WO2019162300A1

WO2019162300A1 - Transmission device for a hybrid vehicle

Info

Publication number: WO2019162300A1
Application number: PCT/EP2019/054162
Authority: WO
Inventors: Thierry Guinot; Fabien LEBEAU; Pierre Tisserand; Jean-Christophe Pecoul; Radhouane KHLISSA
Original assignee: Valeo Embrayages
Priority date: 2018-02-20
Filing date: 2019-02-20
Publication date: 2019-08-29
Also published as: FR3078122B1; EP3755563A1; CN112041189A; FR3078122A1

Abstract

The invention relates to a torque transmission device (1), in particular for a motor vehicle, comprising: - a torque input element (2) able to be rotationally coupled to a crankshaft (3) of an internal combustion engine; - a first torque output element (5) able to be rotationally coupled to a first input shaft of a gearbox (6); - a rotary electrical machine (12) comprising a stator (14) comprising a plurality of coils and a rotor (13) disposed in the direction of the transmission of torque, between the input element (2), on the one hand, and the first output element (5), on the other hand, the rotor being selectively connected to the input element by an input multi-disc clutch (15), the rotor being selectively connected to the first output element (5) by a first output multi-disc clutch (16), the clutch having an associated activation member; - a spring stage (31) between the input element and the rotor; - an intermediate element for transmission of torque between the spring stage (31) and the input clutch (15), characterised in that a transverse partition (50) is axially disposed between the spring stage (31) and the stator (14) in order to support and/or centre the intermediate element and/or to form a sealed barrier, the axial distance and/or the material and/or the shape of said partition being selected to minimise the joule losses of the stator field within said partition.

Description

Transmission device for a 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 arranged in the transmission chain between a heat engine and a gearbox.

The invention relates in particular to the transmission devices for a hybrid-type motor vehicle in which an electric machine is also arranged between the engine and the gearbox.

In the state of the art, it is known transmission assemblies, arranged between the gearbox and the engine and comprising an electric machine and a clutch on the motor side for coupling in rotation the crankshaft of the engine to the rotor of the engine. the electric machine. Thus, it is possible to shut down the engine at each stop of the vehicle and restart it with the electric machine. The electric machine can also constitute an electric brake or bring a surplus of energy to the heat engine to assist or prevent it from stalling. The electric machine can also drive the vehicle. Another possibility, when the engine is running, the electric machine plays the role of an alternator. Such a transmission assembly can also link the electric machine to the gearbox.

Such devices are generally integrated in highly constrained environments in which it is necessary to have the functions of mechanical drive, electrical, selective coupling functions, vibration damping function. Such compactness constraints may impose non-optimal arrangements on certain components, for example bringing the filtering device closer to the axis of rotation, for example to make the shape of clutch actuators more complex, for example positioning metal components in the vicinity of the electric machine, in particular in the residual magnetic field generated by the machine.

In particular, there is a need to improve the magnetic environment of the electric machine of such devices so as not to increase losses and thus not degrade its performance. The invention aims to solve this problem.

The invention achieves, in one of its aspects, using a torque transmission device, particularly for a motor vehicle, comprising:

a torque input element, able to be coupled in rotation to a crankshaft of an internal combustion engine,

a first torque output element, able to be coupled in rotation to a first input shaft of a gearbox,

a rotating electrical machine comprising a stator comprising a plurality of coils and a rotor arranged in the torque transmission direction, between the input element on the one hand and the first output element on the other hand, the rotor being connected selectively to the input element by a multi-disk input clutch, the rotor being selectively connected to the first output element by a first gear multi-disk output clutch, the clutch having an associated actuator,

a stage of springs between the input element and the rotor,

an intermediate element for transmitting torque between the spring stage and the input clutch,

characterized in that a transverse partition is disposed axially between the spring stage and the stator coils for supporting and / or centering the intermediate element and / or for forming a sealed barrier, the axial distance and / or the material and or the shape of said partition being chosen to minimize the joules losses of the stator field within said transverse partition.

Such a transverse partition thus defined makes it possible to minimize the losses of joules in order to maintain the efficiency at a satisfactory level without, however, degrading the axial size.

Such a positioning of the transverse partition between the spring stage and the electric machine makes it possible to obtain a compact device and with satisfactory performance.

