• 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 an elastic return device comprising a seal and a clutch mechanism (10) whose actuating system (300) comprises a control chamber (750) arranged to receive a pressurized fluid, a piston (105) movable axially in the control chamber (750) to engage or disengage the corresponding clutch (100), a counterbalance chamber (700) located opposite the control chamber (750) by relative to the piston (105), and an elastic return device (800) housed in the balancing chamber and arranged to exert an axial force against said piston (105). According to the invention, the elastic return device (800) comprises, on one of its faces bearing against the piston (105), an inner peripheral end which extends radially under the piston (105) and which carries a seal to seal the balancing chamber (700) with respect to the control chamber (750). The invention also relates to a transmission system (1) comprising such a dual clutch mechanism (10).
    公开号:FR3063322A1
    申请号:FR1751607
    申请日:2017-02-28
    公开日:2018-08-31
    发明作者:Laurent Caumartin；Rabah Arhab；Herve RIBOT；Guillaume VUAROQUEAUX；David Delplace
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    Technical area
    The present invention relates to an elastic return device making it possible to generate a force against a member making it possible to engage or disengage a clutch of a clutch mechanism of the wet type and as used in the field of the automobile. The invention also relates to a clutch mechanism comprising such an elastic return device as well as a transmission system incorporating such a 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 , to transmit to said clutch the force generated at the force generator.
    In known manner, an actuation system can be formed by a hydraulic force generator comprising (i) a control chamber arranged to receive a pressurized fluid, (ii) a piston movable axially in the control chamber and extending radially outside the control chamber in order to engage or disengage the clutch, (iii) a balancing chamber situated opposite the control chamber relative to the piston, the balancing chamber comprising an elastic return device making it possible to generate a force, called a return force, against the piston.
    The control chamber is supplied with a pressurized hydraulic fluid in order to allow the displacement of the piston 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 conveyed to the control chamber via so-called high pressure fluid lines.
    Conversely, the balancing chamber is supplied with a hydraulic fluid called cooling making it possible to lubricate the components of the clutch mechanism, and incidentally the balancing chamber. To do this, the hydraulic fluid of
    -2 cooling is routed in particular to the balancing chamber by means of so-called low pressure fluid conduits.
    In known manner, the pressure of the hydraulic cooling fluid necessary for the lubrication of the clutch mechanism is lower than that of the pressurized hydraulic fluid necessary for the generation of the force making it possible to configure the clutch in one or the other. of the configurations listed above.
    In addition, the piston of the clutch mechanism being located in an intermediate position between the balancing chamber and the control chamber, it thus delimits the two chambers of the clutch mechanism. It is therefore necessary to ensure the seal between the balancing chamber and the control chamber at the piston in order to guarantee on the one hand the pressurization of the control chamber, and the lubrication of the balancing on the other hand, preferably without leakage between the two chambers.
    In known manner, the seal between the two chambers has hitherto been achieved by a seal located at an inner radial end of the piston, the seal being pressed against a clutch support delimiting radially to the inside both the control chamber and the balancing chamber. Such a configuration is known in document DE 10 2014 102 515 Al.
    A drawback associated with this configuration is linked to the complex manufacturing of the piston, obtained for example by stamping and numerous resumptions of machining in order to adapt said piston to the different clutch mechanisms. Indeed, the piston is an adjustment part machined as a function of the other constituent parts of the clutch mechanism and of the mechanical characteristics of said clutch mechanism. Generally, the piston is a stamped sheet metal part which applies an axial force to a stack of friction elements in order to transmit engine torque within the clutch. For example, the torque to be transmitted to the constrained clutch and in particular defines the number of friction elements forming said clutch. Subsequently, the torque to be transmitted at the clutch level also constrains an axial extension of the piston in order to allow the latter to couple or decouple the friction elements between them while keeping the axial and / or radial size of the piston as constant as possible. clutch mechanism, despite the variability of the transmitted torques. Thus, the greater the torque to be transmitted, the greater the number of friction elements, and it is therefore necessary to reduce the axial extension
    -3 of the piston in order to take account of the dimensional variations of the clutch inherent in its mechanical characteristics. Subsequently, the piston is a part whose geometry is difficult to standardize for several applications of clutch mechanisms and / or several geometries.
    The insertion of a seal at an inner radial end of the piston of a clutch mechanism therefore fits into a complex industrialization context, and it appears necessary to simplify the manufacturing process in order to better control the tightness at the pressure and balancing chambers on the one hand, and reduce manufacturing costs on the other. This is all the more critical when the seal is obtained by overmolding directly on the piston: this vulcanization operation is generally carried out by an external subcontractor, which adds to the complexity of industrialization.
    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 elastic return device and a new clutch mechanism to solve at least one of these problems.
    Another object of the present invention is to propose a new elastic return device making it possible to seal between a balancing chamber and a control chamber of a clutch mechanism when said elastic return device is mounted on said clutch mechanism.
    Statement of the invention
    According to a first aspect of the invention, at least one of the abovementioned objectives is achieved with an elastic return device for a wet clutch mechanism, said elastic return device being intended to generate a force against a piston set in motion by a system for actuating a clutch of the clutch mechanism, said elastic return device comprising:
    - A first annular part intended to bear against a bearing face of the clutch mechanism;
    -4- a second annular part intended to bear against the piston of the clutch mechanism;
    - a plurality of elastic elements extending between the first annular part and the second annular part;
    the second annular part comprising at its inner peripheral end a seal, and the second annular part being in abutment against a face of the piston oriented axially opposite the plurality of elastic elements.
    Cleverly, the elastic return device according to the first aspect of the invention makes it possible to facilitate the methods of manufacturing the clutch mechanism on which said elastic return device is intended to be mounted. In contrast to the industrial context described for the prior art, such an elastic return device forms an independent module which is easier to handle and to insert on the clutch mechanism than the manipulation and insertion of the seal at one end. piston. The seal is pre-assembled on the module formed by the elastic return device.
    The elastic return device is configured to generate a force opposing a force exerted on its second annular part. In particular, the elastic return device is configured to generate a force substantially perpendicular to the second annular part when a force substantially perpendicular to said second annular part is applied to the elastic return device. The positioning of the seal on the inner peripheral end of the second annular part ensures precise positioning of the seal with respect to the face of the piston oriented axially opposite the plurality of elastic elements.
    The advantageous configuration of the second annular part relative to the bearing face of the piston makes it easier to assemble the elastic return device according to the first aspect of the invention on the clutch mechanism and to avoid that, under the effect of the force generated axially by the plurality of elastic elements, the second annular part is detached from the piston against which it is applied.
