Torque vectoring device

Abstract

Disclosed is a torque vectoring device (1) for a transmission line of a vehicle, comprising a differential (5), an electric machine (2), a torque superposition unit (4) and a speed reduction gear (3), the speed reduction gear (3) being a cycloidal reduction gear or an elliptical reduction gear.

Description

Description Title of the invention: Torque vectoring device Technical field [1] The invention relates to the field of transmission systems for motor vehicles, particularly for hybrid or electric vehicles. The invention relates more specifically to a torque vectoring device intended to distribute torque to the wheels of a vehicle. Technological background [2] Document W02017072329 describes a torque adaptation device for a vehicle axle. This type of device aims to correct the dynamic behavior of the vehicle, in particular allowing the improvement of trajectory control in bends. The torque adaptation device is capable of providing a torque vectoring function via an electric motor controlling the torque difference between two output shafts of a differential. [3] However, such a device is not satisfactory because its compactness, cost and efficiency require improvements to meet the increased specifications of recent vehicle applications. [4] Furthermore, document W02012066035 describes a torque vectoring device where a single gear set composed of two planetary gears connected to a propulsion motor provides both a differential function, a torque vectoring function and a reduction function for the output speed of said propulsion motor. Since these three functions are performed by a single gear set, it is impossible to make the torque vectoring device simpler and more compact. Summary [5] In all that follows, ordinal numeral adjectives are used to differentiate features. They do not define the position of a feature. For Therefore, for example, a third characteristic of a product does not mean that the product has a first and / or a second characteristic. [6] An idea underlying the invention is a torque vectoring device that solves one or more technical problems of the prior art, for example the aforementioned problems. [7] The invention relates to a torque vectoring device for a transmission line of a vehicle, the torque vectoring device comprising: - a differential comprising a first input element receiving a main torque, the first input element being capable of kinematically driving in rotation a first lateral shaft and a second lateral shaft, via a first set of gears; - an electric machine capable of providing a secondary torque and comprising a first rotor shaft capable of rotating around a first axis of rotation; - a speed reducer comprising a second input element and a first output element, - a torque superposition unit comprising a second set of gears configured to cooperate kinematically in rotation with the differential in order to ensure the transmission of an additional torque to the first lateral shaft; in which the speed reducer comprises: - a fixed support comprising a first circular circumference on which a first toothing is arranged; - a rotating support comprising a second periphery on which a second set of teeth is arranged, the second set of teeth having a rotating radial eccentric movement causing at least one tooth of the second set of teeth to engage at least one tooth of the first set of teeth of the fixed support, the rotating support kinematically driving the first output element in rotation; - an eccentric exerting at least one radial support on the second toothing in order to generate the rotating radial eccentric movement of the second toothing, the eccentric being linked in rotation to the second input element; [8] For the purposes of this application: “axially” means “parallel to the first axis of rotation”; “radially” means “along an axis belonging to a plane orthogonal to the first axis of rotation and intersecting this first axis of rotation”; "angularly" or "circumferentially" means "around the first axis of rotation"; the terms "external" and "internal" are used to define the relative position of one component with respect to another, by reference to the axis of rotation for which they are concentric, a component close to said axis is thus qualified as internal as opposed to an external component located radially on the periphery; "rotationally linked" means "assembled so that they do not rotate relative to each other". In other words, it is a rotationally integral connection, possibly with very little play such as spline play; the term "rotor shaft" should be understood broadly as the output component linked to the rotor of a rotating machine. [9] According to an additional characteristic of the invention - the second input element of the speed reducer is rotationally connected to the first rotor shaft of the electric machine; and - the second set of gears of the torque superposition unit comprises a first input-output, a second input-output and a third input-output, the first input-output, the second input-output and the third input-output being configured to kinematically cooperate in rotation with the first output element of the speed reducer, the first input element of the differential and the first side shaft.

[0010] Thanks to the characteristics of this architecture, it is possible to ensure torque vectoring with a small number of components in a reduced space. The speed reducer according to the invention makes it possible to obtain high reduction ratios in a very compact space. As a comparative example, in an identical footprint, the speed reducer according to the invention allows a reduction ratio 2 to 4 times greater than that which would have been possible with a planetary gear set.

