• 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 torque transmission device, in particular for a motor vehicle, comprising: - a torque input element (2), capable of being coupled in rotation to a crankshaft of an internal combustion engine, - a first torque output member (5), adapted to be rotatably coupled to a first input shaft (6) of a gearbox, - a rotary electric machine (12) comprising a rotor (13) arranged in the sense of the transmission of torque between the input element (2) and the first output element (5), the rotor being selectively connected to the input element by an input clutch (15) of multidisc type, the rotor being selectively connected to the first output element by a first multi-disk output clutch (16), - a first spring stage (31) between the input element and the rotor, characterized in that the device comprises a rotor support (35) having a partition (36) sensibly A transverse section disposed axially between the input clutch (15) and the first output clutch (16).
    公开号:FR3069296A1
    申请号:FR1756970
    申请日:2017-07-21
    公开日:2019-01-25
    发明作者:Thierry Guinot；Jerome BOULET
    申请人:Valeo Embrayages SAS；
    IPC主号:
    专利说明:

    Transmission device for hybrid vehicle
    The present invention relates to the field of transmissions for motor vehicles. It relates in particular to a transmission device intended to be disposed, in the transmission chain, between an internal combustion engine and a gearbox.
    The invention relates in particular to transmission devices for a hybrid type motor vehicle in which an electric machine is also arranged between the engine and the gearbox.
    In the prior art, transmission assemblies are known, arranged between the gearbox and the heat engine and comprising an electric machine and a clutch on the engine side allowing the crankshaft of the heat engine to be coupled in rotation to the rotor of the electric machine. Thus, it is possible to shut down the heat engine each time the vehicle is stopped and restart it using the electric machine. The electric machine can also constitute an electric brake or provide a surplus of energy to the heat engine to assist it 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 can also link the electric machine to the gearbox by two separate torque paths each comprising an output clutch and a gearbox input shaft. Such a device is notably disclosed in document DE 10 2007 003 107 A1.
    In document DE 10 2007 003 107 A1, the device comprises three separate actuators for actuating the clutches. These actuators are here stacked radially and offset relative to the clutches which makes the device not very compact, in particular radially. Furthermore, the supply of oil for the actuator furthest from the axis of rotation of the device requires a complex course to be carried out. Finally, the intermediate piece has a complex shape, in particular between the input and output clutches. Finally, the oil is supplied on the internal combustion engine side in a congested environment.
    In this device, it is also not intended to have a torsional damper in the interior of the electric machine. Such devices are optionally ineffective in terms of filtration of acyclicism or bulky axially if such a damper is provided upstream, between the device and the engine.
    The invention aims to make it possible to benefit from a torque transmission device making it possible to reconcile the requirements of axial compactness without however degrading the filtration of torsional oscillations.
    The invention achieves this, according to one of its aspects, using a torque transmission device, in particular for a motor vehicle, comprising:
    - a torque input element, capable of being coupled in rotation to a crankshaft of an internal combustion engine,
    - a first torque output element, capable of being coupled in rotation to a first input shaft of a gearbox,
    - a rotary electrical machine comprising a rotor arranged in the direction of the torque transmission, between the input element and the first output element, the rotor being selectively connected to the input element by an input clutch of multi-disc type, the rotor being selectively connected to the first output element by a first multi-disc type output clutch,
    - a first stage of springs between the input element and the rotor, characterized in that the device comprises a rotor support comprising a substantially transverse partition disposed axially between the input clutch and the first output clutch.
    Such a rotor support makes it possible to effectively guide the rotor of the electric machine. Such a rotor support enables the functional connection to be made between the input clutch and the output clutches.
    According to one aspect of the invention, the partition can transmit the torque between the input element and the first output element. The bulkhead transmits the torque from the internal combustion engine to the gearbox. The partition also transmits the torque from the electric motor to the gearbox, in a direct direction of torque transmission, or to the internal combustion engine, in a retro direction of torque transmission.
    According to one aspect of the invention, the partition can form a counter-support for the input clutch and / or for the first output clutch.
    The partition allows to extract from specific room to realize the counter-support of the multi-disc assemblies.
    The back-up function makes it possible to limit the axial displacement of the multidisc assembly in reaction to the actuation force. The counter-bearing is therefore biased in the clutch position of the clutch.
    In particular, the partition can form a counter-support for the input clutch and for the first output clutch.
    The abutment can be applied in a localized area of the clutch, in particular a central area so that the clutch does not flex in reaction to the actuation force.
    The counter-supports can be bosses formed in the partition. They can also be formed by an added element. The counter-supports preferably extend over the entire circumference. The counter-supports can be continuous over the entire circumference or have discrete parts distributed over a circumference.