Within the meaning of the invention, a minimization of the additional joules losses is acceptable when the reduction of the efficiency of the electric machine remains less than 1%, preferably less than 0.75%, preferably less than 0.5%.

At least one of the criteria chosen from the axial distance, the material and the shape of the transverse partition is selected so as to minimize the joules losses of the stator field within said transverse partition.

In the sense of demand, the coils generate residual magnetic fields.

According to a variant, the transverse partition may be arranged axially between the spring stage and the stator coils for supporting the intermediate element.

According to one variant, the transverse partition may be arranged axially between the spring stage and the stator coils in order to center the intermediate element.

According to a variant the transverse partition may be arranged axially between the spring stage and the stator coils for support and center the intermediate element.

According to a variant, the transverse partition may be arranged axially between the spring stage and the stator coils to form a sealed barrier.

According to a variant the transverse partition may be arranged axially between the spring stage and the stator coils for support and center the intermediate element and to form a sealed barrier.

The axial distance of the transverse partition can be chosen to minimize the joules losses of the stator field within said partition.

The material of said transverse partition may be chosen to minimize joule losses of the stator field within said partition. The shape of said partition may be chosen to minimize joule losses of the stator field within said partition.

According to one aspect of the invention, the transverse partition is axially offset by at least 12 mm with respect to the stator, in particular at the nearest point between said partition and the stator coils. Such spacing makes it possible to leave the transverse partition out of the high-intensity stator field, which makes it possible to minimize joule losses. The distance makes it possible to reduce the joules losses so that the reduction in the efficiency of the electric machine is less than 0.5%.

In particular, the partition may comprise a recess facing the coils or several recesses, each facing one of the coils, each recess being offset by at least 12mm facing the coils.

The transverse partition can be defined so that said partition remains at least 12 mm away from the stator coils.

Other minimum distances may be chosen depending on the material of the partition and the characteristics of the stator so that the reduction in the efficiency of the electric machine is less than 1%, preferably less than 0.5%.

According to another aspect of the invention, the transverse partition may comprise openings to the right of each of the stator coils. The openings may be defined so that there is no portion of the transverse wall less than 12 mm from the stator coils, in particular facing the buns of the coils.

In the aforementioned aspects of the invention, the transverse partition may be metallic, since its shape is chosen so that the partition is out of the residual stator field.

According to one aspect of the invention, the transverse partition may comprise a non-magnetic material.

Such a material allows the transverse partition to reduce joules losses within it, particularly regardless of its proximity to the stator coils. The joules losses can thus be reduced so that the reduction in the efficiency of the electric machine is less than at least 1%, preferably less than 0.5%.

In the sense of the application, a material is non-magnetic when its relative magnetic permeability is less than 10, preferably less than 1.5.

The non-magnetic material may be a non-magnetic metal, for example stainless steel 316L, 304 and 304L. A non-magnetic metal makes it possible to obtain the rigidity necessary for the centering or support function of the transverse partition.

Alternatively, the non-magnetic material may be a composite material. The material may be a plastic for example a plastic type PA filled with glass fibers, PPS, PA66. The transverse partition may be completely non-magnetic material, for example made of a single piece of non-magnetic metal to facilitate its manufacturing process.

According to another aspect of the invention, the transverse partition may be offset by at least 12 mm and comprise a non-magnetic material.

Thus, the axial distance and the material are chosen to minimize joule losses of the stator field within said transverse partition.

The effects are accumulated so that the joules losses can thus be reduced so that the reduction in the efficiency of the electric machine is less than 0.5%, preferably less than 0.25%.

According to one aspect of the invention, only the portions of the transverse partition which are on the same radial height as the stator are non-magnetic. When the transverse partition has one or more recesses, they may be of non-magnetic material.

According to another aspect of the invention, the transverse partition may be formed of a skeleton for the mechanical strength and portions of non-magnetic material.

In this configuration, the transverse partition can be sealed.

The non-magnetic portions may be facing the coils so that the skeleton remains at a predefined distance, for example 12 mm, from said coils.

The skeleton may be metallic, preferably in a non-magnetic metallic material.

The skeleton may comprise radial arms, each disposed circumferentially between two coils.

