Torque transmission system with torque adaptation module

Abstract

The invention relates to a torque transmission system (1) for an electric or hybrid vehicle, comprising a propulsion unit (10) and a torque adaptation module (100), the torque adaptation module (100) comprising a planetary gear device (110) and a second electric machine (120) comprising a rotor shaft (121) rotationally coupled with a planet carrier (113) of the planetary gear device. Figure to be published: 1

Description

Title of the invention: Torque transmission system with torque adaptation module technical field

[0001] The invention relates to the field of transmission systems for hybrid or electric vehicles. The invention relates more particularly to a torque transmission system equipped with a torque adaptation module.

[0002] Document WO2019 / 192806 describes a torque adaptation device for a vehicle axle equipped with a differential. The torque adaptation device is capable of providing a torque vectoring function.

[0003] This device is unsatisfactory because the proposed speed ratios do not allow for proper torque adaptation and compact integration of the torque adaptation module alongside the propulsion unit. The problems of assembling the module with the propulsion unit are also not addressed in this document.

[0004] According to a first aspect, the invention relates to a torque transmission system for a hybrid or electric vehicle, comprising a propulsion unit and a torque adaptation module, the propulsion unit comprising: - a first electrical machine comprising a stator and a rotor as well as a rotor shaft capable of rotating around a first axis of rotation, - a differential comprising a torque input element movable about a second axis of rotation, the torque input element of the differential being capable of driving in rotation about the second axis of rotation, a first lateral shaft and a second lateral shaft, via a set of gears, - a reduction device capable of transmitting torque between the rotor shaft of the electric machine and the differential such that the rotational speed of the first and second lateral shafts is lower than the rotational speed of the rotor shaft when torque is transmitted between the first electric machine and the differential, characterized in that the torque adaptation module comprises: - on the one hand, a planetary gear system comprising a first planetary train and a second planetary train arranged around the second axis of rotation, axially aligned with each other; the first planetary train comprising a first set of planet gears, a first input member formed by a first sun gear and a first output member formed by a planet carrier carrying the first set of planet gears; the second planetary train comprising a second set of planet gears, a second input member formed by the planet carrier which carries also the second set of satellite gears and a second output element formed by a second solar; the first solar being coupled in rotation along the second axis of rotation with the input element of the differential; and the second solar being coupled in rotation, along the second axis of rotation to the first lateral shaft, - on the other hand a second electric machine comprising a rotor shaft coupled in rotation, along the second axis of rotation, with the satellite carrier.

[0005] The expression "rotationally coupled" means that the two rotationally coupled elements are assembled in such a way that they do not rotate relative to each other. In other words, it is a rotationally fixed joint, possibly exhibiting very small clearance such as spline clearance.

[0006] The torque transmission system may also include at least one of the following features:

[0007] - The planetary gear device is devoid of crown(s) inside which engage the first set of satellite gears and the second set of satellite gears.

[0008] - The planetary gear device has a first speed ratio The velocity factor R should be between 0.975 and 0.995, preferably between 0.98 and 0.99. This range offers a good compromise, providing both good efficiency and an appropriate level of stress. Indeed, when the speed of the first solar element is zero, the second velocity ratio k between the satellite carrier and the second solar element is equal to l / (1 - R). Also, when the first stationary velocity ratio of the planetary gear system is greater than 0.995, the second velocity ratio k between the satellite carrier and the second solar element is 200. Such a ratio is significant and increases exponentially as it approaches 1, which can damage the system. The second velocity ratio k is therefore preferably between 40 and 200, preferably between 50 and 100, and especially between 60 and 80.

[0009] - The first set of satellite gears and the second set of satellite gears com each take 4 or more satellite gears. Thus, compared to planetary trains with 3 or fewer satellite gears, the increase in the number of contact teeth makes it possible to reduce the area of ​​the different contact surfaces and therefore to decrease the size of the satellites and reduce the overall size of the planetary gear system, especially radially.

[0010] - The first set of satellite gears and the second set of satellite gears com each takes exactly 5 satellite gears.

[0011] - The peripheral teeth of the satellite gears of the first set of satellite gears each have the same number of teeth which is different from the number of teeth of the peripheral teeth of the satellite gears of the second set of satellite gears.

