• 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 wet clutch (1) comprising two clutches (4, 5), each clutch (4, 5) comprising an inlet disk carrier (8, 9); an output disk carrier (15, 30); a multi-disk assembly (10, 11); and a movable force transmitting member (25, 38) which is adapted to move the multi-disc assembly (10, 11) from its disengaged position to its engaged position; the double clutch further comprising a control system (21) comprising: a housing (41) for attachment to the gearbox and having an inner tube (42) extending axially about the X axis; a first and a second annular piston (45, 46) respectively carrying a first and a second rotary stop (49, 50) cooperating respectively with the force transmission member (25, 38) of one and the other of the two clutches (4, 5); said double clutch being remarkable in that the input disk carriers (8, 9) of the two clutches (4, 5) are rotatably mounted about the X axis on the inner tube (42) of the control system (21 ) with a bearing (20).
    公开号:FR3049023A1
    申请号:FR1652226
    申请日:2016-03-16
    公开日:2017-09-22
    发明作者:Arnaud Dole；Francois Thibaut
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    DOUBLE WET CLUTCH SUPPORTED ON ITS SYSTEM
    ORDERED
    TECHNICAL FIELD The invention relates to the field of transmissions for a motor vehicle. The invention relates more particularly to a double wet clutch intended to be arranged, in a transmission chain of a motor vehicle, between an engine block and a gearbox comprising two input shafts.
    Technological background
    A wet double clutch comprises an input hub intended to be secured in rotation to a flywheel attached to the crankshaft of the engine and two clutches each having an inlet disk holder rotatably connected to the input hub, a disk holder an output shaft rotatably connected to one or both of the input shafts of a gearbox and a multi-disk assembly for transmitting torque between the input disk carrier and the disk carrier of output of said clutch when said clutch is in its engaged position. One of the input shafts of the gearbox, rotatably connected to the output disk carrier of one of the clutches, corresponds to the odd gearbox ratios while the other input shaft is connected in rotation to the output disk carrier of the other clutch, corresponds to even reports. Thus, to effect a shift, one of the clutches is moved from its engaged position to its disengaged position while the other clutch is moved from its disengaged position to its engaged position. Such a double clutch thus makes it possible to change speed ratio without breaking torque.
    It is known from the state of the art, and particularly from US20150219167, such a double wet clutch in which the input disk carriers are supported by a hub which is rotatably mounted on a control shaft fixed on the casing. of the gearbox. Each of the clutches is controlled by a respective piston which is axially movably mounted on the hub between a disengaged position and an engaged position in which it presses the disks of the multi-disk assembly of said clutch against each other in order to transmit a torque between the clutches. respective input and output disk carriers. Each of the pistons is disposed between an activation chamber, which when pressurized moves the piston from its disengaged position to its engaged position, and a balancing chamber that compensates for the dynamic pressure induced by the piston. centrifugal force. The control shaft has a plurality of oil supply channels each connected with one or more respective holes in the hub; said holes each opening into one of the activation or balancing chambers. Dynamic sealing seals are arranged between the control shaft and the hub and allow the channels of the control shaft to be sealed. In addition, the clearing chambers allow the flow of fluid to the multi-disk assemblies so as to ensure lubrication and cooling of said multi-disk assemblies.
    Such a double clutch is not completely satisfactory since the presence of dynamic sealing seals, has the effect of generating friction that induce a drag torque responsible for a surplus of energy consumption.
    It is also known, and in particular DE102014212805, double wet clutches which are actuated by means of a hydraulic control system comprising, a housing, intended to be fixed on the gearbox, having two concentric annular chambers and two pistons annular axially movable respectively in one and the other of the two annular chambers. Each of the pistons carries a rotating stop which is in abutment against a force transmission member cooperating with one or the other of the two clutches so as to move said clutch between a disengaged position and a position engaged during the movement of the piston. inside its respective annular chamber. Such a control system limits the drag torque and therefore provides satisfactory energy consumption performance. However, the input disk carriers are rotatably mounted via a rolling bearing on an output hub of the output disk carrier of one of the clutches, said output means being mounted on one of the input shafts of the gearbox. Such support of the input disk carriers is not completely satisfactory because the rolling bearing ensuring their support is subjected to axial and / or radial displacements of the input shaft of the gearbox, which is night at its service life. summary
    An idea underlying the invention is to overcome the disadvantages of the prior art by providing a double wet clutch with low energy consumption and ensuring a simple and reliable support.
