 20180810 |
    2018-08-30| PLFP| Fee payment|Year of fee payment: 2 |
    2019-08-30| PLFP| Fee payment|Year of fee payment: 3 |
    2020-08-31| PLFP| Fee payment|Year of fee payment: 4 |
    2021-08-31| PLFP| Fee payment|Year of fee payment: 5 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1750992A|FR3062695B1|2017-02-07|2017-02-07|MECHANISM WITH DOUBLE CLUTCHABLE HOUSING|
    FR1750992|2017-02-07|EP18703587.8A| EP3580469A1|2017-02-07|2018-02-06|Clutch support|
    PCT/EP2018/052929| WO2018146087A1|2017-02-07|2018-02-06|Clutch support|
    CN201880010640.7A| CN110268178A|2017-02-07|2018-02-06|Clutch support|
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