    According to one aspect of the invention, the support can be carried by the first output element. The support can be centered on the first output element.
    In the sense of demand, there is no torque transmission at the interface, when one part is carried by another.
    A plurality of, in particular two, axially offset support ball bearings can be provided between the support and the first output element. Alternatively, plain bearings can be used.
    Alternatively, the support can be carried by the input element. The input element then comprises an axial skirt disposed between the first output element and the support. The support ball bearings are then provided between this skirt and the rotor support.
    According to another aspect of the invention, the support may include an internal sleeve for the arrangement of an actuating member of the input clutch.
    The inner sleeve can extend from an inner end of the partition. The sleeve can be in one piece with the partition or assembled together, in particular by welding.
    The actuating member may comprise an actuating chamber delimited in part by the internal sleeve and by a force transmitting member movable axially relative to the internal sleeve and able to cooperate with the input clutch. The force transmission member is mobile under the effect of the pressure of the fluid in the actuation chamber. This actuator is also called a "piston" type actuator.
    Associated with the actuating chamber, the actuating member may include a compensation chamber delimited in part by the force transmitting member and by the internal sleeve. This chamber can also be waterproof.
    The force transmission device can form a barrier between the two chambers. The compensation chamber is intended to counteract the effects linked to the hydrodynamic oil pressure of the actuating chamber on the transmission member. The force transmission member can thus be moved axially by variation of the relative oil pressure of the actuation and compensation chambers.
    The support ball bearings can be arranged axially on either side of the actuation chamber, preferably on either side of the actuation and compensation chambers.
    According to another aspect of the invention, the first output element can be centered on the input element.
    The first output element may comprise a first web connected in rotation, for example by splined connection, to a first output shaft which may be the first input shaft of the gearbox.
    The input element may include a primary inertia capable of being fixed to a crankshaft nose, for example by a plurality of screws.
    A centering ring may be provided between the nose of the crankshaft and the first output shaft to make up for the mounting clearances between the heat engine and the gearbox.
    According to another aspect of the invention, the first output element comprises a fluid network for the supply of the actuating member of the input clutch.
    The fluidic network may comprise a first series of axial channels, at least one, circumferentially offset, formed in the first output shaft and which open onto the same circumferential groove to supply the actuator chamber of the actuator with fluid. input clutch. The first output shaft is thus a hollow shaft.
    Opposite the circumferential groove, openings are provided in the internal sleeve for the passage of the fluid towards the actuation chamber. When the rotor support is carried by the input element, openings are also provided in the axial skirt, facing the circumferential groove.
    According to another aspect of the invention, the fluidic network can also include a second series of axial channels, at least one, circumferentially offset, which open onto the same circumferential groove at the level of the input clutch for the passage of an input clutch coolant.
    Finally, according to another aspect of the invention, the fluid network can also include a third series of axial channels, at least one, circumferentially offset, which open onto the same circumferential groove to supply the actuator compensation chamber with fluid. of the input clutch. According to another aspect of the invention, the cooling and compensating fluids can be identical.
    The series of axial channels can be offset circumferentially two by two.
    Sealing rings, for example plastic, can be provided on either side of each circumferential groove.
    According to another aspect of the invention, the device can also include a second torque output element, capable of being coupled in rotation to a second input shaft of the gearbox.
    The second output element can be arranged in parallel with the first torque output element in the direction of the torque transmission, the rotor being selectively connected to the second output element by a second multidisc type output clutch. The second clutch can be on the same side as the first output clutch relative to the partition.
    The second output element can comprise a second web connected in rotation, for example by splined connection, to a second output shaft which can be the second input shaft of the gearbox.
    The second output shaft can be coaxial with the first output shaft, in particular it can be hollow and surround the first output shaft.
    According to another aspect of the invention, the support can comprise a secondary partition arranged substantially axially on the other side of the first and second output clutches relative to the partition. The output clutches are therefore axially framed by two partitions of the rotor support.
    The secondary partition can be extended radially inside by an internal secondary sleeve for the arrangement of a first actuating member and a second actuating member respectively of the first and second output clutches. The sleeve is thus shared for the two actuating members.
    The secondary sleeve can be carried by a fixed distributor. The dispenser may include a fluid network for supplying fluid to the first and second actuators.
    The actuating members may comprise an actuating chamber delimited in part by the secondary sleeve and by a force transmitting member movable axially relative to the secondary sleeve and able to cooperate with one of the output clutches.
    Associated with the actuating chamber, each actuating member may include a compensation chamber delimited in part by the force transmitting member and by the secondary sleeve. This chamber can also be sealed, at least radially outward.