    According to one embodiment, the invention provides a double wet clutch intended to be arranged in a motor vehicle chain, between a motor having a crankshaft and a gearbox comprising two input coaxial shafts extending in a direction X axis, said double wet clutch comprising two clutches which are respectively capable of transmitting a torque of the crankshaft towards one and the other of the two input shafts of the gearbox, each clutch comprising: a disk holder; inlet intended to be coupled in rotation to the crankshaft; an output disk carrier intended to be coupled in rotation to one or the other of the two input shafts of the gearbox; a multi-disk assembly comprising at least one friction disc integral in rotation with one of the inlet and outlet disk carriers and at least two plates respectively arranged on either side of each friction disk, integral in rotation on the other hand input and output disc carriers, and movable axially between a disengaged position and an engaged position in which said trays pinch said friction disc so as to transmit a torque between the input disk carrier and the output disc holder; and - a movable force transmission member which is adapted to move the multiisque assembly from its disengaged position to its engaged position; said double wet clutch further comprising a control system comprising: - a casing intended to be fixed on the gearbox, said casing comprising an inner tube extending axially about the X axis and providing an internal space intended for the passage two input shafts of the gearbox; - A first and a second annular pistons which are mounted to slide axially on the housing, outside the inner tube and respectively carry a first and a second rotary stops; the first and second rotary stops cooperating respectively with the force transmission member of one and the other of the two clutches and being movable between a rest position and an active position respectively corresponding to a disengaged position and a position engaged with said clutch; said double clutch being remarkable in that the input disc holders of the two clutches are rotatably mounted about the X axis on the inner tube of the control system via a bearing. Therefore, such a wet double clutch does not require the presence of dynamic seals, which limits the drag torque and, therefore, to limit the energy consumption of the engine.
    In addition, the input disk carriers being supported on the control system, intended to be fixed on the gearbox, the bearing is mounted on a stable and rigid element which is not subjected to axial movements and / or radial, which ensures a stability of the double clutch and a greater reliability of the bearing.
    In addition, the bearing being mounted on an inner tube having a relatively small diameter, the diameter of the bearing is limited, which reduces its cost, especially if it is a rolling bearing.
    According to other advantageous embodiments, such a double wet clutch can have one or more of the following characteristics.
    According to one embodiment, the inner tube is made of material, that is to say formed integrally with the housing.
    The entry disc carriers of the two clutches are fixed to each other.
    According to one embodiment, the bearing is a rolling bearing.
    According to one embodiment, the rolling bearing comprises an inner ring which is mounted around the inner tube, an outer ring mounted inside an inlet disk holder housing of one of the clutches and the bodies. rollers interposed between the inner ring and the outer ring.
    According to one embodiment, the inner ring is retained on the inner tube in a direction opposite to the control system by an elastic ring which is mounted in a groove on the inner tube.
    According to another embodiment, the ring is retained by a shoulder formed directly on the inner tube.
    According to one embodiment, the inner tube is secured axially with the housing so that the axial clutch forces exerted by the annular pistons are taken directly by the housing.
    According to one embodiment, the rolling bearing is angular contact. Advantageously, the recovery of the axial forces exerted by the annular pistons is done by the oblique contacts of the rolling bearing and the elastic ring, which releases a radial passage for the cooling fluid between the input disk carrier and one of the output disc holders.
    According to one embodiment, the bearing is mounted on a bearing surface of the inner tube, said bearing surface being positioned, in the direction of the two clutches, beyond the races of the first and second annular pistons between their rest position and their position. active position, at least as long as the friction linings of the multi-disk assemblies are not worn.
    According to one embodiment, the double clutch comprises an inlet hub comprising splines intended to cooperate with complementary splines of an element attached to the crankshaft of the engine, such as a flywheel. The input disk carriers are attached to the input hub, for example via an inlet web.
    According to one embodiment, the input disk carriers are arranged radially outside the outlet disk holder of their respective clutch.
    According to one embodiment, each input or output disk carrier comprises a cylindrical skirt; each friction disk or plate being axially movably mounted on the cylindrical skirt of one of the output or inlet disk carriers and integrally in rotation with the latter and in which one of the disk carriers of inlet comprises a support portion directed radially inwardly from an edge of its cylindrical skirt directed towards the control system; said support portion having a radially inner edge cooperating with the bearing.
    According to one embodiment, the two clutches are arranged radially one inside the other, which limits the axial size of the double clutch.
    According to one embodiment, the multi-disk assembly of one of the clutches is disposed radially inside the multi-disk assembly of the other clutch and the bearing is disposed radially inside the multi-disk assemblies of the clutches.
    According to one embodiment, the support portion has an inner zone that is folded in a direction opposite to the control system, within the multi-disk assemblies.
    According to one embodiment, the force transmission member of each of the clutches has an outer periphery equipped with a plurality of axially oriented fingers each passing through the support portion through a respective opening; said fingers being in abutment against the multi-disk assembly of said clutch.
    According to one embodiment, each of the force transmission members comprises an inner portion having an axial recess towards the two clutches inside which are at least partially housed the first and second annular pistons of the control system. Such an arrangement also contributes to increasing the axial compactness of the double clutch.
    According to one embodiment, the inner tube has at least one channel for passing a cooling fluid for conducting said cooling fluid to the clutches. Thus, the clutch cooling circuit is integrated with the dual clutch control system, which reduces the number of wet double clutch components, reduces its size and contributes to increasing the standardization of its components.
