FR3069199A1 - TRANSMISSION DEVICE FOR A HYBRID VEHICLE - Google Patents

Abstract

The invention relates to a torque transmission device (1) comprising: - a torque input element (2), which can be coupled in rotation to a crankshaft (3) of an internal combustion engine, - a first torque output member (5), adapted to be rotatably coupled to a first input shaft of a gearbox (6), - a second torque output member (8), adapted to be rotatably coupled to a second input shaft of a gearbox (9), the second output element being arranged in parallel with the first output element in the torque transmission sense, - a rotary electrical machine (12) comprising a rotor (13) disposed in the torque transmission direction, between the input element (2) on the one hand and the first and second output elements (5, 8) on the other hand, the rotor being selectively connected to the input element by an input clutch (15) of multidisc type, the rotor being connected selec the first and second output members (5, 8), respectively, by a first and a second output clutch (16, 17) of multi-disk type, each clutch comprising an associated actuating member (56, 71, 72 ), a first stage of springs (31) between the input element and the rotor, characterized in that the fluid supply of the actuating members (56, 71, 72) is shared.

Description

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 a heat 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 2011 117 781 A1.

In document DE 10 2011 117 781 A1, the device comprises three separate actuating members for actuating the three clutches. Several oil paths are provided to supply the actuators, in particular a path on the internal combustion engine side and a path on the gearbox side which complicates the manufacture of the device.

In this device, it is also not intended to have a torsional damper in the interior of the electric machine. Such devices are optionally not very efficient in terms of filtration of acyclisms or bulky axially if such a damper is provided upstream, between the device and the heat 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 second torque output element, capable of being coupled in rotation to a second input shaft of a gearbox, the second output element being arranged in parallel with the first output element in the direction of the torque transmission ,

- a rotary electrical machine comprising a rotor arranged in the direction of the torque transmission, between the input element on the one hand and the first and second output elements on the other hand, the rotor being selectively connected to the element input by a multidisk type input clutch, the rotor being selectively connected to the first and second output elements, respectively, by a first and a second multidisk type output clutch, each of the clutches comprising an actuating member partner,

- a first stage of springs between the input element and the rotor, characterized in that the supply of fluid to the actuating members is shared.

Such a device makes it possible to have a single fluid inlet for actuating the clutches, which simplifies the manufacture of the device and of the oil supply devices.

According to one aspect of the invention, the device can also include a rotor support comprising an internal sleeve for the arrangement of the clutch actuating members.

Such a rotor support makes it possible to get out of the need to have several separate parts for the arrangement of the actuating members and for the support of the rotor. The radial support is shared for the actuating members and for the rotor.

According to another aspect of the invention, each actuating member can 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 capable of cooperating with the associated clutch. Each force transmission member is mobile under the effect of the pressure of the fluid in the actuation chamber. These actuators are also called "piston" type actuators.

Associated with the actuating chamber, each actuating member, in particular with the exception of the actuating member of the input clutch, may comprise a compensation chamber delimited in part by the transmission member of force 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.

According to another aspect of the invention, the actuating members can succeed one another axially. The actuators are all left close to the axis of rotation, the clutches can be arranged in the space between the rotor and said actuators. The supply of fluid to the actuators is also simplified.

According to another aspect of the invention, the internal sleeve can be carried radially by a fixed distributor. The distributor may include a fluid network for the supply of each of the actuating members. The distributor advantageously makes it possible to have only one fluid supply for all of the actuating members, which simplifies the device. The fluidic network is formed in a fixed rotating part whose construction and operation are simplified with respect to a supply of fluid in a rotating part, for example a gearbox shaft.

According to one aspect of the invention, the rotor can be carried radially, in particular only, by the distributor. Bearings, in particular needle bearings, are provided between the sleeve and the distributor. Preferably two bearings are provided, each being positioned at one end of the sleeve. The rolling members can be on the same radial height. The radial support function of the actuating members and the rotor is thus pooled.

In the sense of demand, there is no torque transmission at the interface, when one part is carried by another.

