• 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 double-clutch mechanism (10) in which each actuating system (300A, 300B) comprises a pressure chamber (750A, 750B), an axially movable piston (105, 205), a balancing chamber ( 700A, 700B) and an elastic return member (800A, 800B) housed in the balancing chamber and arranged to exert an axial force against said piston. The resilient biasing member (800A, 800B) includes a plurality of apertures (8104) collaborating with a plurality of complementary apertures (5004) located on the central hub (500) to permit fluid communication between a flow conduit fluidic fluid of the central hub and the corresponding balancing chamber and comprises an angular indexing means (8107) collaborating with a complementary angular indexing means (5007) located on the central hub. The invention relates to a transmission system (1) comprising such a double-clutch mechanism (10).
    公开号:FR3062696A1
    申请号:FR1751018
    申请日:2017-02-07
    公开日:2018-08-10
    发明作者:Laurent Caumartin；Vincent Cornet；Herve RIBOT；Guillaume VUAROQUEAUX
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    Technical area
    The present invention relates to a compact double clutch mechanism as used in the automotive field. The invention also relates to a transmission system incorporating such a double clutch mechanism.
    State of the art
    Clutch mechanisms are known comprising a clutch in rotation about an axis of rotation and a force generator arranged to configure the clutch in a configuration known as disengaged or engaged by means of a moving part, called piston , allowing the force generated at the force generator to be transmitted to said clutch.
    In known manner, an actuation system can be formed by a hydraulic force generator comprising (i) a pressure chamber arranged to receive a pressurized fluid, (ii) a piston movable axially in the pressure chamber and extending radially outside the pressure chamber in order to engage or disengage the clutch, (iii) a balancing chamber situated opposite the pressure chamber relative to the piston, the balancing chamber comprising an elastic return element making it possible to generate a force, called a return force, against the piston.
    The pressure chamber is supplied with a pressurized hydraulic fluid in order to allow the piston to move between a first position corresponding to a clutched configuration of the clutch and a second position corresponding to a disengaged configuration of the clutch. To do this, the pressurized hydraulic fluid is routed to the pressure chamber via so-called high pressure conduits allowing fluid circulation of said pressurized hydraulic fluid.
    Conversely, the balancing chamber is supplied with a hydraulic fluid called cooling making it possible to lubricate said balancing chamber as well as the other components of the clutch mechanism. To do this, the hydraulic cooling fluid is routed in particular to the balancing chamber via so-called low pressure conduits allowing fluid circulation of said hydraulic cooling fluid.
    In known manner, the conduits pass through the double clutch mechanism in order to convey the hydraulic cooling fluid to the balancing chamber and to the clutches of said double clutch mechanism. In particular, a central hub supporting the clutches comprises the conduits which open into the balancing chamber of the actuation systems of the double clutch mechanism. In known manner, the prior double clutch mechanisms are difficult to assemble, in particular during the step of inserting the elastic return element in the corresponding balancing chamber, since it is necessary not to obstruct the conduits low pressure during this step.
    In document EP 2 909 052 B1, the conduits arranged in a hub of the clutch mechanism open out below the elastic return element, so that the flow of pressurized hydraulic fluid can be disturbed if part of the 'elastic return element is located just opposite said conduits.
    The object of the present invention is to respond at least in large part to the above problems and also to lead to other advantages by proposing a new double-clutch mechanism to solve at least one of these problems.
    Another object of the present invention is to facilitate the mounting of the double clutch mechanism, and in particular the insertion of the elastic return element in the balancing chamber.
    Another object of the present invention is to improve the circulation of the cooling fluid within the double clutch mechanism.
    Statement of the invention
    According to a first aspect of the invention, at least one of the abovementioned objectives is achieved with a double clutch mechanism comprising:
    - a first clutch and a second clutch in rotation around a central hub
    - a first actuation system arranged to engage or disengage the first clutch;
    - a second actuation system arranged to engage or disengage the second clutch, each actuation system comprising:
    o a pressure chamber arranged to receive a pressurized fluid; o a piston movable axially in the pressure chamber and extending radially outside the pressure chamber in order to engage or disengage the corresponding clutch;
    o a balancing chamber located opposite the pressure chamber relative to the piston, o an elastic return element housed in the balancing chamber, said elastic return element extending between the corresponding piston and the hub central, said elastic return element being arranged to exert an axial force against said piston.
    According to the present invention, the elastic return element comprises a plurality of openings opening directly into a plurality of complementary openings made on the central hub in order to allow fluid communication between a fluid duct of the central hub and the balancing chamber. .
    This advantageous configuration thus allows better fluid circulation of the hydraulic cooling fluid inside the fluid conduits housed in the central hub and opening into the balancing chambers. Subsequently, the double clutch mechanism according to the first aspect of the invention is better lubricated and pressure balancing between the actuating chambers and the balancing chambers is facilitated.
    In the following description and in the claims, the following terms will be used without limitation and in order to facilitate understanding:
    - "longitudinal" to characterize a direction and / or an elongation of a part which is parallel to a longitudinal axis O,
    - "radial" to characterize a direction and / or an elongation of a part which is orthogonal to the longitudinal axis O and therefore parallel to a transverse axis T, which is orthogonal to the longitudinal axis O.
    It will be understood in this that the longitudinal axis O and the transverse axis T participate in a geometric coordinate system R of the description of the present invention.
    Likewise, in the following description and in the claims, the following terms will be used without limitation and in order to facilitate understanding:
    - “front” AV or “rear” AR in a direction relative to an axial orientation determined by the longitudinal axis O which is the main axis of rotation of the transmission system, “the rear” designating the part situated to the right figures, on the side of the transmission, and the "front" AV designating the left part of the figures, on the side of the engine; and
    - "inside / inside" and / or "outside / outside" with respect to the transverse axis T and along the transverse axis T, "inside" designating a proximal part of the longitudinal axis O and "l 'exterior' designating a distal part of the longitudinal axis O.