[0012] - The first solar element has peripheral teeth comprising 37 teeth, the The second solar gear has a peripheral toothing system with 33 teeth, the planetary gears of the first set of planetary gears each have a peripheral toothing system with 21 teeth, and the planetary gears of the second set of planetary gears each have a peripheral toothing system with 19 teeth. With this configuration, a first steady-state speed ratio R of 0.985775 is achieved, which is within the preferred range.

[0013] - In a plane perpendicular to the second axis of rotation Y, the outer periphery The planetary gear system is inscribed in a circle of diameter DI, and the outer periphery of the second electric machine is inscribed in a circle of diameter D2. The second electric machine and the planetary gear system are dimensioned such that 0.9 <D1 / D2<1,1. En particulier, le diamètre D2 correspond au diamètre externe du stator.

[0014] - The second electrical machine is an air-cooled machine. This allows for limiting the radial footprint of the second electric machine.

[0015] - The first electrical machine, in particular its stator, has a diameter external diameter D4 and the second electrical machine, in particular its stator, has an external diameter D2, the first electrical machine and the second electrical machine being dimensioned such that 2 <D4 / D2<5.

[0016] - The differential input element comprises an input ring having a external diameter D3, the input ring being driven in rotation by the reduction device, the diameter D2 being less than the external diameter D3 of the input ring.

[0017] - The second axis of rotation is parallel to the first axis of rotation.

[0018] - The torque adaptation module is arranged entirely in axial space occupied by the first electric machine, in particular in the axial space occupied by the rotor (without the rotor shaft) and / or the stator of the first electric machine.

[0019] - The planetary gear device is arranged axially between the second electric machine and the differential.

[0020] - The differential's torque input element is a housing enclosing the play differential gears.

[0021] - The differential gear set includes a first output coupled in rotation with the first lateral shaft and a second output coupled in rotation with the second lateral shaft.

[0022] - The transmission system includes a first casing, the differential housing comprising a first sleeve arranged around the second axis of rotation, and the first housing comprising a first opening through which the second axis of rotation passes, the first sleeve extending from the first housing along the second axis of rotation through the first opening.

[0023] - The first opening is located axially opposite the first solar element.

[0024] - The first casing comprises a first part having a housing in which was the first electric machine assembled.

[0025] - The first housing comprises a second part fixed to the first part in closing the housing of the first part.

[0026] - The second part encloses a portion of the space occupied by the device reduction and differential (except for the first sleeve).

[0027] - The first housing comprises a third part fixed to the second part and in expanding the rest of the space occupied by the reduction device and the differential (with the exception of the first sleeve).

[0028] - The satellite carrier includes a sail mounted rotationally fixed to the rotor shaft of the second electric machine.

[0029] - The satellite carrier comprises rods extending parallel to the second axis of rotation and around which are mounted respectively in pairs and in an axially offset manner, a satellite pinion from the first set of satellite pinions and a satellite pinion from the second set of satellite pinions.

[0030] The satellite carrier includes a cover, the first set of satellite gears and the second set of satellite gears being arranged axially between the web and the cover.

[0031] - The cover has an annular shape around the second axis of rotation.

[0032] - The rods extend axially between the veil and the cover.

[0033] - The propulsion assembly includes a second casing covering the module torque adaptation, the second housing comprising a bell in which the planetary gear device is arranged, the bell being open axially in the direction of the differential, the satellite carrier cover being arranged radially between the edge of the bell opening and a tubular portion of the first housing, in particular its second part.

[0034] - The tubular portion of the first housing, in particular its second part, protrudes axially in the direction of the first solar ray.

[0035] - A bearing is arranged radially between the tubular portion of the first housing, particularly its second part, and the satellite carrier cover.

[0036] - The second casing also includes a chamber in which the stator and the rotor of the second electric machine.

[0037] The chamber is axially delimited by two bearings arranged radially, each between the rotor shaft of the second electric machine and a chamber flange.

[0038] - The chamber flange located on the side of the planetary gear device forms the bottom of the bell.

[0039] - The first housing, in particular the first part of the first housing, comprises a sheath (or concavity) inside which the second casing is mounted.

[0040] - A bearing is mounted radially between the first lateral shaft and the sleeve of the first crankcase.

[0041] - A shoulder is arranged at the end of the grooves of the first sleeve located towards the differential gear set.

[0042] - The first solar element is capable of coming into axial contact with the sleeve during the assembly of the planetary gear system with the propulsion assembly.