According to one aspect of the invention, the fluid network opens on the side of the gearbox in an accessible environment relative to the opposite side of the congested and hardly accessible internal combustion engine.

According to one aspect of the invention, the fluid network of the distributor can comprise, for each actuation chamber, a first series of axial channels, at least one channel and preferably two channels, circumferentially offset, which open onto the same circumferential groove , also provided in the dispenser, to supply the actuating chambers with fluid.

Opposite each circumferential groove, openings are provided in the sleeve for the passage of the fluid towards the actuation chamber.

The fluid network may also include a second series of axial channels, at least one channel and preferably two channels, circumferentially offset, which open onto the same circumferential groove for the passage of a coolant for the clutches.

The fluidic network can also include, for each actuating member, a third series of axial channels, at least one and preferably two, circumferentially offset which open onto the same circumferential groove to supply the compensation chamber with fluid. Cooling and compensating fluids can be the same.

For each clutch, the fluid network can include a single series of axial channels for cooling and supplying fluid to the compensation chamber.

Preferably, the fluid network can comprise a single series of axial channels for cooling the output clutches and supplying fluid to the compensation chambers of the output clutches.

According to one aspect of the invention, the compensation chambers, in particular that of the input clutch, may not be supplied with fluid.

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.

The dispenser thus has a notched outer periphery formed by the succession of circumferential grooves.

According to another aspect of the invention, the clutches can be stacked radially at least two by two.

According to another aspect of the invention, the clutches can all be stacked radially. There is a plane axis perpendicular to the axis of rotation of the device which cuts each clutch.

The input clutch can be radially outside the output clutches. The input clutch can in particular be at the same radial height as the rotor.

According to another aspect of the invention, the input clutch is offset from the output clutches away from the input element. The input clutch is thus on the gearbox side and the output clutches are on the side of the internal combustion engine. The output clutches can be axially between the input element and the input clutch. There is a plane perpendicular to the axis of rotation which leaves the input clutch on the gearbox side and which leaves the output clutches on the engine side.

In this configuration, the output clutches can be stacked radially to minimize the axial space allocated to the clutches.

Alternatively, the output clutches can also succeed one another axially. There is thus an axis parallel to the axis of rotation which intersects each of the clutches. Such an arrangement makes it possible to have a very compact device radially and to make the best use of the interior space of the electric machine. Such an arrangement also makes it possible to provide identical clutches and thus to improve the industrialization of the device.

When the input clutch is on the gearbox side, the output clutches are driven by the rotor support, in particular by the sleeve.

According to another aspect of the invention, the rotor support comprises a transverse partition, this partition being on the same axial side as all the clutches. This partition can also be on the same axial side as the actuators. The rotor support can encapsulate both clutches and actuators.

Such a partition therefore does not have a dedicated opening for the passage of a force transmission member, the clutches and the actuating members all being on the same side of the partition. The partition is thus simple to manufacture and robust because it is not weakened by holes.

The partition can be assembled with the internal sleeve, for example by welding. Alternatively, the partition and the inner sleeve may be in one piece.

The rotor support can also include a grooved outer sleeve which cooperates with the rotor. The external sleeve may be in one piece with the partition or assembled together, in particular by welding.

Alternatively, the partition may be between the input clutch and the associated actuator. The partition then includes openings for the passage of the force transmission member of at least one of the actuators. The force transmission member may have an external periphery equipped with a plurality of fingers having an axial orientation and each passing through the partition through an opening. The fingers are suitable and intended to cooperate with the first clutch.

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 one of the first and second output elements relating respectively to the first and the second output clutch d 'somewhere else,

- 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 carrier and the output disc carrier.

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, 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 three, 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 one aspect of the invention, all of the clutches can be carried by the rotor support so that it is not necessary to provide a specific radial guide. The fixed distributor supports the rotor, all of the actuators and clutches.

When the input clutch is on the gearbox side, the input disc carriers for the output clutches can extend from a secondary bulkhead that extends radially from the sleeve. The rotor support, more precisely the secondary partition, rotates the output clutches.