[0011] The secondary torque delivered by the electric machine is amplified by the gear reducer. The torque superposition unit can then amplify the torque delivered by the gear reducer to form an additional torque which is distributed to the first side shaft.

[0012] The first gear set of the differential is therefore separate from the second gear set of the torque superposition unit. Thus, the torque passing through the torque superposition unit according to the invention is only the additional torque coming out of the speed reducer. The main torque supplied by the traction machine does not pass through the torque superposition unit. Consequently, since the torque passing through the second gear set is low, the torque superposition unit according to the invention can be dimensioned so as to obtain a more compact structure.

[0013] According to an additional feature of the invention, the torque vectoring device may comprise an additional device. This additional device may be positioned, for example, between the electric machine and the speed reducer or between the speed reducer and the torque superposition unit. This additional device may in particular make it possible to amplify, divert, distribute or interrupt the torque within the torque vectoring device. This additional device may in particular be an additional speed reducer.

[0014] According to an additional characteristic of the invention, the torque vectoring device constitutes an independent module, in particular an independent pre-assembled module.

[0015] It should be understood here that the module is self-sufficient and does not need to interact with other components or additional devices to ensure the transmission of additional torque to the first side shaft. In other words, the torque vectoring device is operational, for example, for a test / trial, without it being necessary to place this module in its final environment. Another advantage is that this module can be manufactured in a factory and then be transported conveniently, before being assembled with other components, such as a traction machine. In addition, this module can be implemented on several different types of transmission lines in a simple way and without the need for major adaptation of the design.

[0016] According to an additional characteristic of the invention, the speed reducer is a cycloidal reducer type reducer.

[0017] According to an additional characteristic of the invention, the architecture of the cycloidal type speed reducer can be as follows: - the rotating support is in the form of a mobile disc which has an external profile describing a cycloidal or trochoidal curve to form the second toothing, and an internal profile of circular shape capable of cooperating, directly or via a plain bearing or via rolling elements, with the external contour of the eccentric; - the fixed support is in the form of an annular crown with an undulating internal contour forming the first toothing; - the first output element is in the form of a drive disc comprising drive shafts extending axially and arranged circumferentially, the drive shafts being intended to engage, directly or via plain bearings or via rolling elements, in corresponding openings provided in the rotating support.

[0018] According to an additional characteristic of the invention, the cycloidal type speed reducer may comprise two rotating supports arranged axially opposite each other. Correspondingly, the eccentric comprises two distinct external contours axially opposite each other and circumferentially spaced by an angle of 180 degrees, the first and second external contours of the eccentric each exerting radial support respectively on the first and second rotating supports.

[0019] According to an additional characteristic of the invention, the speed reducer is a reducer of the elliptical reducer type.

[0020] As is well known, elliptical type reducers can also be referred to as "strain wave reducers" or "harmonic reducers".

[0021] According to an additional characteristic of the invention, the architecture of the elliptical type speed reducer can be as follows: - the rotating support is in the form of a deformable disc comprising on its external periphery a flexible toothing to form the second toothing, the deformable disc being linked in rotation directly to the first output element; - the fixed support is in the form of an annular crown comprising internal teeth forming the first toothing; - the eccentric has an external circumference comprising two radially eccentric portions, for example an external circumference of elliptical shape, force-mounted in the flexible teeth of the deformable disc to exert two radial supports on the flexible teeth, directly or via a plain bearing or via rolling elements.

[0022] According to an additional characteristic of the invention, the reduction ratio of the speed reducer is between 10:1 and 200:1, preferably the reduction ratio of the speed reducer is between 20:1 and 50:1.

[0023] The reduction ratio is the ratio between the input rotational speed and the output rotational speed of a speed reducer.

[0024] According to an additional characteristic of the invention, the reduction ratio of the speed reducer is n / [Nn] where N is the number of teeth of the first toothing of the fixed support and n is the number of teeth of the second toothing of the rotating support.

[0025] Advantageously, this high reduction ratio value of the speed reducer can enable the torque vectoring device to use the electric machine in a rotational speed range where its efficiency is optimal, thus promoting the overall efficiency of the torque vectoring device.

