• 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 transmission assembly for a motor vehicle, intended to be arranged between a heat engine equipped with a crankshaft and a gearbox equipped with an input shaft, said assembly comprising: - an electric machine (3) ; - a clutch (2); - a torsion damper with elastic members (70) comprising: ▪ an input member (71, 72) and an output member (73, 74); A plurality of groups of elastic members (77a, 77b) arranged in series via a phasing member (80); and a pendulum damper (55) comprising: a support member (56) movable in rotation about the axis X and integral in rotation with the phasing member (80) of the torsion damper with elastic members ( 70); and pendulum weights (57) movably mounted on the support member (56).
    公开号:FR3015380A1
    申请号:FR1363122
    申请日:2013-12-19
    公开日:2015-06-26
    发明作者:Fabien Lebeau；Gilles Lebas
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    [0001] TECHNICAL FIELD OF THE INVENTION The invention relates to the field of transmissions for a motor vehicle. It relates in particular to a transmission assembly intended to be disposed between a heat engine and a gearbox of a motor vehicle. It relates in particular to a transmission assembly for a hybrid type of motor vehicle in which an electric machine is disposed in the transmission chain between the engine and the gearbox. STATE OF THE ART In the state of the art, it is known transmission assemblies, arranged between the gearbox and the engine and comprising an electric machine and a clutch on the motor side for coupling in rotation the crankshaft of the engine. thermal motor at the rotor of the electric machine. Thus, it is possible to shut down the internal combustion engine at each stop and restart it with the electric machine. The electric machine can also constitute an electric brake or bring a surplus of energy to the heat engine to assist or prevent it from stalling. The electric machine can also drive the vehicle. When the engine is running, the electric machine acts as an alternator. Such a transmission assembly is disclosed in particular in document FR 2 830 589. An explosion engine exhibits acyclisms due to successive explosions in the cylinders of the engine, the frequency of the acyclisms varying in particular as a function of the number of cylinders and the rotational speed of the engine. In order to filter the vibrations generated by the acyclisms of the heat engine, it is known to integrate torsion dampers with elastic members and / or pendulum dampers, also known as pendulum oscillators or pendulums, into the aforementioned transmission assemblies. In the absence of such dampers, vibrations penetrating into the gearbox would cause in operation shocks, noises or noise particularly undesirable.
    [0002] However, the torsion dampers equipping such transmission assemblies are not fully satisfactory. This is all the more problematic as the development of new fuel-efficient engines leads to an increase in their acyclisms.
    [0003] OBJECT OF THE INVENTION An idea underlying the invention is to propose a transmission assembly for a hybrid vehicle that is equipped with means for effectively absorbing vibrations. According to one embodiment, the invention provides a transmission assembly for a motor vehicle, intended to be disposed between a heat engine equipped with a crankshaft and a gearbox equipped with an input shaft, said assembly comprising: an electric machine comprising a stator and a rotor movable in rotation about an axis X; A clutch arranged to couple or uncouple in rotation the crankshaft of the engine and the rotor; a torsion damper with elastic members arranged to transmit a torque and dampen the rotation acyclisms between the rotor and the input shaft of the gearbox, the torsion damper comprising: an input element; an output member, rotatable relative to each other about the X axis, the input member being rotatably connected to the rotor and the output member being configured to be rotationally connected to the input shaft of the gearbox; a plurality of groups of resilient members arranged to rotatably couple the input member and the output member and each having at least two resilient members interposed circumferentially between the input member and the output member ; and a phasing member interposed circumferentially between the two resilient members of each elastic member group to arrange them in series; and a pendulum damper comprising: a support member movable in rotation about the axis X and integral in rotation with the phasing member of the torsion damper with elastic members; and pendulum weights movably mounted on the support member. Thus, the vibrations due to the acyclisms generated by a heat engine upstream of such a transmission assembly are filtered efficiently.
    [0004] Indeed, a shock absorber with elastic members comprising a plurality of groups of elastic members arranged in series via a phasing member provides a large clearance between its inlet and its outlet so that the elastic members may have sufficiently low stiffnesses to effectively filter the vibrations.