When the output clutches are stacked radially, the input disc carriers can extend on the same axial side. The secondary partition can define a compensation chamber for one of the actuating members. The output clutches can be symmetrical in this configuration.

When the output clutches succeed one another axially, the input disc carriers for the output clutches can be on either side of the secondary partition. The secondary partition can define at least one compensation chamber, preferably the two compensation chambers, of the output clutches. This allows not to multiply the parts of the device.

According to another aspect of the invention, a pendulum damping device is arranged between the first stage of springs and the rotor.

The pendulum damping device may comprise a pendulum support, at least one pendulum body movable relative to the support and at least one rolling member cooperating with at least one raceway integral with the support and with at least one raceway integral of 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.

According to another aspect of the invention, a drive element can be arranged between the first stage of springs and the input clutch to transmit the torque. The drive element may include the pendulum support. This drive element may include in particular a cylindrical skirt. This cylindrical skirt can extend radially between the rotor and the output clutches. This cylindrical skirt allows the torque to be transmitted from the side of the engine to the side of the gearbox.

The cylindrical skirt of the drive element may be integral with the disc carrier of the input clutch. The cylindrical skirt may in particular be in one piece with the disc holder or assembled together, in particular by welding.

According to another aspect of the invention, the pendulum support can be carried by the first outlet element. A rolling member, in particular a needle bearing, can be disposed between a radial end of the pendulum support and the first outlet element.

According to another aspect of the invention, the first stage of springs can be encapsulated. For this purpose, a wall can be arranged so as to isolate the first stage of springs and, optionally, the pendulum damping device from the rest of the device. The first stage of springs can be in a sealed space filled with a lubricating fluid, in particular grease. Alternatively, the pendulum damping device can be outside this sealed chamber.

According to another aspect of the invention, a second stage of springs can be provided between the input element and the rotor, the two stages of springs being arranged in series. The two spring stages can be arranged upstream of the input clutch.

According to one aspect of the invention, the first stage of springs and possibly the second stage of springs can be arranged in an interior space of the rotor.

The drive element can be arranged between the second stage of springs and the input clutch, in the sense of the torque transmission.

An intermediate element can be arranged between the two stages of springs to transmit the torque and to synchronize the springs.

When stages of springs are provided, the pendulum damping device can be arranged between the two stages of springs. The pendulum support can be integral with this intermediate element, in particular come integrally with said element or be assembled together.

The intermediate element can be carried by the input element. A rolling member, in particular a ball bearing, may be disposed between a radial end of the intermediate element and the input element, in particular the axial protuberance of the input element.

The drive element can be carried radially by the first torque output element. A rolling member, in particular a needle bearing, in particular a ball bearing, in particular a plain bearing can be arranged between a radial end of the drive element and the first torque output element. Alternatively, the drive element can be carried by the input element. A rolling member, in particular a ball bearing, can be arranged between a radial end of the drive element and an axial protuberance of the input element.

Alternatively, the pendulum damping device can be arranged between the second stage of springs and the input clutch.

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 in which the clutches are according to a first variant of their relative positioning,

FIG. 2 is a view in axial section according to a second example of the device according to the first variant,

FIG. 3 is a view in axial section according to a third example of the device in a second variant of relative positioning of the clutches,

FIG. 4 is a view in axial section according to a fourth example of the device according to the second variant,

FIG. 5 is a view in axial section according to a fifth example of the device according to the second variant,

FIG. 6 is a view in axial section according to a sixth example of the device in a third variant of relative positioning, and

- Figure 7 is an axial sectional view according to a seventh example of the device according to the third variant.

In relation to FIGS. 1 and 2, 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 examples considered, the second output element 8 is arranged in parallel with the first output element 5 in the direction of the torque transmission. Each of these elements rotate around an axis of rotation of the device X.

The device also comprises a rotary electrical machine 12 comprising a rotor 13 arranged 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. The device 1 also includes a rotor support 35 for its radial retention.