    The force transmission device can form a barrier between the two chambers. The compensation chamber is intended to counteract the effects linked to the hydrodynamic oil pressure of the actuating chamber on the transmission member. The force transmission member can thus be moved axially by variation of the relative oil pressure of the actuation and compensation chambers.
    The actuating chambers of each of the actuating members can be arranged on the same radial height, which makes it possible to free up space under the rotor, for example to insert the first spring stage therein.
    Like the fluid network of the first outlet element, the fluid network of the distributor can include, for each actuation chamber, a first series of axial channels, at least one, circumferentially offset, which open onto the same circumferential groove, also provided in the dispenser, to supply fluid to the actuating chambers.
    Opposite the circumferential groove, openings are provided in the secondary sleeve for the passage of the fluid towards the actuation chamber.
    The fluid network can also include a second series of axial channels, at least one, circumferentially offset, which open onto the same circumferential groove for the passage of a coolant for the output clutches. Openings in the secondary sleeve may be provided in the secondary partition or at the foot of said partition for the passage of the cooling fluid.
    The fluid network can also include, for each compensation chamber, a third series of axial channels, at least one, circumferentially offset which open onto the same circumferential groove to supply the compensation chamber with fluid.
    Cooling and compensating fluids can be the same.
    Preferably, the second and third series of axial channels are identical and there is only one circumferential groove for the coolant and the compensating fluid.
    The axial channels can be offset circumferentially two by two.
    Sealing rings, for example plastic, can be provided on either side of each circumferential groove.
    The dispenser thus has a notched outer periphery formed by the succession of circumferential grooves.
    The secondary partition can be framed by the actuating chambers of each of the actuating members.
    Needle roller bearings can be provided between the secondary sleeve and the distributor, preferably two, arranged axially on either side of the actuation chambers so that they are at the axial ends of the secondary sleeve.
    According to another aspect of the invention, the first and second output clutches are stacked radially. This improves the axial compactness of the device.
    The first output clutch can be radially outside the second output clutch.
    The force transmission member of the first output clutch may have an external periphery equipped with a plurality of fingers having an axial orientation and each passing through the secondary partition through an opening.
    The fingers are suitable and intended to cooperate with the first clutch.
    The secondary partition can form a counter-support for the second output clutch to limit the axial displacement of the multi-disc assembly in response to the actuation force. This counter-support can be a boss of the secondary partition, it can also be formed by an added element. The counter support preferably extends over the entire circumference.
    According to another aspect of the invention, each of the clutches of the device can include:
    - an input disc carrier driven in rotation by the input element relating to the input clutch on the one hand and integral in rotation with the rotor support concerning the first and second output clutches on the other hand,
    - an output disc holder integral in rotation with the rotor support concerning the input clutch on the one hand and integral with the first and second output elements relating respectively to the first and the second output clutch on the other hand,
    - A multi-disc assembly comprising at least one friction disc integral in rotation with one of the input and output disc holders, at least two plates respectively disposed on either side of each friction disc, integral in rotation on the other, input and output disc holders and friction linings arranged between the plates and a friction disc, the clutch describing a disengaged position and a engaged position in which said plates and the friction disc pinch the friction linings so as to transmit a torque between the input disc holder and the output disc holder.
    The linings can be fixed to the friction discs, in particular by gluing, in particular by riveting, in particular by overmolding. As a variant, the linings are fixed to the plates.
    Each disc holder can synchronize all the plates or all the friction discs in rotation. The disc holders may include a cylindrical skirt on which the plates and the friction discs are mounted.
    The plates and the discs can cooperate with the disk carriers along one of their radial peripheries by complementarity of shape. Cylindrical skirts, plates and friction discs can for example be grooved.
    According to another aspect of the invention, for each clutch, the plates can be integral in rotation with the disc holder integral in rotation with the rotor support. This makes it possible to produce the counter-support for each clutch by the partitions which are integral with the rotor support.
    According to another aspect of the invention, the output disc holder of the first output clutch is radially inside and the output disc holder of the second output clutch is radially outside.
    The clutches can be wet or dry. Preferably, the clutches have between two and seven friction discs, preferably four or five friction discs.
    The clutches can be of the “normally open” type, an effort must be exerted by the force transmission members to transmit a torque.
    The force transmission members can exert an axial force on the multidisk assemblies to move the plates towards the discs, in particular on an end plate of the multidisc assembly. The actuation is thus of the "pushed" type.
    According to another aspect of the invention, the first stage of springs is arranged between the input element and the input clutch in the direction of the torque transmission. The first stage of springs can be arranged in the interior space of the electric machine, in particular radially between the input clutch and the rotor.