    [0005] Furthermore, the transmission assembly also comprises a pendulum damper. However, such a pendulum damper ensures good filtration performance over a large part of the engine speed ranges. Moreover, it turns out that such a pendulum damper is all the more efficient that the pendulum damper is implanted in the kinematic chain, at the level of the member ensuring the phasing between the elastic members of the damper to elastic members. It has indeed been found that the pendulum damper was more effective, when mounted rotatably mounted elements having a low mass, that when it was integral in rotation with a member having a larger mass, such as that the input shaft of the gearbox or the rotor of the electric machine. According to other advantageous embodiments, such an assembly may have one or more of the following characteristics: the support member of the pendular damper is offset axially with respect to the torsion damper with elastic members. the input element comprises a front guide washer and a rear guide washer, integral in rotation with the rotor, and having support seats extending circumferentially between each group of elastic members, and the element of the outlet comprises a web extending axially between the guide washers and having radial bearing lugs extending circumferentially between each group of elastic members and a splined hub, integral with the web, intended to cooperate with the drive shaft. input of the gearbox. - The phasing member is a phasing washer having a plurality of radial phasing tabs which are each disposed between the two members of the same group. the front guide washer, intended to be disposed opposite the gearbox, is provided with a central orifice, the phasing washer having a radially outer zone extending axially between the sail and the washer; front guide means and a radially inner region for fixing the support member of the pendular damper projecting forwards through the central orifice of the front guide washer. the support member of the pendular damper comprises an annular zone and radially inner tabs fixed, by means of fasteners, to the phasing member, in its radially inner zone projecting forwards. through the central hole of the front guide washer. - The phasing member is centered and guided in rotation on the splined hub via a bearing. - The rear guide washer is guided and centered in rotation on the splined hub via a bearing. the clutch comprises a friction disc which is integral in rotation with the rotor by means of an intermediate shaft, the rotor having a central opening through which the intermediate shaft passes, the rotor being mounted integral in rotation with the intermediate shaft via a support hub and the rear guide washer being fixed to the rotor support hub. the intermediate shaft comprises a flange, the rotor support hub comprising an axial rotor support skirt and an inner flange extending radially inwardly of the axial skirt, the flange of the intermediate shaft and the washer; rear guide being secured to the inner flange by common fasteners. the transmission assembly further comprises a double damping flywheel equipped with a primary flywheel intended to be fixed to the crankshaft of the heat engine and a secondary flywheel forming a reaction plate for the clutch arranged to couple or uncouple in rotation the crankshaft; motor and rotor. the elastic members are housed in a sealed chamber filled with a lubricating agent. According to one embodiment, the invention provides a motor vehicle equipped with a aforementioned transmission assembly.
    [0006] The invention will be better understood, and other objects, details, characteristics and advantages thereof will appear more clearly in the course of the following description of several particular embodiments of the invention, given solely for illustrative and non-limiting purposes. with reference to the appended figures. In these figures: - Figure 1 is a half-sectional view of a transmission assembly intended to be disposed between a heat engine and a gearbox; - Figure 2 is a front view, in perspective of the damping device of Figure 1, for acting between the rotor and an input shaft of a gearbox, the front guide washer of the damper to resilient members and the pendulum damper being partially cut away. - Figure 3 is a detailed perspective view of a pendulum feeder, a sidewall is shown partially broken away. 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 transmission assembly. By convention, the "radial" orientation is directed orthogonally to the X axis of rotation of the transmission assembly determining the "axial" orientation and, from the inside to the outside away from said axis X, the "circumferential" orientation is directed orthogonally to the X axis of rotation of the transmission assembly and orthogonal to the radial direction. The terms "external" and "internal" are used to define the relative position of one element with respect to another, with reference to the X axis, an element close to the axis is thus described as internal as opposed to 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 the rear and an element intended to be placed close to the gearbox being designated by before. Referring to Figure 1, we see a transmission assembly, intended to be disposed between a heat engine and a gearbox. The transmission assembly comprises a double damping flywheel 1 intended to be fixed to the crankshaft of the heat engine, a clutch 2 and an electric machine 3 comprising a stator 4 and a rotor 5. The clutch 2 makes it possible to couple or uncouple in rotation the crankshaft of the heat engine, not shown, to the rotor 5 of the electric machine 3. Furthermore, the rotor 5 of the electric machine 3 is intended to be coupled in rotation to an input shaft of the gearbox by via a torsion damper 70. The assembly is therefore able to transmit a torque between the crankshaft of the engine and the input shaft of the gearbox. The electric machine 3 is a reversible rotary electric machine of the alternator-starter type. In starter mode, the clutch 2 is engaged and the electric machine 3 allows the start of the engine. In alternator mode, the electric machine 3 can recharge a battery of the vehicle and / or power organs or equipment consuming energy when the engine is running. It is further configured to recover energy when braking the vehicle. The electric machine 3 can in particular be configured to stop the engine, for example, at a red light or in the caps, and then restart it (stop and go function in English). In one embodiment, it is capable of providing a surplus of power to prevent the engine stalls (boost function in English). Moreover, the electric machine 3 is able to drive the vehicle at least for a short distance, the clutch 2 then being disengaged and the engine stopped. The double damping flywheel 1 comprises a primary flywheel 6, intended to be fixed to the crankshaft of the heat engine, not shown, and a secondary flywheel 7 which is centered and guided on the primary flywheel 6 by means of a Rolling bearing 8. The primary 6 and secondary 7 flywheels are movable about the axis of rotation X and are furthermore movable in rotation relative to each other about said axis X.