    According to one embodiment, the passage channel of a cooling fluid has an outlet opening opening axially beyond the races of the first and second annular pistons between their rest position and their active position.
    According to one embodiment, the outlet orifice is oriented radially.
    According to one embodiment, the cooling fluid passage channel has an outlet opening opening axially between the input disk carrier and the force transmission member.
    According to another embodiment, the cooling fluid passage channel has an outlet opening opening axially between the input disk carrier and one of the output disk carriers.
    According to another embodiment, the passage channel of the cooling fluid has an opening opening in a plane perpendicular to the X axis, said plane being secant with one of the cylindrical skirts of the output disk carriers.
    According to one embodiment, the inner tube comprises a plurality of cooling fluid passage channels distributed circumferentially around the X axis.
    According to one embodiment, the two clutches are arranged radially one inside the other and the cooling fluid passage channel has an outlet opening radially inside the two clutches.
    According to one embodiment, the passage channel of a cooling fluid has an outlet orifice which is formed in a portion of the inner tube which is arranged axially between the bearing which supports the entry disc holders of the two clutches and the first and second annular pistons of the control system; the inner zone of the support portion having orifices distributed circumferentially around the X axis and intended to allow circulation of the cooling fluid.
    According to another embodiment, the channel for passing a cooling fluid has an outlet orifice which is formed in a portion of the inner tube extending axially beyond the bearing which supports the inlet disk carriers of the two clutches.
    According to one embodiment, the inlet disk carrier and the outlet disk carrier of each of the clutches comprise radial orifices distributed circumferentially around the axis X and intended to allow circulation of the cooling fluid radially towards the outside through the multiisque assembly of each of the clutches from the coolant passage channel.
    According to one embodiment, the housing comprises a first and a second annular chambers and the first and the second annular pistons are respectively movable inside the first and second annular chambers.
    According to one embodiment, the invention also provides a motor vehicle comprising a double clutch of the aforementioned type.
    BRIEF DESCRIPTION OF THE DRAWINGS The invention will be better understood, and other objects, details, features and advantages thereof will become more clearly apparent from the following description of several particular embodiments of the invention, given solely for the purposes of the invention. illustrative and not limiting, with reference to the accompanying drawings. - Figure 1 is a partial sectional view of a double wet clutch, according to a first embodiment. - Figure 2 is a half-sectional view of a double wet clutch according to another embodiment. - Figure 3 is a rear view of the double wet clutch of Figure 1.
    Detailed description of embodiments
    In the description and the claims, the terms "external" and "internal" as well as the "axial" and "radial" orientations will be used to designate, according to the definitions given in the description, elements of the double clutch. By convention, the "radial" orientation is directed orthogonally to the X axis of rotation of the double clutch determining the "axial" orientation and, from the inside towards the outside away from said axis, the orientation " circumferential "is orthogonal to the X axis and orthogonal to the radial direction. The terms "external" and "internal" are used to define the relative position of one element relative to another, with reference to the X axis, an element close to the X axis is thus described as internal by opposition an outer member located radially peripherally. Furthermore, the terms "rear" AR and "front" AV are used to define the relative position of one element relative to another in the axial direction, an element intended to be placed close to the engine being designated by before and an element intended to be placed close to the gearbox being designated by the rear
    In connection with Figure 1, there is a dual clutch 1 which is intended to be disposed between an engine block and a gearbox. Such a double clutch 1 is intended to transmit a torque of the crankshaft of the heat engine selectively to one or the other of the two shafts 2, 3 coaxial input of the gearbox. The shaft 2, inside, passes through the housing of the gearbox and extends longitudinally along the axis X. The shaft 3, hollow, also passes through the housing of the gearbox and surrounds the inner shaft 2. The double clutch 1 comprises two clutches 4, 5 which are each intended to temporarily couple the crankshaft of the engine to one of the shafts 2, 3 input of the gearbox. One of the input shafts 2, 3 of the gearbox corresponds to certain gear ratios, for example the odd-speed gears and the reverse gear, and the other corresponds to the other gears, for example example even gear ratios. Thus, to effect a change of speed ratio, one of the clutches 4, 5 is moved from its engaged position to its disengaged position while the other clutch 4, 5 is moved from its disengaged position to its engaged position, so that the engine torque is progressively transferred from one to the other of the clutches 4, 5. Such a double clutch 1 thus makes it possible to change the speed ratio, without breaking the torque, that is to say while maintaining the transmission engine torque to the wheels of the vehicle.
    The double clutch 1 comprises an inlet hub 6 which has external splines intended to cooperate with complementary splines formed on an element fixed to the crankshaft of the heat engine, such as a flywheel, single or double, not shown.