[0026] According to an additional characteristic of the invention, the electric machine of the vectoring device has a maximum rotation speed of 3000 to 10000 rpm, preferably 3000 to 6000 rpm,

[0027] According to an additional characteristic of the invention, the first set of gears of the differential comprises cylindrical gears, in particular straight-toothed gears, in particular gears arranged in the form of a planetary gear set.

[0028] This type of differential is commonly referred to as a "flat differential". It has the advantages of significantly reducing weight and axial compactness compared to a differential of traditional design using bevel gears.

[0029] According to an additional feature of the invention, the second set of gears of the torque superposition unit comprises at least one planetary gear set.

[0030] According to an additional feature of the invention, the second set of gears of the torque superposition unit comprises a first planetary gear set and a second planetary gear set, the first planetary gear set comprising: - a first planetary pinion linked in rotation with the first output element of the speed reducer; - the first satellite pinions; - a first planet carrier linked in rotation with the first lateral shaft; the second planetary gear comprising: - a second fixed planetary pinion; - second satellite pinions; - a second planet carrier linked in rotation with the first input element of the differential; the first planet pinions and the second planet pinions cooperating kinematically in rotation with a planetary ring gear common to the first and second planetary gears.

[0031] Thanks to this architecture of the torque superposition unit, it is possible to manage the torque transmitted to the two side shafts in a simple and compact way. If the electric machine does not generate secondary torque, the torque vectoring device operates like a conventional differential since there is no relative speed between the two planetary gears of the torque superposition unit. If the electric machine generates secondary torque, the torque superposition unit will ensure the addition and distribution of the torques supplied to the first side shaft.

[0032] According to an additional characteristic of the invention, the first planetary gears of the first planetary gear set and the second planetary gears of the second planetary gear set have the same number of teeth and / or the same pitch diameter.

[0033] According to an additional feature of the invention, the second set of gears of the torque superposition unit comprises a first planetary gear set and a second planetary gear set, the first planetary gear set comprising: - a first planetary pinion linked in rotation with the first output element of the speed reducer; - the first satellite pinions; - a first planet carrier linked in rotation with the first input element of the differential; the second planetary gear comprising: - a second fixed planetary pinion; - second satellite pinions; - a second planet carrier linked in rotation with the first lateral shaft; the first planet pinions and the second planet pinions cooperating kinematically in rotation with a planetary ring gear common to the first and second planetary gears.

[0034] According to an additional feature of the invention, a disconnecting clutch is further provided for transmitting or interrupting the transmission of torque within the torque vectoring device.

[0035] The disconnect clutch allows the disconnection of part of the torque vectoring device during phases of vehicle operation when it is not in use. This improves the overall efficiency of the transmission line by eliminating mechanical losses associated with the rotation of the various unused components.

[0036] The disconnecting clutch is controlled by an actuator, the actuator being for example of the electromechanical or electromagnetic or hydraulic type;

[0037] According to a further feature of the invention, a disconnecting clutch is provided for transmitting or interrupting the transmission of torque between the speed reducer and the torque superposition unit.

[0038] In this case, the rotational drive of the electric machine and the speed reducer is prevented by opening the disconnecting clutch.

[0039] According to a further feature of the invention, a disconnecting clutch is provided for transmitting or interrupting the transmission of torque between the second fixed planetary gear and a frame on which said second fixed planetary gear is fixed.

[0040] In this case, the rotational drive of the electric machine, the speed reducer and the torque superposition unit are avoided by opening the disconnecting clutch. This embodiment has the advantage of easier installation of the disconnecting clutch because the two components to be coupled / uncoupled are fixed.

[0041] According to an additional feature of the invention, the disconnection clutch is a dog clutch. To facilitate the synchronization of speeds during the connection / disconnection phases, an acceleration / deceleration of the rotor shaft of the electrical machine can be applied.

[0042] According to an additional feature of the invention, the disconnecting clutch is a friction clutch, the friction clutch comprising one or more friction discs.

[0043] According to an additional feature of the invention, the speed reducer, the torque superposition unit, the first side shaft and the differential are coaxial with the first axis of rotation of the first rotor shaft of the electric machine.