The non-magnetic portions may be of flexible non-magnetic material such as plastic. The presence of the skeleton makes it possible to use non-magnetic materials without mechanical rigidity, this being provided by the skeleton. Non-magnetic portions to seal the transverse partition

The non-magnetic portions may be overmolded on the skeleton. The non-magnetic portions can be fixed by complementarity of force. The magnetic portions may for example be plugs mounted in holes of the saddle.

According to another aspect of the invention, the device can define a sealed chamber in which the assembly of the clutches is arranged. The bulkhead may partially delimit said sealed chamber.

Alternatively, only a portion of the clutches may be disposed in the sealed chamber.

According to one aspect of the invention, the clutches are wet. The sealed chamber may be filled with a fluid, especially oil.

Having the clutches, all wet, in the same room simplifies the device, especially for the management of sealing between parts rotating at different speeds. In the sense of the application, a wet clutch is a clutch that is adapted to operate in an oil bath.

According to another aspect of the invention, the transverse partition may be integral with the stator and thus be fixed in rotation. The transverse partition can be fixed, for example screwed on a fixed part of the stator. The transverse partition can be fixed by a plurality of fasteners, radially outside the stator.

Alternatively, the wall may be movable, integral in rotation with the intermediate element. Dynamic seals can then be provided between the sealed wall and the stator or a fixed part connected to the stator.

According to another aspect of the invention, the intermediate element is centered by the transverse partition by means of a rolling member, in particular a needle bearing, disposed at the radially inner periphery of the fixed wall.

Such guidance by a fixed part can be removed from a guide by a rotating part (input element, output elements) subject to vibration. Such guidance makes it possible to best guide the rotor of the electric machine.

A sealing means may be disposed between the radially inner end of the fixed wall and the intermediate element, in particular radially inwardly with respect to the needle bearing. The sealing means is for example a lip seal.

According to another aspect of the invention, a rotation guiding means, in particular a needle bearing, in particular a ball bearing, in particular a double row ball bearing, is provided for axially wedging the intermediate element on the second element of the invention. exit.

According to another aspect of the invention, the spring stage may comprise two series of springs connected in series with each other in the sense of torque transmission. There is thus a unique path of torque through the springs.

Alternatively, the two series of springs may be on the same radial height. The two series of springs can be on the same radial height as the input clutch.

Each series of springs may comprise between 1 and 10 springs, preferably 3 springs.

Preferably, the two series of springs are stacked one on the other. The series of radially outer springs can be implanted radially at the same level as the rotor and, possibly, at the same level as the pendular bodies.

The input member may include guide washers for driving the series of radially outer springs which itself causes a haze. The opposite is also possible.

The veil of the outer spring series can drive the second set of springs. The series of radially inner springs can drive guide washers belonging to the intermediate element. According to another aspect of the invention, the series of radially inner springs can be divided into two subsets of springs between which is disposed a phasing member. This phasing member may be free to rotate and can solicit in phase the springs of each subassembly.

Regardless of the number of sets of springs, membranes may be provided between the guide washers and the one or more webs or between the various guide washers to form a spring chamber. These membranes can be attached to the intermediate element, for example by means of a rivet common to the webs, and these membranes rub on the guide washers. Grease, useful for the proper functioning of the springs, can be provided in the spring chamber.

According to another aspect of the invention, the device may comprise a pendulum damping device comprising a pendulum support and at least one pendular body movable relative to the pendulum support by means of rolling members, in particular two cooperating with at least one running track of the support and at least one running track of the pendulum body.

The pendulum damping device is thus disposed between the spring stage and the rotor in the sense of torque transmission.

According to one aspect of the invention, the pendular device may be disposed outside the sealed chamber. Alternatively, the pendulum damping device may be disposed in the sealed chamber.

The pendulum support may belong to the intermediate element. In particular, the pendulum support can be fixed on one of the guide washers associated with the series of radially inner springs.

The pendulum damping device may comprise a plurality of pendular bodies regularly arranged on a periphery of the axis of rotation. Each pendular body can cooperate with two rolling members. Each pendulum body may comprise two pendular masses arranged on either side of the support.

The pendulum bodies can be arranged on the same radial height as the springs of the series of radially inner springs. The pendular bodies can be arranged axially between the clutches and the springs.