    According to another aspect of the invention, a second stage of springs can be provided between the input element and the rotor, in the sense of the torque transmission, the two stages of springs being arranged in series.
    The two spring stages can be arranged upstream of the input clutch. The two spring stages can be arranged radially between the input clutch and the rotor. The two stages of springs can be arranged on the same radial height.
    According to another aspect of the invention, a pendulum damping device can be arranged between the two stages of springs. Alternatively, the pendulum damping device can be arranged between the first stage of springs and the input clutch when a single stage of springs is provided.
    An intermediate element is arranged between the spring stages to transmit the torque and to synchronize the springs.
    The pendulum damping device may comprise a pendulum support integral with the intermediate element, at least one pendular body movable relative to the support and at least one rolling member cooperating with at least one rolling track integral with the support and with at minus one track attached to the pendulum body.
    The pendulum damping device may comprise a plurality of pendulum bodies regularly arranged around a periphery of the axis of rotation. Each pendulum body can cooperate with two rolling members, Each pendulum body can comprise two pendulum masses arranged on either side of the support. The pendulum bodies can be arranged radially outside the springs, preferably at the same radial height as the stator.
    The pendulum support can be integral with the intermediate element or they can be assembled, for example by riveting.
    The intermediate element can be carried by the input element. A ball bearing can be provided between the intermediate element and the input element.
    According to an alternative arrangement of the second spring stage, the input clutch can be arranged in the direction of the torque transmission between the two spring stages.
    According to another aspect of the invention, the electric machine can be a synchronous permanent magnet machine. Such a machine has a large diameter which is favorable for integrating the parts of the device.
    The invention will be better understood, and other objects, details, characteristics and advantages thereof will appear more clearly during the following description of several particular embodiments of the invention, given solely by way of illustration and without limitation. , with reference to the appended figures.
    FIG. 1 is a view in axial section of an example of the device according to the invention,
    FIG. 2 is a view in axial section according to a second example of the device, and
    - Figure 3 is an axial sectional view according to a third example of the device.
    In connection with FIG. 1, there is a torque transmission device 1 comprising:
    - a torque input element 2, capable of being coupled in rotation to a crankshaft 3 of an internal combustion engine,
    - a first torque output element 5, capable of being coupled in rotation to a first input shaft 6 of a gearbox,
    - a second torque output element 8, capable of being coupled in rotation to a second input shaft 9 of the gearbox.
    In the example considered, the second output element 8 is arranged in parallel with the first output element 5 in the direction of the torque transmission.
    The device also comprises a rotary electrical machine 12 comprising a rotor 13 disposed in the direction of the torque transmission, between the input element 2 on the one hand and the first output element 5 and the second output element 8 of somewhere else.
    In the example considered, the rotor 13 is selectively connected:
    - to the input element 2 by an input clutch 15 of the multi-disc type,
    to the first outlet element 5 by a first outlet clutch 16 of the multi-disc type, and
    - the second output element 8 by a second output clutch 17 of the multi-disc type.
    The first gearbox input shaft 6 is coupled in rotation to the crankshaft 3 and driven by it in rotation when the first clutch 15 and the first output clutch 16 are configured in a so-called engaged position. In this configuration, the rotor 13 can also supply excess energy to the gearbox.
    The first gearbox input shaft 6 is coupled in rotation to the rotor 13 and driven by it in rotation when the first clutch 15 is configured in a so-called disengaged position and when the first output clutch 16 is configured in the engaged position. The first gearbox shaft is then only driven by the rotor. In this configuration, the electric machine can also act as a brake and be in an energy recovery mode.
    Similarly, the second gearbox input shaft 9 is coupled in rotation to the crankshaft 3 and driven by it in rotation when the first clutch 15 and the second output clutch 17 are configured in a so-called engaged position.
    The second gearbox input shaft 6 is coupled in rotation to the rotor 13 and driven by it in rotation when the first clutch 15 is configured in a so-called disengaged position and when the first output clutch 16 is configured in the engaged position. The second gearbox shaft is then only driven by the rotor.
    When the first and second output clutches 16, 17 are in the disengaged configuration and the input clutch is in the engaged configuration, the rotor 13 can be driven by the internal combustion engine. The electric motor is then in an energy recovery mode.
    Of course, each clutch can take any configuration between the engaged configuration and the disengaged configuration.
    In all of the examples considered with reference to FIGS. 1 to 7, the first output clutch 16 is arranged to engage the odd ratios of the gearbox and the second output clutch is arranged to engage the even ratios and the reverse gear of the gearbox. Alternatively, the ratios supported by said first output clutch 16 and second output clutch 17 can be respectively reversed.