In the examples 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 input shaft 6 of the gearbox 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 input shaft 6 of the gearbox 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 the first output clutch 16 is configured in the engaged position. The first shaft of the box 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 input shaft 9 of the gearbox 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 input shaft 9 of the box 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 the second output clutch 17 is configured in the engaged position. The second shaft of the gearbox 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.

In all of the examples considered in FIGS. 1 to 7, the first output clutch 16 is arranged to engage the odd ratios of the gearbox and the second output clutch 17 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, 17 and the input clutch 15. The device is then in so-called "direct" mode.

The input clutch 15 can also transmit torque to the heat engine, the device is then in so-called "retro" mode.

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 in FIG. 1, the clutches 15, 16, 17 are all stacked radially. There is a same plane perpendicular to the axis X which intersects each clutch 15, 16, 17. The input clutch 15 is radially outside the output clutches. The input clutch is notably to be on the same radial height as the rotor.

The example in FIG. 2 differs from that in FIG. 1 in that the clutches are offset axially so that they are only stacked radially in pairs. There is a first plane perpendicular to the X axis which cuts the input clutch 15 and the first output clutch 16. There is a second plane perpendicular to the X axis, distinct from the first, which cuts the output clutches 16, 17.

In the examples considered, the input element 2 is 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.

In the example considered in FIG. 1, 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 shaft 9 of the box is hollow and surrounds the first input shaft 6 of the box.

In the example considered, the electric machine 12 is a synchronous permanent magnet machine. The electric machine comprises a fixed stator 14 arranged around the rotor 13.

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 springs. 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 in an interior space of the rotor 13, in particular over the same radial height as one of the output clutches 16, 17.

A drive element 33 is arranged between the second stage of springs 32 and the input clutch 15 to transmit the torque. This drive element 33 comprises a cylindrical skirt which cooperates with the input clutch 15 and a support part which cooperates with the first output element for the radial maintenance of this drive element 33. A rolling member, in particular a needle bearing 110 is here arranged between a radial end of the drive element 33 and the first torque output element 5. There is therefore no torque transmission between the drive element 33 and the first output element 5.

An intermediate element 34 is also arranged between the two stages of springs 31, 32 for transmitting the torque and synchronizing the springs. The intermediate element 34, of X-axis revolution, here has a section substantially in the shape of "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.

Still in the example considered in FIG. 1, the input clutch 15 comprises:

- an input disc holder 42, radially on the inside, driven in rotation by the input element 2 via the spring stages 31, 32,

- an outlet disc holder 43, radially outside, integral in rotation with the support 35, and

a multi-disc assembly 44 comprising three friction discs integral in rotation with the input disc holder, three plates respectively disposed on either side of each friction disc, integral in rotation with the outlet disc holder and the linings of friction plates arranged between the plates and the friction discs.

In the example considered, the input disc holder 42 is in one piece with the cylindrical skirt of the drive element 33 and the output disc holder is defined by the rotor support 35.

In the example considered, the first output clutch 16 comprises:

- an input disc holder 46, radially outside, integral in rotation with the rotor 13,

- 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 three friction discs integral in rotation with the input disc holder, four plates respectively arranged on either side of each friction disc, integral in rotation with the outlet disc holder and the linings friction plates arranged between the plates and the friction discs.

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 four friction discs integral in rotation with the input disc holder, five plates respectively disposed on either side of each friction disc, integral in rotation with the outlet disc holder and the linings of friction placed between the plates and the friction discs,

The linings are fixed here on the friction discs.

In the clutch configuration of 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.

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 for example 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 output disc holders 47, 50 of the output clutches are in one piece with the webs of the respective output elements.

In the example considered, the support 35 includes in particular a substantially transverse partition 36. This partition is on the same axial side as all the clutches 15, 16, 17.

The support 35 also includes an internal sleeve 55 for the arrangement of a first actuating member 56 of the input clutch, of a first actuating member 71 first output clutch 16 and of a second member actuating 72 of the second output clutch 17. The internal sleeve 55 is thus shared for the three actuating members 56, 71, 72.

In the example considered, the actuating members 56, 71, 72 follow one another axially. The actuators are all on the same radial height and they are all left close to the axis so that the clutches can be placed in the interior space of the rotor 13.

