Power unit for a motor vehicle

Abstract

The invention relates to a power unit (1) for a motor vehicle, having a traction electric machine (2), a torque converter (3), a variable-speed transmission (4) and a differential transmission (5), wherein the traction electric machine (2) is coupled in a given sequence via the torque converter (3) and the variable-speed transmission (4) in a drive-technical manner to the differential transmission (5). It is provided here that the traction electric machine (2) is coupled in a drive-technical manner to the torque converter (3) via a spur gear transmission (20) or without a transmission.

Description

Technical Field

[0001] This invention relates to a power unit for a motor vehicle, comprising a traction motor, a torque converter, a transmission mechanism, and a differential transmission mechanism, wherein the traction motor is driven technically connected to the differential transmission mechanism via the torque converter and the transmission mechanism in a given order, wherein the traction motor is driven technically connected to the torque converter via a spur gear transmission mechanism or without a transmission mechanism, wherein the transmission mechanism is designed as a planetary gear transmission mechanism, a single-stage or multi-stage spur gear transmission mechanism, or a belt drive mechanism, the planetary gear transmission mechanism having a sun gear, a ring gear, and at least one planetary gear rotatably supported on a planetary gear carrier and engaging the sun gear and the ring gear, wherein the sun gear is driven technically arranged on the torque converter side, the planetary gear carrier is driven technically arranged on the differential side, and the ring gear is fixed. Background Technology

[0002] For example, document DE 10 2015 215 965 A1 is known from the prior art. This document describes a power unit for a motor vehicle having at least one traction motor for driving the motor vehicle and a hydraulic torque converter that can be driven by the traction motor, wherein a transmission mechanism that can be driven by the traction motor is provided, through which the torque converter can be driven.

[0003] Patent document DE 10 2019 103 242 A1 relates to an electric drive device for a motor vehicle, comprising a drive motor with a rotor and a stator, and a transmission mechanism and a differential arranged coaxially with the drive motor. The transmission mechanism has planetary gears, wherein the differential is operatively connected to a first driven shaft and a second driven shaft, wherein a torque converter with a bushing is arranged between the drive motor and the transmission mechanism, and wherein one of the two driven shafts is axially guided through the bushing and the drive motor.

[0004] The prior art also includes patent documents US 11 535 094 B2, DE 10 2019 103711 A1, JP2011 231857 A, US 2020 / 325972 A1, DE 10 2018 127701 A1 and DE102020 114063 A1. Summary of the Invention

[0005] The object of this invention is to provide a power unit for motor vehicles that has advantages over known power units, particularly in that it can operate flexibly and can be implemented in a small structural space.

[0006] According to the present invention, this is achieved by a power unit for a motor vehicle. Here, the gear ring is fixed by a gear ring shaft that overlaps with the traction motor in an axial direction based on the rotation axis of the traction motor.

[0007] The power unit is used to drive the motor vehicle, that is, to provide the driving torque intended to drive the motor vehicle. To provide the driving torque, the power unit has a traction motor, and the driving torque is provided entirely by means of the traction motor, at least temporarily or continuously. The motor vehicle is preferably an electric vehicle or an electrically driven motor, and preferably does not have an internal combustion engine.

[0008] In addition to the traction motor, the power unit also includes a hydraulic torque converter, a transmission mechanism, and a differential transmission mechanism. The hydraulic torque converter is technically positioned between the traction motor and the transmission mechanism, thus the transmission mechanism is technically connected to the traction motor via the torque converter. The differential transmission mechanism is connected to the torque converter via the transmission mechanism; correspondingly, the transmission mechanism is technically located between the torque converter and the differential transmission mechanism. Therefore, in general, the traction motor is technically connected to the differential transmission mechanism via the torque converter and the transmission mechanism, wherein the torque converter and the transmission mechanism are arranged technically in a given order.

[0009] A transmission mechanism is understood as a transmission mechanism that generates a transmission ratio that is not equal to 1. In this sense, there is always a speed ratio that is not equal to 1 between the output shaft and the input shaft of the transmission mechanism when the speed is not zero.

[0010] Preferably, the differential transmission mechanism is an axle differential transmission mechanism. This means that exactly one axle of the vehicle is connected to the power unit via the differential transmission mechanism in terms of drive technology. The axle has multiple sub-axles, which are interconnected via the differential transmission mechanism and individually connected to the power unit in terms of drive technology. Alternatively, the differential transmission mechanism can of course be a central differential transmission mechanism. In this case, multiple axles are connected to the power unit or traction motor in terms of drive technology via the differential transmission mechanism. For example, each of the multiple axles is connected to the differential transmission mechanism of the power unit via an axle differential transmission mechanism, thus there are a total of multiple differential transmission mechanisms.