    [0007] The primary flywheel 6 comprises a central hub 9, radially internal, bearing the rolling bearing 8, an annular portion 10 extending radially and a cylindrical portion 11 extending axially, forwards, from the outer periphery of the portion The primary flywheel 6 also has an annular cover 12 fixed to the cylindrical portion 11. The annular cover 12 defines with the annular portion 10 and the cylindrical portion 11, an annular chamber. The central hub 9 has a radial annular portion in which are formed orifices. These orifices are arranged vis-à-vis orifices formed in the radially inner portion of the annular portion 10 of the primary flywheel 6. Fixing screws, not shown, engaged in the orifices allow the attachment of the primary flywheel 6 to the end of the crankshaft. The dual damping flywheel 1 further comprises a torsion damper with resilient members for transmitting the torque and damping the rotation acyclisms between the flywheels of primary 6 and secondary inertia 7 to reduce vibrations from the engine. In the embodiment shown, the torsion damper has first and second damping stages arranged in series. The first damping stage comprises curved elastic members 13 with a circumferential effect, such as helical springs, housed in the annular chamber and distributed circumferentially about the axis X. In order to limit the friction between the curved elastic members 13 and the cylindrical portion 11 of the primary flywheel 6, the annular chamber is filled with a lubricating agent, preferably grease. The curved elastic members 13 extend, on the one hand, between two support seats 25 carried by the primary flywheel 6 and, on the other hand, between two support lugs formed on an intermediate web 14. The second stage damping element comprises a plurality of groups of two elastic members, not shown, extending radially inside the curved resilient members 13, and providing a coupling between the intermediate web 14 and two guide washers 15, 16. guide washers extend axially on either side of the intermediate web 14. The straight elastic members of each group are connected in series via a phasing member, not shown, free to rotate relative to the veil intermediate 14 and the guide washers 15, 16. The guide washers 15, 16 are integral in rotation with the secondary flywheel 7. For more details, such a dual damping flywheel is described in particular in WO2010079273. The secondary flywheel 7 is intended to form the reaction plate of the clutch 2. Said clutch 2 comprises a cover 17, fixed on the outer periphery of the secondary flywheel 7, a pressure plate 18, an annular diaphragm 19 axially biasing the plate pressure 18 to the secondary flywheel 7, a friction disc 20 and a clutch abutment 21 adapted to rotate the diaphragm 19 to move the clutch 2 to its disengaged position. The clutch disc 20 is equipped with friction linings 22 and a corrugated hub 23 cooperating with splines formed on an intermediate shaft 24. The pressure plate 18 is rotatably connected to the cover 17 by tangential elastic tabs, no illustrated, axial action permitting axial movement of the pressure plate 18 relative to the reaction plate. Thus, the pressure plate 18 is movable, relative to the reaction plate, between an engaged position, in which the friction linings 22 are clamped between an annular friction surface of the secondary flywheel 7, forming a reaction plate, and the plateau pressure 18, and a disengaged position. In the engaged position, the clutch 2 is engaged and the torque is transmitted from the crankshaft to the intermediate shaft 24 via the clutch 2. The diaphragm 19 is in contact, on the one hand, at its inner periphery, with the abutment clutch 21 and, on the other hand, with a boss of the pressure plate 18. The diaphragm 19 urges the pressure plate 18 towards the reaction plate. To disengage the clutch 2, the clutch abutment 21 axially displaces the inner periphery of the diaphragm 19 rearwardly so as to tilt the diaphragm 19. Thus, the load exerted by the diaphragm 19 on the pressure plate 18 decreases so that the pressure plate 18 is biased forward by the action of the tangential tangential tongues. In a variant not shown, the clutch can be of the normally open type. In this case, it is the movement of the clutch abutment 21 towards the rear which makes it possible to solicit, via the diaphragm 19, the pressure plate 18 in the direction of the reaction plate. In such a normally open clutch, the diaphragm 19 has a resilience to return his fingers to a position before rest.