    In its first aspect, the invention addresses all the embodiments of such an elastic return device. Certain embodiments will be described more precisely, in particular in the particular context of an implementation on a clutch mechanism. Indeed,
    -5 in general but not limited to, the elastic return device according to the first aspect of the invention is intended to be housed in a balancing chamber of an actuation system of the clutch mechanism.
    The elastic return device 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 inner peripheral end of the second annular part is formed by a bent end part, so that the seal extends over the bent end part of the second annular part of the elastic return device. The bent end part is advantageously intended to be inserted near the piston of the clutch mechanism with which the elastic return device can collaborate in order to improve the tightness of the control chamber of said clutch mechanism delimited by said piston. . In particular, but not limited to, the bent part may have an extension substantially perpendicular to the second annular part of the elastic return device, and in particular substantially parallel to an axis of symmetry of said second annular part;
    - the seal is fitted on the inner peripheral end of the second annular part. The seal thus forms a liner of at least the inner peripheral end of the second annular part of the elastic return device;
    - the seal extends along a radial elongation edge of the second annular part. In other words, the seal extends radially outward beyond the inner peripheral end of the second annular part. This advantageous configuration makes it possible to have a larger seal, covering both the inner end and the adjacent radial elongation edge of the second annular part of the elastic return device, in order to increase the surface of said seal that can be pressed against a facing face and also improve its attachment to the second annular part of said elastic return device;
    - the seal comprises a first seal and a second seal, the second seal extending radially beyond the first seal on the
    -6second annular piece. Each packing of the seal is located against an opposite face of the second annular part of the elastic element, thus forming an external lining of a portion of said second annular part. In other words, the portion of the second annular part of the elastic return device is located in the seal, between the first and second linings;
    - the seal is vulcanized to make it more elastic. In particular, the seal of the elastic return device is obtained by an overmolding process, for example vulcanization. The seal is glued or overmolded or vulcanized on the inner peripheral end of the second annular part;
    - the seal includes a lip. The lip extends projecting from the first and / or second packing of the seal. The lip makes it possible to better control the support of the seal against a face opposite said lip. The lip also makes it possible to improve the seal when there is a relative movement between the seal and the opposite face, in particular of the clutch mechanism, against which it is supported. The lip extends axially in a direction opposite to the first annular part, advantageously beyond the second annular part;
    - The elastic return device according to the first aspect of the invention comprises a centering means intended to collaborate with a complementary centering means of the piston in order to center the elastic return device relative to said piston. According to a first alternative, the centering means takes the form of at least one cylindrical stud of axial extension forming a radial shoulder surface substantially parallel to an axis of symmetry of the elastic return device. According to a second alternative, the centering means takes the form of at least one axial opening formed in the second annular part;
    - The elastic return device according to the first aspect of the invention comprises a fixing means intended to secure the elastic return device to the piston of the clutch mechanism. According to a first alternative, the fixing means takes the form of a first locking means intended to collaborate with a complementary locking means located on the piston. According to a second alternative, the fixing means takes the form of an axial opening located on the second annular part. According to a third alternative, the fixing means takes the form of a rivet, preferably extruded;
    The fixing means is of the detachable type;
    - when the elastic return device according to the first aspect of the invention comprises both a centering means and a fixing means, the centering means is the fixing means. In other words, the centering means and the fixing means are combined;
    - the bent end part of the second annular part extends axially in an opposite direction relative to the first annular part;
    - the plurality of elastic elements is of the coil spring type.
    According to a second aspect, the invention also relates to a clutch mechanism intended to be installed between an engine and a vehicle transmission, which clutch mechanism comprises:
    - a clutch rotating around an axis of rotation;
    - an actuation system arranged to engage or disengage the clutch, said actuation system comprising:
    o a control chamber arranged to receive a pressurized fluid;
    o a balancing chamber delimited in part by a piston, the piston being axially movable and delimiting the control chamber radially outwards by an axial extension surface, said piston extending radially outside said chamber control in order to engage or disengage the clutch under the effect of the pressurized fluid contained in the control chamber;
    o an elastic return device according to the first aspect of the invention or according to any one of its improvements, said elastic return device being housed in the balancing chamber and extending between the piston and a lateral face of the balancing chamber of the clutch mechanism.
    According to its second aspect, the invention thus provides a clutch mechanism in which the sealing of the balancing chamber is ensured by the elastic return device according to the first aspect of the invention. This advantageous configuration simplifies the industrialization methods of such a clutch mechanism and, consequently, reduces manufacturing costs.
    -8In the following description and in the claims, the following terms will be used without limitation and in order to facilitate understanding thereof:
    - "front" or "rear" depending on the direction with respect to an axial orientation determined by the main axis O of rotation of the transmission system, "the rear" designating the part situated to the right of the figures, on the transmission side , and “the front” designating the left part of the figures, on the engine side; and
    - "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 "the exterior »Designating a distal part of the axis O.
