FR3095488A1 - Torque transmission system for a hybrid or electric vehicle. - Google Patents

Abstract

Transmission system (1) for a vehicle, in particular for a hybrid or electric motor vehicle, comprising: - an electric machine (20) arranged around an X axis and comprising a stator (21), a rotor (22) and an output member (23), the output member (23) of the electric machine (20) being rotated by the rotor (22) around the X axis, - a clutch device (10), the clutch device (10) being disposed at least partly inside the stator (21). Figure for the abstract: Figure 1

Description

Torque transmission system for a hybrid or electric vehicle.

The invention relates to a torque transmission system for an electric or hybrid vehicle, in particular for an electric or hybrid motor vehicle.

State of the prior art

The invention applies more particularly to hybrid vehicles and to electric vehicles. The speeds of an electric machine can be very high, greater than or equal to 15,000 revolutions per minute for example, especially for two-speed electric transmission chains.

To match speed and torque, the use of electric motors typically requires a transmission with a gear reduction device to achieve the desired speed and torque output levels at each wheel, and a differential to vary the speed between two laterally opposite wheels.

To adapt to the different vehicle speeds, it is known to use clutches which make it possible to select the desired reduction ratio at the level of the speed reduction device. This type of device is for example disclosed in the document DE102016202723.

The combination of a clutch device and an electric machine is nevertheless difficult to achieve in certain environments in which the available space is limited. The invention provides a solution to this problem.

Presentation of the invention

To this end, the invention relates to a transmission system for a vehicle, in particular for a hybrid or electric motor vehicle, comprising:
- an electric machine arranged around an X axis and comprising a stator, a rotor and an output member, the output member of the electric machine being driven in rotation by the rotor around the X axis,
- a clutch device,
characterized in that the clutch device is arranged at least partly inside the stator.

In other words, the clutch device is arranged at least partly in the space radially separating the X axis and the stator.

Thus, by introducing at least part of the clutch device inside the stator, the axial bulk of the torque transmission system is reduced.

The stator here comprises both a stator body and a winding.

The transmission system may also include one or more of the following characteristics:

The electric machine has a cavity extending around the X axis and the clutch device has a protrusion also extending around the X axis and disposed in the cavity of the electric machine.

The protuberance can have the shape of a cylindrical, conical or frustoconical growth, of a dome or of a boss. The protuberance can have several stages, each stage being able to have one of these shapes.

According to one embodiment, only the protrusion is arranged in the cavity of the electric machine.

The stator, the rotor and the output member of the electric machine extend circumferentially around the X axis.
The stator is provided with a stator body and a winding.

The stator body is tubular in shape and extends along the X axis.

The winding extends axially along the stator body.

The clutch device is axially offset from the stator body.

The winding protrudes axially from the stator body, at least in the direction of the clutch device.

The clutch device is arranged at least partly inside the winding. In other words, the clutch device is arranged at least partly in the space radially separating the X axis and the winding.

The clutch device is arranged at least partly inside the winding but outside the stator body.

Interior of the stator body means the space axially separating the X axis and the stator body. By exterior of the stator body is meant the space located outside the space axially separating the X axis and the stator body.

The winding comprises winding heads which are formed in the part of the winding protruding axially from the stator body.

The clutch device is arranged at least partly inside the winding heads. In other words, the clutch device is disposed at least partly in the space radially separating the X axis and the winding heads.

The clutch device comprises a first input member, a first output member and a first clutch extending circumferentially around the axis X, the first clutch being capable of interrupting the transmission of a torque between the first member input and the first output member of the clutch device.

The first input member of the clutch device is driven by the output member of the electric machine and disposed at least partly inside the stator.

The first clutch is arranged outside the stator.

In other words, the first input member of the clutch device is arranged at least partly in the space radially separating the axis X and the stator.

The first input member of the clutch device is arranged at least partly inside the winding. In other words, the first input member of the clutch device is arranged at least partly in the space radially separating the axis X and the winding.

The first input member of the clutch device is arranged at least partly inside the winding but outside the stator body.

The first input member of the clutch device is arranged at least partly inside the winding heads. In other words, the first input member of the clutch device is arranged at least partly in the space radially separating the axis X and the winding heads.

The first input member of the clutch device is driven in rotation by the output member of the electric machine around the X axis.

The first input member includes an input veil.

The inlet veil is arranged between the rotor of the electric machine and the first clutch.

The output member of the electric machine and the first input member of the clutch device are mounted integral in rotation around the axis X thanks to a first coupling connection in rotation which is arranged partially or totally at the inside the stator, in particular inside the winding but outside the stator body.

The stator generally has the shape of a tube having an internal diameter and an external diameter and whose axis of revolution is the axis X, the clutch device, in particular the first input member, being disposed at least in part radially inside the inside diameter of the stator.

“Arranged at least partly inside the stator” therefore means the fact of being at least partly inside the tubular shape of the stator.
The clutch device further comprises a second input member, a second output member and a second clutch arranged around the axis X, the second clutch being capable of interrupting the transmission of a torque between the second member of input and the second output member of the clutch device.

The transmission system further comprises a speed reduction device, the speed reduction device comprising a first reducer and a second reducer, the first reducer comprising a first input element driven in rotation by the first output member of the device clutch and the second reduction gear comprising a second input element driven in rotation by the second output member of the clutch device.

The second input member of the clutch device is driven in rotation by the output member of the electric machine around the X axis.