    [0008] The reversible rotary electric machine 3 comprises an external stator 4 and an internal rotor 5. The stator 4 surrounds the rotor 5. The rotor 5 has a central opening for the passage of the intermediate shaft 24. The stator 4 is carried by a support member 25 which is, on the one hand, intended to be fixed on the engine block and, secondly, intended to be fixed on the housing of the gearbox. The support member 25 is inserted between the transmission case and the engine block and is arranged to allow attachment of the gearbox to the engine block. In other words, the support member 25 forms, so to speak, a spacer between the engine block and the casing of the gearbox. In the embodiment shown, the support member 25 comprises a rear flange provided with orifices 64 allowing the passage of fasteners for fixing the support member 25 on the engine block. The support member 25 has an outer peripheral wall whose inner surface is of cylindrical shape in order to cooperate with the outer periphery 15 of the stator 4. The mounting of the stator 4 in the support member 25 can be made by hooping or by clamping by force. The support element 25 also has an internal web 26, extending behind the stator 4 and the rotor 5 and forming a separation wall between the clutch 2, on the one hand, and the electric machine 3, on the other hand. The support element 25 also defines a housing 20 extending inside the rotor 5 and within which the clutch abutment 21 extends at least partially. Such an arrangement makes it possible to optimize the axial size of the assembly. The housing is defined by an axial skirt 27 and a bottom 28 of radial orientation. The bottom 28 is provided with a bore allowing the passage of the intermediate shaft 24. Furthermore, an axial flange 29 extends from the bottom 28 of the housing, towards the front, and forms with the front face of the bottom 28 of the housing, a cylindrical bore housing a bearing 30. In other words, the bottom 28 of the housing limits, on the motor side, the bearing housing cylindrical bore 30 and defines a radial bearing rear bearing surface 30. The bearing 30 cooperates, moreover, with the intermediate shaft 24, with the aid of a shoulder 31 which defines a bearing surface before the bearing 30. The bearing 30 thus allows the centering of the intermediate shaft 24 with respect to the support member 25.
    [0009] The bearing 30 comprises an outer ring, an inner ring and rolling bodies extending between said outer and inner rings. The outer ring is coupled axially to the support member 25 while the inner ring is axially coupled to the intermediate shaft 24. Thus, the bearing 30 is axially fixed with respect to the support member 25, a part, and the intermediate shaft 24, on the other hand. In addition, such a mounting of the bearing 30 makes it possible axially to maintain the intermediate shaft 24 with respect to the support element 25. In order to axially couple the inner and outer rings, these can be force-fitted or glued. Alternatively, it is also possible to use one or more locking members, such as elastic rods or circlips. In one embodiment, not shown, the rear end of the intermediate shaft 24 is centered relative to the primary flywheel 6 by means of a controlled bearing mounted inside the central hub 9 of the primary flywheel 6. 15 The clutch abutment 21 is a fluid-controlled abutment. The stop 21 is concentric with the axis X and traversed by the intermediate shaft 24. The stop 21 comprises two parts in piston cylinder relation, that is to say a fixed part 32, delimiting a blind annular cavity of axial orientation, and a piston 33 mounted axially movable relative to the fixed portion 32. The piston 33 enters the cavity 20 to define therewith a variable volume working chamber. The cavity communicates via a channel with a connection arrival to a fluid supply pipe 34 connected to a master cylinder. The working chamber is therefore allowed to be pressurized or depressurized. In the embodiment shown, the fixed part 32 of the abutment 21 comprises a guide tube 35 and an outer body 36 surrounding the guide tube 35. The guide tube 35, for example a metal tube, defines the annular cavity in FIG. which the piston 33 is movable and thus guides the piston 33. The guide tube 35 is assembled to the outer body 36. The guide tube 35 is traversed by the intermediate shaft 24. The outer body 36 is equipped with fastening means, not shown in the support member 25. In an embodiment not shown, the clutch abutment 21 is a stop controlled by an electric actuator. The stop 21 is here of the self-centering type. It comprises a ball bearing with a profiled rotating ring for a point contact with the inner ends of the fingers of the diaphragm 19 and a non-rotating ring coupled axially to the piston 33. A sealing bellows 37 extends between the outer body 36 and the non-rotating ring. Alternatively, the stop 21 is of pulled type, the stop 21 then acting by pulling on the fingers of the diaphragm 29. The inner web 26 of the support member 25 comprises a recess 5 for the passage of the feed pipe 34. The rotor 5 is supported by a hub 38. The hub 38 has an axial skirt 39 for supporting the rotor 5. The rotor 5 comprises a bundle of sheets which is shrink-fitted on the outer surface of the skirt. axial 39. Thus, the hot pack of sheets is mounted by fitting on the outer surface of the axial skirt 39. The hub 38 for supporting the rotor 5 is fixed to the intermediate shaft 24. To do this, the end front of the intermediate shaft 24 comprises a flange 40 against which abuts an internal flange 41 formed in the support hub 38 and extending radially inwardly of the axial skirt 39. Fastening means, such as screws 42, allow to fix the internal flange 41 of the mo 38 in the collar 40 of the intermediate shaft 24. In one embodiment, the intermediate shaft 24 is equipped at its front end with a bore 43 intended to receive a rear end 44 of a drive shaft. the gearbox to ensure its centering. Such an arrangement, however, is optional. The electric machine 3 is a polyphase electric machine. The stator 4 of the electric machine 3 comprises a winding equipped with a plurality of coils 45 distributed circumferentially around the axis X. The coils 45 are interconnected with each other by means of an interconnector 46. The interconnector 46 is 25 offset axially with respect to the coils 45, towards the gearbox. In the illustrated embodiment, the interconnector 46 has four ring-shaped frames 47, 48, 49, 50 extending in a radial plane. The frames 47, 48, 49, 50 are electrically conductive, for example made of copper or advantageously of another weldable metallic material. These frames 47, 48, 49, 50 are stacked axially on each other and electrically isolated from each other. Preferably, the frames are embedded in a body made of electrically insulating material, such as plastics material. Each frame 47, 48, 49, 50 carries on its inner periphery lugs 51 extending radially inwards towards the frame, which are welded to the ends 52 of the stator coils 45. Each coil 45 has a first end called "Input" intended to be connected with one of the phase frames 47, 48, 49 and a second end called "output" intended to be connected to the neutral frame 50. The "inputs" of the coils are alternately connected to the frames of phases 47, 48, 49. Each phase frame 47, 48, 49 comprises on its outer periphery a connection terminal, not shown, for interconnection with a power connector itself connected to an inverter described for example in EP 0 831 580.