    The clutch mechanism according to the second 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 balancing chamber is located opposite the control chamber relative to the piston;
    - the elastic return device is separate from the piston;
    - the bent end part of the elastic return device extends in an axial direction, said bent end part being located radially between an inner end of the piston and a hub supporting the clutch mechanism. This clever configuration allows the sealing gasket located in particular on the bent end part of the elastic return device to be inserted between the piston and the support hub;
    - The seal of the elastic return device is at least partially in abutment against the support hub and against the piston;
    - the seal is axially prestressed between the second annular part and the piston;
    - The seal of the elastic return device is simultaneously in radial support against the support hub and in axial support against the piston. By radial support is meant that the seal of the elastic return device bears against a circumferential bearing against the support hub;
    -9- at the radial elongation edge of the second annular part of the elastic return device, the second seal gasket is interposed between said second annular part and the piston of the clutch mechanism;
    - An axial space is formed between the piston and the second annular part of the elastic return device along which extends the second seal gasket, the axial space, taken along an axial direction, being less than or equal to the thickness of the second seal gasket. This advantageous configuration makes it possible to pinch the second seal against the piston in order to improve the resistance of the seal on the elastic return device on the one hand, and on the other hand to improve the seal between the piston and said elastic return device, and subsequently improve the tightness of the control chamber. According to a first alternative embodiment, the axial space is formed on a part of the piston located opposite the second annular part of the elastic return device along which extends the second seal of the seal. According to a second alternative embodiment, the axial space is formed on an area of the second annular part of the elastic return device along which the second gasket packing extends, said area being located opposite the piston. ;
    - The seal of the elastic return device bears against the support hub at the level of the first lining of said seal;
    - The lip of the seal of the elastic return device is located at an axial end of said seal, the lip being in abutment against the support hub of the clutch mechanism;
    - There is a radial clearance between the second packing of the seal of the elastic return device and an inner radial end of the piston;
    - the elastic return device of the clutch mechanism comprises a centering means collaborating with a complementary centering means of the piston in order to center said elastic return device with respect to said piston. According to a first alternative, the centering means takes the form of a cylindrical surface of axial extension forming a radial shoulder surface substantially parallel to an axis of symmetry of the elastic return device. According to a second alternative, the centering means takes the form of an axial opening formed in the second annular part;
    -10- the elastic return device of the clutch mechanism comprises a fixing means securing the elastic return device to the piston of the clutch mechanism. According to a first alternative, the fixing means takes the form of a first locking means intended to collaborate with a complementary locking means located on the piston. According to a second alternative, the fixing means takes the form of an axial opening located on the second annular part. According to a third alternative, the fixing means takes the form of a rivet, preferably extruded;
    - The fixing means is of the detachable type;
    - When the elastic return device comprises both a centering means and a fixing means, the centering means is the fixing means. In other words, the centering means and the fixing means are combined;
    - The elastic return device comprises a means for centering elastic return device formed by at least one axial opening collaborating with at least one complementary cylindrical stud of axial extension and formed on one face of the piston opposite the elastic return device;
    - The side face of the balancing chamber against which the elastic return device is supported is formed by one face of a clutch disc input of the clutch mechanism located opposite the piston;
    - The clutch mechanism according to the second aspect of the invention is of the multi-disc type;
    - According to a preferred embodiment, the clutch mechanism according to the second aspect of the invention is of the double clutch type and comprising a first clutch controlled by a first actuation system and a second clutch controlled by a second system d actuation. According to a first variant, the first and second clutches are arranged radially, the second clutch being located radially inside the first clutch. According to a second alternative embodiment, the first and second clutches are arranged axially, the second clutch being located axially behind the first clutch.
    According to a third aspect of the invention, there is proposed a transmission system for a motor vehicle comprising a clutch mechanism according to the second aspect of the invention or to any one of its improvements and in which the clutch is coupled in rotation to:
    - an output shaft of the transmission via an input disc holder; and
    - An entry sail, said entry sail being coupled in rotation to an entry shaft driven in rotation by at least one crankshaft of an engine.
    According to a preferred variant embodiment, a transmission system for a motor vehicle is proposed comprising a double clutch mechanism in accordance with the second aspect of the invention and according to its preferred embodiment and in which:
    - the first clutch is rotatably coupled 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 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 appear further 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 perspective view and partially cut away of an elastic return device according to the first aspect of the invention;
    FIG. 2 illustrates a view in axial section of an exemplary embodiment of the clutch mechanism in accordance with the second aspect of the invention;
    - FIGURE 3 illustrates a detailed view of the actuation systems of the clutch mechanism of FIGURE 2
    - FIGURE 4 illustrates a perspective view and partially cut away of the clutch mechanism illustrated in FIGURE 2;
    - FIGURE 5 illustrates a front view of an elastic return device mounted on a piston, seen from a balancing chamber of the clutch mechanism illustrated in FIGURE 2;
    - FIGURE 6A illustrates an axial sectional view along the cutting axis PP shown in FIGURE 5;
    - FIGURE 6B illustrates the detail view Q shown in FIGURE 6A.
    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 FIGURE 1, an exemplary embodiment of an elastic return device 800 in accordance with the first aspect of the invention is shown. Such an elastic return device 800 is configured to be able to generate a force against a piston 105, 205 set in motion by an actuation system 300 of a clutch 100, 200 of a clutch mechanism. To this end, the elastic return device 800 comprises:
    -13- a first annular part 810A intended to bear against a bearing face of the clutch mechanism;
    - A second annular part 820A intended to bear against the piston 105, 205 of the clutch mechanism;
    - A plurality of elastic elements 830A extending between the first annular part 810A and the second annular part 820A. In the example illustrated in FIGURE 1, the plurality of elastic elements 830A is of the type with helical springs, said helical springs being angularly regularly distributed around an axis of symmetry S of the elastic return device 800.
    In particular, the second annular part 820A of the elastic return device 800 comprises at its inner peripheral end 821 IA a seal 402A said second seal 402A. The seal 402A extends axially in a direction opposite to the first annular part 810A relative to the second annular part 820A.
    The second annular part 820 of the elastic return device 800 has an axis of symmetry S. According to the invention, the second annular part 820 is in abutment against a face of the corresponding piston 105, 205, said face being oriented axially opposite of the plurality of elastic elements 830. In the embodiment illustrated in LIGURE 1, the second annular part 820A is formed by a radial elongation edge 821A which extends from the inner peripheral end 821 IA towards a 822A oblique intermediate span. The oblique intermediate bearing 822A is extended radially outwards by an external radial extension bearing 823A which carries at its external end 8231A another seal 403A, called the third seal 403A.
    In the embodiment illustrated in LIGURE 1, the inner peripheral end 821 IA of the second annular part 820A of the elastic return device 800 is located in the radial extension of the radial elongation edge 821A of said second annular part 820A . Alternatively, the inner peripheral end 821 IA of the second annular part 820A can be formed by a bent end part which preferably extends axially in a direction opposite to the first annular part 810A.
    The second annular part 820A also comprises a plurality of openings 860A regularly angularly distributed around the axis of symmetry S. The openings 860A form holes opening out through the second annular part 820A. The openings 860A are intended to allow centering and / or fixing of the elastic return device on the corresponding piston of the clutch mechanism.
    The second seal 402A is advantageously formed by a first lining 4021A situated axially on the side of the first annular part 810A relative to the second annular part 820A, and a second lining 4022A which is situated on the side opposite to the first annular part 810A compared to the second annular part 820A. Thus, the second seal 402A is fixedly attached to the second annular part 820A, and more particularly at its inner peripheral end 821 IA, for example by fitting.
    Advantageously, the second lining 4022A of the second seal 402A extends over the radial elongation edge 821A of the second annular part 820A, radially beyond the first lining 4021A.
    In the embodiment illustrated in LIGURE 1, the second seal 402A comprises a lip 4023 which extends simultaneously radially inside the inner peripheral end 821 IA of the second annular part 820A and axially in a direction opposite to the first annular part 810A relative to the second annular part 820A.