In other words, the clutch device can be produced by a double clutch and the transmission system can have two speed ratios, the double clutch making it possible to alternately select one of the two speed ratios.

Thus, the introduction of a part of the clutch device inside the stator is particularly advantageous in a transmission architecture with two clutches and two speed reduction paths, since this type of architecture is generally very bulky.

The first output member of the clutch device is rotationally coupled to the first input element of the first reducer but not to the second input element of the second reducer.

The second output member of the clutch device is rotationally coupled to the second input element of the second reducer but not to the first input element of the first reducer.

The first reducer has a first speed ratio, and the second reducer has a second speed ratio.

The first gear ratio and the second gear ratio are different.

The first gear ratio is lower than the second gear ratio.

The first reducer has a gear ratio between 0.2 and 1.

The second reducer has a gear ratio between 0.25 and 1.5.

The first clutch and the second clutch are arranged outside the stator.

The first input member of the clutch device is driven in rotation by the output member of the electric machine around the axis X, and the second input member of the clutch device is driven in rotation by the output member of the electric machine around the X axis.

The first input element of the speed reduction device is driven in rotation around the axis X by the first output member of the clutch device and the second input element of the speed reduction device is driven in rotation around the X axis by the second output member of the clutch device.

The first input element of the speed reduction device is able to drive in rotation around the axis X a first input pinion and the second input element of the speed reduction device is able to drive in rotation around the axis X from the X axis a second input pinion.

The first input pinion and the second pinion are offset axially on the X axis. With this architecture, it is particularly advantageous to save space axially by introducing part of the clutch device inside the stator.

The first clutch and the second clutch are axially offset from the stator.

The first input gear and the second input gear are axially offset relative to the first clutch and relative to the second clutch.

The first clutch and the second clutch are arranged axially between on the one hand the stator of the electric machine and on the other hand the first input pinion and the second input pinion.

With this architecture in which the elements are superimposed axially along the X axis, it is particularly advantageous to introduce part of the clutch device inside the stator.

The first clutch is arranged radially outside the second clutch and the first clutch radially overlaps the second clutch. In other words, there is a plane perpendicular to the X axis passing through the first clutch and the second clutch. Thus, this arrangement of the clutches saves space axially.

The first input member of the clutch device comprises, radially from the inside outwards, a radially inner portion at least partly disposed inside the stator, an axial uneven portion and a radially outer portion, the radially inner portion being offset axially, in the direction of the electric machine, with respect to the radially outer portion thanks to the portion of axial unevenness. Thus, the shape of the portion of axial unevenness of the first input member of the clutch device makes it possible to introduce at least part of the first input member inside the stator.

The radially outer portion of the first input member is arranged outside the stator, in particular at least partly radially outside the inside diameter of the stator. In other words, the radially outer portion of the first input member comprises at least one part which is farther from the axis X than the internal diameter of the stator and which is axially offset with respect to the stator.

The axial uneven portion may be an axial uneven step, the radially outer portion and the radially inner portion of the first input member being connected by this axial uneven step.

The first input member of the clutch device comprises a first splined hub coupled in rotation with a complementary splined portion of the output member of the electric machine.

The first splined hub is located partly inside the stator, in particular inside the winding.

The first splined hub is rotationally coupled with a complementary splined portion of the output member of the electric machine.

The first coupling connection in rotation between the output member of the electric machine and the first input member of the clutch device is therefore formed by this first splined hub and the complementary splined portion of the output member of the electric machine.

The first splined hub is formed on the radially inner portion of the first input member.

The radially internal portion comprises this first splined hub and an annular part developing radially around the axis X. This annular part can extend radially outwards from the splined hub to the leveling step.

According to one embodiment, the radially internal portion comprises this first splined hub and a part in the form of a cone section extending, from the first splined hub, radially outward, away from the electric machine.

According to one embodiment, the radially outer portion also comprises an annular part developing radially around the axis X. This annular part of radial extension can extend radially outwards from the axial difference in level portion.

The first input member of the clutch device comprises a first input disc carrier.

The second input member of the clutch device comprises a second input disc carrier.

The second input disc holder and the first input disc holder are formed on two parts fixed to each other.

The radially internal portion and the axial uneven portion are formed on the inlet veil.

The first entry disc carrier is connected to the first splined hub via the entry veil.

The second entry disk carrier is connected to the first splined hub via the entry veil and the first entry disk carrier,

According to one embodiment, the first splined hub has splines on its external diameter and the complementary splined portion of the output member has splines on its internal diameter. In other words, the first splined hub is housed radially inside the first complementary hub.

The electric machine includes a protective casing.

The protective casing of the electric machine is rotatably mounted relative to the output member of the electric machine, in particular by means of a bearing, for example a roller bearing.

There is a plane perpendicular to the X axis passing through both the first splined hub, the first complementary splined hub, and the bearing.

There is a plane perpendicular to the X axis passing through both the first splined hub, the first complementary splined hub, the bearing and the stator.

The casing of the electric machine includes a shoulder on which the bearing rests, in a direction opposite to the clutch device.

The casing is formed to go around the winding heads so as to allow the radial superposition of the first splined hub, of the splined portion complementary to the output member of the electric machine, and of the bearing.

The first output member of the clutch device comprises a radially inner portion and a radially outer portion, the radially inner portion being offset axially, in the direction of the electric machine, relative to the radially outer portion.