[0011] In some cases, motor vehicles require very high or even extremely high driving torque, especially off-road vehicles. It's possible to design traction motors accordingly and set corresponding rated torques. However, this results in large traction motors and consequently, a large structural space requirement for the power unit. The same applies to using multiple traction motors that are technically interconnected, where multiple motors drive the same axle of the vehicle. Alternatively, a shiftable transmission or gearbox can be used to meet the high torque requirements. Regardless, this leads to a high complexity of the power unit and a large structural space requirement.

[0012] For this reason, the power unit has a torque converter. The torque converter at least temporarily increases torque, thereby providing a greater drive torque at the vehicle's axles than could be achieved at the axle's current speed or when the axles are connected to the power unit without a torque converter. Therefore, the torque converter provides, at least temporarily, a very large drive torque, and enables particularly responsive driving at low speeds. This is especially important, for example, when starting off-road and traversing obstacles. In principle, the axle speed can be adjusted more responsively. Furthermore, overload decoupling is achieved, or at least possible, between the traction motor and the axles.

[0013] For example, it is known that the traction motor is connected to the torque converter via a planetary gear transmission mechanism. However, this results in a relatively large structural space, especially since the traction motor must always be mounted coaxially with this planetary gear transmission mechanism, and there are no other options for the arrangement of the traction motor. For this reason, according to the present invention, the traction motor should be connected to the torque converter via a spur gear transmission mechanism or without a transmission mechanism. The key feature of the spur gear transmission mechanism is that the gears are on parallel shafts, that is, the gears have rotational axes spaced parallel to each other. Thus, it differs from the planetary gear transmission mechanism in which the sun gear, planet carrier, and ring gear are arranged coaxially with each other.

[0014] Alternatively, the traction motor is connected to the torque converter without a transmission mechanism, i.e., without an intermediate connecting transmission mechanism. This means that the drive shaft of the traction motor is connected to the input shaft of the torque converter in such a way that it always maintains the same rotational speed. On the one hand, the described power unit design enables the aforementioned flexible operation; on the other hand, its construction is extremely compact and it offers great flexibility in the arrangement of the traction motor.

[0015] This invention specifies that the transmission mechanism is designed as a planetary gear transmission mechanism. In other words, the transmission mechanism is a planetary gear transmission mechanism. The planetary gear transmission mechanism has a sun gear, a ring gear, and a planetary gear carrier, wherein at least one planetary gear is rotatably supported on the planetary gear carrier. At least one planetary gear engages not only with the sun gear but also with the ring gear, i.e., meshes with them. Preferably, multiple planetary gears are rotatably supported on the planetary gear carrier, wherein each of the planetary gears meshes not only with the sun gear but also with the ring gear. Particularly high transmission ratios can be achieved through the planetary gear transmission mechanism.

[0016] Alternatively, the transmission mechanism is designed as a single-stage or multi-stage spur gear transmission. This means that the transmission mechanism has two gears in the first variant and at least three gears in the second variant, wherein the input gear is technically connected to the output gear only via at least one intermediate gear. If multiple intermediate gears exist, these intermediate gears are connected in series in the drive mechanism. In another design, the transmission mechanism is a belt drive mechanism, in which drive torque is transmitted when a traction device is used. Corresponding to the design of the transmission mechanism, either the arrangement of the power unit is flexible and space-saving, or a relatively high gear ratio is available.

[0017] An improved embodiment of the present invention specifies that the torque converter has a pump impeller located on the traction motor side in terms of drive technology, a turbine located on the differential transmission side in terms of drive technology, and a guide wheel, wherein the guide wheel is arranged on a guide wheel shaft. This design of the torque converter is known in principle. The pump impeller is connected to the traction motor in terms of drive technology, either via a spur gear transmission mechanism or without a transmission mechanism. Conversely, the turbine is connected to the differential transmission mechanism in terms of drive technology and is connected to the traction motor only via the pump impeller.

[0018] The pump impeller pumps fluid toward the turbine, thereby driving the turbine. The pump impeller and turbine are fluidically or hydrodynamically connected to each other. Fluidically, a guide wheel is arranged between the pump impeller and the vortex, guiding the fluid. The guide wheel is arranged on a guide wheel shaft, for example, rigidly connected to the guide wheel shaft.

[0019] It can be specified that the guide wheel can rotate in one direction of rotation by means of a free wheel, but is fixed in the opposite direction of rotation. Accordingly, the torque converter is implemented as a Trilok torque converter / triple-locking torque converter. For example, the free wheel is located between the guide wheel and the guide wheel shaft, wherein the guide wheel shaft is arranged rigidly. However, it can also be specified that the guide wheel is rigidly connected to the guide wheel shaft, and the guide wheel shaft is supported in a manner that allows it to rotate in only one direction of rotation by means of the free wheel. This design of the torque converter can achieve a particularly significant increase in torque.