[0043] - The first solar element is able to come into axial contact against said shoulder.

[0044] - The torque transmission system includes a first inverter associated with the first electric machine and a second inverter associated with the second electric machine, the torque transmission system comprising a common control unit to drive the first inverter and the second inverter.

[0045] The invention also relates to a vehicle, electric or hybrid, comprising this transmission system. Brief description of the figures

[0046] The invention will be better understood, and other objects, details, features and advantages thereof will become more apparent from the following description of several particular embodiments of the invention, given solely by way of illustration and not limitation, with reference to the accompanying drawings.

[0047] [Fig-1] Fig. 1 is a cross-sectional view of a torque transmission system according to a first method of implementation.

[0048] [Fig.2] The [Fig.2] is an enlarged view of the torque adaptation module of the [Fig.1].

[0049] [Fig.3] Fig.3 is a representation of the function l / (1-R)

[0050] [Fig.4] The [Fig.4] shows a preferred selection range for the first stationary velocity ratio R in the graph of the [Fig.3].

[0051] [Fig.5] The [Fig.5] is a front view of an embodiment of a first planetary gear train of a torque adaptation module, when the cover is removed.

[0052] [Fig.6] The [Fig.6] is a perspective view of the torque adaptation module of the [Fig.5] without the satellite carrier cover.

[0053] [Fig.7] The [Fig.7] is a perspective view of the satellite carrier of the [Fig.5]. Description of the implementation methods

[0054] In the description and claims, the terms "external" and "internal," as well as the orientations "axial" and "radial," shall be used to designate, according to the definitions given in the description, elements of the transmission system. By convention, the axes of rotation of the rotating parts of the transmission system define the "axial" orientation. The "radial" orientation is directed orthogonally to the axis in question and, from the inside out, away from the axis of rotation of the rotating part in question. The terms "external" and "internal" are used to define the relative position of one element with respect to another, with reference to the axis of rotation in question; an element close to the axis is thus described as internal, as opposed to an external element located radially on the periphery.

[0055] Figures 1 and 2 represent, according to a first embodiment, a torque transmission system 1 for a hybrid or electric vehicle. It comprises a propulsion unit 10 and a torque adaptation module 100.

[0056] The propulsion assembly 10 includes a first electric machine 11, a differential 20, and a reduction device 30.

[0057] The first electric machine 11 comprises a stator 6 and a rotor 7 fixed in rotation to a rotor shaft 12. The rotor 7 and the rotor shaft 12 are capable of rotating around a first axis of rotation X.

[0058] The differential 20 includes a torque input element 21 movable about a second axis of rotation Y that is parallel to the first axis of rotation X. The torque input element 21 of the differential 20 is capable of driving, in rotation about the second axis of rotation Y, a first lateral shaft 31 and a second lateral shaft 32, via a gear set 25. The first lateral shaft 31 and the second lateral shaft 32 are each configured to drive a drive wheel of the vehicle. The torque input element 21 of the differential 20 is a housing within which the gear set 25 of the differential 20 is housed. As it is a differential, the lateral shafts 31 and 32 can rotate at different speeds.

[0059] The gear set 25 of the differential 20 includes a first output coupled in rotation with the first lateral shaft 31 and a second output coupled in rotation with the second lateral shaft 32.

[0060] The reduction device 30 can transmit a torque between the rotor shaft 12 of the electric machine 11 and the torque input element 21 of the differential 20. The rotational speed of the first and second lateral shafts 31, 32 is thus lower than the rotational speed of the rotor shaft 12 when a torque is transmitted between the first electric machine 11 and the differential 20.

[0061] The torque adaptation module 100 comprises, on the one hand, a planetary gear device 110 and, on the other hand, a second electric machine 120. The second electric machine comprises a stator 126 and a rotor 127 fixed in rotation to a rotor shaft 121. The rotor 127 and the rotor shaft 121 are able to rotate about the second axis of rotation Y.

[0062] The planetary gear system 110 comprises a first planetary gear train 111 and a second planetary gear train 112 arranged in series around the second axis of rotation Y. "Arranged in series" means an arrangement of the system in planetary gears such that the output element of the first planetary train is rotationally fixed to the input element of the second planetary train along the second axis of rotation Y.

[0063] The first planetary train 111 and the second planetary train 112 are arranged axially next to each other.