The second output member of the clutch device comprises a radially inner portion and a radially outer portion, the radially inner portion being offset axially, in the direction of the electric machine, relative to the radially outer portion.

The first output member comprises at least one portion of axial difference in level, the radially outer portion and the radially inner portion of the first output member being connected by this portion of axial difference in level.

The second output member comprises at least one portion of axial difference in level, the radially outer portion and the radially inner portion of the second output member being connected by this portion of axial difference in level.

The radially internal portion of the first output member can be arranged at least partly inside the stator, in particular inside the winding but outside the stator body.

The radially internal portion of the second output member can be arranged inside the stator, in particular inside the winding but outside the stator body.

The radially outer portion of the first output member is disposed outside the stator.

The radially outer portion of the second output member is arranged outside the stator.

The axial uneven portion of the first output member of the clutch device, the axial uneven portion of the second output member of the clutch device, and the axial uneven portion of the first input member of the clutch device are nested in each other.

The first output member of the clutch device 10) and the first input member of the speed reduction device are mounted integral in rotation around the axis X thanks to a second coupling connection in rotation which is arranged partially or totally inside the stator, in particular inside the winding but outside the stator body.

The first input element of the speed reduction device comprises a splined portion and the radially internal portion of the first output member comprises a second splined hub coupled in rotation around the axis X with the splined portion of the first input element of the speed reduction device.

The second output member of the clutch device and the second input member of the speed reduction device are mounted integral in rotation around the axis X thanks to a third coupling connection in rotation

The second input element of the speed reduction device comprises a splined portion and the radially internal portion of the second output member comprises a third splined hub coupled in rotation about the axis X with the splined portion of the second input element of the speed reduction device.

The second splined hub extends axially in the direction of the electric machine.

The third splined hub extends axially in a direction away from the electric machine.

There is a plane perpendicular to the X axis passing both through the first splined hub, the splined portion of the output member of the electric machine, the second splined hub, the splined portion of the first input element of the device reduction gear and stator.

The first input element of the first reducer is a first transmission shaft.

The second input element of the second reducer is a second drive shaft.

The first driveshaft extends radially inside the second driveshaft, along the X axis.

The second driveshaft is a hollow shaft.

The first clutch comprises a first multi-plate assembly having a plurality of input plates and a plurality of output plates arranged to rub against each other when pressure is exerted axially on these input and output plates.

The second clutch comprises a second multi-disc assembly having a plurality of input discs and a plurality of output discs arranged to rub against each other when pressure is exerted axially on these input and output discs.

The input discs of the first clutch are mounted integral in rotation with the first input disc carrier.

The output discs of the first clutch are mounted integral in rotation with the second input disc carrier.

The second clutch input discs are mounted integral in rotation with the second input disc carrier.

The output discs of the second clutch are mounted integral in rotation with the second output disc carrier.

The first input disc holder and the second input disc holder are fixed to each other and together with the first input disc form a rigid subassembly.

According to one embodiment, the first splined hub is arranged entirely inside the stator, in particular inside the winding but outside the stator body.

According to one embodiment, the first input veil is arranged at least partly inside the stator, in particular inside the winding but outside the stator body.

The first and second clutches are at least partially radially outside the inside diameter of the stator. Thus, the radial size of the electric machine is reduced.

The transmission system is powered solely by one or more electric machines.

The torque transmission system is configured so that only the electric machine is capable of supplying the torque traveling from the clutch device to the speed reduction device.

Brief description of figures

shows a block diagram of a first embodiment of the torque transmission system.

shows a perspective diagram of the first embodiment of the torque transmission system.

shows a sectional view of the first embodiment of the torque transmission system.

shows a sectional view of the clutch device of the first embodiment of the torque transmission system.

shows a sectional view of the connection between a clutch device and an electric machine of a second embodiment of the torque transmission system.

In the description and the claims, the terms “external” and “internal” as well as the “axial” and “radial” orientations will be used to designate, according to the definitions given in the description, elements of the torque transmission system. By convention, the "radial" orientation is directed orthogonally to the axis X of rotation of the electrical machine determining the "axial" orientation. The "circumferential" orientation is directed orthogonally to the X axis of rotation and orthogonal to the radial direction. The terms "external" and "internal" are used to define the relative position of an element with respect to another, with reference to the X axis of rotation, an element close to the axis is thus qualified as internal by opposed to an external element located radially on the periphery.

A block diagram of a first embodiment of the invention is shown in Figure 1. This block diagram represents a transmission system 1 for an electric motor vehicle. This is a transmission system driven solely by an electrical source. This transmission system can drive two laterally opposite wheels of the vehicle.

Transmission system 1 includes:
- an electric machine 20 arranged around an axis X and comprising a stator 21, a rotor 22 and an output member 23, the output member 23 of the electric machine 20 being driven in rotation by the rotor 22 around the X axis, and
- a clutch device 10.

Here, the term “stator” means the component comprising the stator body and the winding. The stator 21, the rotor 22 and the output member 23 of the electric machine extend circumferentially around the axis X.

To reduce the overall size of the transmission system 1, the clutch device 10 is arranged partly inside the stator 21, that is to say in the space radially separating the axis X and the stator 21. The electric machine 20 has a cavity 29 extending around the axis X and the clutch device has a protrusion 19 also extending around the axis X and placed in the cavity 29 of the electric machine 20. On this diagram, the protuberance here has an end zone which is cylindrical and a base which is frustoconical. The protuberance 19 is arranged in the cavity 29 of the electric machine 20.