    The clutches are arranged to alternately transmit a so-called input power - a torque and a rotation speed - from the internal combustion engine, to one of the two gearbox input shafts, depending on the respective configuration of each output clutch 16 and 17 and the input clutch 15.
    The output clutches 16, 17 are arranged so as not to be simultaneously in the same engaged configuration. However, they can simultaneously be configured in their disengaged position.
    In the example considered, the output clutches 16, 17 are stacked radially, the first output clutch is radially outside.
    In the example considered, the input element 2 comprises a primary inertia 20 fixed to a crankshaft nose 21 by a plurality of screws 23, for example distributed regularly over a whole periphery of the axis of rotation X of the device 1 The primary inertia extends radially to the periphery of the electric machine 12, in particular to the periphery of a stator 14 of the electric machine. The primary inertia 20 is here a slice of revolution arranged on the side of the internal combustion engine (not shown).
    In the example considered, the first and second output elements 5, 8 respectively comprise a first and a second web 25, 28 connected by a splined connection respectively to the first and to the second input shaft 6, 9 of the gearbox . The second input 9 is hollow and surrounds the first input shaft 6.
    In the example considered, the electric machine 12 is a synchronous permanent magnet machine. The stator 14, fixed, is outside the rotor
    13. The electric machine 12 also includes a rotor position sensor 30, in particular a contactless sensor.
    In the example considered, the device 1 also comprises a first stage of springs 31 and a second stage of springs 32, in series with the first stage of spring. The two spring stages are arranged between the input element 2 and the rotor 13, in particular upstream of the input clutch 15, in the direction of the torque transmission. In a variant not shown, the input clutch can be placed between the two stages of springs.
    In the example considered, the two stages of springs 31, 32 are radially between the input clutch and the rotor, over the same radial height and an intermediate element 34 is arranged between the two stages to transmit the torque and synchronize the springs. The intermediate element 34 here has a section substantially in the shape of a "Y".
    In the example considered, the springs are curved springs arranged regularly around the periphery of the X axis. The spring stages are here axially offset from one another, but one can imagine that the first and second groups of springs are on the same axial height. Circumferentially, a portion of the intermediate element is then placed between each spring of the first group and each spring of the second group. In this configuration, the springs can be straight springs.
    In the example considered, the spring stages 31, 32 each comprise four springs.
    In the example considered, the device 1 also comprises a rotor support 35 for its radial retention. This support 35 comprises in particular a substantially transverse partition 36 disposed axially between the input clutch 15 on the one hand and the first and second output clutches 16, 17, on the other hand.
    The support 35 also includes a grooved outer sleeve 37 which cooperates with the rotor, the inner surface of which is also grooved. A translational stop means 38, for example a circlip, is also provided between the rotor 13 and the partition 36 to allow the correct positioning of the rotor relative to the stator during the assembly of said rotor to the rest of the device 1.
    In the example considered, the support 35 also comprises a secondary partition 40 disposed substantially axially on the other side of the first and second output clutches relative to the partition 36. The output clutches 16, 17 are therefore axially framed by two support partitions 35.
    For clarity, the numerical references associated with the clutches of the device 1 have been given in FIG. 2. There is no structural difference with respect to the example considered in FIG. 1 with regard to these clutches.
    In the example considered, the input clutch 15 comprises:
    - an input disc holder 42, radially on the outside, rotated by the input element 2 via the spring stages 31, 32,
    - an outlet disc holder 43, radially inside, integral in rotation with the support 35, and
    a multi-disc assembly 44 comprising a plurality of friction discs integral in rotation with the inlet and outlet disc holder, at least two plates respectively disposed on either side of each friction disc, integral in rotation with the holder output discs and friction linings arranged between the plates and a friction disc.
    In the example considered, the first output clutch 16 comprises:
    - an input disc holder 46, radially outside, integral in rotation with the support 35,
    - an outlet disc holder 47, radially inside, secured to the first web 25, in particular made in one piece with said web,
    a multi-disc assembly 48 comprising a plurality of friction discs integral in rotation with the inlet and outlet disc holder, at least two plates respectively disposed on either side of each friction disc, integral in rotation with the holder output discs and friction linings arranged between the plates and a friction disc,
    In the example considered, the second output clutch 17 comprises:
    - an input disc holder 49, radially inside, integral in rotation with the support 35,
    an outlet disc holder 50, radially on the outside, integral with the second web 28, in particular made in one piece with said web,
    a multi-disc assembly 51 comprising a plurality of friction discs integral in rotation with the inlet and outlet disc holder, at least two plates respectively disposed on either side of each friction disc, integral in rotation with the holder output discs and friction linings arranged between the plates and a friction disc,
    In their clutch configuration of the clutches 15, 16, 17, said plates and the friction disc pinch the friction linings so as to transmit a torque between the input disc holder and the output disc holder.