The pendulum support can be in one piece or formed of several parts, for example riveted together.

The transverse partition may include a recess to protect the pendulum bodies. The recess associated with the spring and the recess or the recesses associated with the stator are opposed so that the transverse partition has substantially an "S" shape. In particular, there may be a plane perpendicular to the X axis which intersects the zones defined by the two recesses.

According to another aspect of the invention, the device may comprise a second torque output element, able to be coupled in rotation to a second input shaft of a gearbox, the second output element being arranged in parallel of the first output element in the sense of torque transmission. The rotor may be selectively connected to the first and second output members, respectively, by the first and second multi-disk output clutches, each of the clutches having an associated actuator.

According to another aspect of the invention, the input clutch is shifted from the output clutches away from the input element. The input clutch is thus on the side of the gearbox and the output clutches on the side of the internal combustion engine. The output clutches may be axially between the input member and the input clutch. There is a plane perpendicular to the axis of rotation which leaves the side of the gearbox input clutch and leaves the side of the engine output clutches. This plane does not cut any of the three clutches. Such an arrangement makes it possible to obtain a compact device radially.

According to another aspect of the invention, the device may comprise a rotor support for its radial retention. The rotor support comprises a transverse wall, this wall being on the same axial side as all the clutches. This wall can also be on the same axial side as the actuators. The rotor support can encapsulate both clutches and actuators. The rotor support may partially delimit the sealed chamber.

Indeed, such a wall therefore has no dedicated opening for the passage for the actuation of the clutches, the clutches and the actuating members being all on the same side of the wall. The wall is thus simple to manufacture and robust because it is not weakened by holes. It is not necessary to provide a dedicated room to define the sealed chamber on the side of the gearbox.

Preferably, the rotor support comprises no other transverse wall so that the rotor support is simple construction.

According to another aspect of the invention, the intermediate element may comprise:

- a splined hub for the passage of torque between the inside and the outside of the sealed chamber,

a cylindrical skirt for driving the input clutch,

- A connection portion between the splined hub and the cylindrical skirt.

The connection portion may be welded to the splined hub.

The cylindrical skirt can extend radially between the rotor and the output clutches. This cylindrical skirt makes it possible to transmit the torque on the side of the heat engine to the side of the gearbox.

According to a first construction variant of the intermediate element, the connecting portion and the cylindrical skirt are in one piece. The pendulum holder can be riveted to the connecting portion. Such a variant is simple of construction.

According to a second variant of construction of the intermediate element, the pendulum support and the connection portion are in one piece. The support of The pendulum is therefore directly fixed to the splined hub, for example by welding. The cylindrical skirt can then be fixed on the connection portion, for example by riveting. Thus, there is no fastening tolerance, including riveting to take into account for the pendulum support. The pendulum support is firmly attached.

Finally, according to a third variant of construction of the element

intermediate, the cylindrical skirt is disposed between the pendulum support and the connecting portion. The pendulum support is thus connected to the connection portion the pendulum support via the cylindrical skirt, for example the pendulum support and the connection portion are welded to the cylindrical skirt.

According to one aspect of the invention, the rotor support may also include an inner sleeve for the arrangement of the clutch actuators.

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 maintenance is mutualized for the actuating members and for the rotor.

According to another aspect of the invention, each actuating member may comprise an actuating chamber delimited in part by the inner sleeve and by a force transmission member axially movable relative to the inner sleeve and adapted to cooperate with the associated clutch. Each force transmission member is movable under the effect of the pressure of the fluid in the actuating 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 the force and through the inner sleeve. This room can also be waterproof.

The force transmitting member can form a barrier between the two chambers. The compensation chamber is intended to oppose the effects related to the hydrodynamic oil pressure of the actuating chamber on the transmission member. The force transmission member can thus be moved axially by relative oil pressure variation of the actuating and compensating chambers.

The wall of the rotor support can be assembled with the inner sleeve, for example by welding. Alternatively, the wall and the inner sleeve can be in one piece.

The rotor support may also include a splined outer sleeve which cooperates with the rotor. The outer sleeve may be integral with the wall or assembled together, in particular by welding.