[0044] Thanks to this feature, the torque vectoring device can be very compact radially, thus allowing its easy integration into the available space allocated to the vehicle's transmission line.

[0045] The invention also relates to a powertrain comprising the torque vectoring device, the powertrain according to the invention further comprising: - a traction motor comprising a second rotor shaft capable of rotating around a second axis of rotation; - a third set of gears cooperating kinematically in rotation with on the one hand the second rotor shaft of the traction motor and on the other hand with the first input element of the differential to form one or more speed reduction ratios.

[0046] Thanks to this feature, the traction motor can axially overlap the torque vectoring device, thus making the entire powertrain axially compact.

[0047] The third gear set is therefore separate from the first gear set of the differential and the second gear set of the torque superposition unit. Thus, the torque passing through the third gear set according to the invention is the main torque provided by the traction machine. The additional torque coming out of the torque superposition unit does not pass through the third gear set. Consequently, since the torque passing through the third gear set according to the invention is lower, the third gear set can be dimensioned so as to obtain a more compact structure.

[0048] The torque vectoring device according to the invention advantageously remains an independent module, and in particular independent of the traction motor and the third set of gears with which it is associated.

[0049] The traction motor can be, for example, an electric motor capable of providing the power necessary to drive the vehicle.

[0050] According to an additional feature of the invention, the third gear set may comprise several gear trains so as to achieve the high reduction ratio values ​​necessary for the drive and driving pleasure of the vehicle. The gear trains may be, for example, parallel-axis cylindrical gear trains or planetary gear trains.

[0051] According to an additional feature of the invention, the third set of gears comprises gears and actuating means configured to allow one or more gear ratio changes.

[0052] According to an additional characteristic of the invention, the first axis of rotation of the electric machine is coaxial with the second axis of rotation of the traction motor.

[0053] Thanks to this feature, the powertrain is made radially compact.

[0054] The invention may have one or other of the characteristics described below combined with each other or taken independently of each other: - the secondary torque supplied by the electrical machine may be of positive sign in a first direction of rotation of the rotor shaft, or negative in a second direction of rotation of the rotor shaft; - the torque vectoring device can be installed on a front and / or rear axle of the vehicle.

[0055] Other characteristics and advantages of the invention are highlighted by the following description of non-limiting examples of embodiments of the different aspects of the invention. Brief description of the figures

[0056] Figure 1 illustrates a schematic sectional view of a powertrain comprising a torque vectoring device according to the invention.

[0057] Figure 2 is a sectional view of the torque vectoring device according to a first embodiment.

[0058] Figure 3 is an exploded perspective view of the torque vectoring device according to a first embodiment.

[0059] Figure 4 is an exploded perspective view of the speed reducer of the torque vectoring device according to a first embodiment.

[0060] Figure 5 is an exploded perspective view of the speed reducer of the torque vectoring device according to a second embodiment.

[0061] Figure 6 is a front view of the speed reducer of the torque vectoring device according to a second embodiment.

[0062] Figure 7 is a sectional view of the torque superposition unit of the torque vectoring device according to a first embodiment.

[0063] Figure 8 is a schematic sectional view of the vectoring device according to a third embodiment.

[0064] Figure 9 is a schematic sectional view of the vectoring device according to a fourth embodiment. Description of the embodiments

[0065] For clarity, functionally identical or similar elements are identified by identical reference signs throughout the figures.

[0066] The descriptive elements already explained are not systematically repeated; only the particularities of the different embodiments and examples are detailed.

[0067] Figure 1 shows a powertrain 10 according to one embodiment of the invention. The powertrain 10 may be intended in particular for a motor vehicle with a hybrid or fully electric engine. The powertrain 10 comprises a casing 9 containing a traction machine 11 and a torque vectoring device 1. The structure of the casing 9 may be a single piece or composed of several sub-parts.