On the other side, a speed reduction device 40 is driven by the clutch device 10. A differential, not shown schematically in Figure 1, then transmits the torque coming out of the speed reduction device 40 to two laterally opposite wheels. of the vehicle. This transmission system 1 is also shown in perspective in Figure 2.

The transmission system 1 according to the first embodiment is shown in section in Figure 3.

The stator body 211 is tubular in shape and extends along the X axis. The winding 212 extends axially along the stator body 211. It is noted that the winding 212 protrudes axially from the stator body 211, towards the clutch device 10. The winding 212 comprises winding heads which are formed in the part of the winding 212 projecting axially from the stator body 211.

The clutch device 10 is axially offset with respect to the stator body 211. The clutch device 10 is arranged partly inside the coil 212, that is to say in the space radially separating the X axis and the winding 212, but outside the stator body 211.

The clutch device 10 comprises a first input member 101, a first output member 102 and a first clutch 100 extending circumferentially around the axis X. The first clutch 100 is capable of interrupting the transmission of a torque between the first input member 101 and the first output member 102 of the clutch device 10. The clutch device 10 also comprises a second input member 201, a second output member 202 and a second clutch 200 arranged around the axis X. The second clutch 200 is capable of interrupting the transmission of a torque between the second input member 201 and the second output member 202 of the clutch device 10.

The clutch device 10 is therefore here a double clutch. The first clutch 100 is arranged radially outside the second clutch 200 by radially covering the second clutch 200. This arrangement of the clutches also saves space axially. Alternatively, dual clutch mechanism 10 may be in an axial configuration, with first clutch 100 located ahead of second clutch 200.

The first input member 101 of the clutch device 10 is driven, integrally in rotation, by the output member 23 of the electric machine around the axis X. The second input member 201 of the clutch device The clutch is also driven, integrally in rotation, by the output member 23 of the electric machine 20 around the axis X.

The speed reduction device 40 includes a first reducer 410 and a second reducer 420.

The first reducer 410 comprises a first input element 411 driven in rotation by the first output member 102 of the clutch device 10 and the second reducer 420 comprises a second input element 412 driven in rotation by the second output member 202 of the clutch device 10. The transmission system 1 can thus have two speed ratios, the double clutch making it possible to alternately select one of these two speed ratios.

The first reducer 410 has a first speed ratio, and the second reducer 420 has a second speed ratio, the first speed ratio being lower than the second speed ratio. For example, the first gear ratio is between 0.2 and 1 and the second gear ratio is between 0.25 and 1.5.

The speed reduction device 40 comprises:

- a transmission shaft 45 extending along a Y axis parallel to the X axis,

- the first reducer 410 arranged to transmit a torque between the first input element 411 of the speed reduction device and the transmission shaft 45, according to the first gear ratio.

- the second reducer 420 arranged to transmit a torque between the second input element 412 of the speed reduction device 40 and the transmission shaft 45 according to the second gear ratio.

- a connection element 46 arranged to authorize or interrupt the mutual drive in rotation between the first input element 411 of the first reducer 410 and the transmission shaft 45.

The clutches 100 and 200 are kinematically placed as close as possible to the electric machine 20, upstream of the reduction devices, which means that the two clutches 100 and 200 are placed in a portion of the transmission chain where the torque is the most weak. In the case of progressive clutches by friction, this makes it possible to have a better compactness of the 100, 200 clutches.

The first reducer 410 and the second reducer 420 comprise a gear train. These gear sets can be mounted to splash in oil. Since the first gear 410 has a lower gear ratio than the second gear 420, the first gear is used to propel the vehicle at relatively low speeds, and the second gear is used to propel the vehicle at relatively high speeds.

The first reducer 410 comprises the first input element 411 which is integral in rotation with a first input pinion 415, and a first toothed wheel 416 here meshing directly with the first input pinion 415. The second reducer 420 comprises the second input element 412 which is integral in rotation with a second input pinion 421, and a second toothed wheel 422 here meshing directly with the second input pinion 421. The output toothed wheels 416 and 422 rotate around of the Y axis.

The second input shaft is a hollow shaft 412 and the first input element 411 is a shaft which extends inside this hollow shaft 412. The second input shaft 412 and the first input shaft 411 are coaxial. As can be seen in the diagram of Figure 3, the first input shaft 411 can be formed in one piece with the pinion 415. Similarly, the second input shaft 412 can be formed in one piece with pinion 421.

The connection element 46 is arranged to allow mutual drive in rotation between the first input element 411 and the transmission shaft 45 of the speed reduction device 40, when the first clutch 100 is closed, and to interrupt the mutual drive between the first input element 411 and the shaft 45 of the speed reduction device 40 when the first clutch 100 is open. By avoiding driving the first reduction gear unnecessarily, there is no loss of efficiency which could be linked in particular to the bubbling of the rotating transmission elements.

The second toothed wheel 422 is integral in rotation with the transmission shaft 45, for example via splines. The first toothed wheel 416 can be made integral in rotation with the transmission shaft 45, via the connection element 46. In addition, the first toothed wheel 416 is rotatably mounted on a portion of the transmission shaft. transmission 45, for example via a rolling or needle bearing. Another portion of the transmission shaft 45 allows the coupling of the transmission shaft 45 and the first toothed wheel 416 via the connection element 46.