[0020] An improved embodiment of the invention specifies that the guide wheel shaft is received by an input shaft designed as a hollow shaft, or the guide wheel shaft is designed as a hollow shaft and received by an output shaft or differential transmission output shaft located technically between the torque converter and the transmission mechanism. In the first case, the guide wheel shaft is arranged coaxially with the input shaft; in the latter case, the guide wheel shaft is arranged coaxially with the output shaft or differential transmission output shaft. This enables a compact design of the power unit.

[0021] One improvement of the invention specifies that the traction motor is arranged coaxially with or eccentrically relative to the output shaft. A coaxial arrangement of the traction motor is particularly advantageous when the traction motor is connected to the torque converter without a transmission mechanism. An eccentric arrangement is achieved using a spur gear transmission mechanism. This, in turn, contributes to a particularly compact power unit.

[0022] An improved embodiment of the invention specifies that a lock-up clutch is arranged between the traction motor and the torque converter, or on the side of the torque converter away from the traction motor, viewed in the axial direction based on the rotation axis of the traction motor. The rotation axis of the traction motor is understood to be the rotation axis of the driven shaft / output shaft or the shaft of the traction motor, which is connected to the torque converter via a spur gear transmission mechanism or without a transmission mechanism. The described option for arranging the lock-up clutch further ensures space-saving design of the power unit.

[0023] An improved embodiment of the present invention specifies that, viewed in the axial direction based on the rotation axis of the traction motor, the turbine is arranged on the side of the pump impeller facing the traction motor, or, viewed in the axial direction based on the rotation axis of the traction motor, the pump impeller is arranged on the side of the turbine facing the traction motor. These different arrangements of the turbine or pump impeller further contribute to a compact design of the power unit, thereby achieving the minimum structural space requirements.

[0024] This invention specifies a planetary gear transmission mechanism comprising a sun gear, a ring gear, and at least one planetary gear rotatably supported on a planetary gear carrier and engaging with the sun gear and ring gear. The sun gear is technically located on the torque converter side, the planetary gear carrier is technically located on the differential transmission side, and the ring gear is fixed. This should be understood as the sun gear being technically connected to the torque converter, and the planetary gear carrier being connected to the torque converter only via the sun gear. Conversely, the planetary gear carrier is connected to the differential transmission, and the sun gear is connected to the differential transmission only via the planetary gear carrier. The ring gear is arranged in a fixed position, for example, being fastened to the housing of the transmission mechanism or designed as a single piece therewith. This achieves a compact design of the power unit.

[0025] This invention specifies that the gear ring is fixed via a gear ring shaft arranged to overlap with the traction motor in an axial direction based on the rotation axis of the traction motor. The gear ring is fixed by means of the gear ring shaft, which is rigidly connected to the gear ring. The gear ring shaft extends from the gear ring in an axial direction based on the rotation axis of the traction motor to such a distance that it overlaps with, or even completely spans or passes through, the traction motor. This achieves reliable fixing of the gear ring.

[0026] An improved embodiment of the present invention specifies that the gear ring shaft is arranged coaxially with the output shaft and / or guide wheel shaft of the differential transmission mechanism. This coaxial arrangement enables a particularly compact power unit implementation scheme.

[0027] The features and combinations thereof described in the specification, especially those described and / or shown in the accompanying drawings, may be used not only in the given combinations, but also in other combinations or individually, without departing from the scope defined by the claims. Therefore, embodiments not expressly shown or explained in the specification and / or drawings but which can be derived from or inferred from the explained embodiments are also considered to be included within the scope of the claims. Attached Figure Description

[0028] The invention is explained below with reference to the initial example shown in the accompanying drawings. Wherein:

[0029] Figure 1 A schematic diagram of a power unit for a motor vehicle, representing a first embodiment, is shown, but it is not within the scope of protection of claim 1.

[0030] Figure 2 A schematic diagram of the power unit of the second embodiment is shown, which is not within the scope of protection of claim 1.

[0031] Figure 3 A schematic diagram of a third embodiment of the power unit is shown, which is not within the scope of protection of claim 1.

[0032] Figure 4 A schematic diagram of the power unit of the fourth embodiment is shown, which is not within the scope of protection of claim 1.