[0068] In Figures 2 and 3 is illustrated the torque vectoring device 1 which comprises: - a differential 5 comprising a first input element 51 receiving a main torque, the first input element 51 being capable of kinematically driving in rotation a first lateral shaft 6 and a second lateral shaft 7, via a first set of gears 52; - an electric machine 2 capable of providing a secondary torque and comprising a first rotor shaft 21 capable of rotating around a first axis of rotation (XI); - a speed reducer 3 comprising a second input element 31 and a first output element 32, the second input element 31 being linked in rotation with the first rotor shaft 21 of the electrical machine 2; - a torque superposition unit 4 comprising a second set of gears 40 comprising a first input-output 41, a second input-output 42 and a third input-output 43, the first input-output 41, the second input-output 42 and the third input-output 43 being configured to cooperate kinematically in rotation with the first output element 32 of the speed reducer 3, the first input element 51 of the differential 5 and the first lateral shaft 6 in order to provide torque amplification and / or torque transmission to said first lateral shaft 6.

[0069] The first lateral shaft 6 and the second lateral shaft 7 driven by the differential 5 can rotate at different speeds and are each connected, directly or indirectly, to a wheel of a vehicle.

[0070] In the embodiment shown in Figure 1, the first gear set 52 of the differential 5 comprises bevel gears.

[0071] In the embodiment shown in Figures 2 and 3, the first gear set 52 of the differential 5 comprises cylindrical gears, more particularly straight-toothed gears arranged in the form of a planetary gear set.

[0072] In the embodiment illustrated by Figures 1 and 2, the speed reducer 3, the torque superposition unit 4, the first side shaft 6 and the differential 5 are coaxial with the first axis of rotation XI of the first rotor shaft 21 of the electric machine 2.

[0073] Alternatively, in another embodiment of the invention not shown, the torque superposition unit 4, the differential 5 and the first lateral shaft 6 may be coaxial with a separate axis and parallel to the first axis of rotation XI.

[0074] The electrical machine 2 comprises a stator 22 secured to the casing 9, and a rotor 23 comprising at its output the first rotor shaft 21. The first rotor shaft 21 comprises an open central part crossed by the first lateral shaft 6.

[0075] The second input element 31 of the speed reducer 3 is rotationally connected to the first rotor shaft 21 of the electric machine 2 by splines.

[0076] Figures 2 and 4 illustrate a cycloidal reducer type speed reducer 3. The speed reducer 3 comprises: - a fixed support 33 comprising a first circular circumference on which a first toothing 330 is arranged; - a rotating support 35 comprising a second periphery on which a second toothing 350 is arranged, the second toothing 350 having a rotating radial eccentric movement causing the meshing of at least one tooth of the second toothing 350 on at least one tooth of the first toothing 330 of the fixed support 33, the rotating support 35 kinematically driving the first output element 32 in rotation; - an eccentric 37 exerting at least one radial support on the second toothing 350 in order to generate the rotating radial eccentric movement of the second toothing 350, the eccentric 37 being linked in rotation to the second input element 31.

[0077] On the cycloidal reducer of Figure 4, the rotating support 35 is in the form of two axially facing mobile discs 35, 35' which each comprise an external profile describing a cycloidal curve to form the second toothing 350, 350', and an internal profile of circular shape cooperating via a bearing 351, 351' with an external contour of the eccentric 37. The eccentric 37 comprises two distinct external contours 370, 370' axially facing each other and spaced circumferentially by an angle of 180 degrees, the first and second external contours 370, 370' each exerting radial support respectively on the first and second movable discs 35, 35'. The fixed support 33 is in the form of an annular crown comprising an undulating internal contour forming the first toothing 330. The fixed support 33 is integral with the casing 9. The first output element 32 is in the form of a drive disc which comprises drive axes 320 extending axially and arranged circumferentially, the drive axes 320 being intended to engage in corresponding openings 352, 352' arranged in the two movable discs 35, 35'.An operating clearance is provided radially and circumferentially between the drive shafts 320 and the corresponding openings 352, 352', so that the radial movement of the two movable discs 35, 35' is not transmitted to the first output element 32.

[0078] In this example in Figure 4, the number of teeth in the first set of teeth is 34 and the number of teeth in the second set of teeth is 33. The reduction ratio of the speed reducer is therefore in this case 33 / (34-33] = 33:1.