    The elastic return device 800 advantageously comprises a diameter reducer 900 comprising a cylindrical bearing 910 and a radial bearing 920. The cylindrical bearing 910 is in radial contact against a bearing part of the clutch mechanism, for example a second holder output discs 206 as shown in FIGURE 1. The radial bearing 920 of the diameter reducer 900 is advantageously interposed between the first annular part 810A and the bearing part of the clutch mechanism. More particularly, the radial reach 920 of the diameter reducer 900 is in axial abutment against the first annular part 810A.
    Advantageously, the elastic return device 800 also comprises means 850A for fixing the reducer of diameter 900 to the first annular part 810A. in
    -15Γexample illustrated in FIGURE 1, the fixing means 850A are of the type of at least one rivet angularly regularly distributed around the axis of symmetry S. Preferably, the bearing part of the clutch mechanism comprises an opening 2069 located opposite the fixing means 850 of the elastic return device 800.
    Referring to FIGURES 2 to 4, the illustrated embodiment of the clutch mechanism 10 according to the second aspect of the invention is preferably of the wet double clutch type, and preferably still in a so-called radial position, the first clutch 100 being 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. Of course, the invention conforms to its second aspect is not limited to double clutch mechanisms 10 but also includes wet single clutch mechanisms.
    The double clutch mechanism 10 is integrated on a transmission chain 1 comprising a transmission coupled in rotation to the clutch mechanism 100.
    In general, the double clutch mechanism 10 is arranged to be able to couple in rotation an input shaft not shown to a first drive shaft A1 or alternatively to a second drive shaft A2 via the first clutch respectively 100 or the 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 coaxial and intended to be coupled in rotation to the transmission such as for example a gearbox of the type of those fitted to motor vehicles.
    As illustrated in FIGURES 2 to 4, 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 drive shaft A1 is coupled in rotation to the input shaft and driven by it in rotation when the first clutch 100 is configured in a so-called engaged position for which the plurality of first friction elements 101 is coupled in rotation. to the plurality of second friction elements 102. Alternatively, the first transmission 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 to the plurality of second friction elements 102.
    Similarly, the second transmission shaft A2 is coupled in rotation to the input shaft and driven by it in rotation when the second clutch 200 is configured in a engaged position for which the plurality of first friction elements 201 is coupled in rotation with 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 elements friction element 201 is decoupled in rotation to the plurality of second friction elements 202.
    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. In contrast, the first and second clutches 100, 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. of 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. On its internal elongation, the input hub 130 is linked in rotation and / or axially to the input shaft via
    -17de its internal elongation 1301, and possibly via a damping device not shown 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 an interior end 1091 of the input veil 109. The interior end 1091 is located towards the front AV of the 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 comprises 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 external axial elongation span 1061 of a first input disk carriers 106, the first input disk carriers 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 span external axial extension 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 actuation system 300A, 300B is arranged to be able to configure the first clutch 100 and the second clutch 200 respectively 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 the first piston 105 comprising a first radially outer part and a second radially inner part. In general, the first piston 105 is arranged to transmit to the first clutch 100 an axial force El exerted parallel to the axis O via its first radially outer part, its second radially inner part collaborating with a force generator to configure the first clutch 100 in one of the configurations detailed above. At its first radially inner part, the first piston 105 comprises a plurality of first axial extension surfaces 1051 which extend axially towards the front AV in order to be able to press the first friction elements 101 against the second friction elements 102 on the one hand, and against an external reaction means 103 mechanically linked to the entry web 109 on the other hand. When the first friction elements 101 are spaced from the second friction elements 102, then the first clutch 100 is configured in its configuration
    -18 disengaged. 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 metal curved axially forwards AV at its outer radial end.
    The first piston 105 comprises an upper radial extension range 1052 located behind the rear AR of the first axial extension ranges 1051. The first upper radial extension range 1052 extends radially parallel to the transverse axis T from the first clutch 100 to the inner limit of the second clutch 200.
    An intermediate axial extension reach 1053 of the first piston 105, parallel to the longitudinal axis O extends the upper radial extension reach 1052 of the first piston 105 partially under the second clutch 200 and towards the front AV of the double clutch mechanism 10. The intermediate axial extension range 1053 is located radially under the second clutch 200 and axially towards the rear AR.
    Finally, the first piston 105 comprises a first inner radial extension surface 1055 and connected to the intermediate axial extension surface 1053 by means of a first curved zone 1054. The inner radial end of the extension surface inner radial 1055 is located at a distance from a support hub 500 which will be described later.
    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 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 of the first clutch 100 are
    Separate from the second friction elements 102, 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 via 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 has on its outer radial periphery an 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 axial elongation 107 of the first output disc holder 110 is located radially under the first 101 and second 102 friction elements of the first clutch 100. The first output disc holder 110 is thus coupled in rotation by meshing with the second friction elements 102 of the first clutch 100.
    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 a second piston 205.
    The second piston 205 is located axially between a second outlet disc holder 206 and the second clutch 200.
    The second actuation system 300B is linked to the second clutch 200 by means of the second piston 205 comprising a first radially outer part and a second radially inner part. In general, the second piston 205 is arranged to transmit to the second clutch 200 an axial force E2 exerted parallel to the longitudinal axis O via its first radially outer part collaborating with the friction elements 201, 202 of said second clutch 200, and its second radially inner part collaborating with a force generator to configure the second clutch 200 in one of the configurations detailed above. At its first radially inner part, the second piston 205 comprises a plurality of second axial extension surfaces 2051 which extend axially towards the front AV in order to be able to press the first friction elements 201 against the second friction elements 202 on the one hand, and against an internal reaction means 203 of the second clutch 200 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 metal curved axially towards the front AV at its outer radial end.
    The second piston 205 includes an upper radial extension range 2052 located behind the rear AR of the second axial extension ranges 2051. The upper radial extension range 2052 of the second piston 205 is interposed axially between a second input disc port 206 and the second clutch 200. The upper radial extension range 2052 extends radially from the second clutch 200 to the inside of the second clutch 200, and more particularly outside of an intermediate axial extension range 2063 of the second output disc holder 206.
    An intermediate axial extension span 2053 of the second piston 205 extends forwards AV and parallel to the axis O the upper radial extension span 2052 of the second piston 205. The intermediate axial extension span 2053 is located radially to
    -21 inside the second clutch 200 and outside the intermediate axial extension range 2063 of the second output disc holder 206.