    The double clutch mechanism 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 elastic return element of at least one of the actuation systems comprises an angular indexing means collaborating with a complementary angular indexing means located on the central hub. This configuration advantageously makes it possible to match the elastic return element with the balancing chamber and / or with the central hub through a predetermined number of particular assembly configurations. In other words, the angular indexing means makes it possible to define a predetermined number of configurations for assembling the elastic return element with the central hub when said elastic return element is inserted into the balancing chamber;
    - the elastic return element of at least one actuation system comprises:
    o a first annular part intended to bear against a wall of the central hub, the first annular part comprising the angular indexing means;
    o a second annular part intended to bear against the corresponding piston;
    o a plurality of elastic elements extending between the first annular part and the second annular part;
    - The plurality of elastic elements is of the type of a plurality of helical springs;
    - The plurality of openings formed in the first annular part are angularly distributed between the helical springs;
    - The angular indexing means of at least one of the actuation systems is of the male type and the complementary angular indexing means of the central hub is of the female type;
    the angular indexing means is of the type of at least one tab extending radially outside the corresponding elastic return element, each tab collaborating with a corresponding groove on the central hub, the groove or grooves forming collectively the complementary angular indexing means. Alternatively, the angular indexing means is of the type of at least one tab extending radially inside the corresponding elastic return element, each tab collaborating with a corresponding hole on the central hub, the hole or holes collectively forming the complementary angular indexing means. According to another alternative, the angular indexing means is of the type of at least one extruded rivet extending axially beyond the elastic return element in the direction of the central hub and the complementary angular indexing means is of the type of at least one axial bore;
    - The angular indexing means and the complementary angular indexing means are respectively angularly regularly distributed around a longitudinal axis of the double clutch mechanism. Optionally, the angular indexing means comprises a plurality of means which are angularly distributed around the longitudinal axis in a non-symmetrical manner;
    - The angular indexing means of at least one of the actuation systems is of the female type and the complementary angular indexing means of the central hub is of the male type;
    in this case, the complementary angular indexing means is of the type of at least one lug extending radially inside the central hub, each lug collaborating with a corresponding groove on the corresponding elastic return element, the or the grooves collectively forming the angular indexing means;
    the complementary indexing means is of the type of at least one extruded rivet extending axially beyond the central hub in the direction of the elastic return element and the angular indexing means is of the type of at least an axial bore;
    - The central hub comprises a means for centering the elastic return element of at least one of the actuation systems and relative to the longitudinal axis;
    - an internal face of the at least one tab forms the centering means on a bottom of the groove of the central hub;
    - the plurality of openings of the elastic return element is formed on the first annular part;
    - The second annular part and an inner end of the piston of at least one of the actuation systems are fixed integrally together or form a single piece;
    - The means of angular indexing complementary to the central hub is common with the means of angular indexing of the first and second elastic return elements;
    - part of the first annular part of the elastic return element is force fitted into the central hub;
    - the first and second clutches are in a radial configuration, the second clutch being located radially inside the first clutch. Alternatively, the first and second clutches are in an axial configuration.
    According to a second aspect, the invention also relates to a transmission system for a motor vehicle comprising such a double-clutch mechanism in which:
    - the first clutch is coupled in rotation to a first output shaft of the transmission by means of a first output disc holder;
    - The second clutch is coupled in rotation to a second output shaft of the transmission by means of a second output 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.
    Various 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 1 illustrates a view in axial section of a double clutch mechanism according to the first aspect of the invention;
    - FIGURE 2 illustrates a perspective view and partially cut away of a double clutch mechanism according to the first aspect of the invention;
    - FIGURE 3A illustrates a detailed view in axial section of the actuation systems of the double clutch mechanism illustrated in FIGURE 1;
    - FIGURE 3B illustrates another detail view in axial section showing the openings of the central hub and of the elastic return elements;
    - FIGURE 4 illustrates a perspective view of a first annular part of an elastic return element forming one of the actuation systems of the double clutch mechanism illustrated in FIGURES 1 or 2;
    - FIGURE 5 illustrates a detailed view of the first annular part illustrated in FIGURE 4:
    - FIGURE 6 illustrates a partial perspective view of a central hub provided with the first annular part illustrated in FIGURES 4 and 5;
    - FIGURE 7 illustrates a front view of the central hub and the first annular part illustrated in FIGURES 5 and 6;
    - FIGURE 8 illustrates another embodiment of the angular indexing of the elastic return element on the central hub of the double clutch mechanism.
    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.
    In the figures, the elements common to several figures keep the same reference.
    Detailed description of the invention
    With reference to FIGURES 1 to 3, the illustrated embodiment of a double clutch mechanism 10 according to the first aspect of 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 located 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 integrated on a transmission chain 1 comprising a transmission coupled in rotation to the double clutch mechanism 10.
    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 possibly takes the form of a hollow cylinder inside which the first transmission shaft A1 can be inserted.
    As illustrated in FIGURES 1 to 3, 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.
    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 ίο in a so-called disengaged position for which the plurality of first friction elements 201 is decoupled in rotation at the plurality of second friction elements 202.
    In the double clutch mechanism 10 illustrated in FIGURES 1 to 3, the first clutch 100 is arranged to engage the odd ratios of the transmission and the second clutch 200 is arranged to engage the even ratios and the reverse gear of the transmission. Alternatively, the ratios supported by the first clutch 100 and the 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 1301 which is linked in rotation and / or axially to the input shaft, optionally by means of a damping device, such as a double damping flywheel for example.
    The input hub 130 comprises an external elongation 1302 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 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. This connection is produced by means of an outer axial elongation span 1061 of a door entry discs 106, the entry disc holder 106 being linked in rotation to the entry veil 109, preferably by cooperation of shapes, for example by grooves at the front end AV of said axial elongation span outdoor 1061.
    The first clutch 100 and the second clutch 200 are each controlled by an actuation system 300A, 300B which will be described later. Each actuating system 300A, 300B is arranged to be able to configure the first clutch 100 and the second clutch 200 in any configuration between the engaged configuration and the disengaged configuration.
    The first actuation system 300A is linked to the first clutch 100 by means of a first piston 105 comprising a first part 105P - described here and a second part 105Q - which will be described later. In general, the first piston 105 is arranged to transmit a first axial force El, exerted parallel to the longitudinal axis O, to the first clutch 100 by means of its first part 105P collaborating with the friction elements 101, 102 of said first clutch 100, and of its second part 105Q collaborating with a force generator to configure the first clutch 100 in one of the configurations detailed above. At its first part 105P, the first piston 105 includes first axial extension surfaces 1051 which extend axially forward AV to be able to press the first friction elements 101 against the second friction elements 102 of on the one hand, and against an external reaction means 103 mechanically linked to the entry veil 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 piston 105 takes the form of a corrugated sheet and is curved axially forwards AV at its outer radial end. The first external axial extension surfaces 1051 extend parallel to the longitudinal axis O towards the front AV and through an opening 1064 arranged through the input disc holder 106.
    The first piston 105 includes a first upper radial extension seat 1052 located behind the external axial extension seats 1051. The first upper radial extension seat 1052 extends radially parallel to the transverse axis T from the first clutch 100 to the lower limit of the second clutch 200.