For clarity, the reference numbers associated with the actuating members 56, 71 and 72 of the device 1 have been given in FIG. 2. The structural differences between the example in FIG. 1 and the example in FIG. 2 will be explained.

In the example considered in FIGS. 1 and 2, each actuating member 56, 71, 72 comprises an actuating chamber, respectively numbered 58, 76, 77, delimited in part by the internal sleeve 55 and by a transmission member of force, respectively numbered 59, 79, 80, axially movable relative to the internal sleeve 55 and able to cooperate with the associated clutch, in particular with an end plate of the multidisk assembly of said associated clutch. These actuators are also called "piston" type actuators.

The force transmission members 59, 79, 80 are movable under the effect of the pressure of the fluid in the actuation chamber. The force transmission members act on the multi-disc assemblies to modify the configuration of the clutches.

In the examples considered in FIGS. 1 and 2, the partition 36 is between the input clutch 15 and the associated actuating member 56 and between the first output clutch 16 and the associated actuating member 71.

The force transmission member of the input clutch 59 has an external periphery equipped with a plurality of fingers 82 having an axial orientation and each passing through the partition through an 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.

The force transmission member of the first output clutch 79 has an external periphery also equipped with a plurality of fingers 84 having an axial orientation and each passing through the partition through an opening 85. The fingers are suitable and intended to cooperate with the first output clutch 16, in particular with an end plate of the multi-disc assembly 51. The partition is thus perforated in different places for the passage of the force transmission members.

Each actuating member 56, 71, 72 also includes a compensation chamber, respectively numbered 130, 131, 132, delimited in part by the associated force transmission member and by the internal sleeve 55. These chambers are sealed radially towards the exterior by means of seals.

The force transmission members 59, 79, 80 each form a barrier between the two chambers of the actuating members.

For each actuator, an axial stop means 60 is provided to limit the movement of the actuator chamber so that it is only the force transmission members 59, 79, 80 which move axially. The axial stop means here comprises a circlip 61 and a reinforcing ring 62.

Each actuator comprises an open position return means 64 also provided for recalling the force transmission member when the pressure in the actuation chamber is less than a threshold value.

In the example considered in FIG. 1, this return means 64 is a Belleville washer placed inside the clearing house

130, 131, 132.

In the example considered in FIG. 2, the return means 64 is a straight spring interposed between two contact cups, also arranged inside the compensation chamber 130, 131, 132. Combinations of the different types of means recall are possible.

In the example considered in FIGS. 1 and 2, the supply of fluid to the actuating members 56, 71, 72 is shared.

In the example considered, the internal sleeve 55 is carried radially by a fixed distributor 74. This distributor 74 includes a fluid network 66 for the supply of each of the actuating members 56, 71, 72. The fluid network opens on the side of the gearbox.

In the example considered, the fluid network 66 comprises, for each actuation chamber, a first series of axial channels, which open onto the same circumferential groove, also provided in the distributor, to supply the actuation chambers with fluid. . A channel 67 of the first series of channels and the circumferential groove 68 associated with the actuation chamber of the first output clutch 76 are visible in the cutting plane of Figures 1 and 2. Although not visible in the figures, openings are also provided in the sleeve 55 for the passage of the fluid towards the actuation chambers 58, 76, 77.

The fluid network also includes a second series of axial channels associated with the output clutches 16, 17 which open onto the same circumferential groove 140 for the passage of a coolant for the output clutches 16, 17. This second series of channels can also supply fluid to the compensation chambers of the output clutches 131,132.

The fluidic network finally comprises a second series of axial channels associated with the input clutch 15 which open onto the same circumferential groove 141 for the passage of a cooling fluid.

Six sealing rings 142, for example plastic, are provided on either side of each circumferential groove. These rings are worn by the distributor 74.

The distributor 74 thus has a notched external periphery formed by the succession of the circumferential grooves.