    Finally, the second piston 205 comprises a plurality of second internal radial extension surfaces 2055 and connected to the intermediate axial extension surface 2053 via a curved area 2054 of the second piston 205. The curved area 2054 of the second piston 205 takes the form of an "S" in the transverse cutting plane illustrated in FIGURE 2.
    As a nonlimiting example, the second piston 205 can be obtained by stamping.
    The second output disc holder 206 of the double clutch mechanism 10 comprises an external axial elongation part 2061 facing forward AV. The external axial elongation part 2061 of the second output disc holder 206 is located radially outside the second clutch 200, and it extends axially over the entire length of said second clutch 200. The second output disc holder 206 also includes an upper radial extension range 2062 situated behind the rear of the external axial elongation part 2061. The upper radial extension range 2062 extends radially from the outside of the second clutch 200 to the inside the second clutch 200.
    An intermediate axial extension span 2063 of the second output disc carrier 206 extends forwards AV and parallel to the axis O the upper radial extension span
    2062 of the second output disc holder 206. The intermediate axial extension span
    2063 is located radially under the second axial bearing 2053 of the second piston 205.
    Finally, the second output disc holder 206 comprises an internal radial extension range 2065 connected to the intermediate axial extension range 2063 by means of a curved zone 2064. The internal radial end of the range of internal radial extension 2065 is fixed integrally against the support hub 500, for example by welding.
    Thus, the first outlet disc holder 106 and the second outlet disc holder 206 are coupled in rotation by means of the support hub 500: each outlet disc holder 106, 206 is respectively fixed integrally to said support hub 500 by through its inner radial end.
    The internal reaction means 203 is integral with the second input disc holder 206, and more particularly at its external axial elongation part 2061 to which the internal reaction means 203 is fixed by any means, such as by example by welding or riveting. Alternatively, the internal reaction means 203 and the second input disc port 206 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 actuation system 300B exerts an axial force E2 towards the front AV to configure the second clutch 200 in its engaged position. Conversely, when the second piston 205 is pushed backwards AR by elastic return elements which will be described later, then the first friction elements 201 of the second clutch 200 separate from the second friction elements 202, making it possible to decouple said elements friction elements 201, 202 and thus allowing the second clutch 200 to be configured in its disengaged configuration.
    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 has on its outer 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.
    To this end, the second outlet hub 220 comprises at its inner end 2102 axial grooves arranged to cooperate with complementary grooves located on the second drive shaft A2, so as to achieve rotation coupling.
    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 force between the two outlet disc holders 110, 210 which can rotate different speeds when the first and second clutches 100, 200 are configured in a different configuration.
    Preferably, and as illustrated more particularly in FIGURE 3, each actuation system 300A, 300B further comprises an elastic return device 800A, 800B arranged to generate an axial force oriented towards the rear AR and opposing the displacement of the corresponding piston 105, 205 when it is pushed forward AV to engage the corresponding clutch 100, 200.
    In particular, the first elastic return device 800A associated with the first clutch 100 comprises:
    - A first annular part 810A intended to bear against a bearing face of the double clutch mechanism 10, and more particularly at the level of the inner radial extension surface 2065 of the second input disc holder 206;
    - A second annular part 820A intended to bear against the first piston 105, and more particularly at the level of the inner radial extension surface 1055 of said first piston 105;
    - A plurality of elastic elements 83OA extending between the first annular part 810A and the second annular part 820A of the first elastic return device 800A. Advantageously, the plurality of elastic elements 83OA are of the type of the coil spring type.
    Similarly, the second elastic return device 800B associated with the second clutch 200 comprises:
    - A first annular part 810B intended to bear against a bearing face of the double clutch mechanism 10, and more particularly at the level of a liner plate 332 which is locked axially forwards AV by an axial locking ring 333 housed in a circumferential groove on the outer face of the support hub 500;
    - A second annular part 820B intended to bear against the second piston 205, and more particularly at the level of the inner radial extension range 2055 of said second piston 205;
    A plurality of elastic elements 83OB extending between the first annular part 810B and the second annular part 820B of the second elastic return device 800B. Advantageously, the plurality of elastic elements 83OB are of the type of the coil spring type.
    According to the invention taken in its second aspect, each actuation system 300A, 300B of the double clutch mechanism 10 illustrated in FIGURES 2 to 4 comprises:
    - a control chamber 750A, 750B arranged to receive a pressurized fluid;
    a balancing chamber 700A, 700B delimited in part by a piston, the piston being axially movable and delimiting the control chamber radially towards the outside by an axial extension surface, said piston extending radially outside said control chamber in order to engage or disengage the clutch under the effect of the pressurized fluid contained in the control chamber;
    - an elastic return device 800A, 800B as described above, said elastic return device being housed in the corresponding balancing chamber 700A, 700B and extending between the piston 105, 205 and the corresponding bearing face of the mechanism with double clutches 10.
    The control chamber 750A of the first actuation system 300A is arranged to receive a certain volume of hydraulic fluid under pressure in order to generate the axial force El on the internal radial extension range 1055 of the first piston 105 and thus to configure the first clutch 100 in one of the configurations described above. The pressurized hydraulic fluid is advantageously conveyed by means of high-pressure fluidic circulation conduits passing at least partially through the support hub 500 and opening into the control chamber 750A of the first actuation system 300A at an external face of said support hub 500 by a supply duct 5002A.
    The control chamber 750A of the first actuation system 300A is thus advantageously delimited:
    - radially inwards, by a portion of the support hub 500;
    -25- axially towards the rear AR, by a portion of internal radial elongation of the first input disc holder 106;
    - Radially outwards, by the intermediate axial extension surface 1053 and the first curved zone 1054 of the first piston 105; and
    - Axially forwards AV, by the internal radial extension surface 1055 of the first piston 105.
    It will also be noted that the tightness of the control chamber 750A of the first actuation system 300A is guaranteed by the presence:
    - a first seal 401A located between the inner radial part of the first input disc holder 106 and the intermediate axial extension surface 1053 of the first piston 105;
    - A second seal 402A located axially between the inner radial end of the inner radial extension surface 1055 of the first piston 105 and the support hub 500. According to the invention taken according to its first aspect, the second seal 402A is advantageously carried by the elastic return device 800A of the first actuation system 300A, as described in particular through FIGURE 1 for a first embodiment, and as will be described later through of FIGURES 5 and 6.