    A first intermediate axial extension span 1053, parallel to the longitudinal axis O, extends the first upper radial extension span 1052 partially under the second clutch 200, towards the front AV of the double clutch mechanism 10. The first span 1053 intermediate axial extension is located radially in line with the 1051 external axial extension spans. The first intermediate axial extension span 1053 is formed parallel to the longitudinal axis O and parallel to the outer axial extension spans 1051.
    Finally, the first piston 105 comprises a plurality of first internal radial extension surfaces 1055 connected to the intermediate axial extension surface 1053 via a first curved zone 1054. The first internal radial extension surfaces 1055 are connected to the second part 105Q of the first piston 105 via a first connection means 400A which will be described below. Alternatively, the first part 105P and the second part 105Q of the first piston 105 can be made from material.
    By way of nonlimiting example, the first piston 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 holder 106.
    The external reaction means 103 notably has external grooves which cooperate with corresponding internal grooves of the input disc holder 106.
    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 actuation system 300A exerts the first axial force El towards the front AV to configure the first clutch 100 in its engaged position. Conversely, when the first piston 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 drive shaft via a first output disc holder 110 forming an output element of said first clutch 100. More particularly, the first output disc holder 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.
    The first outlet hub 120 has radially inside the axial grooves arranged to cooperate with complementary grooves located on the first drive shaft A1, 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 actuation system 300B is linked to the second clutch 200 by means of at least one second piston 205 comprising a first part 205P described here - and a second part 205Q - which will be described later. The second piston 205 is located axially between the entry veil 109 and the first piston 105.
    Generally, the second piston 205 is arranged to transmit a second axial force E2, exerted parallel to the longitudinal axis O, to the second clutch 200 via its first part 205P collaborating with the friction elements 201, 202 of said second clutch 200, and of its second part 205Q collaborating with a force generator to configure the second clutch 200 in one of the configurations detailed above. At its first part 205P, the second piston 205 comprises second external axial extension surfaces 2051 which extend obliquely towards the rear AR and towards the outside in order to be able to spread 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 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 piston 205 takes the form of a corrugated sheet and has a second outer radial end 205 which is curved axially towards the rear AR.
    The second piston 205 includes a second upper radial extension seat 2052 located in front of its second external axial extension seats 2051. The second upper radial extension seat 2052 extends radially from the second clutch 200 to the inside of the second clutch 200, and radially opposite the first intermediate axial extension seat 1053 of the first piston 105.
    A second intermediate axial extension reach 2053 extends the second upper radial extension reach 2052 under the second clutch 200, towards the rear AR of the double clutch mechanism 10. The second intermediate axial extension reach 2053 is located radially at outside the second clutch 200 and opposite the first upper radial extension seat 1052 of the first piston 105. More particularly, it is located opposite the input disc holder 106.
    Finally, the second piston 205 comprises a second inner radial extension part 2055 which is connected to the intermediate axial extension bearing 2053 via a radial extending bearing 2054. The second inner radial extending part 2055 is connected to the second part 205Q of the second piston 205 via a second connection means 400B which will be described below. Alternatively, the first part 205P and the second part 205Q of the second piston 205 can be made from material.
    By way of nonlimiting example, the second piston 205 can be obtained by stamping.
    The internal reaction means 203 is integral with an internal axial elongation part 1062 of the input disc holder 106.
    The internal reaction means 203 here takes the form of a locking ring carried by the internal axial elongation part 1062 of the input disc carrier 106 and located at the rear AR of the first and second friction elements 201, 202 of the second clutch 200, so as to allow friction coupling of the first and second friction elements 201, 202 when the second actuation system 300B exerts an axial force towards the rear AR to configure said second clutch 200 in its position engaged. Conversely, when the second piston 205 is pushed forward AV 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.
    Alternatively, the internal reaction means 203 can take the form of a boss on an external face of the input disc carrier 106 and located behind the rear of the friction elements 201, 202 of the second clutch 200. Alternatively, the internal reaction means 203 and the input disc holder 106 are made from material.
    The second clutch 200 is intended to be coupled in rotation to the second transmission shaft A2 via a second output disc holder 210 forming an output element of said second clutch 200. More particularly, the second output disc holder 210 is rotatably coupled to the second friction elements 202 via an upper end 2101 that the second outlet disc holder 210 comprises. The second outlet disc holder 210 is rotatably coupled to a second outlet hub 220 via an inner end 2102, which the second outlet disc holder 210 includes.
    The second outlet disc holder 210 comprises on its outer radial periphery a second 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 second outlet disc holder 210 is linked to the second outlet hub 220 via its inner end 2102; they are preferably fixed together by welding or by riveting.
    Furthermore, an axial bearing 116 is interposed between the first outlet disc holder 110 and the second outlet disc holder 210 so as to be able to transmit an axial load 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 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.
    The input disc holder 106 is configured to be coupled in rotation with the first friction elements 101, 201 of the first 100 and second 200 clutches, it being recalled that the input disc holder 106 is also coupled in rotation to the web input 109. For this purpose, the input disc holder 106 comprises the external axial elongation part 1061 which is located outside the first clutch 100 and which is coupled, for example by engagement of complementary shapes, with the first friction elements 101 of the first clutch 100. The input disc carrier 106 also includes a radial elongation range 1063 which extends the external axial extension range 1061 towards the rear AR, and more particularly behind AR of the first 100 and second 200 clutches. At its inner end, the radial elongation surface 1063 of the input disc carrier 106 comprises an internal axial elongation surface 1062 which is located radially inside the second clutch 200 and which is coupled in rotation, for example by engagement of complementary shapes, with the first friction elements 201 of the second clutch 200.
    The input disc holder 106 is carried and coupled in rotation at its internal part of the radial elongation surface 1063 and its internal axial elongation surface 1062 by a first balancing cover 450A of the first system d actuation 300A and by a second balancing cover 450B of the second actuation system 300B.
    The first balancing cover 450A comprises a cylindrical bearing surface 4502A of axial extension and carrying both an external radial arm 4501A and an internal radial leg 4503 A. The cylindrical bearing surface 4502A is preferably oriented parallel to the longitudinal axis O; while the outer radial arm 4501A and the inner radial leg 4503A are oriented orthogonally to the longitudinal axis O.
    The outer radial arm 4501A is integral with the input disc holder 106, and more particularly with the radial elongation span 1063 of the input disc holder 106 interposed between the opening 1064 of said input disc holder 106 and its internal axial elongation part 1062. The external radial arm 4501A and the radial elongation surface 1063 of the input disc holder 106 are for example welded or riveted or associated by any other similar means.