    The dual clutch 1 is intended to be housed in a clutch housing, not shown, which is fixed on the gearbox. The clutch housing is closed forward by means of a closing cap, not shown, which is guided in rotation on the outer cylindrical surface of the inlet hub 6 by means of a bearing, not shown. The closure cap carries at its outer periphery an annular seal which cooperates with the inner surface of the clutch housing to seal the double clutch 1.
    The double clutch 1 also comprises an inlet web 7 which is welded to the inlet hub 6 or formed integrally therewith. The entry web is rotatably connected to an input disk carrier of each of the two clutches 4, 5.
    The two clutches 4, 5 each comprise a multidisk assembly 10, 11, that is to say an axial stack of friction discs and trays. The multi-disk assemblies 10, 11 of one and the other of the two clutches are arranged radially one inside the other, so as to limit the axial size of the double clutch 1.
    The first clutch 4, that is to say the clutch whose multi-disk assembly 10 is radially outside that of the other clutch 5, comprises an inlet disk carrier 8 which is fixed on the 7. To this end, the inlet web 7 has on its outer periphery an external toothing 12 which cooperates with an internal toothing 13 formed on the inner surface of the inlet disk holder 8 of the first clutch 4 of FIG. in order to join the inlet web 7 in rotation to said inlet disk carrier 8. Furthermore, the inlet web 7 is retained axially rearwardly relative to the inlet disk carrier 8 of the first clutch 4 by means of a stop ring 14. The stop ring 14 is for example an elastic coupling rod which is housed in a groove formed at the front end of the inlet disk holder 8 of the first clutch 4.
    The first clutch 4 also includes an output disc holder 15 which is attached to or integrally formed with an outlet hub 16. The output hub 16 is splined and cooperates with complementary splines formed on the outer periphery of the end of one of the input shafts of the gearbox, here the inner shaft 2. Thus, the output hub 16 of the output disk carrier 15 is integral in rotation with the inner shaft 2. The output hub 16 has, at the front, on its outer periphery a shoulder defining an axial bearing surface for a bearing 17. The bearing 17 also cooperates with a shoulder formed on the inner periphery of the inlet hub 6 and defining an axial bearing surface for said bearing 17. The bearing 17 thus ensures the axial positioning of the output disk carrier 15 the first clutch 4 with respect to the inlet web 7. The bearing 17 is for example a rolling bearing.
    The inlet disk holder 8 comprises a cylindrical skirt 18 of axial orientation in which is provided an internal toothing and a support portion 19 of annular shape which extends radially inwards from the rear end of the cylindrical skirt 18. The support portion 19 and the cylindrical skirt 18 may be formed in one piece, in the same sheet, as in the embodiment shown, or be formed of two separate pieces attached to each other. 'other. The inlet disk holder 8 is rotatably mounted on the hydraulic control system 21 via a bearing 20, described in more detail below, which cooperates on the one hand with the control system 21 and on the other hand with the radially inner edge of the support portion 19. Advantageously, in order to limit the axial size of the double clutch, the support portion 19 of the input disk carrier 8 comprises an external zone 19a which has a radial orientation and is arranged at the rear of the multi-disk assemblies 10, 11 of the two clutches 4, 5 and an inner zone 19b which is folded forward and thus extends radially inside the multi-disk assemblies 10, 11.
    The output disc holder 15 comprises a cylindrical skirt 22 of axial orientation which is arranged radially inside the cylindrical skirt 18 of the input disc holder 8 and in which is provided an external toothing. The outlet disc holder 15 also has a radially oriented portion 23 which extends radially from the front end of the cylindrical skirt 22 of the output disc holder 15 to the outlet hub 16. The multi-disc assembly 10 comprises a plurality of annular plates, of steel for example, which are integral in rotation with the input disk holder 8 and axially slidably mounted relative to said input disk holder 8. To this end, each plate comprises on its external periphery an external toothing which is in engagement with the internal toothing formed on the internal face of the cylindrical skirt 18 of the input disc holder 8. The multi-disc assembly 10 further comprises a plurality of friction discs which are each interposed between two plates and are integral in rotation with the output disk carrier 15 with an axial translation freedom. To do this, each friction disc has on its inner periphery an internal toothing which is engaged with the external toothing carried by the cylindrical skirt 22 of the output disc holder 15. Each friction disc has friction linings disposed on each of its faces, front and back. The multi-disk assembly 10 is supported forwards against a reaction zone formed on the inlet web 7. In the embodiment shown, the reaction zone is formed by means of an annular flange 24 formed in the vicinity of the outer periphery of the inlet web 7. Furthermore, the plate disposed at the rear end of the multi-disk assembly 10 cooperates with a force transmission member 25. The force transmission member 25 is slidably mounted axially and cooperates with the hydraulic control system 21, described in more detail later, which is adapted to axially slide the force transmission member 25 forward to move the first clutch 4 from its disengaged position towards its engaged position. The force transmission member 25 here consists of a metal sheet which comprises at its outer periphery a plurality of fingers 26 of axial orientation, regularly distributed about the axis X. As shown in Figure 3, each finger 26 passes through the support portion 19 of the input disk carrier 8 through a dedicated opening 27. Returning to FIG. 1, it can be seen that each finger 26 is thus in abutment with the plate disposed at the rear end of the multi-disk assembly 10 of the first clutch 4.