According to another aspect of the invention, the inner sleeve can be worn radially by a fixed distributor. The distributor may have a network fluidic for supplying each of the actuating members. The dispenser advantageously makes it possible to have only one supply of fluid for all the actuating members, which simplifies the device. The fluidic network is formed in a fixed part in rotation whose construction and operation are simplified with respect to a supply of fluid in a rotating part, for example a gearbox shaft. Such a device allows to have a single fluid inlet for the actuation of the clutches which simplifies the manufacture of the device.

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

According to one aspect of the invention, the rotor can be carried radially, in particular only by the distributor. Bearings, especially 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 may be on the same radial height. The radial support function of the actuating members and the rotor is thus shared.

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

According to one aspect of the invention, the fluidic network of the dispenser may comprise, for each operating chamber, a first series of axial channels, at least one channel and preferably two channels, circumferentially offset, which open on the same circumferential groove , also arranged in the distributor, for supplying fluid to the actuating chambers.

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

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

The fluidic network may also comprise, for each actuating member, a third series of axial channels, at least one and preferably two, offset circumferentially which open on the same circumferential groove for supplying fluid to the compensation chamber. Cooling and compensation fluids can be identical.

For each clutch, the fluidic network may comprise a single series of axial channels for cooling and fluid supply of the compensation chamber.

Preferably, the fluidic network may comprise a single series of axial channels for cooling the outlet clutches and the fluid supply of 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 may be circumferentially shifted two by two.

Sealing rings, for example made of plastic, may be provided on either side of each circumferential groove.

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

According to one aspect of the invention, the rolling members of the sleeve can frame the circumferential grooves.

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

According to another aspect of the invention, the output clutches can be stacked radially to minimize the axial space allocated to the clutches.

As a variant, the output clutches can also succeed one another axially. There is thus an axis parallel to the axis of rotation which cuts each of the clutches. All clutches can succeed one another axially. 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 makes it possible to provide identical clutches and thus to improve the industrialization of the device.

According to another aspect of the invention, each of the clutches of the device may comprise:

an input disk carrier driven in rotation by the input element relating to the input clutch on the one hand and rotatably connected to the rotor support relating to the first and second output clutches on the other hand; ,

an output disk carrier integral in rotation with the rotor support for the input clutch on the one hand and integral with one of the first and second output elements respectively concerning the first and the second output clutch; 'somewhere else,

a multi-disk assembly comprising at least one friction disk integral in rotation with one of the input and output disk carriers, at least two plates respectively arranged on either side of each friction disk, integral in rotation on the other hand, inlet and outlet disc carriers and friction linings disposed between the platens and a friction disc, the clutch defining a disengaged position and an engaged position in which said platters and the disc of friction pinch the friction linings so as to transmit torque between the input disk carrier and the output disk carrier.

The gaskets may be fixed on the friction discs, in particular by gluing, in particular by riveting, in particular by overmolding. Alternatively, the fittings are fixed on the trays.

Each disk carrier can synchronize in rotation all the trays or the set of friction discs. The disk carriers may comprise a cylindrical skirt on which the plates and the friction discs are mounted.

The plates and the disks can cooperate with the disk carriers according to one of their radial periphery by complementarity of form. The cylindrical skirts, trays and friction discs may for example be fluted.

According to another aspect of the invention, the output disk carrier of the first output clutch is radially inward and the output disk carrier of the second output clutch is radially outward.

Preferably, the clutches comprise between two and seven friction discs, preferably three, four or five friction discs.

The clutches may be of the "normally open" type, a force must be exerted by the force transmission members to transmit a torque.

The force transmission members may exert an axial force on the multi-disk assemblies to move the trays to the disks, in particular on an end plate of the multi-disk assembly. The actuation is thus of the "pushed" type.

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

According to one aspect of the invention, the input disk holders of the output clutches may extend from a secondary partition which extends radially from the inner sleeve. The rotor support, in particular via its inner sleeve and the secondary partition, thus rotates the output clutches.

When the output clutches are stacked radially, the input disk carriers can extend on the same axial side. The secondary partition may define a compensation chamber of one of the actuating members.

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

The invention also relates to an assembly comprising a fixed housing and a device as defined above, the device being disposed inside the housing. The stator may be integral with the housing.