    [0010] The rotor 5 is a rotor with permanent magnets. It comprises a body formed of a stack of laminations stacked in the axial direction and permanent magnets radially implanted in the laminations of the laminations, at the outer periphery of the rotor 5. Furthermore, the transmission assembly comprises a buffer of 15 torsion with resilient members 70 and a pendulum damper 55. The torsion damper with elastic members 70 has an input member rotatably connected to the rotor 5 of the electric machine and an output member configured to be rotatably coupled to the input shaft of the gearbox. The input member comprises a front guide washer 71 and a rear guide washer 72. The output member comprises a web 73 and a splined means 74, attached to the web 73 via rivets, and for to cooperate with complementary shaped grooves carried by the rear end of the input shaft of the gearbox, not shown. The front and rear guide washers 71 are disposed axially 25 on either side of the web 73. The rear guide washer 72 is fixed to the rotor support hub 5 by means of fasteners 42, such as screws or rivets. In the embodiment shown, the rear guide washer 72 and the flange 40 of the intermediate shaft 24 are fixed to the hub 38 for supporting the rotor 5 by common fastening means 42. Furthermore, the rear guide washer 72 is centered and guided in rotation on the splined hub 74 by means of a bearing, such as a rolling bearing 75. To do this, the rear guide washer 72 comprises a flange internal axial orientation, extending forwardly, and defining a bearing surface for the outer ring of the rolling bearing 75. Furthermore, the inner ring of the rolling bearing 75 cooperates with an annular outer surface of the hub As a variant, the rear guide washer 72 is not centered and guided in rotation on the splined hub. In this case, the centering and the rotational guiding of the rear guide washer 72 with respect to the support element 25 is ensured by means of its attachment to the intermediate shaft 24, via the fixing screws 42, and by the bearing 30 ensuring the rotational guidance of the intermediate shaft 24 relative to the support member 25. The two front guide washers 71 and rear 72 are secured in rotation, here by means of rivets passing through through holes provided at the outer periphery of the guide washers 71, 72. In the embodiment shown, a ring 76 forming a spacer is inserted between the two guide washers 71, 72 at their radially outer portion, in order to maintaining the required axial spacing between the guide washers 71, 72. The torsion damping device with elastic members 70 comprises a plurality of groups of two elastic members 77a, 77b ensuring a coupling between the two they are guide washers 71, 72 and the web 73. The elastic members 77a, 77b here are straight elastic members distributed circumferentially on the same diameter about the axis X. Each elastic member 77a, 77b may comprise two coaxial springs mounted l one in the other. In the embodiment shown, the torsion damper 70 has three groups of two straight elastic members 77a, 77b. The elastic members 77 are housed in a housing chamber defined by pressed annular portions formed in the guide washers 71, 72. Furthermore, each group of elastic members 77a, 77b extends, on the one hand, between two support seats carried by the guide washers 71, 72 and, secondly, between two circumferentially consecutive support tabs 79 of the web 73. Furthermore, the tabs 79 of the web 73, shown in FIG. two substantially planar bearing faces serving to support the ends of the elastic members 77a, 77b. The tabs 79 of the web 73 further comprise retaining lugs 85 which extend circumferentially on either side of the lugs 79 and make it possible to retain the ends of the elastic members 77a, 77b radially. The tabs 79 of the web 73 also comprise, at their radial end, projecting elements 88 arranged to co-operate at the end of travel with abutment surfaces 89 carried by the ring 76. Thus, the angular travel of the guide washers 71, 72 by relative to the web 79 is limited to protect the elastic members 77.