The transmission system further comprises an actuator capable of causing the connection element 46 to pass from a first mode of operation in which the first toothed wheel 416 is integral in rotation with the transmission shaft 45 to a second mode of operation. wherein the first toothed wheel 416 is rotatable relative to the transmission shaft 45.

The connection element here is a synchronizer 46. The synchronizer 46 comprises a hub 461 integral in rotation with the transmission shaft 45. The synchronizer 46 comprises a synchronization ring 462 forming with the first toothed wheel 416 a conical clutch by friction . The synchronizer 46 further comprises a slider 463 integral in rotation with the hub 461. The slider 463 can slide axially, parallel to the axis X, relative to the hub 461. The slider 463 comprises teeth 467 and the first output wheel 416 comprises complementary teeth 468 capable of cooperating with the teeth 467 of the player 63, to drive the player 463 (and therefore the transmission shaft 45) and the first output wheel 416 at the same speed during the first mode of operation.

The conical friction link allows a gradual change of speed between the second mode of operation and the first mode of operation of the synchronizer. Friction occurs between the first toothed wheel 416 and the synchronization ring 462 as long as the speeds of the first toothed wheel 416 and of the transmission shaft 45 are not substantially equal. The actuator makes it possible to move the slider 463 to engage the connection element 46.

The differential 80 then transmits the torque coming from the speed reduction device 40 to two opposite wheels of the vehicle. To increase the torque and lower the speed of rotation at the output of the torque transmission system 1, a speed reduction stage is also formed with an output pinion 49 integral in rotation with the transmission shaft 45 and a toothed wheel output 81 arranged at the input of the differential, the output toothed wheel 81 meshing with the pinion 49.

The torque transmission system 1 further comprises a parking brake mechanism comprising a toothed locking wheel 70 mounted integral in rotation on the second torque input element 412 of the speed reduction device 40 (FIG. 3).

The locking toothed wheel 70 is associated with a locking lever (not shown) piloted and movable between a locking position in which it engages in the toothing of the locking toothed wheel so as to prevent the drive in rotation of the second torque input element 412, and a release position in which it is disengaged from the toothing of the locking toothed wheel 70 so as to allow the rotational drive of the second torque input element 412.

We see in Figure 4 that the first input member 101 is arranged partly inside the stator 21, that is to say in the space radially separating the axis X and the stator. More specifically, the first input member 101 of the clutch device is arranged partly inside the winding, that is to say in the space radially separating the axis X and the winding, in particular at the inside the winding heads, but outside the stator body.

The output member 23 of the electric machine 20 and the first input member 101 of the clutch device 10 are mounted integral in rotation around the axis X thanks to a first coupling connection in rotation which is located at inside the stator 21, in particular inside the winding 212 but outside the stator body 211.

The stator 21 has the overall shape of a tube whose axis of revolution is the axis X and having an inside diameter 27 and an outside diameter 28. The clutch device 10, in particular its first input member 101, is arranged partly radially inside the inner diameter 27 of the stator 21.

The first clutch 100 and the second clutch 200 are on the other hand arranged outside the stator.

The first input pinion 415 and the second pinion 421 are axially offset on the X axis and also axially offset with respect to the first clutch and with respect to the second clutch.

The first clutch 100 and the second clutch 200 are arranged axially between on the one hand the stator 21 of the electric machine 20 and on the other hand the first input pinion 411 and the second input pinion 421. It is noted that with this architecture, it is particularly advantageous to save space axially by introducing part of the clutch device 10 inside the stator 21.

The first input member 101 of the clutch device 10 comprises, radially from the inside outwards, a radially internal portion 1011 at least partially disposed inside the stator 21, an axial uneven portion 1013 and a radially outer portion 1012, the radially inner portion 1011 being offset axially, in the direction of the electric machine 20, relative to the radially outer portion 1012 thanks to the axial uneven portion 1013. Thus, the shape of the axial uneven portion of the first input member 101 of the clutch device 10 makes it possible to introduce at least a part of the first input member 101 inside the stator 21. The axial uneven portion 1013 comprises an axial uneven step.

The radially outer portion 1012 of the first input member 101 is arranged outside the stator 21, in particular at least partly radially outside the inside diameter 27 of the stator 21.

The radially inner portion 1011 of the first input member 101 comprises a first splined hub 1015 coupled in rotation with a complementary splined portion of the output member 23 of the electric machine 20. The first rotational coupling connection between the output member 23 of the electric machine 20 and the first input member 101 of the clutch device 10 is therefore formed by this first splined hub 1015 and the complementary splined portion of the output member 23 of the electric machine 20.

The radially internal portion 1011 of the first input member 101 also comprises a portion in the form of a cone section extending, from the first splined hub 1015, radially outward, away from the electric machine 20.

The radially outer portion 1012 comprises an annular part developing radially around the axis X. This radially extending annular part extends radially outwards from the leveling step.

The first input member 101 of the clutch device comprises a first input disc carrier 106 and the second input member 201 of the clutch device 10 comprises a second input disc carrier 206. The second input disc carrier input 206 and the first input disc carrier 106 are formed on two parts fixed to each other.

The first input member 101 comprises an input web which connects the first input disc carrier 106 to the first splined hub 1015. The second input disc carrier 206 is also connected to the first splined hub 1015 via the veiled input, and the first door discs input 106. The radially inner portion 1011 and the portion of axial unevenness 1013 are formed on the input veil.