    To move the first clutch 4 from its disengaged position to its engaged position, the force transmission member 25 is moved forward so that each of the friction discs is clamped between two plates and the torque is thus transmitted between the input disk carrier 8 and the output disk carrier 15 and therefore between the crankshaft of the engine and the input shaft 2 of the gearbox. Conversely, when the force transmission member 25 is no longer forced forward, the friction discs and trays find their disengaged position in which they are spaced axially from each other. In order to facilitate the return of the friction discs and plates to their disengaged position, corrugated elastic washers, not shown, are interposed between the plates. In each gap between two adjacent plates, a spring washer is disposed radially outside the friction disc located in said gap.
    In order to limit the axial size of the double clutch 1, the force transmission member 25 comprises at its inner portion an axial recess 28 forwards inside which is, at least partly, housed the system. hydraulic control 21.
    The second clutch 5, that is to say the clutch whose multi-plate assembly 11 is disposed radially inside that of the other clutch 4, has a similar structure to the first clutch. The second clutch 5 comprises an inlet disk carrier 9 integral in rotation with the inlet web 7. To do this, the inlet disk carrier 9 of the second clutch 5 is fixed, for example by welding, to the portion of support 19 of the input disk carrier 8 of the first clutch 4. The input disk carrier 9 has a cylindrical skirt 29 of axial orientation which is arranged radially inside the cylindrical skirt 22 of the output disk carrier 15 of the first clutch 4. The cylindrical skirt 29 has an internal toothing.
    The second clutch 5 also includes an outlet disk carrier 30 which is attached to or is integrally formed with an outlet hub 31. The outlet hub 31 has internal splines which cooperate with complementary splines formed on the outer periphery of the end of one of the input shafts of the gearbox, here the outer shaft 3. In order to ensure the axial positioning of the output disk carrier 30, a first axial bearing 32 is interposed between the output hub 16 of the first clutch 4 and the output hub 31 of the second clutch 5 and a second axial bearing 33 is interposed between the hub of output 31 of the second clutch 5 and an inner tube 42 of the hydraulic control system 21.
    The outlet disc holder 30 comprises a cylindrical skirt 34 of axial orientation, arranged radially inside the cylindrical skirt 29 of the inlet disc holder 9 and having external toothing. The outlet disc holder 30 also has a radially oriented portion 35 which extends radially from the front end of the cylindrical skirt 34 of the output disc holder 30 to the outlet hub 31. The multi-disc assembly 11 of the second clutch 5 comprises a plurality of annular plates having a structure similar to that of the annular plates of the first clutch 4. Each plate has on its outer periphery an external toothing which cooperates with the complementary toothing formed on the internal face of the cylindrical skirt 29 of the input disc holder 9. The multi-disc assembly 11 further comprises a plurality of friction discs which have a structure similar to those of the first clutch 4 and are mounted integral in rotation with the output disc holder 30 and sliding axially on it. To do this, each friction disc has on its inner periphery an internal toothing which is in engagement with the external toothing formed on the cylindrical skirt 34 of the output disc holder 30. Each friction disc is interposed between two plates.
    The plate disposed at the front end of the multi-disk assembly 11 cooperates with a reaction member 36. The reaction member 36 is in turn held forward by means of a stop ring 37 which is attached to the input disk carrier 9 of the second clutch 5, at the front end of its cylindrical skirt 34.
    The second clutch 5 is actuated by means of a force transmitting member 38 which, on the one hand, cooperates with the plate disposed at the rear end of the multi-disk assembly 11 of the second clutch 5 and, on the other hand , cooperates with the hydraulic control system 21 which is able to slide axially forwardly so as to move the second clutch 5 from its disengaged position to its engaged position. The force transmitting member 38 here consists of a metal sheet which comprises at its outer periphery a plurality of axially oriented fingers 39 regularly distributed around the axis X. Each finger 39 passes through a dedicated opening formed in the support portion 19 of the input disk carrier 8 of the first clutch 4 and is thus in abutment against the plate disposed at the rear end of the multi-disk assembly 11 of the second clutch 5.
    To move the second clutch 5 from its disengaged position to its engaged position, the force transmitting member 38 is moved forwardly so that each of the friction discs is clamped between two platens and the torque is thereby transmitted between the input disk carrier 9 and the output disk carrier 30 and therefore between the crankshaft of the engine and the external shaft 3 input of the gearbox.
    In order to limit the axial size of the double clutch, the force transmission member 38 comprises at its inner portion an axial recess 40 forwards inside which is, at least partly, housed the hydraulic system order 21.