In the examples considered in Figures 1 and 2, the rotor 13 is only carried radially by the distributor 74. Two bearings 90 are provided are provided between the sleeve 55 and the distributor 74, each being positioned at one of the ends of the sleeve. All of the seals and circumferential grooves are between the bearings 90.

In the example considered in FIG. 3, the input element comprises a primary inertia 20 which 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 heat engine.

In the example considered in FIG. 3, a pendulum damping device 98 is disposed between the two stages of springs 31, 32. The pendulum damping device 98 comprises a pendulum support 99 integral with the intermediate element 34, at least one pendular 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 pendular body. The pendulum damping device 98 can comprise a plurality of pendulum bodies regularly arranged on a periphery of the axis X. Each pendulum body can cooperate with two rolling members, Each pendulum body comprises two pendulum masses 100 arranged on either side other from 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, which is here formed in two riveted parts, is integral with the intermediate element 34. The intermediate element and the pendulum support are carried by the input element 2. A ball bearing 102 is disposed between a radial end of the intermediate element 34 and an axial projection 103 of the input element.

In the example considered in FIG. 3, the cylindrical skirt of the drive element extends between the rotor 13 and the output clutches 16, 17. The drive element 33 is here carried radially by the input element 2. A ball bearing 104 is disposed between a radial end of the drive element 33 and the axial protuberance 103 of the input element. The input element 2 thus carries the two stages of springs 31, 32 and the pendulum damping device 98.

In the example considered in FIG. 3, the electric machine 12 also includes a rotor position sensor 30, in particular a contactless sensor.

The support 35 also includes an outer grooved sleeve 37 which cooperates with the rotor 13, the inner surface of which is also grooved. A translational stop means 38 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. This stop means 38 is here a notch on the outer periphery of the outer sleeve 37.

The input clutch 15 of the device 1 of FIG. 3 is inverted with respect to those of FIGS. 1 and 2. The input disk carrier 42 is outside the output disk carrier 43.

In the example considered in Figure 3, the input disc carriers of the output clutches are rotated by the rotor support

35, in particular by means of the sleeve 55 and a secondary partition 40 which extends radially from said sleeve 55. From this secondary partition 40 extend the input disc carriers 46, 49 of the output clutches . The secondary partition 40 also defines the compensation chamber 131 of the actuating member of the first output clutch.

The device of FIG. 3 is particularly remarkable in that the partition 36 is not only on the same side of all the clutches 15, 16, 17 but also on the same side of all the associated actuating members 56, 71,72. The rotor support thus encapsulates all clutches and all actuators.

The partition 36 is assembled with the sleeve 55, for example by welding. In the example of FIG. 3, the partition therefore does not have a dedicated opening for the passage of a force transmission member, which facilitates its manufacture.

In the example considered in FIG. 3, the input clutch 15 is offset from the output clutches 16, 17 away from the input element 2. The input clutch 15 is thus on the side of the gearbox and output clutches 16, 17 on the side of the internal combustion engine. The output clutches are axially between the input element and the input clutch. The output clutches 16, 17 are stacked radially.

In the example considered in FIG. 4, the drive element 33 is this time carried in the first output element. A needle bearing 110 is provided between the radial end of the drive element 33 and the first output element 5. The axial protrusion 103 of the input element then only serves to carry the device pendulum damping 98 arranged between the two stages of springs 31,32.

In the example considered in Figure 4, a guide element 150 of the drive member is also provided between the cylindrical skirt of said drive member and the disc holder so 43 of the input clutch. This guide element 150 is here a plain bearing.

In the example considered, a needle bearing 90 is arranged on a recess of the sleeve 55 and two needle bearing 90 are also arranged so as to frame the circumferential grooves.

The example considered in FIG. 5 differs from FIG. 1 in that the device 1 only comprises a first stage of springs 31.

In this configuration, the drive element 33 comprises the pendulum support 99. The cylindrical skirt formed integrally with the input disc carrier 42 of the input clutch is welded to the pendulum support .

The drive element 33 is again carried by the first output element 5. The needle bearing 110 is here disposed between an axial end of the pendulum support 99 and the first output element 5.