[0064] The first planetary train 111 comprises a first sun gear 1111 and a first set of planetary gears 1110 each meshing with the first sun gear 1111. The planetary gears 1110 of the first set of planetary gears are carried by a planet carrier 113.

[0065] The first solar element 1111 forms a first input element of the first planetary train 111. The satellite carrier 113 forms a first output element of the first planetary train 111.

[0066] The second planetary train 112 includes a second sun gear 1121 and a second set of satellite gears 1120 each meshing with the second sun gear 1121. The satellite gears 1120 of the second set of satellite gears are also carried by the satellite carrier 113.

[0067] The satellite carrier 113 forms a second input element of the second planetary train 111. The second solar 1121 forms a second output element of the second planetary train 112.

[0068] The first solar 1111 is coupled in rotation along the second axis of rotation Y with the input element 21 of the differential 20 and the second solar 1121 is coupled in rotation, along the second axis of rotation Y, to the first lateral shaft 31.

[0069] The rotor shaft 121 of the second electric machine is itself coupled in rotation, along the second axis of rotation Y, with the satellite carrier 113. Thus, the second electric machine, by transmitting an additional torque to the satellite carrier, makes it possible to adapt the value of the torque transmitted to the first and second lateral shafts 31 and 32 by differentiating in particular the value of torque transmitted by the first lateral shaft 31 from the value of torque transmitted by the second lateral shaft 32.

[0070] The planetary gear device 110 is arranged axially between the second electric machine 120 and the differential 20.

[0071] It is noted that the planetary gear device is devoid of crown(s) inside which the first set of satellite gears and the second set of satellite gears mesh.

[0072] Advantageously, the planetary gear device 110 has, between the first input member 1111 and the second output member (1121), a first stationary speed ratio R between 0.975 and 0.995, preferably between 0.98 and 0.99.

[0073] This range offers a good compromise, providing both good efficiency and an adequate level of stress. Indeed, when the speed of the first solar 1111 is If zero, the second velocity ratio k between the satellite carrier 113 and the second solar array 1121 is equal to 1 / (1-R). Therefore, when the first stationary velocity ratio R of the planetary gear system is greater than 0.995, the second velocity ratio k between the satellite carrier and the second solar array 1121 is 200. Such a ratio is significant and increases exponentially as it approaches 1, which could damage the system.

[0074] Figures 3 and 4 show the evolution of the second speed ratio k with respect to the first stationary speed ratio R. [Fig.3] shows the exponential evolution of the second ratio k as the first speed ratio R approaches 1. [Fig.4] shows the preferred range of values ​​for the first stationary speed ratio R.

[0075] In the first embodiment shown in Figures 1 and 2, as well as in the embodiment shown in Figures 5 to 7, the first set of planetary gears 1110 and the second set of planetary gears 1120 each comprise exactly 5 planetary gears. Thus, compared to planetary gear trains with 3 or fewer planetary gears, increasing the number of contact teeth makes it possible to reduce the area of ​​the various contact surfaces and therefore to decrease the size of the planetary gears and reduce the overall size of the planetary gear system, particularly radially.

[0076] With regard to the planetary gear device 110, the satellite carrier 113 includes a sail 115 mounted rotationally fixed to the rotor shaft 121 of the second electric machine 120.

[0077] As can be seen in [Fig.7], it can for this purpose be provided with splines cooperating with splines of the rotor shaft 121.

[0078] The satellite carrier 113 has rods 117 extending parallel to the second axis of rotation Y and around which are mounted respectively in pairs and in an axially offset manner, a satellite pinion 1110 of the first set of satellite pinions and a satellite pinion 1120 of the second set of satellite pinions.

[0079] On the side opposite the disc 115, the planet carrier 113 includes a cover 114. The rods 117 are fixed at their first end to the disc and at their second end to the cover. Consequently, the first set of planet gears 1110 and the second set of planet gears 1120 are arranged axially between the disc 115 and the cover 114. The cover 114 has an annular shape around the second axis of rotation Y.

[0080] The satellite carrier 113 can also be provided with spacers 124 arranged between the disc 115 and the cover 114. Preferably, each spacer 124 is arranged circumferentially between two pairs of satellite gears, each pair of satellite gears comprising one satellite gear from the first set of satellite gears and one gear satellite of the second set of satellite pinions.