    The double clutch 1 further comprises a hydraulic control system 21 for actuating the two clutches 4, 5. The hydraulic control system 21 comprises a housing 41 which is fixed against a wall of the gearbox, not shown. The housing 41 has an inner tube 42 extending axially about the axis X and providing an internal space through which pass the shafts 2, 3 input of the gearbox. The inner tube 42 is made of material with the casing 41. The casing 41 also has first and second concentric annular chambers 43, 44 arranged radially outside the inner tube 42. First and second pistons 45, 46 of annular shape are respectively movably mounted in axial translation inside the first and second chambers 43, 44.
    The housing 41 further has, for each of the first and second chambers 43, 44, a channel 47, 48 for supplying pressurized fluid opening into said chamber 43, 44 so as to allow its supply of fluid. Each of the channels 47, 48 is connected to a hydraulic circuit equipped with a pump. The first and second chambers 43, 44 are thus intended to be fed with fluid to cause the displacement of the respective piston 45, 46 towards the front of its rest position towards its active position.
    Each of the first and second pistons 45, 46 carries a rotary stop 49, 50 which is fixed to the end of said piston 45, 46. Each rotary stop 49, 50 comprises a ring which is fixed to the piston 43, 44, another ring bearing against one of the force transmission members 25, 38 and rolling bodies, such as balls, interposed between the two rings.
    The inner tube 42 extends axially forwardly beyond the first and second chambers 43, 44. Furthermore, beyond the stroke of the first and second pistons 45, 46 corresponding to the displacement of the first and second clutches 4 5 of their disengaged position towards their engaged position, the inner tube 42 has a cylindrical bearing surface 51 on which is mounted the bearing 20 supporting the input disk carriers 8, 9 of the clutches 4, 5. The bearing 20 is here a rolling bearing comprising an inner ring which is mounted around the cylindrical bearing surface 51 of the inner tube 42, an outer ring which is mounted inside a housing 52 formed at the radially inner edge of the portion support 19 of the inlet disk holder 8 of the first clutch 4 and the rolling bodies, such as balls, interposed between the outer ring and the inner ring. The rolling bearing is angular contact. The housing 52 has, rearwardly a shoulder 53 for retaining the outer ring backwards. Furthermore, the inner ring is retained forward by an elastic ring 54 of the "circlip" type which is mounted in a groove in the inner tube 42, in front of the cylindrical bearing surface 51. The diameter outside of the cylindrical bearing surface 51 is smaller than the internal bore of the force transmitting member 38.
    The inner tube 42 of the hydraulic control system 21 comprises a plurality of channels 55 for the passage of a cooling fluid, such as gearbox oil, for cooling and lubricating the multi-disk assemblies 10, 11 The channels 55 are equitably distributed around the X axis.
    Each channel 55 extends axially between an inlet orifice 56 opening at the rear face of the housing 41 of the hydraulic control system and an outlet orifice 57 opening at the front end of the inner tube 42. The orifices input 55 are connected to a hydraulic circuit equipped with a pump. The outlet orifices 57 are regularly distributed around the X axis and open radially inside the multi-disk assemblies 10, 11. The outlet orifices 57 are directed radially outwards in order to guide the cooling fluid radially towards the outside. In the illustrated embodiment, the outlet orifices 57 open axially at a portion of the inner tube extending beyond the cylindrical bearing surface 51 on which is 20. The coolant then passes between the input disk carriers 8, 9 and the output disk carriers 15, 30.
    In order to allow oil to flow from the outlet ports to the outside of the double clutch, passing through the multi-disk assemblies 10, 11, the cylindrical skirts 29, 34 of the inlet and outlet disk carriers 9, 30 of the second clutch 5 and the cylindrical skirts 18, 22 of the inlet and outlet disc holders 8, 15 of the first clutch 4 have radial orifices 58. In FIG. 1, only the orifices 58 of the exit disc holder 30 of the second clutch 5 are visible.
    Figure 2 illustrates a double clutch 1 according to another embodiment. This embodiment differs from the previous embodiment only in that, if the outlet orifices 57 of the channels 55 intended to ensure the circulation of the cooling fluid open radially inside the multi-disk assemblies 10, 11, they open in a portion of the inner tube 42 disposed axially between the chambers 43, 44 of the hydraulic control system 21 and the cylindrical bearing surface 51 receiving the bearing 20. The cooling fluid then passes between the input disk carriers 8, 9 and the force transmission member 38. In such an embodiment, the inner zone 19a of the support portion 19 of the inlet disk carrier 8 of the first clutch 4 is then provided with orifices 59, regularly distributed around the X axis, so as to allow the circulation of the cooling fluid to the multi-plate assemblies 10, 11.
    According to another embodiment not shown, the outlets of the channels 55 open out along the X axis alternately on either side of the cylindrical bearing surface 51 receiving the bearing 20.