    The inner radial leg 4503A of the first balancing cover 450A has an inner end which is integral with a central hub 500. The central hub 500 is arranged in “T” in the transverse plane of the sectional view illustrated in FIGURE 1 or 3, and comprises a central body 510 of radial elongation and substantially orthogonal to the longitudinal axis O connecting a cylindrical bearing of axial elongation 520 parallel to the longitudinal axis O. The inner radial end of the inner radial leg 4503A is integral with an upper radial end 515 of the central body 510 of the central hub 500.
    The second balancing cover 450B is arranged in a square in the transverse plane of the sectional view illustrated in FIGURE 1 or 3, and it comprises a cylindrical seat 4502B of axial extension and an inner radial leg 4503B. The cylindrical seat 4502B extends substantially parallel to the longitudinal axis O while the inner radial leg 4503B extends orthogonally to the longitudinal axis O.
    The inner radial leg 4503B of the second balancing cover 450B comprises an inner end which is integral with the central hub 500, and more particularly at the level of the upper radial end 515 of the central body 510 of the central hub 500. The inner radial leg 4503A of the second balancing cover 450B and the inner radial leg 4503A of the first balancing cover 450A are preferably parallel to one another.
    Thus, the central hub 500 supports the first and second clutches 100, 200 through the input disc holder 106 on the one hand, and the first and second balancing covers 450A, 450B. The central hub 500 is therefore coupled in rotation to the input hub 130 of the double clutch mechanism 10 according to the first aspect of the invention. When the input hub 130 is coupled to a motor shaft driven in rotation by the crankshaft of an engine, as described above, then the central hub 500 is driven in a rotation movement similar to that of the engine shaft .
    The central hub 500 is supported radially by a clutch support 600 which extends at least partially parallel to the longitudinal axis O, by means of a plurality of radial decoupling bearings 650 making it possible to decouple the rotation of the hub central 500 with respect to the clutch support 600 which is fixed in this configuration of double clutch mechanism 10.
    Also referring to FIGURES 2 to 3, the first actuation system 300A and the second actuation system 300B will be described below.
    Each actuation system 300A, 300B includes:
    - a pressure chamber 750A, 750B arranged to receive a pressurized fluid;
    a piston 105, 205 movable axially inside the pressure chamber 750A, 750B, said piston 105, 205 being formed by:
    o a first part 105P, 205P extending radially outside the pressure chamber 750A, 750B in order to engage or disengage the corresponding clutch, as described above;
    o a second part 105Q, 205Q located radially inside the first part 105, 205 and collaborating with the pressure chamber 750A, 750B, said second part 105Q, 205Q being fixedly joined to said first part 105P, 205P;
    o at least one connecting means 400A, 400B interposed between the first part 105P, 205P and the second part 105Q, 205Q of the corresponding piston 105, 205;
    - a balancing chamber 700A, 700B located opposite the pressure chamber 750A, 750B relative to the second part 105Q, 205Q of the piston 105, 205.
    The first actuation system 300A comprises a first liner plate 910A which adjoins a first reaction plate 920A making it possible to produce an axial reinforcement on the first liner plate 910A. The first reaction plate 920A is in particular arranged in a ring gear intended to drive pumps of the transmission chain 1 able to circulate a lubrication fluid in the double clutch mechanism 10 when the latter is driven in rotation.
    The first liner plate 910A is formed by a radial part 912A and a longitudinal part 911A located at the outer end of the radial part 912A. The radial part 912A of the first lining plate 910A is in axial abutment against the first reaction plate 920A and is oriented parallel to the transverse axis T. The radial part 912A of the first lining plate 910A comprises at its end inner radial a fourth seal 404A which ensures a sealed radial support of said radial part 912A of the first liner plate 910A against the cylindrical surface 520 of the central hub 500. The longitudinal part 911A is of axial orientation and extends inside the intermediate axial extension range 1053 of the first piston 105.
    The first actuation system 300A is also formed by the second part 105Q of the first piston 105. The second part 105Q of the first piston 105 is arranged in a "U" shape: it comprises a first base 1057, a first branch 1056 and a second branch 1058. The first base 1057 is of radial extension and connects the first branch 1056 and the second branch 1058 which are formed parallel to the longitudinal axis O. The first branch 1056 is located radially outside with respect to the second branch 1058. The first branch 1056 is located at the outer radial end of the first base 1057; and the second branch 1058 is located at the inner radial end of said first base 1057.
    Advantageously, the first base 1057 comprises for example a boss for centering the second annular part 820A of the first elastic return element 800A.
    The first branch 1056 of the second part 105Q of the first piston 105 has an axial termination 415 which is integral with the first part 105P of the first piston 105, more particularly at the level of the inner radial extension range 1055. The second branch 1058 of the second part 105Q of the first piston 105 has an axial termination 1059 which bears against the cylindrical bearing surface of axial extension 520 of the central hub 500 by means of a third seal 403A.
    The first pressure chamber 750A of the first actuation system 300A is arranged to receive a certain volume of hydraulic fluid under pressure in order to generate an axial force on the second part 105Q of the first piston 105 and thus to configure the first clutch 100 in the 'one of the configurations described above. The pressurized hydraulic fluid is advantageously conveyed by means of high-pressure fluidic circulation conduits crossing at least partially the cylindrical bearing surface of axial extension 520 of the central hub 500 and opening into the pressure chamber 750A at the level of an external face. of said cylindrical bearing surface with axial extension 520.
    The first pressure chamber 750A of the first actuation system 300A is thus advantageously delimited:
    - radially inwards, by a portion of the cylindrical surface 520 of the central hub 500,
    - axially towards the rear AR, by the radial part 912A of the first lining plate 910A,
    - radially outwards, by the intermediate axial extension surface 1053 and the first curved zone 1054 of the first part 105P of the first piston 105 and by the longitudinal part 911A of the first liner plate 910A, and
    - Axially forwards AV, by the internal radial extension surface 1055 of the first part 105P of the first piston 105 and by the second part 105Q of the first piston 105.
    It will also be noted that the tightness of the pressure chamber 750A of the first actuation system 300A is guaranteed by the presence:
    a first seal 401A situated between the longitudinal part 911A of the first liner plate 910A and the internal radial extension surface 1055 and / or the intermediate axial extension surface 1053 of the first part 105P of the first piston 105;
    - the third seal 403A located between the inner radial end of the second part 105Q of the first piston 105 and the cylindrical seat 520 of the central hub 500;
    - the fourth seal 404A located between the inner radial end of the radial part 912A of the first liner plate 910A and the cylindrical seat 520 of the central hub 500.