    Each of the multi-disc assemblies 44, 48, 51 comprises five discs on which a friction lining is fixed on each side. Each set also includes six trays, the trays define the axial ends of the multi-disc assembly.
    In the example considered, each disc holder synchronizes in rotation the set of plates or the set of friction discs. Each disc holder has a cylindrical skirt on which the plates and the friction discs are mounted. The plates and the discs cooperate with the disc holders along one of their radial peripheries by complementarity of shape. The cylindrical skirts, the plates and the friction discs are grooved.
    In the example considered, the disc holders of the output clutches 47, 50 are facing each other, no part is interposed between them. The disc carrier of the first output clutch allows the secondary partition 40 to be driven in rotation by the partition 36, this disc carrier transmits the torque to the second output clutch 17.
    In the example considered, the input disc carrier 50 of the second clutch extends axially from the secondary partition 40.
    In the example considered, the support 35 also includes an internal sleeve 55 for the arrangement of an actuating member 56 of the input clutch. This internal sleeve comes as an extension of an internal end of the partition 36. The sleeve is here in one piece with the partition 36. The reference numerals associated with the actuation of the clutches are also given in FIG. 2.
    In the example considered, the actuating member 56 comprises an actuating chamber 58 delimited in part by the internal sleeve 55 and by a force transmitting member 59 movable axially relative to the internal sleeve and capable of cooperating with the input clutch 16, in particular with an end plate of the multi-disc assembly 44. The force transmission member is mobile under the effect of the pressure of the fluid in the actuation chamber. This actuator is also called a "piston" type actuator.
    An axial stop means 60 is provided to limit the movement of the actuation chamber so that it is only the force transmission member 59 which moves axially. The axial stop means here comprises a circlip 61 and a reinforcing ring 62.
    A return means in the open position 64 also provided for recalling the force transmission member when the pressure in the actuation chamber is below a threshold value. This return means is here a Belleville washer arranged, outside the actuation chamber 56 between the transmission member and a support element secured to the support 35, in particular secured to the output disc holder 43.
    In the example considered, the first input shaft 6 of the gearbox comprises a fluid network 66 for supplying the actuating member 56. The fluid network comprises an axial channel 67 of a first series, which open onto a circumferential groove 68 to supply the actuating chamber 58 with fluid.
    Opposite the circumferential groove, openings, not visible in the section plane of the figures, are provided in the internal sleeve 55 for the passage of the fluid towards the actuation chamber 58.
    The fluid network 66 also comprises a second series of axial channels, at least one, circumferentially offset, which open onto the same circumferential groove 69 at the level of the input clutch for the passage of a clutch coolant. input.
    Three sealing rings 70, for example plastic, are provided on either side of each circumferential groove.
    In the example considered, the secondary partition 40 is extended radially inside by an internal secondary sleeve 71 for the arrangement of a first 72 and a second 73 actuating members of the first and second output clutches respectively. 16, 17. The secondary sleeve 71 is thus shared for the two actuating members 72, 73.
    In the example considered, the secondary sleeve 71 is carried by a fixed distributor 74. This distributor is concentric with the box input shafts. The distributor 74 includes a fluid network 75 for supplying fluid to the first and second actuating members 72, 73.
    The actuating members 72, 73 each comprise an actuating chamber respectively 76, 77 delimited in part by the secondary sleeve 71 and by a force transmitting member movable axially, respectively 79, 80 relative to the secondary sleeve and able to cooperate with one of the output clutches.
    In the example considered, the force transmission member of the first output clutch 73 has an external periphery equipped with a plurality of fingers 82 having an axial orientation and each passing through the secondary partition in favor of a opening 83. The fingers 82 are suitable and intended to cooperate with the first output clutch, in particular with an end plate of the multi-disc assembly 44.
    Identical to the actuating member 56 of the input clutch 15, the actuating members each comprise a means for returning to the open position, respectively 84, 85, and an axial stop means 86, 87 in the same configurations as those of the actuating member of the input clutch. In particular, the return means 84 in the open position of the first output clutch is a Belleville washer placed between the secondary partition 40 and the force transmission member 79.
    In the example considered, the actuation chambers 76, 77 can be arranged on the same radial height. The secondary partition 40 is framed by the actuation chambers 76, 77.
    In the example considered, the fluid network 75 of the distributor comprises an axial channel 110 which opens onto a circumferential groove 111 formed in the distributor 74, for supplying fluid to the actuation chamber 76 of the first output clutch. Other axial channels offset circumferentially from the axial channel 110 and opening onto the same circumferential groove 111 may define a first series of axial channels. Opposite the circumferential groove, openings, not visible in the section plane of the figures, are provided in the secondary sleeve 71 for the passage of the fluid towards the actuation chamber 76.