The first splined hub 1015 has splines on its outer diameter and the complementary splined portion has splines on its inner diameter. Thus, the first splined hub 1015 is housed radially inside the complementary splined portion of the output member 23 and can be driven in rotation by the latter.

The electric machine 20 comprises a protective casing 25 mounted so as to be able to rotate relative to the output member 23 of the electric machine 20, in particular by means of a bearing 24, for example a rolling bearing.

There is a plane perpendicular to the X axis passing both through the first splined hub 1015, the additional splined portion of the output member 23, and the bearing 24. There is also a plane perpendicular to the X axis passing simultaneously through the first splined hub 1015, the complementary splined portion of the output member 23, the bearing 24 and the stator 21, in particular the winding 212 of the stator. The casing 25 is formed to go around the winding heads 218 so as to allow the radial superimposition of the first splined hub, of the splined portion complementary to the output member 23 of the electric machine 20, and of the bearing 24.

The casing 25 of the electric machine 20 comprises a shoulder on which the bearing 24 rests, in a direction opposite to the clutch device 10.

The first output member 102 of the clutch device 10 comprises a radially inner portion and a radially outer portion, the radially inner portion being offset axially, in the direction of the electric machine 20, with respect to the radially outer portion. The first output member comprises at least one portion of axial difference in level, the radially outer portion and the radially inner portion of the first output member being connected by this portion of axial difference in level. As can be seen in Figure 4, the radially internal portion of the first output member 102 is arranged partly inside the stator 21, in particular inside the winding 212 but not outside the body of stator 211. The radially outer portion of the first output member 102 is arranged on the outside of the stator 21.

Similarly, the second output member 202 of the clutch device 10 comprises a radially inner portion and a radially outer portion, the radially inner portion being offset axially, in the direction of the electric machine 10, with respect to the radially outer portion. The second output member 202 comprises at least one portion of axial unevenness, the radially outer portion and the radially inner portion of the second output member 202 being connected by this portion of axial unevenness.

The axial difference in level portion 1013 of the first output member 102, the axial difference in level portion of the second output member 202, and the axial difference in level portion of the first input member 101 are nested one inside the other.

The first output member 102 of the clutch device 10 and the first input member 101 of the speed reduction device 40 are mounted integral in rotation around the axis X thanks to a second coupling connection in rotation which is arranged partially inside the stator 21, in particular inside the winding 212 but outside the stator body 211. The first input shaft 411 of the speed reduction device 40 comprises a splined portion and the radially internal portion of the first output member 102 comprises a second splined hub 1025 coupled in rotation about the axis X with the splined portion of the first input shaft 411. There is a plane perpendicular to the axis X passing both by the first splined hub 1015, the splined portion of the output member 23 of the electric machine 23, the second splined hub 1025, the splined portion of the first input shaft 411 of the speed reduction device 44 and the stator 21 , in particular winding 212.

Similarly, the second output member 202 of the clutch device 10 and the second input shaft 412 of the speed reduction device 40 are mounted integral in rotation around the axis X thanks to a third coupling connection in spin. The second input shaft 412 of the speed reduction device 40 comprises a splined portion and the radially internal portion of the second output member comprises a third splined hub 2025 coupled in rotation around the axis X with the splined portion of the second shaft input 412.

The second splined hub 1025 extends axially in the direction of the electric machine 20 while the third splined hub 2025 extends axially in a direction opposite to the electric machine 20.

The first clutch 100 comprises a first multi-disc assembly having a plurality of input discs 103 and a plurality of output discs 104 arranged to rub against each other when pressure is exerted axially on these input and output discs.

The second clutch 200 comprises a second multi-disc assembly having a plurality of input discs 203 and a plurality of output discs 204 arranged to rub against each other when pressure is exerted axially on these input and output discs.

The input discs 103 of the first clutch 100 are mounted integral in rotation with the first input disc carrier 106 and the output discs of the first clutch 100 are mounted integral in rotation with a first output disc carrier 110.

The input discs 203 of the second clutch are mounted integral in rotation with the second input disc carrier 206 and the output discs 204 of the second clutch 200 are mounted integral in rotation with a second output disc carrier 210.

The first entry disk carrier 106 and the second entry disk carrier 206 are fixed to each other and together with the first entry web form a rigid subassembly.

The first output member 102 includes a first output web that connects the first output disc carrier 110 to the second splined hub 1025. Similarly, the second output member 202 includes a first output web that connects the second output disc carrier 210 to third splined hub 2025

The clutch device 10 is a mechanism with double clutches 10, preferably of the type with double wet clutches.

The first clutch 100 and the second clutch 200 are advantageously of the multi-disc type. Each multi-disc clutch comprises on the one hand a plurality of input discs 103, 203, such as for example flanges, and on the other hand a plurality of output discs 104, 204, such as for example friction discs.

The first input element 411 is rotationally coupled to the output member 23 of the electric machine 20 via the first clutch 100. The first input member 411 is driven by the output member of the machine electric 23 in rotation when the first clutch 100 is configured in a so-called engaged position.

Alternatively, the first input element 411 is decoupled in rotation from the output member of the electric machine when the first clutch 100 is configured in a so-called disengaged position.

Similarly, the second input element 412 is coupled in rotation to the output member 23 of the electric machine 20 via the second clutch 200. The second input element 412 is driven by the output of the electrical machine in rotation when the second clutch 200 is configured in an engaged position. Alternatively, the second input element 412 is decoupled in rotation from the output member of the electric machine when the second clutch 200 is configured in a so-called disengaged position.