Description of figures The invention will be better understood, and other objects, details, characteristics and advantages thereof will appear more clearly in the course of the following description of several particular embodiments of the invention, given solely for illustrative and non-limiting purposes. with reference to the appended figures.

FIG. 1 is a view in axial section of an example of the device according to the invention in which the stage of springs comprises two series of springs,

FIGS. 2a and 2b schematically show construction variants of the transverse partition.

In relation to FIG. 1, a torque transmission device 1 comprising:

a torque input element 2, able to be coupled in rotation to a crankshaft of an internal combustion engine,

a first torque output element 5, able to be coupled in rotation to a first input shaft 6 of a gearbox,

- A second torque output member 8, adapted to be rotatably coupled 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 torque transmission sense. Each of these elements rotate around an axis of rotation of the device X.

The device also comprises a rotating electrical machine 12 comprising a rotor 13 arranged in the torque transmission direction, between the input element 2 on the one hand and the first output element 5 and the second output element 8 of FIG. somewhere else. The device 1 also comprises a rotor support 10 for its radial retention.

In the examples considered, the rotor 13 is connected selectively:

to the input element 2 by an input clutch 15 of multidisc type,

at the first output element 5 by a first output clutch 16 of the mul tidisc type, and

at the second output element 8 by a second output clutch 17 of multi-disk type. Each of the clutches 15, 16, 17 has an associated actuating member.

The first input shaft 6 of the box is rotatably coupled to the crankshaft 3 and rotated by it 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 provide a surplus of energy to the gearbox.

The first input shaft 6 of the box is rotatably coupled 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 driven only by the rotor. In this configuration, the electric machine can also act as a brake and be in a mode of energy recovery. Similarly, the second input shaft 9 of the gearbox is rotatably coupled 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 rotatably coupled 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 box is then driven only 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 a mode of energy recovery.

In the example considered in FIG. 1, the first output clutch 16 is, for example, arranged to engage the odd gearbox ratios and the second output clutch 17 is, for example, arranged to engage the even gearing. and the reverse 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 rotational speed - of the internal combustion engine, to one of the two gearbox input shafts, depending on the respective configuration of the gearbox. 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 not to be simultaneously in the same engaged configuration. On the other hand, they can simultaneously be configured in their disengaged position.

In the example considered in FIG. 1, the first and second output elements 5, 8 respectively comprise first and second webs 25, 28 connected by a splined connection to the first and second input shafts 6, 9, respectively. 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 electrical machine comprises a stationary stator 14 arranged around the rotor 13. The stator 14 comprises a plurality of coils, whose buns 20 are visible in FIG.

In the example considered, the device 1 also comprises a stage of springs 31 between the input element and the rotor 12.

In the example considered, the spring stage 31 comprises two series of springs 85, 86 connected in series with each other in the sense of the transmission of torque. Each series of springs may comprise between 1 and 10 springs, preferably 3 springs. These two series of springs 85, 86 are stacked one on the other. The series of radially outer springs 85 can be implanted radially at the same level as the rotor 13.

In the example considered, the input element 2 comprises guide washers 36 for driving the series of radially outer springs 85 which itself drives a web 37. This web 37 in turn drives the series of radially inner springs. 86.

In the example considered, the series of radially inner springs 86 drives guide washers 38 belonging to the intermediate element. These guide washers 38 are interconnected by a fixing member which also fix them to the rest of the intermediate element.

In the example considered, the series of radially inner springs 86 can be divided into two sub-sets of springs between which is disposed a phasing member which is here a phasing veil 39. This phasing veil 39 can be free in rotation and makes it possible to solicit in phase the springs of each subassembly.

In the example considered, membranes 40 are provided to form a spring chamber. These membranes 40 may be fixed to the intermediate element, for example by means of a rivet common to the guide washers 38 and these membranes rub on the guide washers. Grease, useful for the proper functioning of the springs, can be provided in the spring chamber.

In the example considered, the device 1 also comprises a pendular damping device 70 comprising a pendulum support 71 and at least one pendular body 72 movable relative to the pendulum support by means of rolling members, in particular two, cooperating with at least one running track of the support and at least one running track of the pendulum body.

The pendulum damping device 70 may comprise a plurality of pendular bodies regularly arranged on a periphery of the X axis. Each pendulum body comprises two pendular masses 73 arranged on either side of the support 71.