    Such an axial channel is not visible in the section plane of the figures, but the preceding paragraph also applies to the second output clutch 17.
    The fluid network may also include a second series of axial channels, at least one, circumferentially offset, which open onto the same circumferential groove 113 for the passage of a coolant for the output clutches 16, 17. Openings in the sleeve secondary may be provided in the secondary partition or at the foot of said partition for the passage of the coolant.
    Four sealing rings 114, for example plastic, can be provided on either side of each circumferential groove.
    In the example considered, two needle bearings 90 are provided between the secondary sleeve 71 and the distributor 74 arranged axially on either side of the actuation chambers 76, 77.
    In the example considered, the secondary partition 40 forms a counter-support 95 for the second output clutch 17 to limit the axial movement of the multidisk assembly 51 in reaction to the actuation force. Against the support 95 is here a boss preferably extending over the entire circumference.
    In the example considered, the partition 36 forms a counter-support 96 for the input clutch 15 and a counter-support 97 for the first output clutch 16. This partition makes it possible to extract from specific part to carry out the counter support for multi-disc assemblies.
    The counter-support is applied in a localized area of the multi-disc assemblies 44, 48.
    The counter-supports 96, 97 are bosses of the partition 36 which preferably extend over the entire circumference.
    In the example considered, the first input shaft 6 is centered on the input element 2, in particular by means of a centering ring 92 provided between the nose of the crankshaft 21 and the first shaft entry 6.
    In the examples considered in Figures 1 and 2, the support 35 is carried by the first input shaft 6 and centered on the first input shaft 6 of the gearbox. Two axially offset support ball bearings 93 are provided, they axially frame the actuation chamber of the input clutch 15 and the radial channels 68 of the fluid network. The bearings 93 are mounted at "O" so as to support a misalignment of the first gearbox input shaft 6.
    In the example considered in Figure 3, the support 35 is carried by an axial skirt 105 of the input element 2 disposed between the inner sleeve and the first shaft 6 of the gearbox. The support ball bearings 93 are then provided between this skirt and the rotor support. Openings are also provided in the axial skirt 105, facing the circumferential grooves associated with the actuation chamber and the cooling fluid.
    In the example considered in FIG. 3, the internal sleeve 55 and the partition 36 come from two separate parts assembled together by welding. Openings are also provided in the axial skirt opposite the openings 69 of the sleeve.
    What has been described with reference to FIG. 1 applies to the description of FIG. 3 with the exception of the last two paragraphs.
    Finally, in the example considered in FIG. 2, differs from that of FIG. 1 in that a pendulum damping device 98 is arranged between the two stages of springs 31, 32. The pendulum damping device 98 comprises a pendulum support 99 secured to the intermediate element, at least one pendulum body movable relative to the support and at least one rolling member cooperating with at least one rolling track secured to the support and with at least one rolling track secured to the body pendulum.
    The device may include a plurality of pendulum bodies regularly arranged around the periphery of the X axis. Each pendulum body can cooperate with two rolling members, Each pendulum body comprises two pendulum masses 100 arranged on either side of the support 99.
    In the example considered, the pendulum bodies are arranged radially outside the springs, preferably at the same radial height as the stator 14.
    The pendulum support 99 is here formed in two parts riveted between them and welded to the intermediate element 34. The intermediate element is carried by the input element 2 by means of a ball bearing 102 provided between the 'intermediate element 34 and the input element 2.
    权利要求:
    Claims (11)
    [1" id="c-fr-0001]
    1. Torque transmission device (1), in particular for a motor vehicle, comprising:
    - a torque input element (2), capable of being coupled in rotation to a crankshaft of an internal combustion engine,
    - a first torque output element (5), capable of being coupled in rotation to a first input shaft (6) of a gearbox,
    - a rotary electric machine (12) comprising a rotor (13) arranged in the direction of the torque transmission, between the input element (2) and the first output element (5), the rotor being selectively connected to the the input element by an input clutch (15) of the multi-disc type, the rotor being selectively connected to the first output element by a first output clutch (16) of the multi-disc type,
    - A first stage of springs (31) between the input element and the rotor, characterized in that the device comprises a rotor support (35) comprising a substantially transverse partition (36) disposed axially between the clutch of input (15) and the first output clutch (16).
    [2" id="c-fr-0002]
    2. A device (1) for transmitting torque according to claim 1, the partition (36) forming a counter-support (86, 87) for the input clutch (15) and / or for the first output clutch ( 16).