The first clutch 100 and the second clutch 200 are arranged to alternately transmit a so-called input power from the output member 23 of the electric machine 20, to one of the two transmission shafts 411, 412, depending on the respective configuration of each clutch 100 and 200.

A first axial bearing 117 is interposed between the first output member 102 and the first input member 101 in order to be able to transmit axial forces during operation of the clutch module despite the different rotational speeds at which the member can respectively turn. output 23 of the electric machine 20 and the first input element 411.

In a comparable manner, a second axial bearing 116 is interposed between the first output member 102 and the second output member 202 in order to be able to transmit an axial force between the two output members 102, 202 which can rotate at different speeds when the first and second clutches 100, 200 are configured in a different configuration.

At its inner end, the input disc carrier 106 comprises a heel 118 bearing radially on a support bearing 15 arranged to support the radial load of the clutch mechanism 10.

The clutch device 10 is assembled on an actuation system 30 of the clutch device 10, thus forming a clutch module.

Indeed, the first and second clutches 100 and 200 of the clutch device 10 are controlled by the actuation system 30 which is arranged to be able to configure them in any configuration between the engaged configuration and the disengaged configuration. To this end, the actuation system 30 comprises:

- a first actuator 32 arranged to configure the first clutch 100 in a configuration between the engaged configuration and the disengaged configuration;

- a second actuator 33 arranged to configure the second clutch 200 in a configuration between the engaged configuration and the disengaged configuration;

– a casing 34 in which are housed at least a part of the first and second actuators 32, 33.

The first actuator 32 is linked to the first clutch 100 via a first decoupling bearing 36 on the one hand and a first force transmission member 38 on the other hand. The first decoupling bearing 36 is arranged to transmit axial forces generated by the first actuator 32 to the first force transmission member 38.

The first force transmission member 38 is arranged to transmit an axial force, exerted parallel to the longitudinal axis X, to the first clutch 100 in order to be able to separate or press the first input discs 103 against the first output discs 104. When the first input discs 103 are separated from the first output discs 104, then the first clutch 100 is configured in its disengaged configuration. On the other hand, when the first input discs 103 are pressed against the first output discs 104, then the first clutch 100 is configured in its engaged configuration.

The second actuator 33 is linked to the second clutch 200 via a second decoupling bearing 37 on the one hand and a second force transmission member 39 on the other hand. The second decoupling bearing 37 is arranged to transmit axial forces generated by the second actuator 33 to the second force transmission member 39. The second force transmission member 39 is globally located axially between the first input disc carrier 106 and the first force transmission member 38.

The second force transmission member 39 is arranged to transmit an axial force to the second clutch 200 in order to be able to separate or press the second input discs 203 against the second output discs 204. When the second input discs 203 are separated second output discs 204, then the second clutch 200 is configured in its disengaged configuration. On the other hand, when the second input discs 203 are pressed against the second output discs 204, then the second clutch 200 is configured in its engaged configuration.

When the clutch device 100 is assembled to the actuation system 30, as shown in Figures 3 and 4, the clutch device 100 is fitted to an axial end of the cylindrical bearing surface 35 of the housing 34 of the actuation system 30. In other words, the support bearing 15 bears radially against the cylindrical bearing surface 35 of the housing 34 via its inner annular ring 151. In addition, the lubrication ring 31 is located in an axially intermediate position. between the support bearing 15 and the output disc carriers 102, 202. More particularly, the lubrication ring 31 is located axially against the support bearing 15, through an axial bearing against its inner annular ring 151. In order to guarantee its correct operation, the clutch device 10 is axially blocked to allow an axial force to be transmitted from the actuation system 30 to the clutches 100, 200. To this end, the cylindrical bearing surface 35 of the housing 34 comprises a circumferential groove visible on figure 4. The circumferential groove houses a stop ring (not referenced) which makes it possible to achieve an axial stop of the lubrication ring 31 with respect to the casing 34 of the actuation system 30.

The lubricating ring 31 bears axially against the stop ring which is for example snapped into the groove.

In order to lubricate and cool the first 100 and second 200 clutches during their operation, the double clutch 10 further comprises a hydraulic circuit making it possible to convey a hydraulic fluid to the first 100 and second 200 clutch. More particularly, the casing 34 of the actuation system 30 comprises a channel (not referenced) allowing a hydraulic fluid to circulate. The channel comprising an axial extension part and a radial extension part located at the front axial end of the axial extension part. The axial extension part of the channel extends axially along the cylindrical bearing surface 35 of the casing 34 which is located radially inside the first 32 and second 33 actuators and which extends axially beyond the said first 32 and second 33 actuators, in the direction of the electric machine 20. The radial extension part of the channel is in fluid communication with at least one lubrication channel of the lubrication ring 31.

In Figure 5 is shown a detail sectional view of a second embodiment of the invention. The output member 23 of the electric machine 20 and the first input member 101 of the clutch device 10 are mounted integral in rotation around the axis X thanks to a first coupling connection in rotation which is arranged here totally inside the stator 21, particularly inside the winding 212 but outside the stator body 211. In this embodiment, the first input web is arranged at least partly inside of the stator 21, in particular inside the winding 212 but outside the stator body 211.