[0079] The speed reducer illustrated in Figures 5 and 6 is an elliptical type reducer. The rotating support 35 is in the form of a deformable disc having on its external periphery a flexible toothing to form the second toothing 350, the deformable disc being connected in rotation directly to the first output element 32, for example via fixing screws. The fixed support 33 is in the form of an annular crown having an internal toothing forming the first toothing 330. The fixed support 33 is integral with the casing 9. The eccentric 37 has an external periphery 370 of elliptical shape, force-mounted in the flexible toothing of the deformable disc to exert two radial supports on the flexible toothing, via a bearing 351.

[0080] The torque superposition unit 4 illustrated in Figure 2 and 7 comprises a first planetary gear set 44 and a second planetary gear set 45. The first planetary gear set comprises a first planetary pinion 440 rotatably connected via splines with the first output element 32 of the speed reducer 3, first planet gears 441 and a first planet carrier 442 rotatably connected via splines to the first lateral shaft 6. The second planetary gear set 45 comprises a second planet gear 450 fixed to the casing 9, second planet gears 451 and a second planet carrier 452 rotatably connected via splines to the first input element 51 of the differential 5. The first planet gears 441 and the second planet gears 451 cooperate kinematically in rotation with a common planetary ring gear 443. In this exemplary embodiment, the first planet gears 441 and the second planet gears 451 are identical. In this exemplary embodiment, the first planet gear 440 and the second planet gear 450 have the same pitch diameters and the same number of teeth.

[0081] In the embodiment schematically illustrated in Figure 8, a disconnecting clutch 8 is provided for transmitting or interrupting the transmission of torque between the speed reducer 3 and the torque superposition unit 4. More particularly, the disconnecting clutch 8 may be provided between the first output element 32 and the first planetary gear 440.

[0082] In the embodiment schematically illustrated in Figure 9, a disconnecting clutch 8 is provided to transmit or interrupt the transmission of torque between the second planetary gear 450 and the housing 9.

[0083] As illustrated in Figure 1, the powertrain 10 further comprises the traction motor 11 comprising a second rotor shaft 110 rotating about a second axis of rotation X2 and a third set of gears 12 cooperating kinematically in rotation with on the one hand the second rotor shaft 110 of the traction motor 11 and on the other hand with the first input element 51 of the differential 5 to form one or more speed reduction ratios.

[0084] In this non-limiting example, the third set of gears 12 comprises a first cylindrical gear train 120, coaxial with the second axis of rotation X2, and cooperating kinematically in rotation with a second cylindrical gear train 121, coaxial with a third axis of rotation X3 parallel to the second axis of rotation X2, to form a first reduction ratio. The second cylindrical gear train 121 cooperates kinematically in rotation with a toothed wheel 122 secured to the first input element 51 of the differential 5 to form a second reduction ratio.

[0085] It is emphasized that all features, as they emerge for a person skilled in the art from this description, the drawings and the attached claims, even if they have been specifically described only in relation to other specific features, both individually and in any combinations, may be combined with other features or groups of features disclosed herein, provided that this has not been expressly excluded or that technical circumstances make such combinations impossible or meaningless.

[0086] The use of the verb “comporter”, “comprendre” and its conjugated forms does not exclude the presence of other elements or other steps than those stated in a claim.

[0087] In the claims, any reference sign in parentheses cannot be interpreted as a limitation of the claim.

Claims

Claims 1. Torque vectoring device (1) for a transmission line of a vehicle, the torque vectoring device comprising: - a differential (5) comprising a first input element (51) receiving a main torque, the first input element being capable of kinematically driving in rotation a first lateral shaft (6) and a second lateral shaft (7), via a first set of gears (52); - an electric machine (2) capable of providing a secondary torque and comprising a first rotor shaft (21) capable of rotating around a first axis of rotation (XI); - a speed reducer (3) comprising a second input element (31) and a first output element (32); - a torque superposition unit (4) comprising a second set of gears (40) configured to cooperate kinematically in rotation with the differential in order to ensure the transmission of an additional torque to the first lateral shaft; characterized in that the speed reducer comprises: - a fixed support (33) comprising a first circular circumference on which a first toothing (330) is arranged; - a rotating support (35) comprising a second periphery on which a second toothing (350) is arranged, the second toothing having a rotating radial eccentric movement causing the meshing of at least one tooth of the second toothing on at least one tooth of the first toothing of the fixed support, the rotating support kinematically driving the first output element in rotation; and - an eccentric (37) exerting at least one radial support on the second toothing in order to generate the rotating radial eccentric movement of the second toothing, the eccentric being linked in rotation to the second input element.