    [3" id="c-fr-0003]
    3. Device (1) for transmitting torque according to one of the preceding claims, characterized in that the support (35) is carried by the first output element (5) or by the input element (2).
    [4" id="c-fr-0004]
    4. Device (1) for transmitting torque according to one of the preceding claims, the support (35) comprises an internal sleeve (55) for the arrangement of an actuating member (56) of the clutch. Entrance.
    [5" id="c-fr-0005]
    5. Device (1) for transmitting torque according to any one of the preceding claims, characterized in that the first output element (5) is centered on the input element (2).
    [6" id="c-fr-0006]
    6. Device (1) for transmitting torque according to one of the preceding claims, the first output element (5) comprises a fluid network (66) for supplying the actuating member (56) of the input clutch.
    [7" id="c-fr-0007]
    7. Device (1) for transmitting torque according to one of the preceding claims, characterized in that it also comprises a second torque output element (8), capable of being coupled in rotation to a second input shaft (9) of a gearbox, the second output element being arranged in parallel with the first torque output element (5) in the direction of the torque transmission, the rotor (12) being selectively connected to the second output element by a second output clutch (17) of the multi-disc type.
    [8" id="c-fr-0008]
    8. Device (1) for transmitting torque according to the preceding claim, characterized in that the support (35) comprises a secondary partition (40) disposed substantially axially on the other side of the first and second output clutches (16, 17 ) relative to the partition (35), the secondary partition (40) extending radially inside by an internal secondary sleeve (71) for the arrangement of a first actuating member (72) and a second actuator (73) respectively of the first and second output clutches (16, 17), the secondary sleeve (71) being carried by a fixed distributor (74), the distributor comprising a fluid network (75) for the supply of fluid to the first and second actuator.
    [9" id="c-fr-0009]
    9. Device (1) for transmitting torque according to claim 7 or 8, characterized in that the first and second output clutches (16, 17) are stacked radially.
    5
    [10" id="c-fr-0010]
    10. Device (1) for transmitting torque according to one of the preceding claims, characterized in that a second stage of springs (32) is provided between the input element (2) and the rotor (13 ), the two spring stages (31, 32) being arranged in series, the two spring stages being arranged upstream of the input clutch (15).
    o
    [11" id="c-fr-0011]
    11. Device (1) for transmitting torque according to the preceding claim, characterized in that a pendular damping device (98) is disposed between the two stages of springs (31, 32).
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    同族专利:
    公开号 | 公开日
    FR3069296B1|2020-02-28|
    DE102018116587A1|2019-01-24|
    CN109278526A|2019-01-29|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    EP1777426A1|2005-10-20|2007-04-25|Getrag Ford Transmissions GmbH|Double clutch|
    EP2383140A1|2008-11-11|2011-11-02|Kabushiki Kaisha F.C.C.|Power transmitting device for hybrid vehicle|
    EP2287487A1|2009-08-21|2011-02-23|Volkswagen Aktiengesellschaft|Power transmission module for a motor vehicle|WO2020169141A1|2019-02-19|2020-08-27|Schaeffler Technologies AG & Co. KG|Compact clutch assembly of a triple clutch for an axially parallel hybrid module|DE102007003107B4|2006-01-16|2011-05-05|Borgwarner Inc., Auburn Hills|Triple clutch for hybrid drive with dual-clutch transmission|DE102019115903A1|2019-03-07|2020-09-10|Schaeffler Technologies AG & Co. KG|Hybrid module with triple clutch and drive train|
    DE102019117059A1|2019-06-25|2020-12-31|Schaeffler Technologies AG & Co. KG|Hybrid module and drive arrangement for a motor vehicle|
    DE102020100832A1|2020-01-15|2021-07-15|Schaeffler Technologies AG & Co. KG|Coupling device and hybrid arrangement|
    法律状态:
    2019-01-25| PLSC| Search report ready|Effective date: 20190125 |
    2019-07-31| PLFP| Fee payment|Year of fee payment: 3 |
    2020-07-31| PLFP| Fee payment|Year of fee payment: 4 |
    2021-07-29| PLFP| Fee payment|Year of fee payment: 5 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1756970|2017-07-21|
    FR1756970A|FR3069296B1|2017-07-21|2017-07-21|TRANSMISSION DEVICE FOR HYBRID VEHICLE|FR1756970A| FR3069296B1|2017-07-21|2017-07-21|TRANSMISSION DEVICE FOR HYBRID VEHICLE|
    DE102018116587.0A| DE102018116587A1|2017-07-21|2018-07-09|Transmission device for a hybrid vehicle|
    CN201810810924.6A| CN109278526A|2017-07-21|2018-07-23|Transmission device for hybrid vehicle|
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