    The first balancing chamber 700A of the first actuation system 300A is arranged to receive a certain volume of hydraulic fluid making it possible to lubricate the first elastic return element 800A housed in said balancing chamber 700A. The lubrication fluid is advantageously conveyed by means of low pressure fluidic circulation conduits crossing at least partially the cylindrical bearing surface of axial extension 520 of the central hub 500 and opening into the balancing chamber 700A at the level of a face. outside of said cylindrical bearing surface with axial extension 520. The balancing chamber 700A of the first actuation system 300A is advantageously delimited:
    - radially inwards, by a portion of the cylindrical surface 520 of the central hub 500,
    - axially rearward AR, by the internal radial extension surface 1055 of the first part 105P of the first piston 105 and by the second part 105Q of the first piston 105,
    - radially outwards, through the cylindrical surface 4502A of the first balancing cover 450A, and
    - Axially forwards AV, by the central body 510 of the central hub 4501A and by the inner radial leg 4503A and the cylindrical bearing surface 4502A of the first balancing cover 450A.
    It will also be noted that the tightness of the first balancing chamber 700A of the first actuation system 300A is guaranteed by the presence:
    - the second seal 402A which extends between the internal radial extension surface 1055 and the intermediate axial extension surface 1053 of the first part 105P of the first piston on the one hand, and the cylindrical surface 4502A of the first balancing cover 450A on the other hand; and
    - the third seal 403A located between the inner radial end of the second part 105Q of the first piston 105 and the cylindrical seat 520 of the central hub 500.
    The second actuation system 300B is associated with a second reaction plate 920B which comprises a curved portion 923B interposed between a first radial extension span 921B and a second radial extension span 922B. The curved part 923B is a part forming a forward prominence AV with respect to the first radial extension range 921B and the second radial extension range 922B in order to reinforce the behavior of the reaction plate 920B with regard to the forces axial generated by the second actuation system 300B. Advantageously, the second reaction plate 920B is stopped axially forwards by a locking ring housed in a circumferential groove in the central hub 500.
    The second actuation system 300B also includes a second liner plate 910B which adjoins the second reaction plate 920B. The second lining plate 910B comprises a radial part 912B and a longitudinal part 91 IB. The radial part 912B of the second liner plate 910B is in contact with the second lug 922B of the second reaction plate 920B and is oriented parallel to the transverse axis T. The longitudinal part 91 IB of the second liner plate 910B is as for it oriented parallel to the longitudinal axis O and is in contact with the second intermediate axial extension bearing surface 2053 of the second piston 205.
    The second actuation system 300B is also formed by the second part 105Q of the second piston 105. The second part 205Q of the second piston 105 is arranged in a "U" shape and it comprises a first base 2057, a first branch 306b and a second branch 2058. The first base 2057 of the second part 205Q of the second piston 105 is of radial extension and connects the first branch 2056 and the second branch 2058 which are formed parallel to longitudinal tax O. The first branch 2056 of the second part 205Q of the second piston 105 is located radially outside relative to the second branch 2058. The first branch 2056 of the second part 205Q of the second piston 105 is located at the radial outer end of the first base 2057; and the second branch 2058 is located at the inner radial end of said first base 1057.
    Advantageously, the first base 1057 comprises for example a boss for centering the second annular part 800A of the first elastic return element 800A.
    The first branch 2056 of the second part 205Q of the second piston 205 has an axial termination 425 which is integral with the first part 205P of the second piston 205, more particularly at the level of the inner radial extension range 2055. The second branch 2058 of the second part 205Q of the second piston 205 has an axial termination 2059 which bears against the cylindrical bearing surface of axial extension 520 of the central hub 500 by means of a third seal 403B.
    The second pressure chamber 750B of the second actuation system 300B is arranged to receive a certain volume of hydraulic fluid under pressure in order to generate an axial force on the second part 205Q of the second piston 205 and thus to configure the second clutch 200 in the 'one of the configurations described above. The pressurized hydraulic fluid is advantageously conveyed by means of high pressure fluidic circulation conduits crossing at least partially the cylindrical bearing surface of axial extension 520 of the central hub 500 and opening into the pressure chamber 750B of the second actuation system 300B at an external face of said cylindrical bearing surface with axial extension 520.
    The second pressure chamber 750B of the second actuation system 300B is thus advantageously delimited:
    - radially inwards, by a portion of the cylindrical surface 520 of the central hub 500,
    - axially towards the rear AR, by the radial part 912B of the second lining plate 910B,
    - radially outwards, by the intermediate axial extension surface 2053 and the first curved zone 2054 of the second part 205Q of the second piston 205 and by the longitudinal part 91 IB of the second liner plate 920B, and
    - Axially forwards AV, by the internal radial extension surface 2055 of the first part 205P of the second piston 205 and by the second part 205Q of the second piston 205.
    It will also be noted that the tightness of the pressure chamber 750B of the second actuation system 300B is guaranteed by the presence:
    - a first seal 401B located between the longitudinal part 91 IB of the second liner plate 910B and the inner radial extension surface 2055 and / or the intermediate axial extension surface 2053 of the first part 205P of the second piston 205;
    - a third seal 403B located between the inner radial end of the second part 205Q of the second piston 205 and the cylindrical seat 520 of the central hub 500;
    - a fourth seal 404B located between the inner radial end of the radial part 912B of the second liner plate 910B and the cylindrical seat 520 of the central hub 500.
    The second balancing chamber 700B of the second actuation system 300B is arranged to receive a certain volume of hydraulic fluid making it possible to lubricate the second elastic return element 800B housed in said balancing chamber 700B. The lubrication fluid is advantageously conveyed via low pressure fluidic circulation conduits crossing at least partially the cylindrical bearing surface of axial extension 520 of the central hub 500 and opening into the balancing chamber 700B of the second actuation system 300B at an external face of said cylindrical bearing surface with axial extension 520. The balancing chamber 700B of the second actuation system 300B is advantageously delimited:
    - Radially inwards, by a portion of the cylindrical seat 520 of the central hub 500;
    - Axially rearward AR, by the central body 510 of the central hub 500 and by the inner radial leg 4503 A and the cylindrical surface 4502B of the second balancing cover 450B;
    - Radially outwards, through the cylindrical surface 4502B of the second balancing cover 450B; and
    - Axially forwards AV, by the internal radial extension surface 2055 of the first part 205P of the second piston 205 and by the second part 205Q of the second piston 205.