In the example considered, the pendulum support is fixed on one of the guide washers 38. The pendulum support therefore belongs to the intermediate element.

In the example considered, the pendular bodies 72 are arranged on the same radial height as the springs of the series of radially inner springs 86. The pendular bodies 72 are arranged axially between the clutches and the springs.

In the example considered, the transverse partition 50 comprises a recess 105 to protect the pendular bodies 72.

In the example considered, the device 1 also comprises an intermediate element for transmitting torque between the spring stage 31 and the input clutch 15. In the example, the device 1 defines a sealed chamber 45 filled with oil in which is disposed the set of clutches. The clutches are therefore all wet type.

In the example considered, the sealed chamber 45 is delimited in part by the rotor support 10, by the intermediate element and leaves a transverse partition 50, thus forming a sealed barrier.

In the example considered, the pendular device 70 is disposed outside the sealed chamber 45.

This partition 50 is here secured to the stator 14 and thus it is fixed in rotation. The partition 50 is integral with the stator through a housing 100 on which is screwed. The housing 100 forms with the device 1 a set. The transverse partition 50 extends axially between the spring stage 31 and the clutches 15, 16, 17. Seals 101 are mounted between the casing 100 and the partition 50 to seal the chamber 45.

In the example considered, the intermediate element is centered on the transverse partition 50 by means of a needle bearing 51 disposed at the radially inner periphery of the transverse partition.

In addition, a sealing means, here a lip seal 52 is disposed between the radially inner end of the fixed wall and the intermediate element radially inwardly relative to the needle bearing 51 to ensure the sealing of the chamber 45.

Rotating guide means here, again a needle bearing 53, is provided for axially wedging the intermediate element on the second output element. The same guide means is provided between the two output elements 5 and 8.

In the example considered, the input clutch 15 is offset from the output clutches 16, 17 away from the input element 2.

In the example considered, the rotor support 10 comprises a transverse wall 60, this wall being on the same axial side as all the clutches 15, 16, 17. This wall can also be on the same axial side as the actuators. The rotor support encapsulates both clutches and actuators.

In the example considered, the intermediate element is also carried radially by the rotor support 10 by means of a rolling member, here a needle bearing disposed a radial extension ring 61 and the rotor support 10. ring 61 is disposed axially between the input clutch 15 and the output clutches 16, 17.

For more details concerning the clutches 15, 16, 17 and the associated actuators, reference may be made to French Patent Application No. 1756978 filed on July 21, 2017 in the name of Valeo Clutchings.

In the example considered, the intermediate element comprises:

a splined hub 75 for the passage of the torque between the inside and the outside of the sealed chamber,

a cylindrical skirt 76 for driving the input clutch 15, - A connection portion 77 between the splined hub and the cylindrical skirt.

The cylindrical skirt 76 extends radially between the rotor 13 and the output clutches 16, 17. This cylindrical skirt makes it possible to transmit the torque on the side of the heat engine towards the side of the gearbox.

In the example considered, a fixed distributor 80 which carries the rotor support 10 and which defines in part the actuating members is fixed to the housing 100 which is itself adapted to be fixed on the gearbox.

In the example under consideration, the axial distance and the shape of the transverse partition 50 of said partition are chosen to minimize joule losses of the stator field within said transverse partition 50.

In the example considered, the transverse partition 50 is shifted axially at least 12 mm from the stator to the stator 14.

More specifically, the partition comprises a recess 106 facing the coils. The bottom of the recess 106 is axially offset by a distance d facing the coils, the distance d being greater than 12 mm. The transverse partition 50, in particular the recess 106, is defined so that said partition remains at least 12 mm away from the coils of the stator 106.

In the example considered, the transverse partition 50 thus comprises two recesses 105, 106, one to protect the pendular bodies, the other to minimize the joules losses. These recesses 105, 106 are opposed so that the transverse partition 50 has substantially an "S" shape.

In particular, there is a plane perpendicular to the X axis which intersects the zones defined by the two recesses 105, 106.

In the example considered, the transverse partition 50 can be integral, for example metal. Alternatively, the transverse partition 50 may comprise a non-magnetic material and be integral with this non-magnetic material.