    [0011] The elastic members 77a, 77b of each group are connected in series by means of a phasing member 80. The phasing member 80 is free to rotate relative to the guide washers 72, 71, on the one hand , and with respect to the web 73, on the other hand. The phasing member 80 is centered and guided in rotation on the splined hub 74 by means of a bearing, such as a sliding bearing 82 in the embodiment shown in FIG. 1. To do this, the phasage 80 has an inner flange extending axially rearwardly and resting on a plain bearing ring 86 itself resting on an outer surface of the splined hub 74. Such a plain bearing ring 86 is made of a material having a low coefficient of friction. Alternatively, the bearing may also be a ball bearing, a needle cage or the like. Moreover, the phasing member 80 comprises radial phasing tabs 81, shown in FIG. 2, which are each interposed between the two consecutive elastic members 77a, 77b of the same group, so that the two elastic members 77a, 77b consecutive of the same group are arranged in series. The radial phasing tabs 81 comprise two substantially flat bearing faces, forming an angle between them and serving to support the ends of the elastic members 77a, 77b. Each radial phasing lug 81 further comprises, on its radially outer edge, two opposite external retaining lugs 83 extending on either side of each radial phasing lug 81 and enabling the ends of the straight elastic members to be retained radially. . Moreover, the radial phasing tabs 81 also include centering pins 84 projecting from the bearing faces towards the inside of the elastic members 77a, 77b and making it possible to retain the elastic members 77a, 77b radially and axially.
    [0012] The phasing member 80 ensures a deformation of the elastic members 77a, 77b in phase with each other so that the elastic forces generated in the torsion damper 70 are distributed circumferentially, homogeneously.
    [0013] Thus, in operation, each group comprises a first elastic member 77a or 77b bearing at a first end against a bearing seat carried by the guide washers 71, 72 and at a second end against a radial phasing tab 81 of the phasing member 80 while the second elastic member 77b or 77a is supported at a first end against said radial phasing lug 81 of the phasing member 80 and at a second end against a bearing lug 79 of the web 73. Therefore, a driving torque is transmitted from the guide rings 71, 72 to the web 73 via the elastic members 77a, 77b.
    [0014] The phasing member 80 has a radially outer portion extending axially between the front guide washer 71 and the web 73. Furthermore, the front guide washer 71 is provided with a central orifice through which extends a radially internal zone of the phasing member 80. The radially inner zone of the phasing member 80 is, as we shall see later, a zone for fixing the support member 56 of the pendular damper 55. Note also that the web 73 and the phasing member 80 are provided with openings for the passage of the fasteners 42 ensuring the fixing of the rear guide washer 72 on the hub 38 of the rotor support 5. Similarly, The central orifice of the front guide washer 71 has a diameter allowing the passage of said fastening members 42. In the embodiment shown, the front and rear guide washers 71 and 71 define a sealed chamber for housing the members. elastic members 77a, 77b which is filled with a lubricating agent, such as grease. In order to guarantee the tightness of the housing, the fixing of the front guide washers 71 and rear 72 may be performed by sealed welding. In addition, the torsion damper with elastic members 70 is equipped with sealing means. These sealing means comprise a first elastically deformable sealing washer 90, fixed to the web 73, sealing between the rear guide washer 72 and the web 73 and a second sealing washer 92 fixed to the member phasing 80, ensuring the seal between the phasing member 80 and the front guide washer 71. In order to limit friction, plastic washers 91, 93 are inserted between the guide washers 71, 72 and the washers. Sealing 90, 91. Furthermore, a plastic sealing washer 94 is inserted between the web 73 and the phasing member 80 and ensures the seal between these two elements. The pendulum damper 55 comprises a support member 56 and a plurality of pendulum weights 57 circumferentially distributed on the support member 56. As shown in FIG. 2, the support member 56 of the pendulum damper 55 is a disk which has radially inner tabs 87 for fixing the support member 56 to the phasing member 80. The radially inner tabs 87 have holes for the passage of fastening members, such as rivets, for securing the support member 56 and the phasing member 80. By fixing the support member 56 to the phasing member 80 in a radially inner region thereof projecting radially inside the central orifice of the front guide washer 71, the support member 56 may advantageously consist of a non-stamped flat piece, which makes it easier to ensure the accuracy of the geometry of the raceways. In addition, the support member 56 is axially offset forwards and extends between the elastic body damper 70 and the gearbox. Thus, the pendulum weights 57 can be implanted at a relatively large radial distance from the X axis, which has the effect of giving the pendulum damper 55 optimum filtration performance.