    The 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 device 800A housed in said balancing chamber 700A. The lubrication fluid is advantageously conveyed by means of low pressure fluidic circulation conduits axially passing through the support hub 500 and opening into the balancing chamber 700A at an external face of said support hub 500 by a supply conduit. 5003A.
    The balancing chamber 700A of the first actuation system 300A is thus advantageously delimited:
    - radially inwards, by a portion of the support hub 500;
    -26- axially towards the rear AR, by the internal radial extension surface 1055 of the first piston 105;
    - Radially outwards, via the intermediate axial extension bearing surface 2063 of the second outlet disc holder 206; and
    - Axially forwards AV, by the internal radial extension surface 2065 of the second output disc holder 206.
    It will also be noted that the tightness of the balancing chamber 700A of the first actuation system 300A is guaranteed by the presence:
    - a third seal 403A which extends between the second annular part 820A of the first elastic return device 800A and an external cylindrical surface 910 of a reducer of diameter 900 housed in the balancing chamber 700A and forming a inner lining of said balancing chamber 700A; and
    - the second seal 402A located axially between the inner radial end of the inner radial extension surface 1055 of the first piston 105 and the support hub 500. According to the invention taken according to its first aspect, the second seal d the seal 402A is carried by the elastic return device 800A of the first actuation system 300A, as described in particular through FIGURE 1 for a first embodiment, and as will be described later through FIGURES 5 and 6.
    In a comparable manner, the control chamber 750B of the second actuation system 300B is arranged to receive a certain volume of hydraulic fluid under pressure in order to generate the axial force E2 on the inner radial extension range 2055 of the second piston 205 and thus configure the second clutch 200 in 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 support hub 500 and opening into the control chamber 750B of the second actuation system 300B at an external face of said support hub 500 by a supply duct 5002B.
    The control chamber 750B of the second actuation system 300B is thus advantageously delimited:
    -27- radially inwards, by a portion of the support hub 500;
    - Axially towards the rear AR, by the internal radial extension surface 2065 of the second input disc holder 206;
    - Radially outwards, by the curved zone 2054 of the second piston 205; and
    - Axially forwards AV, by the radial extension surface 2055 of the second piston 205.
    It will also be noted that the tightness of the control chamber 750B of the second actuation system 300B is guaranteed by the presence:
    - a first seal 401B located between the inner radial extension surface 2065 of the second input disc holder 206 and the curved zone 2054 of the second piston 205;
    - A second seal 402B located axially between the inner radial end of the inner radial extension surface 2055 of the second piston 205 and the support hub 500. According to the invention taken according to its first aspect, the second gasket 402B is advantageously carried by the elastic return device 800B of the second actuation system 300B, as described in particular through FIGURE 1 for a first embodiment, and as will be described later through of FIGURES 5 and 6.
    The 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 device 800B housed in said balancing chamber 700B. The lubrication fluid is advantageously conveyed by means of low pressure fluidic circulation conduits axially passing through the support hub 500 and opening into the balancing chamber 700B of the second actuation system 300B at an external face of said support hub 500 by a supply duct not visible in FIGURES 2 to 4.
    Additionally, the low pressure fluid circulation conduits include a main supply conduit 5001 located at the axial front end AV of the support hub 500. The main supply conduit is radially oriented and allows communication to be established lubrication fluid level with the clutches
    -28100, 200 in order to improve their lubrication during the operation of the double clutch mechanism 10 in accordance with the second aspect of the invention.
    The balancing chamber 700B of the second actuation system 300B is thus advantageously delimited:
    - radially inwards, by a portion of the support hub 500;
    - Axially rearward AR, by the internal radial extension surface 2055 of the second piston 205;
    - radially outward and axially forward AV, by the liner plate 332.
    It will also be noted that the sealing of the balancing chamber 700B of the second actuation system 300B is guaranteed by the presence:
    - a third seal 403B which extends between the second annular part 820B of the second elastic return device 800B and an outer cylindrical surface of the liner plate 332; and
    - the second seal 402B located axially between the inner radial end of the inner radial extension surface 2055 of the second piston 205 and the support hub 500. According to the invention taken according to its first aspect, the second seal d tightness 402B is carried by the elastic return device 800B of the second actuation system 300B, as described in particular through FIGURE 1 for a first embodiment, and as will be described later through FIGURES 5 and 6.
    It will be understood at this stage of the description that, under the effect of the pressurized fluid filling the control chamber 750A, 750B of one of the actuation systems 300A, 300B, the first and second force transmission members 105, 205 are moved axially forward AV according to the axial forces El, E2 in order to respectively configure the first 100 and second 200 clutches in their engaged configuration. Additionally, under the effect of the first and second elastic return devices 800A, 800B housed in the corresponding balancing chambers 700A, 700B, the force transmission members 105, 205 are pushed backwards AR in order to configure the first 100 and second 200 clutches in their disengaged configuration.
    -29The actuating systems 300A, 300B thus form force generators for the force transmission members 105, 205 of the corresponding clutches 100, 200.
    With reference to FIGURES 5 to 6, one of the elastic return devices 800 mounted on one of the pistons 105, 205, seen from one of the balancing chambers 700 of the clutch mechanism 10 according to the second aspect of the invention will now be described in more detail.
    In order to facilitate the understanding of FIGURES 5 and 6, reference will be made to the first elastic return device 800 mounted on the first piston 105, but the technical characteristics described below apply of course to the second elastic return device mounted on the second piston 205.
    The second annular part 820A of the first elastic return device 800A is in axial support against the first piston 105. More particularly, a radial elongation edge 821A of the second annular part 820A is in axial support against the inner radial extension range 1055 of the first piston 105. In particular, the second annular part 820 is - by means of its radial elongation edge 821A - resting against one face of the inner radial extension surface 1055 of the first piston 105 oriented axially in look of the plurality of elastic elements 830.
    The second annular part 820 is coaxial with axis O with the first piston 105. The second annular part 820A is formed by the radial elongation edge 821A which extends from an inner peripheral end 8211A towards an oblique intermediate surface 822A which s 'extends axially in a direction opposite to the first piston 105, towards the inside of the balancing chamber. The oblique intermediate bearing 822A is extended radially outwards by an external radial extension bearing 823A which carries at its external end 8231A another seal 403A, called the third seal 403A.
    The inner peripheral end 8211A of the second annular part 820A is bent and extends substantially perpendicular to the radial elongation edge 821 A, in an opposite direction relative to the upper radial end 8231 A. more particularly , the inner peripheral end 821 IA forms a bend which extends axially in the direction of the first piston 105. Radially, the inner peripheral end
    -30821 IA is located inside the first piston 105, so that there is a radial clearance between the inner peripheral end 821 IA bent of the second annular part 820A and an inner radial end of the radial extension surface interior 1055 of the first piston 105.