Of course, the invention is not limited to the examples which have just been described and many adjustments can be made to these examples without departing from the scope of the invention. In particular, the different characteristics, forms, variants and embodiments of the invention may be associated with each other in various combinations insofar as they are not incompatible or exclusive of each other.

Claims (13)

Transmission system (1) for a vehicle, in particular for a hybrid or electric motor vehicle, comprising:
- an electric machine (20) arranged around an X axis and comprising a stator (21), a rotor (22) and an output member (23), the output member (23) of the electric machine (20 ) being driven in rotation by the rotor (22) around the axis X,
- a clutch device (10),
characterized in that the clutch device (10) is arranged at least partly inside the stator (21). Transmission system (1) according to Claim 1, in which the electric machine has a cavity (29) extending around the X axis and the clutch device has a protrusion (19) also extending around the X axis and disposed in the cavity (29) of the electric machine (20). Transmission system (1) according to Claim 1 or 2, in which the stator (21) is provided with a tubular-shaped stator body (211) extending along the axis X and with a winding (212 ) extending axially along the stator body (211), the clutch device (10) being axially offset from the stator body (21) and the winding (212) projecting axially from the stator body (211) towards the clutch device (10), the clutch device (10) being arranged at least partly inside the winding (212), but outside the stator body (211). Transmission system (1) according to one of Claims 1 to 3, in which the stator (21) has the overall shape of a tube having an inside diameter (27) and an outside diameter (28) and whose axis of revolution is the X axis, the clutch device (10), in particular the first input member (101) of the clutch device, being arranged at least partially radially inside the inside diameter (27) of the stator (21). Transmission system (1) according to one of Claims 1 to 4, in which the clutch device (10) comprises a first input member (101), a first output member (102) and a first clutch (100 ) extending circumferentially around the X axis, the first clutch (100) being adapted to interrupt the transmission of a torque between the first input member (101) and the first output member (102) of the device clutch (10), the first input member (101) of the clutch device (10) being driven by the output member (23) of the electric machine and arranged at least partly inside the stator (21); and the first clutch (100) being disposed outside the stator (21). Transmission system (1) according to Claims 5 and 3, in which the output member (23) of the electric machine (20) and the first input member (101) of the clutch device (10) are mounted integral in rotation around the X axis thanks to a first rotary coupling link which is arranged partially or totally inside the stator (21); especially inside the winding (212) but outside the stator body (211). Transmission system (1) according to claim 5 or 6 wherein the clutch device (10) further comprises a second input member (201), a second output member (202) and a second clutch (200) arranged around the X axis, the second clutch (200) being capable of interrupting the transmission of a torque between the second input member (201) and the second output member (202) of the clutch device (10 ); the transmission system further comprising a speed reduction device (40), the speed reduction device comprising a first reducer (410) and a second reducer (420), the first reducer (410) comprising a first input (411) driven in rotation by the first output member (102) of the clutch device (10) and the second reduction gear (420) comprising a second input element (412) driven in rotation by the second output member (202) of the clutch device (10). Transmission system (1) according to Claim 7, in which the first input member (101) of the clutch device (10) is driven in rotation by the output member (23) of the electric machine (20) around of the X axis, the second input member (102) of the clutch device is driven in rotation by the output member (23) of the electric machine around the X axis; the first input element (411) of the speed reduction device (40) is driven in rotation about the axis X by the first output member (102) of the clutch device (10) and the second element of input (412) of the speed reduction device (40) is driven in rotation about the X axis by the second output member (202) of the clutch device (20); the first input element (411) of the speed reduction device (40) being adapted to drive in rotation around the axis X a first input pinion (411) and the second input element (412) of the speed reduction device (40) being adapted to drive in rotation around the axis X a second input pinion (421), the first input pinion (411) and the second pinion (421) being offset axially on the X axis. Transmission system (1) according to one of Claims 7 to 8, in which the first clutch (100) and the second clutch (200) are arranged axially between, on the one hand, the stator (21) of the electric machine (20) and on the other hand the first input pinion (411) and the second input pinion (421). Transmission system (1) according to one of Claims 7 to 9, in which the first clutch (100) is arranged radially outside the second clutch (200) and the first clutch (100) radially overlaps the second clutch (200 ). Transmission system (1) according to one of Claims 5 to 10, in which the first input member (101) of the clutch device (10) comprises, radially from the inside outwards, a radially internal portion (1011) at least partly disposed inside the stator (21), a portion of axial unevenness (1013) and a radially outer portion (1012), the radially inner portion (1011) being offset axially, in the direction of the electric machine (20), with respect to the radially outer portion (1012) thanks to the axial unevenness portion (1013). Transmission system (1) according to one of Claims 5 to 11, in which the first input member of the clutch device (101) comprises a first splined hub (1015) coupled in rotation with a splined portion of the (23) of the electric machine (20), the electric machine comprising a protective casing (25) mounted so as to be able to rotate with respect to the output member (23) of the electric machine (20) by means of a bearing (24), for example a rolling bearing; and there is a plane perpendicular to the X axis passing through both the first splined hub (1015), the splined portion of the output member (23) of the electric machine (20), and the bearing (24) . Transmission system (1) according to Claim 3 and one of Claims 7 to 10, in which the first output member (102) of the clutch device (10) and the first input member (101) of the reduction device gears (40) are mounted fixed in rotation around the X axis thanks to a second rotational coupling connection which is arranged partially or totally inside the stator (21); especially inside the winding (212) but outside the stator body (211).