    It will also be noted that the tightness of the second balancing chamber 700B of the first second actuation 300B is guaranteed by the presence:
    - the second seal 402B which extends between the internal radial extension surface 2055 and the intermediate axial extension surface 2053 of the first part 205P of the second piston 205 on the one hand, and the cylindrical surface 4502B of the second balancing cover 450B on the other hand; and
    - the third seal 403B located between the inner radial end of the second part 205Q of the second piston 205 and the cylindrical seat 520 of the central hub 500.
    It will be understood at this stage of the description that a characteristic of the present invention lies in the fact that:
    the first part 105P and the second part 105Q of the first piston 105 are made mobile by the control of the pressurized fluid filling the first pressure chamber 750A on the one hand, and by the action of the first elastic return element 800A housed in the first balancing chamber 700A on the other hand;
    - The first part 205P and the second part 205Q of the second piston 205 are made mobile by the control of the pressurized fluid filling the pressure chamber 750B on the one hand, and by the action of the second elastic return element 800B housed in the second balancing chamber 700B on the other hand.
    Each actuating system 300A, 300B further comprises an elastic return element 800A, 800B arranged to generate an axial force opposing the movement of the corresponding piston 105, 205 to engage the corresponding clutch 100, 200. In particular, the central body 510 of the central hub 500 also comprises a cylindrical seat of radial extension 512 against which a first annular part 810A of a first elastic return element 800A and a first annular part 810B of a second return element elastic 800B are in axial support. The first elastic return element 800A extends between its first annular part 810A and a second annular part 820A of said first elastic return element 800A; and the second elastic return element 800B extends between its first annular part 810B and a second annular part 820B of said second elastic return element 800B. For each elastic return element 800A, 800B, a plurality of elastic elements 830A, 830B extend between the corresponding first annular part 810 and the second annular part 820. Advantageously, the plurality of elastic elements 830 are of the type of the coil spring type. The second annular part 820A, 820B of each elastic return element 800A, 800B is in axial abutment against a face opposite the corresponding piston 105, 205, and more particularly at the level of the second part 105Q, 205Q of said piston 105, 205.
    Advantageously, the first 800A and second 800B elastic return elements are identical.
    FIGURES 4 and 5 illustrate a particular embodiment of the first annular part 810 of one of the elastic return elements 800.
    The first annular part 810 takes the form of a circular ring, the longitudinal axis O forming a circular axis of symmetry S of the first annular part 810. The first annular part 810 is preferably of small axial thickness. It is delimited axially between a first face 8101 and a second face 8102, preferably parallel to each other. The axis of symmetry S is advantageously orthogonal to the first 8101 and second 8102 faces. The second face 8102 of the elastic return element 800 is intended to be disposed in axial abutment against the cylindrical seat of radial extension 512 of the central hub
    500. The first face 8101 of the elastic return element 800 is intended to be opposite the second annular part 820 of said elastic return element 800.
    The first annular part 810 comprises, at the edge of the first face 8101 and of the second face 8102, an outer rim 8105 and an inner rim 8106, the inner rim 8106 being located radially closer to the axis of symmetry S than the outer rim 8105 .
    The outside edges 8105 and inside 8106 radially delimit the first annular part 810 inside a plane PI.
    The first face 8101 is provided with at least one receiving pad 8103 of an elastic element 830 of the elastic return element 800, formed more particularly by a helical spring as described above. Each reception pad 8103 is in particular arranged in a cylindrical barrel which emerges orthogonally to the plane PI according to which the first annular part 810 extends. Optionally, each reception stud 8103 is a hollow cylindrical barrel, not opening onto the second face 8102 of the elastic return element 800. Alternatively, each reception stud 8103 is a hollow cylindrical barrel opening onto the second face 8102 of l 'elastic return element 800. Alternatively again, each receiving pad 8103 is a full cylindrical barrel. Each reception stud 8103 is advantageously formed around a barrel axis F which is parallel to the axis of symmetry S. Preferably, the first face 8101 of the elastic return element 800 comprises a plurality of reception studs 8103 angularly regularly distributed around the axis of symmetry S. In the embodiment illustrated in FIGURES 4 and 5, the first face 8101 comprises 24 receiving pads 8103
    Additionally, the first annular part 810 of the elastic return element 800 comprises a plurality of openings 8104 which are formed through the annular part 810, between the first face 8101 and the second face 8102 of said elastic return element 800. In other words, the opening 8104 forms a passage for the lubrication fluid which circulates from the central hub 500 to the corresponding balancing chamber 700 via the low pressure fluidic circulation conduits of the double clutch mechanism 10. Like this is illustrated in FIGURE 3B, the openings 8104 open directly into the complementary openings 5004 arranged in the central hub 500, so that the circulation of the cooling fluid is improved. In the plane of the first face 8101, the shape of the opening 8104 can be any, preferably circular or oblong as shown in FIGURES 4 and 5. Preferably, the first annular part 810 comprises a plurality of openings 8104 which are angularly regularly distributed around the axis of symmetry S.
    Direct communication of the openings 8104 in the complementary openings 5004 is made possible by means of angular indexing means 8107, 5004. Indeed, according to the invention according to its first aspect, the first annular part 810 comprises at least one means of angular indexing 8107 intended to collaborate with an additional angular indexing means 5004 located on the central hub 500. More particularly, the outer rim 8105 of the first annular part 810 is provided with at least one tab 8107 which extends in projection from the first 8101 and second 8102 faces of the first annular part. The at least one tab 8107 thus forms the angular indexing means of the elastic return element 800. More particularly, each tab 8107 is formed inside a second plane P2 perpendicular to the first plane P1. It s advantageously extends in an axial direction opposite to the first face 8101 of the first annular part 810 and relative to its second face 8102. In the plane P2, the tab 8107 can take any shape, in particular rectangular as illustrated in the FIGURE 5.
    In the exemplary embodiment illustrated in FIGURES 4 and 5, the first annular part 810 comprises two tabs 8107 situated diametrically opposite with respect to the axis of symmetry
    Alternatively, the first annular part 810 may comprise a three legs 8107 distributed at 120 ° around the longitudinal axis O.
    Referring also to FIGURES 6 and 7 which illustrate the collaboration of the first annular part 810 of the elastic return element 800 with the central hub 500, it is understood that the tab 8107 forms an angular indexing means collaborating with a additional indexing means 5007 in order to angularly position the first annular part 810 on the central hub 500. Thus, it is possible during assembly of the corresponding elastic return element 800 to easily locate the openings 8104 of the first annular part 810 with complementary openings 5004 equipping the central hub 500. In particular, the complementary openings 5004 are formed through the central body 510 of the central hub 500 which includes within it a portion of the low pressure fluidic circulation conduits. Thus, the complementary openings 5004 of the central hub 500 and the openings 8104 of the elastic return element 800 collectively make it possible to unblock the fluidic circulation conduits of the central body 510 of the central hub 500 in the corresponding balancing chamber 700A, 700B .