    The second annular part 820A comprises at its inner peripheral end 8211A a seal 402A called the second seal 402A. The second seal 402A is advantageously formed by a first lining 4021A situated axially opposite the first piston 105 relative to the second annular part 820A, and a second lining 4022A which is situated on the side of said first piston 105. Thus , the second seal 402A is fixedly attached to the second annular part 820A, and more particularly at its inner peripheral end 821 IA, for example by fitting, by vulcanization, by overmolding or by gluing.
    Advantageously, the second lining 4022A of the second seal 402A extends over the radial elongation edge 821A of the second annular part 820A, radially beyond the first lining 4021A.
    The second seal 402A also comprises a lip 4023A which extends simultaneously radially inside the inner peripheral end 821 IA of the second annular part 820A and axially in a direction opposite to the outer radial end 8231A by relative to the radial elongation edge 821A of the second annular part 820A.
    Radially, the part of the second lining 4022A of the second seal 402A located on the bent part of the inner peripheral end 821 IA of the second annular part 820A is located inside the first piston 105, so that there is a radial clearance D between the second lining 4022A and the inner radial end of the inner radial extension surface 1055 of the first piston 105.
    On the other hand, axially, the part of the second lining 4022A of the second seal 402A located on the radial elongation edge 821A of the second annular part 820A is in abutment against the first piston 105. Preferably still, the part of the second seal 4022A of the second seal 402A located on the radial elongation edge 821A of the second annular part 820A is pinched between the bearing
    -31 of internal radial extension 1055 of the first piston 105 and the radial elongation edge 821A of the second annular part 820A. To do this, an axial space X, taken along an axial direction, is less than or equal to the thickness of the second seal 4022A of the second seal 402A. In the example illustrated in FIGURE 6B, the inner radial end of the inner radial extension surface 1055 of the first piston 105 is axially deformed in the direction opposite to the second annular part 820A in order to achieve such a pinch. The seal is thus axially prestressed between the second annular part and the corresponding piston.
    The second lining 4022A of the second seal 402A is pinched between the inner radial extension surface 1055 of the first piston 105 and the radial elongation edge 821A of the second annular part 820A can be achieved by any other means, such as as for example by means of local machining of one face of the inner radial extension surface 1055 of the first piston 105 situated opposite the second annular part 820A. Alternatively, the pinching can also be achieved by local deformation of one face of the radial extension edge 821A of the second annular part 820A located opposite the first piston 105, or even by machining.
    Advantageously, the first elastic return device 800A comprises a centering means 860A collaborating with a complementary centering means 1050 located on the first piston 105, in order to make said first elastic return device 800A coaxial with said first piston 105. More in particular, the centering means 860A of the first elastic return device 800A is formed by an axial opening 860A located on the radial elongation edge 821A, and the complementary centering means 1050 of the first piston 105 is formed by a cylindrical stud of axial extension 1050 carried by a face of the first piston 105 situated opposite the second annular part 820A.
    Preferably, the second annular part 820A comprises a plurality of axial openings 860A collectively forming the centering means, said plurality of axial openings 860A being angularly regularly distributed around the longitudinal axis O. In addition, the first piston 105 preferably comprises a plurality of cylindrical studs with axial extension 1050, said plurality of cylindrical studs 1050 being angularly regularly distributed around the longitudinal axis O.
    The axial opening 860A of the second annular part 820A is advantageously of a diameter greater than or equal to the diameter of the cylindrical stud 1050 of the first piston 105, so that said cylindrical stud 1050 collaborates with the axial opening 860A by fitting , preferably without play, possibly in force.
    The cylindrical stud 1050 can be produced by specific machining of the first piston 105, or by stamping, for example.
    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 (5)
    [1" id="c-fr-0001]
    Claims
    1. elastic return device (800) for a wet clutch mechanism (10), said elastic return device (800) being intended to generate a force against a piston (105, 205) set in motion by a system for actuating a clutch of the clutch mechanism (10), said elastic return device (800) comprising:
    - A first annular part (810) intended to bear against a bearing face of the clutch mechanism (10);
    - a second annular part (820) intended to bear against the piston (105, 205) of the clutch mechanism (10);
    - a plurality of elastic elements (830) extending between the first annular part (810) and the second annular part (820);
    characterized in that the second annular part (820) comprises at its inner peripheral end (8211) a seal (402), and in that the second annular part (820) is pressed against one face of the piston (105 , 205) oriented axially opposite the plurality of elastic elements (830).
    [2" id="c-fr-0002]
    2. elastic return device (800) according to the preceding claim, wherein the inner peripheral end (8211) of the second annular part (820) is formed by a bent end portion.
    [3" id="c-fr-0003]
    3. Elastic return device (800) according to the preceding claim wherein the bent end portion (8211) of the second annular part (820) extends axially in an opposite direction relative to the first annular part (810).
    [4" id="c-fr-0004]
    4. Elastic return device (800) according to any one of the preceding claims, in which the seal (402) is fitted on the inner peripheral end (8211) of the second annular part (820).
    -345. Elastic return device (800) according to any one of the preceding claims, in which the seal (402) extends along an edge of radial extension (821) of the second annular part (820) .
    6. elastic return device (800) according to the preceding claim, in which the seal comprises a first lining (4021) and a second lining (4022), the second lining (4022) extending radially beyond the first lining (4021) on the second annular part (820).
    7. Elastic return device (800) according to any one of the preceding claims, in which the seal (402) comprises a lip (4023).
    8. Elastic return device (800) according to any one of the preceding claims, in which the plurality of elastic elements (830) is of the helical spring type.
    9. Clutch mechanism (10) intended to be installed between an engine and a vehicle transmission, which clutch mechanism (10) comprises:
    - a clutch (100, 200) rotating around an axis of rotation (O);
    - an actuation system (300) arranged to engage or disengage the clutch (100, 200), said actuation system (300) comprising:
    o a control chamber (750) arranged to receive a pressurized fluid; o a balancing chamber (700) delimited in part by a piston (105, 205), the piston (105, 205) being axially movable and delimiting the control chamber (750) radially outwards by a range of axial extension (1053, 2053), said piston (105, 205) extending radially outside said control chamber (750) in order to engage or disengage the clutch (100, 200) under the effect pressurized fluid contained in the control chamber (750);
    an elastic return device (800) according to any one of the preceding claims, said elastic return device (800) being housed in the balancing chamber (700) and extending between the piston (105, 205) and a side face of the balancing chamber (700).