[0081] The first solar element 1111 is mounted rotationally fixed to the input element 21 of the differential 20 by means of splines formed both on the internal diameter of the first solar element 1111 and on the external diameter of the first sleeve 27. Advantageously, a shoulder 271 is arranged at the end of the splines of the first sleeve located in the direction of the gear set 25 of the differential 20. The first solar element 1111 can thus come to rest axially against the sleeve 27 during the assembly of the planetary gear device with the propulsion assembly.

[0082] The second solar 1121 is mounted rotationally fixed to the first lateral shaft 31 by means of splines provided both on the internal diameter of the second solar 1121 and on the external diameter of the first lateral shaft 31. When assembling the first lateral shaft with the torque adaptation module and with the propulsion assembly, the first lateral shaft 31 is on the one hand fixed in rotation, along the second axis of rotation Y, with the second solar 1121 by means of these splines, and on the other hand with the first output of the gear set 25 of the differential 20 with other splines.

[0083] The peripheral teeth of the satellite gears 1110 of the first set of satellite gears each have the same number of teeth which is different from the number of teeth of the peripheral teeth of the satellite gears 1120 of the second set of satellite gears.

[0084] In the embodiment shown in Figures 5 to 7, it can be seen that the first sun gear 1111 has peripheral teeth comprising 37 teeth, the second sun gear 1121 has peripheral teeth comprising 33 teeth, the planet gears 1110 of the first set of planet gears each have peripheral teeth comprising 21 teeth, and the planet gears of the second set of planet gears 1120 each have peripheral teeth comprising 19 teeth. With this configuration, a first steady speed ratio R, between the first input element and the second output element, equal to 0.985775, is advantageously achieved within the desired range.

[0085] Such a configuration is particularly advantageous from a space-saving perspective. It is indeed beneficial for the torque adaptation module added to the propulsion system to be compact.

[0086] In a plane perpendicular to the second axis of rotation Y, the outer periphery of the planetary gear device 110 is inscribed in a circle of diameter DI and the outer periphery of the second electric machine 120 is inscribed in a circle of diameter D2, the second electric machine 120 and the planetary gear device 110 are dimensioned such that 0.85 <Dl / D2<l a,15, en particulier 0.9 <D1 / D2<1,1.

[0087] To limit the radial footprint of the second electric machine 120, an air-cooled machine is advantageously chosen.

[0088] The second electric machine is relatively small compared to the first electric machine. The first electric machine has an external diameter D4 and the second electric machine has an external diameter D2. The first and second electric machines are dimensioned such that 2 <D4 / D2<5.

[0089] The input element 21 of the differential 20 comprises an input ring having an external diameter D3, the input ring being driven in rotation by the reduction device, the diameter D2 being less than the external diameter D3 of the input ring.

[0090] Axially, the torque adaptation module 100 is arranged entirely in the axial space occupied by the first electric machine 11, in particular in the axial space occupied by the rotor (without the rotor shaft) and the stator of the first electric machine 11.

[0091] Thus, the torque adaptation module can be added to the propulsion assembly in the axial extension of the differential without extending axially or radially beyond the space occupied by the propulsion assembly.

[0092] The torque transmission system includes a first housing 19 arranged around the propulsion assembly and a second housing 109 arranged around the torque adaptation module 100.

[0093] The differential housing 21 comprises a first sleeve 27 arranged around the second axis of rotation Y, and the first housing 19 comprises a first opening 18 through which the first sleeve 27 protrudes from the first housing 19 along the second axis of rotation Y. The opening 18 is located axially opposite the first sun 11.

[0094] The second housing 109 includes a first opening 1090 through which the second axis of rotation Y passes. The first lateral shaft 31 can be threaded through the first opening 1090 of the second housing 109 and then pass inside the torque adaptation module and then inside the first sleeve 27 along the second axis of rotation Y to couple with the first output of the gear set 25 of the differential.

[0095] On the other side, the torque input element 21 of the differential 20 includes a second sleeve 28 arranged around the second axis of rotation Y. The first housing 19 includes a second opening through which the second axis of rotation Y passes. The second sleeve 28 is arranged inside the first housing 19 axially with respect to the second opening.

[0096] The second side shaft 32 can be threaded through the second opening of the housing 19 inside the second sleeve 28 to mate with the second output of the differential gear set 25.