2. Torque vectoring device (1) according to claim 1 wherein: - the second input element (31) of the speed reducer (3) is rotationally connected to the first rotor shaft (21) of the electric machine (2); and - the second set of gears (40) of the torque superposition unit (4) comprises a first input-output (41), a second input-output (42) and a third input-output (43), the first input-output, the second input-output and the third input-output being configured to cooperate kinematically in rotation with the first output element (32) of the speed reducer, the first input element (51) of the differential (5) and the first side shaft (6).

3. Torque vectoring device (1) according to claim 1 or 2, said torque vectoring device (1) constituting an independent module, in particular an independent pre-assembled module.

4. Torque vectoring device (1) according to any one of claims 1 to 3, the speed reducer (3) being a cycloidal reducer type reducer.

5. Torque vectoring device (1) according to any one of claims 1 to 3, the speed reducer (3) being a reducer of the elliptical reducer type.

6. Torque vectoring device (1) according to any one of the preceding claims wherein the reduction ratio of the speed reducer (3) is between 10:1 and 200:1, preferably the reduction ratio of the speed reducer (3) is between 20:1 and 50:

1.

7. Torque vectoring device (1) according to any one of the preceding claims wherein the first set of gears (52) of the differential (5) comprises cylindrical gears, in particular straight-toothed gears, in particular gears arranged in the form of a planetary gear train.

8. Torque vectoring device (1) according to any one of the preceding claims wherein the second set of gears (40) of the torque superposition unit (4) comprises at least one planetary gear set.

9. Torque vectoring device (1) according to claim 8 wherein the second set of gears (40) of the torque superposition unit (4) comprises a first planetary gear set (44) and a second planetary gear set (45), the first planetary gear set comprising: - a first planetary pinion (440) rotatably connected to the first output element (32) of the speed reducer (3); - first satellite pinions (441); - a first planet carrier (442) linked in rotation with the first lateral shaft (6); the second planetary gear comprising: - a second fixed planetary pinion (450); - second satellite pinions (451); - a second planet carrier (452) linked in rotation with the first input element (51) of the differential (5); the first planet pinions and the second planet pinions cooperating kinematically in rotation with a planetary crown (443) common to the first and second planetary gears.

10. A torque vectoring device (1) according to any preceding claim wherein a disconnecting clutch (8) is further provided for transmitting or interrupting the transmission of torque within the torque vectoring device.

11. Torque vectoring device (1) according to claim 10 wherein the disconnecting clutch (8) is provided to transmit or interrupt the transmission of torque between the speed reducer (3) and the torque superposition unit (4).

12. Torque vectoring device (1) according to claim 10 in combination with claim 9 wherein the disconnecting clutch (8) is provided to transmit or interrupt the transmission of torque between the second fixed planetary gear (450) and a frame (9) on which said second fixed planetary gear is fixed.

13. Torque vectoring device (1) according to any one of the preceding claims wherein the speed reducer (3), the torque superposition unit (4), the first side shaft (6) and the differential (5) are coaxial with the first axis of rotation (XI) of the first rotor shaft (21) of the electric machine (2).

14. Powertrain (10) comprising a torque vectoring device (1) according to any one of the preceding claims and further comprising: - a traction motor (11) comprising a second rotor shaft (110) capable of rotating about a second axis of rotation (X2); - a third set of gears (12) cooperating kinematically in rotation with on the one hand the second rotor shaft of the traction motor and on the other hand with the first input element (51) of the differential (5) to form one or more speed reduction ratios.

15. Powertrain (10) according to claim 14 wherein the first axis of rotation (XI) of the first rotor shaft (21) of the electric machine (2) is parallel to the second axis of rotation (X2) of the second rotor shaft (110) of the traction motor (11).

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