    Although the invention has been described in connection with several particular embodiments, it is obvious that it is not limited thereto and that it comprises all the technical equivalents of the means described and their combinations if they are within the scope of the invention. The use of the verb "to include", "to understand" or "to include" and its conjugated forms does not exclude the presence of other elements or steps other than those set forth in a claim.
    In the claims, any reference sign in parentheses can not be interpreted as a limitation of the claim.
    权利要求:
    Claims (13)
    [1" id="c-fr-0001]
    1. Double wet clutch (1) intended to be arranged in a motor vehicle transmission chain, between a motor having a crankshaft and a gearbox comprising two axially-extending coaxial input shafts (2, 3) X "said double wet clutch (1) having two clutches (4, 5) which are respectively capable of transmitting a torque of the crankshaft towards one and the other of the two shafts (2, 3) input of the box of speeds, each clutch (4, 5) comprising: - an inlet disk carrier (8, 9) for coupling in rotation to the crankshaft; an output disk carrier (15, 30) intended to be coupled in rotation to one or the other of the two input shafts of the gearbox; a multi-disk assembly (10, 11) comprising at least one friction disc integral in rotation with one of the input and output disk carriers (8, 9, 15, 30) and at least two plates respectively arranged on each side of each friction disk, integral in rotation with the other of the inlet and outlet disk carriers (8, 9, 15, 30), and movable axially between a disengaged position and a position engaged in which platens clamp said friction disk to transmit torque between the input disk carrier (8, 9) and the output disk carrier (15, 30); and - a movable force transmitting member (25, 38) which is adapted to move the multi-disc assembly (10, 11) from its disengaged position to its engaged position; said double wet clutch (1) further comprising a control system (21) comprising: - a housing (41) for attachment to the gearbox, said housing (41) having an inner tube (42) extending axially about the axis X and providing an internal space for the passage of the two shafts (2, 3) input of the gearbox; - A first and a second annular pistons (45, 46) which are mounted to slide axially on the housing, outside the inner tube and respectively carry a first and a second rotary stops (49, 50); the first and the second rotary stops (49, 50) co-operating respectively with the force transmission member (25, 38) of the one and the other of the two clutches (4, 5) and being movable between a position of rest and an active position corresponding respectively to a disengaged position and an engaged position of said clutch (4, 5); said double clutch being characterized in that the input disk carriers (8, 9) of the two clutches (4, 5) are rotatably mounted about the X axis on the inner tube (42) of the control system (21 ) via a bearing (20).
    [2" id="c-fr-0002]
    2. Double wet clutch (1) according to claim 1, wherein the bearing (20) is a rolling bearing.
    [3" id="c-fr-0003]
    A dual wet clutch (1) according to claim 1 or 2, wherein the bearing (20) is mounted on a bearing surface (51) of the inner tube (42), said bearing surface (51) being positioned, direction of the two clutches, beyond the races of the first and second annular pistons between their rest position and their active position.
    [4" id="c-fr-0004]
    A dual wet clutch (1) according to any one of claims 1 to 3, wherein each inlet or outlet disk carrier (8, 9, 15, 30) has a cylindrical skirt (18, 22, 29). , 34); each friction disk or plate being axially movably mounted on the cylindrical skirt of one of the output or inlet disk carriers and integrally in rotation with the latter and in which one of the disk carriers of inlet (8, 9) has a support portion (19) directed radially inwardly from an edge of its cylindrical skirt (18) directed towards the control system; said support portion (19) having a radially inner edge cooperating with the bearing (20).
    [5" id="c-fr-0005]
    A dual wet clutch (1) according to claim 4, wherein the multi-disc assembly (10) of one of the clutches (4) is radially disposed within the multi-disc assembly (11) of the other clutch (5) and in which the bearing (20) is arranged radially inside the multi-disk assemblies (10, 11) of the clutches (4, 5).
    [6" id="c-fr-0006]
    The dual wet clutch (1) according to claim 5, wherein the support portion (19) has an inner zone (19b) which is folded in a direction opposite to the control system (21), within the assemblies. multidiscs (10, 11).
    [7" id="c-fr-0007]
    A dual wet clutch (1) as claimed in any one of claims 4 to 6, wherein the force transmitting member (25, 38) of each of the clutches (4, 5) has an outer periphery equipped with a plurality of axially oriented fingers (26, 39) each extending through the support portion (19) through a respective opening; said fingers (26, 39) resting against the multi-disk assembly (10, 11) of said clutch (4, 5).
    [8" id="c-fr-0008]
    A dual wet clutch (1) according to any one of claims 1 to 7, wherein each of the force transmitting members (25, 38) has an inner portion having an axial recess (28, 40) towards the two clutches in which at least a portion of the first and second annular pistons (45, 46) of the control system are housed.
    [9" id="c-fr-0009]
    9. Double wet clutch (1) according to any one of claims 1 to 8, wherein the inner tube (42) has at least one channel (55) for passage of a cooling fluid for conducting said cooling fluid. to the clutches (4, 5).