[0097] The first housing 19 comprises a first part 191 having a recess in which the first electric machine is mounted. The first housing also comprises a second part 192 attached to the first part 191 by closing the recess of the first part 191. The second part 192 encloses a portion of the space occupied by the reduction device 30 and the differential 20 (excluding the first sleeve). A third part 193 of the first housing 19 is attached to the second part 192 and encloses the remainder of the space occupied by the reduction device 30 and the differential 20 (excluding the first sleeve). The second part 192 is axially clamped between the first part 191 and the third part 193 of the first housing 19.

[0098] The second housing 109 covering the torque adaptation module 100 includes a bell 1091 open axially towards the differential. This bell houses the planetary gear device.

[0099] A tubular portion 1920 of the first casing 19, in particular of its second part 192, protrudes axially in the direction of the first solar 1111.

[0100] The cover 114 of the satellite carrier 113 is arranged radially between the edge of the opening of the bell 1091 and this tubular portion 1920.

[0101] A bearing 16 can be arranged radially between this tubular portion 1920 of the second part 192 of the first housing 19 and the inner diameter of the cover 114 of the satellite carrier 113.

[0102] Thanks to these characteristics, the torque adaptation module 100 can be added simply, for example as an option, to a drive unit 10.

[0103] The second housing 109 also includes a chamber in which the stator 126 and the rotor 127 of the second electrical machine 120 are housed. The chamber is axially delimited on each side of the rotor by a flange. On each side, a bearing is arranged radially between the rotor shaft 121 of the second electrical machine 120 and one of the two flanges of the chamber.

[0104] The first housing 19, in particular the first part 191 of the first housing 19 includes a sleeve 1910 (or concavity) inside which the second housing 109 is mounted.

[0105] A bearing is mounted radially between the first lateral shaft 31 and the sleeve 1910 of the first housing 19. This sleeve can be formed in one piece or on a part added to the first part 191 of the first housing 19.

[0106] According to one embodiment, the torque transmission system comprises a first inverter associated with the first electric machine and a second inverter associated with the second electric machine, the torque transmission system including a common control unit to operate the first inverter and the second inverter.

[0107] The transmission system is configured to allow reversible operation of the second electric machine, i.e. to allow it to operate in regeneration mode.

[0108] In the claims, any reference sign in parentheses shall not be interpreted as a limitation of the claim.

Claims

Demands

1. Torque transmission system (1) for an electric or hybrid vehicle, comprising a drive unit (10) and a torque adaptation module (100), the drive unit (10) comprising - a first electrical machine (11) comprising a stator (6) and a rotor (7) as well as a rotor shaft (12) capable of rotating around a first axis of rotation (X), - a differential (20) comprising a torque input element (21) movable about a second axis of rotation (Y), the torque input element (21) of the differential (20) being capable of driving in rotation about the second axis of rotation (Y), a first lateral shaft (31) and a second lateral shaft (32), via a gear set (25), - a reduction device (30) capable of transmitting torque between the rotor shaft (12) of the electric machine (11) and the differential (20) such that the rotational speed of the first and second lateral shafts (31, 32) is less than the rotational speed of the rotor shaft (12) when torque is transmitted between the first electric machine (11) and the differential (20), characterized in that the torque adaptation module (100) comprises: - on the one hand, a planetary gear device (110) comprising a first planetary gear train (111) and a second planetary gear train (112) arranged around the second axis of rotation (Y),axially with respect to each other; the first planetary train (111) comprising a first set of planetary gears (1110), a first input member formed by a first sun gear (1111) and a first output member formed by a planet carrier (113) carrying the first set of planetary gears (1110); the second planetary train (112) comprising a second set of planetary gears (1120), a second input member formed by the planet carrier (113) which also carries the second set of planetary gears (1120) and a second output member formed by a second sun gear (1121); the first sun gear (1111) being rotationally coupled about the second axis of rotation (Y) with the input element (21) of the differential (20); and the second sun gear (1121) being rotationally coupled about the second axis of rotation (Y) to the first lateral shaft (31), - on the other hand, a second electrical machine (120) comprising a rotor shaft (121) coupled in rotation, along the second axis of rotation (Y), with the planet carrier (113). The second axis of rotation (Y) being parallel to the first axis of rotation (X) and the torque adaptation module (100) being arranged entirely within the axial space occupied by the first electric machine (11), in particular within the axial space occupied by the stator (6) of the first electric machine (11)

2. Torque transmission system (1) according to claim 1 in which the planetary gear device (110) has a first stationary speed ratio (R) between 0.975 and 0.995, preferably between 0.98 and 0.