    The invention in accordance with its first aspect makes it possible to advantageously take advantage of the angular indexing means 8107 of the first annular part 810 of the elastic return element 800 collaborating with the complementary angular indexing means
    5007 of the central hub 500 to define predetermined relative angular positions between said elastic return element 800 and said central hub 500.
    Advantageously, the central body 510 of the central hub 500 forms a radial extension surface formed in a plane parallel to the plane PI. The central body 510 is delimited radially outwards by its upper radial end 515 which forms a circumferential bearing.
    Each tab 8107 of the first annular part 810 advantageously collaborates with a corresponding groove 5007A of the central hub 500. The groove or grooves 5007A thus form complementary angular indexing means 5007 of the central hub 500.
    In general, the complementary angular indexing means 5007 collaborate with the angular indexing means 8107 by form collaboration. In the example illustrated in FIGURES 6 and 7, the legs 8107 naturally form angular indexing means 8107 of the male type; and the complementary angular indexing means 5007 formed by the grooves 5007 are of the female type. The internal face of the legs 8107 forms a means for centering the elastic return elements on the bottom of the groove 5007 of the central hub 500.
    The complementary angular indexing means 5007 are advantageously regularly distributed around the axis of symmetry S, and preferably still in a manner compatible with the angular distribution of the angular indexing means 7107 of the first annular part 810 of the element elastic return 800.
    These advantageous configurations thus make it possible to improve the circulation of the lubrication fluid in the balancing chamber 700 on the one hand, and also facilitate the operations of assembling the elastic return element 800 in said balancing chamber 700.
    FIGURE 8 illustrates another embodiment of the elastic return element 800A, 800B mounted in the balancing chamber 700A, 700B of the actuation system 30. In this embodiment, the elastic return element 800A, 800B comprises the first annular part 810 bearing against the central hub 500, the second annular part 820 bearing against the corresponding piston 105, 205 and the plurality of elastic elements 830A, 830B extending between the first annular part 810 and the second ring piece
    820. The second annular part 820 is separate from the corresponding piston 105, 205. The first annular part 810 comprises the angular indexing means 8107.
    In the example illustrated in FIGURE 8, the angular indexing means is of the type of at least one tab 8107 extending radially inside the corresponding elastic return element 800A, 800B. More particularly, the inner rim 8106 of the first annular part 810 is provided with at least one lug 8107 collaborating with a corresponding hole 5007B on the central hub 500, the hole or holes 5007B collectively forming the complementary angular indexing means 5007.
    The at least one tab 8107 extends projecting from the first annular part 810 in the direction of the central hub. More particularly, an extension direction of the at least one tab 8107 is parallel to an extension direction of the corresponding hole 5007 with which it collaborates, in order to facilitate its insertion. In the example illustrated in FIGURE 8, the at least one tab 8107 and the corresponding hole 5007 extends in the axial direction, substantially parallel to the longitudinal axis O. The at least one tab is advantageously obtained by bending or stamping.
    In summary, the invention relates to a double clutch mechanism 10, each actuation system 300A, 300B comprises a pressure chamber 750A, 750B arranged to receive a pressurized fluid, a piston 105, 205 movable axially in the pressure chamber 750A , 750B in order to engage or disengage the corresponding clutch 100, 200, a balancing chamber 700A, 700B situated opposite the pressure chamber 750A, 750B relative to the piston 105, 205, and an element of elastic return 800A, 800B housed in the balancing chamber and arranged to exert an axial force against said piston 105, 205. According to the invention, the elastic return element 800A, 800B comprises a plurality of openings 8104 collaborating with a plurality of complementary openings 5004 located on the central hub 500 of the clutch mechanism 10 in order to allow fluid communication between a fluid circulation duct of the central hub 500 and the corresponding balancing chamber 700A, 700B. In order to guarantee their alignment and to facilitate the mounting of the elastic return element 800A, 800B in the balancing chamber 700A, 700B, the elastic return element 800A, 800B of at least one of the actuating systems 300A , 300B comprises an angular indexing means 8107 collaborating with an additional angular indexing means 5007 located on the central hub 500.
    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 (16)
    [1" id="c-fr-0001]
    Claims
    1. Double clutch mechanism (10) comprising:
    - a first clutch (100) and a second clutch (200) rotating around a central hub (500);
    - a first actuation system (300A) arranged to engage or disengage the first clutch (100);
    - a second actuation system (300B) arranged to engage or disengage the second clutch (200), each actuation system (300A, 300B) comprising:
    o a pressure chamber (750A, 750B) arranged to receive a pressurized fluid;
    a piston (105, 205) movable axially in the pressure chamber (750A, 750B) and extending radially outside the pressure chamber (750A, 750B) in order to engage or disengage the clutch ( 100, 200) corresponding;
    o a balancing chamber (700A, 700B) located opposite the pressure chamber (750A, 750B) relative to the piston (105, 205), o an elastic return element (800A, 800B) housed in the balancing chamber, said elastic return element (800A, 800B) extending between the corresponding piston (105, 205) and the central hub (500), said elastic return element (800A, 800B) being arranged to exert a axial force against said piston (105, 205);
    characterized in that said elastic return element (800A, 800B) comprises a plurality of openings (8104) opening directly into a plurality of complementary openings (5004) formed on the central hub (500) in order to allow fluid communication between a fluid circulation duct of the central hub (500) and the balancing chamber (700A, 700B).
    [2" id="c-fr-0002]
    2. Double clutch mechanism (10) according to the preceding claim, in which the elastic return element (800A, 800B) of at least one of the actuation systems (300A, 300B) comprises an angular indexing means ( 8107) collaborating with a complementary angular indexing means (5007) located on the central hub (500).
    [3" id="c-fr-0003]
    3. Double clutch mechanism (10) according to the preceding claim, in which the elastic return element (800A, 800B) of at least one actuation system (3 00A, 300B) comprises:
    - A first annular part (810) intended to bear against a wall (5002) of the central hub (500), the first annular part (8101) comprising the angular indexing means (8107);
    - a second annular part (820) intended to bear against the corresponding piston (105, 205);
    - a plurality of elastic elements (830) extending between the first annular part (810) and the second annular part (820).
    [4" id="c-fr-0004]
    4. Double clutch mechanism (10) according to the preceding claim, wherein the plurality of elastic elements (830) is of the type of a plurality of helical springs.