    -3510. Clutch mechanism (10) according to the preceding claim taken in combination with the elastic return device (800) according to claim 2, wherein the bent end portion (8211) of the elastic return device (800) extends in a axial direction, said bent end portion (8211) being located radially between an inner end of the piston (105, 205) and a hub supporting the clutch mechanism (10).
    11. Clutch mechanism (10) according to the preceding claim, in which the seal (402) of the elastic return device (800) is at least partially in abutment against the support hub (500) and against the piston. (105, 205).
    12. Clutch mechanism (10) according to the preceding claim taken in combination with the elastic return device (800) according to claim 6, wherein, at the level of the radial elongation edge (821) of the second annular part ( 820) of the elastic return device (800), the second lining (4022) of the seal (402) is interposed between said second annular part (820) and the piston (105, 205) of the clutch mechanism (10 ).
    13. Clutch mechanism (10) according to the preceding claim, in which an axial space (X) is formed between the piston (105, 205) and the second annular part (820) of the elastic return device (800), the along which extends the second seal gasket, the axial space (X), taken along an axial direction, being less than or equal to the thickness of the second gasket (4022) sealing (402).
    14. Clutch mechanism (10) according to any one of claims 9 to 13, in which the elastic return device (800) comprises a centering means formed by at least one axial opening (860) collaborating with at least one complementary cylindrical pad with axial extension (1050) and formed on one face of the piston (105, 205) opposite the elastic return device (800).
    15. Clutch mechanism (10) according to any one of claims 9 to 14, wherein the lateral face of the balancing chamber (700) against which the device
    -36 elastic return (800) is supported is formed by one face of an input disc holder (106, 206) of the clutch mechanism (10) located opposite the piston (105, 205).
    16. Clutch mechanism (10) according to any one of claims 9 to 15, which clutch mechanism (10) is of the double clutch type and comprising a first
    [5" id="c-fr-0005]
    5 clutch (100) controlled by a first actuation system (300A) and a second clutch (200) controlled by a second actuation system (300B).
    1/5
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    FR3102815A1|2021-05-07|MULTIDISC CLUTCH MECHANISM INCLUDING IMPROVED SEALING
    FR3058488A1|2018-05-11|COMPACT DOUBLE CLUTCH MECHANISM AND TRANSMISSION SYSTEM COMPRISING SUCH A DOUBLE CLUTCH MECHANISM
    FR3085731A1|2020-03-13|DOUBLE CLUTCH MECHANISM
    FR3066569A1|2018-11-23|DOUBLE CLUTCH MECHANISM
    同族专利:
    公开号 | 公开日
    US20180245643A1|2018-08-30|
    CN108506361A|2018-09-07|
    EP3366938A1|2018-08-29|
    EP3366938B1|2020-11-18|
    KR20180099552A|2018-09-05|
    FR3063322B1|2021-04-23|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    WO2008033701A1|2006-09-15|2008-03-20|Borgwarner, Inc.|Flexplate coupling for a wet clutch transmission|
    DE102008028560A1|2007-07-02|2009-01-08|Luk Lamellen Und Kupplungsbau Beteiligungs Kg|Sealing arrangement for a double-clutch arrangement comprises chambers each sealed via two separate sealing elements which are vulcanized to a sealing support and connected to each other via a flat seal|
    DE102011006027A1|2011-03-24|2012-09-27|Zf Friedrichshafen Ag|Clutch i.e. wet running dual clutch, for transferring torque from drive unit to transmission in drive train of motor car, has ribs arranged such that oil is guided in direction of clutch arrangement after attachment of bearings to hub|
    DE102012023721A1|2012-12-05|2014-06-05|Borg Warner Inc.|Torsional vibration damper for drive train of motor vehicle, has coupling unit that is movable to open state, where counteracting frictional moment is lower in open state than in closed state and coupling unit is biased in closed state|
    DE102014014985A1|2014-02-25|2015-08-27|Borgwarner Inc.|Concentric double clutch device|
    DE102014212701A1|2014-07-01|2016-01-07|Dichtungstechnik G. Bruss Gmbh & Co. Kg|Device for actuating a clutch in a hydraulic system and method for producing such a device|
    DE102008060580B4|2008-06-03|2021-01-21|Borgwarner Inc.|Multiple coupling device with two pressure equalization chambers|
    DE102014102515A1|2014-02-26|2015-08-27|Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg|Spring package, clutch and clutch manufacturing process|KR102186977B1|2018-12-19|2020-12-04|주식회사 카펙발레오|Clutch device|
    JP2020133815A|2019-02-22|2020-08-31|株式会社エクセディ|Lockup device|
    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|
    FR3095021A1|2019-04-09|2020-10-16|Valeo Embrayages|WET CLUTCH MECHANISM INCLUDING IMPROVED SEALING|
    KR102240176B1|2019-08-02|2021-04-13|주식회사 카펙발레오|Dual Clutch Apparatus|
    法律状态:
    2018-02-26| PLFP| Fee payment|Year of fee payment: 2 |
    2018-08-31| PLSC| Search report ready|Effective date: 20180831 |
    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
    FR1751607A|FR3063322B1|2017-02-28|2017-02-28|ELASTIC RETURN DEVICE FOR WET CLUTCH MECHANISM AND WET CLUTCH INCLUDING SUCH AN ELASTIC RETURN DEVICE|
    FR1751607|2017-02-28|FR1751607A| FR3063322B1|2017-02-28|2017-02-28|ELASTIC RETURN DEVICE FOR WET CLUTCH MECHANISM AND WET CLUTCH INCLUDING SUCH AN ELASTIC RETURN DEVICE|
    EP18158271.9A| EP3366938B1|2017-02-28|2018-02-23|Elastic return device for a wet clutch mechanism and wet clutch comprising such an elastic return device|
    CN201810163675.6A| CN108506361A|2017-02-28|2018-02-27|Elastic retraction means and wet clutch for wet clutch mechanism|
    KR1020180023997A| KR20180099552A|2017-02-28|2018-02-27|Elastic return device for a wet clutch mechanism and wet clutch comprising such an elastic return device|
    US15/906,801| US20180245643A1|2017-02-28|2018-02-27|Elastic return device for a wet clutch mechanism and wet clutch comprising such an elastic return device|
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