99.

3. Torque transmission system (1) according to any one of the preceding claims wherein the first set of satellite gears (1110) and the second set of satellite gears (1120) each comprise 4 or more satellite gears.

4. Torque transmission system (1) according to any one of the preceding claims wherein the first set of satellite gears (1110) and the second set of satellite gears (1120) each comprise exactly 5 satellite gears.

5. Torque transmission system (1) according to any one of the preceding claims wherein the peripheral teeth of the satellite gears (1110) of the first set of satellite gears each have the same number of teeth which is different from the number of teeth of the peripheral teeth of the satellite gears (1120) of the second set of satellite gears.

6. Torque transmission system (1) according to any one of the preceding claims wherein the first sun gear (111) has peripheral teeth comprising 37 teeth, the second sun gear (112) has peripheral teeth comprising 33 teeth, the planet gears (1110) of the first set of planet gears each have peripheral teeth comprising 21 teeth and the planet gears of the second set of planet gears (1120) each have peripheral teeth comprising 19 teeth.

7. A torque transmission system (1) according to any one of the preceding claims, wherein, in a plane perpendicular to the second axis of rotation (Y), the outer periphery of the planetary gear device (110) is inscribed in a circle of diameter DI and the outer periphery of the second electric machine (120), in particular the stator, is inscribed in a circle of diameter D2, the second electric machine (120) and the planetary gear device (110) are dimensioned so that 0.9 <D1 / D2<1,1

8. Torque transmission system (1) ) according to any one of the preceding claims wherein the satellite carrier (113) comprises: - a disc (115) mounted rotationally fixed to the rotor shaft (121) of the second electric machine (120); - rods (117) extending parallel to the second axis of rotation (Y) and around which are mounted respectively, in pairs and in an axially offset manner, a satellite pinion (1110) of the first set of satellite pinions and a satellite pinion (1120) of the second set of satellite pinions; - a cover (114), the first set of satellite pinions (1110) and the second set of satellite pinions (1120) being arranged axially between the disc (115) and the cover (114).

9. Torque transmission system (1) according to any one of the preceding claims wherein the transmission system comprises a first housing (19), the torque input element (21) of the differential (20) being a housing enclosing the gear set (25) of the differential (20), the housing (21) of the differential comprising a first sleeve (27) arranged around the second axis of rotation (Y), and the first housing (19) comprising a first opening (18) through which the second axis of rotation (Y) passes, the first sleeve (27) protruding from the first housing (19) along the second axis of rotation (Y) through the first opening (18).

10. Torque transmission system (1) according to the preceding claim in which the first solar element (1111) is mounted rotationally fixed to the input element (21) of the differential (20) by means of grooves formed both on the internal diameter of the first solar element (1111) and on the external diameter of the first sleeve (27).

11. Torque transmission system (1) according to the preceding claim in which a shoulder 271 is arranged at the end of the splines of the first sleeve located in the direction of the gear set 25 of the differential 20, the first solar 1111 being thus able to come into axial support against the sleeve 27 during the assembly of the planetary gear device with the propulsion assembly.

12. Torque transmission system (1) according to any one of claims 9 to 11, wherein the first housing (19) comprises a first part (191) having a housing in which the first electric machine, a second part (192) fixed to the first part (191) by closing the housing of the first part (191), the second part (192) enveloping a portion of the space occupied by the reduction device (30) and the differential (20) (with the exception of the first sleeve), a third part (193) fixed to the second part (192) and enveloping the rest of the space occupied by the reduction device (30) and the differential (20) (with the exception of the first sleeve).

13. Torque transmission system (1) according to any one of claims 9 to 13 in which the propulsion assembly comprises a second housing (109) covering the torque adaptation module (100), the second housing (109) comprising a bell (1091) in which the planetary gear device is disposed, the bell (1091) being axially open in the direction of the differential, the cover (114) of the satellite carrier (113) being disposed radially between the edge of the opening of the bell and a tubular portion (1920) of the first housing (19), in particular of its second part (192).

14. Torque transmission system (1) according to claim 13 in which a bearing (116) is arranged radially between the tubular portion (1920) of the first housing (19) and the cover (114) of the satellite carrier (113).

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