In the example considered, the first stage of springs can be encapsulated. For this purpose a wall 155 is arranged so as to isolate the first stage of springs 31 from the rest of the device 1. In addition, two elastic sheets 156 provided with pads 157 at their ends and integral in rotation with the drive element 33 are intended to rub against two guide washers of the input element 2 which axially frames the first stage of springs 31. The springs are thus isolated from the rest of the device 1.

The first stage of springs 31 may be in a sealed space filled with a lubricating fluid, in particular grease.

The input element 2 here comprises a flexible sheet 160 for connection with the crankshaft. The primary inertia 20 of the input element is here arranged radially outside the spring stage 31.

The examples considered in FIGS. 6 and 7 differ respectively from the examples in FIGS. 4 and 5 in that the three clutches 15, 16, 17 succeed one another axially. The clutches can all be close to the axis of rotation. The supply of actuators with fluid and the transmission of the actuation force are simplified. Such an arrangement makes it possible to have three identical clutches so that the device is less complex to produce and more economical.

In the examples considered, the input disc holders 46, 49 of the output clutches are on either side of the secondary partition 40. The secondary partition has a substantially "T" shape in the plane of FIGS. 6 and 7.

In the example considered in FIG. 6, a ball bearing 160 is provided between the radial end of the drive element 33 and the first output element 5.

The example described in FIG. 7 differs from that of FIG. 5 only by the arrangement of the output clutches 16, 17 and the associated actuating members. In this example, all the clutches and all the actuating members succeed one another axially.

The secondary partition 40 here has two symmetrical parts from one another. The partition here defines the two compensation chambers 131, 132 of the output clutches.

Claims (11)

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 (3) of an internal combustion engine, - a first torque output element (5), capable of being coupled in rotation to a first input shaft of a gearbox (6), - a second torque output element (8), capable of being coupled in rotation to a second input shaft of a gearbox (9), the second output element being arranged in parallel with the first output element at direction of torque transmission, - a rotary electrical machine (12) comprising a rotor (13) arranged in the direction of the torque transmission, between the input element (2) on the one hand and the first and second output elements (5, 8) on the other hand, the rotor being selectively connected to the input element by an input clutch (15) of the multidisc type, the rotor being selectively connected to the first and second output elements (5, 8), respectively, by a first and a second output clutch (16, 17) of the multidisk type, each of the clutches comprising an associated actuating member (56, 71, 72), - a first stage of springs (31) between the input element and the rotor, characterized in that the supply of fluid to the actuating members (56, 71, 72) is shared. 2. Device (1) according to claim 1, characterized in that it also comprises a rotor support (35) comprising an internal sleeve (55) for the arrangement of the clutch actuating members (56, 71, 72). 3. Device (1) according to any one of the preceding claims, characterized in that the actuating members (56, 71, 72) succeed one another axially. 4. Device (1) according to the preceding claim, characterized in that the internal sleeve (55) is carried radially by a fixed distributor (74), the distributor (74) comprising a fluid network (66) for supplying each of the actuating members (56, 71,72). 5. Device (1) according to one of the preceding claims, the clutches (15,16,17) being stacked radially at least two by two. 6. Device (1) according to the preceding claim, the clutches (15,16,17) being all stacked radially. 7. Device (1) according to one of claims 1 to 4, the input clutch (15) being offset from the output clutches (16, 17) away from the input element (2). 8. Device (1) according to the preceding claim, the output clutches (16, 17) are stacked radially or succeed one another axially. 9. Device (1) according to any one of claims 7 and 8, the rotor support (35) comprises a transverse partition (36), this partition being on the same axial side as all the clutches (15, 16, 17) and the actuating members (56, 71, 72) so that the rotor support encapsulates the clutches and the actuators. 10. Device (1) for transmitting torque according to any one of the preceding claims, characterized in that a pendular damping device (98) is arranged between the first stage of springs (31) and the rotor (13) . 11. Device (1) for transmitting torque according to any 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 stages of springs (31, 32) being arranged in series, the two stages of springs being arranged upstream of the input clutch (15).