    [5" id="c-fr-0005]
    5. Double clutch mechanism (10) according to the preceding claim, wherein the plurality of openings (8104) formed in the first annular part (810) are angularly distributed between the coil springs.
    [6" id="c-fr-0006]
    6. Double clutch mechanism (10) according to any one of claims 2 to 5, in which the angular indexing means (8107) of at least one of the actuation systems (300A, 300B) is of the male type and the complementary angular indexing means (5007) of the central hub (500) is of the female type.
    [7" id="c-fr-0007]
    7. Double clutch mechanism (10) according to claim 6, wherein the angular indexing means (8107) is of the type of at least one lug (8107) extending radially outside the element of corresponding elastic return (800A, 800B), each tab (8107) collaborating with a corresponding groove (5007A) on the central hub (500), the groove or grooves (5007A) collectively forming the complementary angular indexing means (5007).
    [8" id="c-fr-0008]
    8. Double clutch mechanism (10) according to claim 6, wherein the angular indexing means (8107) is of the type of at least one lug (8107) extending radially inside the element of corresponding elastic return (800A, 800B), each tab (8107) collaborating with a corresponding hole (5007B) on the central hub, the hole or holes (5007B) collectively forming the complementary angular indexing means (5007).
    [9" id="c-fr-0009]
    9. Double clutch mechanism (10) according to claim 6, in which the angular indexing means (8107) is of the type of at least one extruded rivet extending axially beyond the elastic return element ( 800A, 800B) in the direction of the central hub (500) and the complementary angular indexing means (5007) is of the type of at least one axial bore.
    [10" id="c-fr-0010]
    10. Double clutch mechanism (10) according to any one of claims 6 to 9, in which the angular indexing means (8107) and the complementary angular indexing means (5007) are respectively angularly regularly distributed around a longitudinal axis (O) of the double clutch mechanism (10).
    [11" id="c-fr-0011]
    11. Double clutch mechanism (10) according to any one of claims 2 to 5, in which the angular indexing means (8107) of at least one of the actuation systems (300A, 300B) is of the female type and the complementary angular indexing means (5004) of the central hub (500) is of the male type.
    [12" id="c-fr-0012]
    12. Double clutch mechanism (10) according to any one of the preceding claims, in which the central hub (500) comprises means for centering the elastic return element (800A, 800B) of at least one of the systems actuation (300A, 300B) and relative to the longitudinal axis (O).
    [13" id="c-fr-0013]
    13. Double clutch mechanism (10) according to the preceding claim taken in combination with claim 7, wherein an inner face of the at least one tab (8107) forms the centering means on a bottom of the groove (5007A) from the central hub (500).
    [14" id="c-fr-0014]
    14. Double clutch mechanism (10) according to any one of claims 3 to 13, in which the second annular part (820) and an inner end of the piston (105, 205) of at least one of the actuation systems (300A, 300B) are fixed integrally together or form a single piece.
    [15" id="c-fr-0015]
    15. Double clutch mechanism (10) according to any one of claims 2 to 14, in which the complementary angular indexing means (5007) of the central hub (500) is common with the angular indexing means (8107) first and second elastic return elements (800A, 800B).
    5
    [0016]
    16. Double clutch mechanism (10) according to any one of the preceding claims, in which the first and second clutches (100, 200) are in a radial configuration, the second clutch (200) being located radially inside the first clutch (100).
    1/9
    1002 103 101 102 1061/10641051 oc
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    FR3092373A1|2020-08-07|DOUBLE WET CLUTCH AND ELASTIC RETURN DEVICE FOR SUCH A DOUBLE WET CLUTCH
    FR3101926A1|2021-04-16|"COMPACT WET DOUBLE CLUTCH MECHANISM"
    EP3810947A1|2021-04-28|Lubricating ring and clutch module comprising such a lubricating ring
    FR3066570A1|2018-11-23|INTAKE DISC TRAY OF A DOUBLE CLUTCH MECHANISM AND DOUBLE CLUTCH MECHANISM
    同族专利:
    公开号 | 公开日
    CN108397491A|2018-08-14|
    FR3062696B1|2019-03-22|
    EP3364063B1|2020-04-08|
    EP3364063A1|2018-08-22|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE102007008946A1|2006-02-27|2008-02-14|Borgwarner Inc., Auburn Hills|Twin-clutch system for hybrid automobile with two sets of lamellar packages located between inner and outer lamellar supports|
    US20130153355A1|2011-12-16|2013-06-20|Eaton Corporation|Hydraulic clutch assembly|
    US20150240887A1|2014-02-26|2015-08-27|Getrag Getriebe-Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg|Spring pack, clutch and method of producing a clutch|
    FR3090769A1|2018-12-20|2020-06-26|Valeo Embrayages|INTERIOR DISC HOLDER FOR CLUTCH MECHANISM AND CLUTCH MECHANISM COMPRISING SUCH A DISC HOLDER|
    FR3090772B1|2018-12-21|2021-01-22|Valeo Embrayages|wet double clutch and its cooling process|
    FR3094427B1|2019-03-29|2021-04-23|Valeo Embrayages|Elastic return device for wet clutch mechanism and Wet clutch mechanism comprising such an elastic return device|
    CN110469596A|2019-09-04|2019-11-19|哈尔滨东安汽车发动机制造有限公司|A kind of double clutch connection structure|
    法律状态:
    2018-02-26| PLFP| Fee payment|Year of fee payment: 2 |
    2018-08-10| PLSC| Search report ready|Effective date: 20180810 |
    2020-02-28| PLFP| Fee payment|Year of fee payment: 4 |
    2021-02-26| PLFP| Fee payment|Year of fee payment: 5 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1751018A|FR3062696B1|2017-02-07|2017-02-07|COMPACT DOUBLE CLUTCH MECHANISM AND TRANSMISSION SYSTEM COMPRISING SUCH A DOUBLE CLUTCH MECHANISM|
    FR1751018|2017-02-07|FR1751018A| FR3062696B1|2017-02-07|2017-02-07|COMPACT DOUBLE CLUTCH MECHANISM AND TRANSMISSION SYSTEM COMPRISING SUCH A DOUBLE CLUTCH MECHANISM|
    EP18154166.5A| EP3364063B1|2017-02-07|2018-01-30|Compact dual clutch mechanism and transmission system comprising such a dual clutch mechanism|
    CN201810122715.2A| CN108397491A|2017-02-07|2018-02-07|Compact dual clutch mechanism and the transmission system for including this dual clutch mechanism|
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