    [0015] The weights 57 are able to oscillate with respect to the support member 56 in a plane orthogonal to the axis of rotation X, in response to the irregularities of rotation. As shown in detail in FIG. 3, each weight 57 comprises two flanks 58, 59 which extend axially on either side of the support member 56 and are connected axially to each other by the intermediate of two connecting struts 60. Each connecting strut 60 passes axially through an associated opening 61 of the support member 56. In addition, the oscillations of the weights 57 are guided by guide means comprising, for each flyweight 57, two rolling elements 62 which each cooperate with a first raceway carried by the support member 56 and with a second raceway, carried by the weight 57, and extending vis-à-vis the first track rolling. The first race tracks are formed by the outer edge of the passage openings 61 of the spacers 60. The second raceways are carried by the spacers 60 connecting the flanks of each flyweight 57. The rolling elements 62 are, for example, formed by a cylindrical roller of circular section. The first and second race tracks have a generally epicyclic or circular shape and are arranged such that the oscillation frequency of the flyweights 57 is proportional to the rotational speed of the drive shaft. The weights 57 further comprise stop elements 63 made of elastomer material for damping shocks when the weights 57 arrive at the end of the stroke or when the engine is stopped. The abutment elements 63 are here arranged between the two sides 58, 59 of each counterweight 57 and abut against the edge of the openings 61 for the passage of the spacers 60.
    [0016] 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. In particular, a clutch or a torque converter may be provided in the drive chain between the output of the spring damper 70 and the input shaft of the gearbox. 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 out in a claim. The use of the undefined article "un" or "un" for an element or step does not exclude, unless otherwise stated, the presence of a plurality of such elements or steps. In the claims, any reference sign in parentheses can not be interpreted as a limitation of the claim.
    权利要求:
    Claims (13)
    [0001]
    REVENDICATIONS1. Transmission assembly for a motor vehicle, intended to be arranged between a heat engine equipped with a crankshaft and a gearbox equipped with an input shaft, said assembly comprising: an electric machine (3) comprising a stator (4) ) and a rotor (5) rotatable about an axis X; - a clutch (2) arranged to couple or uncouple in rotation the crankshaft of the engine and the rotor (5); a torsion damper with resilient members (70) arranged to transmit a torque and dampen the rotational acyclisms between the rotor (5) and the input shaft of the gearbox, the torsion damper comprising: an input member (71, 72) and an output member (73, 74), rotatable relative to each other about the X axis, the input member (71, 72) ) being rotatably connected to the rotor (5) and the output element (73, 74) being configured to be rotatably connected to the input shaft of the gearbox; a plurality of groups of resilient members (77a, 77b) arranged to rotatably couple the input member (71, 72) and the output member (73, 74) and each having at least two resilient members ( 77a, 77b) circumferentially interposed between the input member (71, 72) and the output member (73, 74); and a phasing member (80) circumferentially interposed between the two resilient members (77a, 77b) of each elastic member group to arrange them in series; and a pendulum damper (55) comprising: a support member (56) movable in rotation about the axis X and integral in rotation with the phasing member (80) of the torsion damper with elastic members (70); and pendulum weights (57) movably mounted on the support member (56).
    [0002]
    2. Transmission assembly according to claim 1, wherein the support member (56) of the pendulum damper (55) is offset axially relative to the torsion damper elastic members (70).
    [0003]
    Transmission assembly according to claim 1 or 2, wherein the input element comprises a front guide washer (71) and a rear guide washer (72), integral in rotation with the rotor (5), and comprising bearing seats (78) extending circumferentially between each group of elastic members (77a, 77b), and the output member comprises a web (73) extending axially between the guide washers (71, 72 ) and having radial bearing lugs (79) extending circumferentially between each group of elastic members (77a, 77b) and a splined hub (74), integral with the web (73), intended to cooperate with the shaft input of the gearbox.
    [0004]
    4. transmission assembly according to claim 3, wherein the phasing member (80) is a phasing washer having a plurality of radial phasing tabs which are each disposed between the two elastic members (77a, 77b) of a same group.
    [0005]
    5. Transmission assembly according to claim 3 or 4, wherein the front guide washer (71), intended to be disposed opposite the gearbox, is provided with a central orifice, the organ phasing device (80) having a radially outer region extending axially between the web (73) and the front guide washer (71) and a radially inner region for fixing the support member (56) of the swinging damper (55) projecting forwards through the central hole of the front guide washer (71).
    [0006]
    6. Transmission assembly according to claim 5, wherein the support member (56) of the pendulum damper (55) comprises an annular zone and radially inner lugs (87) fixed, via means of fixing, to the phasing washer (80), in its radially inner region projecting forwards through the central orifice of the front guide washer (71).
    [0007]
    7. Transmission assembly according to any one of claims 3 to 6, wherein the phasing member (80) is centered and guided in rotation on the splined hub (74) via a bearing (82) .