In the example, the non-magnetic material may be a non-magnetic metal, for example stainless steel 316L, 304 and 304L.

FIGS. 2a and 2b schematically show in an axial view examples of transverse partition that can replace that described in the example of FIG.

In the example considered, the transverse partition 50 has openings 110 in line with each of the stator coils, in particular at the right of each of the bunches 20 of the stator coils.

These openings may be defined so that there is no portion of the transverse wall within 12 mm of the stator coils 14. An opening may be provided per coil. The example of Figures 2a and 2b can not have the function of sealed barrier, only the support of the intermediate piece.

RECTIFIED SHEET (RULE 91) ISA / EP In the example considered in FIG. 2b and in order to preserve the barrier function of the transverse partition, the transverse partition may be formed of a skeleton 112 for mechanical strength and portions of non-magnetic material 111.

The skeleton can be defined by the structure of the example of FIG. 2a in which portions of non-magnetic material are brought back into the openings 110. The transverse partition 50 of FIG. 2b is thus sealed.

In the example considered, the non-magnetic portions 111 are opposite the coils so that the skeleton remains at a predetermined distance, for example 12 mm, from said coils.

The skeleton 112 may be metallic, preferably in a non-magnetic metal material.

The skeleton may comprise radial arms 113, each disposed circumferentially between two coils.

The non-magnetic portions may be of flexible non-magnetic material such as plastic.

The non-magnetic portions 111 may be overmolded on the skeleton 112. The non-magnetic portions may be fixed by force complementarity. The magnetic portions may for example be plugs mounted in holes 112 of the saddle.

Claims

1. Device (1) for transmitting torque, in particular for a motor vehicle, comprising:

- A torque input element (2), adapted to be coupled in rotation to a crankshaft

(3) an internal combustion engine,

a first torque output element (5), able to be coupled in rotation to a first input shaft of a gearbox (6),

a rotary electric machine (12) comprising a stator (14) comprising a plurality of coils and a rotor (13) arranged in the torque transmission direction, between the input element (2) on the one hand and the first output element (5) on the other hand, 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 (5) by a first output clutch (16) of multidisc type, the clutch having an associated actuating member,

a spring stage (31) between the input element and the rotor,

an intermediate element for transmitting torque between the spring stage (31) and the input clutch (15),

characterized in that a transverse partition (50) is disposed axially between the spring stage (31) and the stator coils (14) for supporting and / or centering the intermediate element and / or for forming a sealed barrier, the axial distance and / or the material and / or the shape of said partition being chosen to minimize joule losses of the stator field within said partition.

2. Device (1) according to the preceding claim, characterized in that the transverse partition (50) is offset axially by at least l2mm relative to the stator (14))

3. Device (1) according to any one of the preceding claims, characterized in that the transverse partition (50) has openings (110) to the right of each of the stator coils.

4. Device (1) according to the preceding claim, characterized in that the transverse partition (50) comprises a non-magnetic material.

5. Device (1) according to claims 2 and 3 taken in combination, the transverse partition (50) being offset by at least 12 mm and comprising a non-magnetic material.

6. Device (1) according to claims 3 and 4 taken in combination, the transverse partition (50) being formed of a skeleton (112) for mechanical strength and portions of non-magnetic material (111).

7. Device (1) according to claim 1, characterized in that it defines a sealed chamber (45) in which is disposed the assembly of the clutches (15, 16, 17), the bulkhead (50) defining in part said waterproof room.

8. Device (1) according to the preceding claim, characterized in that the intermediate element is centered by the transverse partition (50) by means of a rolling member (51), in particular a needle bearing disposed at the periphery radially inner wall of the fixed wall.

9. Device (1) according to any one of the preceding claims, characterized in that the spring stage (31) comprises two series of springs (85, 86) connected in series from one another to the other. sense of torque transmission.

10. Device (1) according to any one of the preceding claims, characterized in that it comprises a pendulum damping device (70) comprising a pendulum support (71) and at least one pendular body (72) movable by relative to the pendulum support by means of rolling members, in particular two, cooperating with at least one raceway of the support and at least one running track of the pendulum body, the pendulum support belonging to the intermediate element, the or the pendular bodies being disposed in a recess of the transverse partition (50).