    [10" id="c-fr-0010]
    A dual wet clutch (1) as claimed in any one of claims 1 to 9, wherein the coolant passage channel (55) has an exit orifice (57) opening axially beyond the races of the first and second annular pistons (45, 46) between their rest position and their active position.
    [11" id="c-fr-0011]
    The dual wet clutch (1) according to any one of claims 1 to 10, wherein the inlet disk carrier (8, 9) and the output disk carrier (15, 30) of each of the clutches ( 4, 5) comprise radial orifices (58) circumferentially distributed about the axis X and intended to allow circulation of the cooling fluid radially outwards through the multi-disk assembly (10, 11) of each of the clutches (4, 5) from the coolant passage channel (55).
    [12" id="c-fr-0012]
    A dual wet clutch (1) according to any one of claims 1 to 11, wherein the housing comprises first and second annular chambers (43,44) and wherein the first and second annular pistons (45,46) ) are respectively movable within the first and second annular chambers (43, 44).
    [13" id="c-fr-0013]
    13. A motor vehicle comprising a double wet clutch (1) according to any one of claims 1 to 12.
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    同族专利:
    公开号 | 公开日
    CN107202081A|2017-09-26|
    KR20170107926A|2017-09-26|
    KR102320711B1|2021-11-02|
    FR3049023B1|2019-04-26|
    CN107202081B|2021-03-30|
    DE102017104458A1|2017-09-21|
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    DE102010051911A1|2009-11-25|2011-06-01|Schaeffler Technologies Gmbh & Co. Kg|Multiple coupling device, component, assemblies and methods of assembly|
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    JP3124493U|2006-06-09|2006-08-17|株式会社ダイナックス|Wet dual clutch cooling structure|
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    EP2286105B1|2008-06-16|2013-02-13|Schaeffler Technologies AG & Co. KG|Dual clutch with rotary vibration damper|
    DE102009001286B4|2009-03-03|2019-10-24|Zf Friedrichshafen Ag|Multiple coupling device, in particular dual clutch device, with a rotating with an external transmission input shaft pressure medium supply element|
    DE102010051147A1|2009-11-25|2011-05-26|Schaeffler Technologies Gmbh & Co. Kg|Dual clutch, has clutch cover sealing and locking clutch housing and comprising circumferential edge region that is arranged and attached between contact surface of motor housing and contact surface of transmission housing|
    EP2469114B1|2010-12-21|2017-11-01|BorgWarner Inc.|Coupling device|
    DE102012006730A1|2012-04-02|2013-10-02|Borgwarner Inc.|coupling device|
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    DE102014212406A1|2014-06-27|2015-12-31|Schaeffler Technologies AG & Co. KG|Wet multi-plate clutch|
    CN204985428U|2015-08-18|2016-01-20|崔博琳|Machinery compresses tightly wet -type double clutch mechanism and mechanical transmission of friction disc|
    CN105179511B|2015-09-28|2018-03-30|上汽通用汽车有限公司|Wet-type dual-clutch|DE102018104372B3|2018-02-27|2019-05-23|Schaeffler Technologies AG & Co. KG|Actuator with axially nested slave cylinder; Coupling system and drive unit|
    KR102073104B1|2018-04-20|2020-02-04|주식회사 카펙발레오|Dual clutch device for vehicle|
    KR102076345B1|2018-04-20|2020-02-11|주식회사 카펙발레오|Dual clutch device for vehicle|
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    WO2022023111A1|2020-07-28|2022-02-03|Punch Powertrain Psa E-Transmissions N.V.|Dual clutch transmission system|
    法律状态:
    2017-03-31| PLFP| Fee payment|Year of fee payment: 2 |
    2017-09-22| PLSC| Publication of the preliminary search report|Effective date: 20170922 |
    2018-03-29| PLFP| Fee payment|Year of fee payment: 3 |
    2020-03-31| PLFP| Fee payment|Year of fee payment: 5 |
    2021-03-30| PLFP| Fee payment|Year of fee payment: 6 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1652226|2016-03-16|
    FR1652226A|FR3049023B1|2016-03-16|2016-03-16|DOUBLE WET CLUTCH SUPPORTED ON ITS CONTROL SYSTEM|FR1652226A| FR3049023B1|2016-03-16|2016-03-16|DOUBLE WET CLUTCH SUPPORTED ON ITS CONTROL SYSTEM|
    DE102017104458.2A| DE102017104458A1|2016-03-16|2017-03-03|WET DOUBLE COUPLING BASED ON YOUR CONTROL SYSTEM|
    KR1020170032703A| KR102320711B1|2016-03-16|2017-03-15|Wet double clutch supported on its control system|
    CN201710156511.6A| CN107202081B|2016-03-16|2017-03-16|Wet dual clutch supported on its control system|
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