    [0008]
    Transmission assembly according to any one of claims 3 to 7, wherein the rear guide washer (72) is guided and centered in rotation on the splined hub (74) via a bearing (75). .
    [0009]
    9. Transmission assembly according to any one of claims 3 to 8, wherein the clutch (2) comprises a friction disk (20) which is integral in rotation with the rotor (5) via a shaft intermediate (24), the rotor (5) having a central opening through which the intermediate shaft (24) passes, the rotor (5) being rotatably mounted to the intermediate shaft via a hub (38) and the rear guide washer (72) being fixed to the support hub (38) of the rotor (5).
    [0010]
    10. Transmission assembly according to claim 9, wherein the intermediate shaft (24) comprises a flange (40), the support hub (38) of the rotor (5) comprising an axial skirt (39) for supporting the rotor ( 4) and an inner flange (41) extending radially inwardly of the axial skirt (39), the flange (40) of the intermediate shaft (24) and the rear guide washer being secured to the inner flange by common fasteners (42).
    [0011]
    11. A transmission assembly according to any one of claims 1 to 10, further comprising a double damping flywheel (1) equipped with a primary flywheel (6) intended to be fixed to the crankshaft of the engine and a secondary flywheel (7). ) forming a reaction plate for the clutch (2) arranged to couple or uncouple in rotation the crankshaft of the engine and the rotor (5).
    [0012]
    12. Transmission assembly according to any one of claims 1 to 11, wherein the resilient members (77a, 77b) are housed in a sealed chamber filled with a lubricating agent.
    [0013]
    13. Motor vehicle equipped with a transmission assembly according to any one of claims 1 to 12.
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    同族专利:
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    引用文献:
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    DE102010027714A1|2010-07-20|2011-05-05|Daimler Ag|Drive train for motor vehicle, comprises drive unit connected with transmission element of vehicle gearbox through starting element|
    FR2976641A1|2011-06-14|2012-12-21|Valeo Embrayages|TORSION DAMPING DEVICE HAVING PENDULUM MASSELOTTES OFFSET AXIALLY IN RELATION TO GUIDE WASHERS|FR3047531A1|2016-02-08|2017-08-11|Valeo Embrayages|TRANSMISSION SYSTEM WITH PENDULAR DAMPING DEVICE|
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    DE102019117525A1|2018-06-28|2020-01-02|Valeo Embrayages|Torsion damping device equipped with a pendulum device|
    FR3086028A1|2018-09-18|2020-03-20|Valeo Embrayages|DISALIGNED HYBRID TORQUE TRANSMISSION DEVICE|
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    FR2830589B1|2001-10-08|2004-04-23|Valeo|AUTOMOTIVE VEHICLE TRANSMISSION KIT INCLUDING TWO CLUTCHES AND AN ELECTRIC MACHINE|
    FR2940825B1|2009-01-08|2014-10-31|Valeo Embrayages|DOUBLE FLYWHEEL DAMPER WITH DOUBLE DAMPING MEANS, IN PARTICULAR FOR A MOTOR VEHICLE|FR3039238B1|2015-07-24|2018-03-02|Valeo Embrayages|TORSION DAMPING DEVICE FOR A MOTOR VEHICLE TRANSMISSION SYSTEM|
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    DE102017203458A1|2017-03-02|2018-09-06|Zf Friedrichshafen Ag|Gear arrangement and method for operating a gear arrangement|
    DE102018126286A1|2018-10-23|2020-04-23|Schaeffler Technologies AG & Co. KG|Drive module with a support bearing device on the gearbox side|
    法律状态:
    2015-12-31| PLFP| Fee payment|Year of fee payment: 3 |
    2016-12-29| PLFP| Fee payment|Year of fee payment: 4 |
    2018-01-02| PLFP| Fee payment|Year of fee payment: 5 |
    2019-12-31| PLFP| Fee payment|Year of fee payment: 7 |
    2020-12-31| PLFP| Fee payment|Year of fee payment: 8 |
    2021-12-31| PLFP| Fee payment|Year of fee payment: 9 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1363122A|FR3015380B1|2013-12-19|2013-12-19|TRANSMISSION ASSEMBLY FOR A HYBRID VEHICLE EQUIPPED WITH A PENDULAR SHOCK ABSORBER|FR1363122A| FR3015380B1|2013-12-19|2013-12-19|TRANSMISSION ASSEMBLY FOR A HYBRID VEHICLE EQUIPPED WITH A PENDULAR SHOCK ABSORBER|
    DE112014005763.0T| DE112014005763T5|2013-12-19|2014-12-09|Transmission unit for a motor vehicle and motor vehicle|
    PCT/FR2014/053227| WO2015092210A1|2013-12-19|2014-12-09|Transmission assembly for motor vehicle and motor vehicle|
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