[0033] Figure 5 The power unit of the fifth embodiment is illustrated in the schematic diagram, which is not within the protection scope of claim 1, and

[0034] Figure 6 An embodiment of the power unit is illustrated in the schematic diagram, which is within the protection scope of claim 1. Detailed Implementation

[0035] Figure 1 A schematic diagram of a power unit 1 for a motor vehicle, representing a first embodiment, is shown. The power unit 1 includes a traction motor 2, a torque converter 3, a transmission mechanism 4, and a differential transmission mechanism 5. The traction motor 2 has a drive shaft 6, which is technically connected to the torque converter 3; in the embodiment shown here, it is connected to the torque converter 3 without a transmission mechanism, i.e., without a transmission mechanism. The drive shaft 6 is connected to a pump impeller 7, preferably rigidly and permanently. In addition to the pump impeller 7, the torque converter 3 also includes a vortex impeller 8 and a guide wheel 9. The guide wheel 9 is technically arranged between the pump impeller 7 and the turbine 8 and is rotatably supported on a guide wheel shaft 11 via a freewheel 10. The guide wheel shaft 11 is fixedly fastened, for example, to the housing 12 of the power unit 1, which is only indicated here.

[0036] Furthermore, the torque converter 3 has a lock-up clutch 13, by means of which the pump wheel 7 and the turbine 8 can be mechanically connected. Therefore, in the first position of the lock-up clutch 13, the pump wheel 7 and the turbine 8 are technically disengaged from each other; conversely, in the second position, the pump wheel and the turbine are mechanically connected to each other, preferably rigidly or at least substantially rigidly connected, i.e., mechanically connected without substantial clutch slippage. The connection of the drive shaft 6 to the pump wheel 7 is achieved via the input shaft 14 of the torque converter 3.

[0037] The turbine 8 is connected to the transmission mechanism 4 via an output shaft 15. In the embodiment shown here, the transmission mechanism is designed as a multi-stage spur gear transmission. The output shaft 15 is connected to the differential transmission mechanism 5 via the transmission mechanism 4, specifically to the input gear 16 of the differential transmission mechanism 5. The transmission mechanism 4 is technically connected to the axle 17 of the vehicle via the differential transmission mechanism 5, and the axle has two branch shafts 18 and 19. Branch shafts 18 and 19 can also be referred to as the output shafts of the differential transmission mechanism.

[0038] As can be seen, the guide wheel shaft 11 is designed as a hollow shaft and houses the output shaft 15 therein. Furthermore, the traction motor 2 is arranged coaxially with the output shaft 15 because it is connected to the torque converter 3 without a transmission mechanism. The lock-up clutch 13 is arranged axially between the traction motor 2 and the torque converter 3 relative to the rotation axis of the traction motor 2 or the drive shaft 6, that is, on the side of the torque converter 3 away from the transmission mechanism 4. Again, looking in the axial direction, the turbine 8 is located on the side of the pump wheel 7 facing the traction motor 2. Thus, a compact design of the power unit 1 is achieved overall. Furthermore, as an alternative to the design shown here, the transmission mechanism 4 can also be implemented as a belt drive mechanism.

[0039] Figure 2A second embodiment of the power unit 1 is illustrated schematically. For the names of individual components and basic design schemes, refer to the description of the first embodiment; only the differences are explained below. The difference lies in that the traction motor 2 is technically connected to the torque converter 3 or the pump wheel 7 via a spur gear transmission mechanism 20. This achieves an eccentric arrangement of the traction motor 2 relative to the output shaft 15.

[0040] The input shaft 14 or pump wheel 7 is connected to the lock-up clutch 13 via a connecting shaft 21. The connecting shaft 21 bridging the turbine 8 in the axial direction, so that the turbine 8 is located between or received between the pump wheel 7 on one side and the lock-up clutch 13 on the other side. Here, the transmission mechanism 4 is a single-stage spur gear transmission mechanism. The guide shaft 11 is arranged coaxially with the output shaft 15 and is partially received by the input shaft 14, which is designed as a hollow shaft. The guide shaft 11 extends axially from the guide wheel 9 or free wheel 10 toward the traction motor 2, and in particular, the guide shaft is connected to the housing 12 on the side of the spur gear transmission mechanism 20 away from the guide wheel 9. The lock-up clutch 13 is arranged axially on the side of the torque converter 3 away from the traction motor 2. In the axial direction, the turbine 8 is located on the side of the pump wheel 7 away from the traction motor 2.

[0041] As an alternative to the diagram shown, the traction motor 2 can also be arranged on the opposite side, i.e., the spur gear transmission mechanism 20 is connected to the pump wheel 7 via the connecting shaft 21. Of course, the transmission mechanism 4 can also be a belt drive mechanism instead of a spur gear transmission mechanism.

[0042] Figure 3 A third embodiment of the power unit 1 is shown schematically again. Referring again to the above description, and only clarifying the differences. In the third embodiment, the traction motor 2 is connected to the torque converter 3 via a spur gear transmission mechanism 20. The transmission mechanism 4 is implemented as a single-stage spur gear transmission mechanism. The difference from the second embodiment lies particularly in the mirror arrangement of the pump impeller 7 and the turbine 8, and the arrangement of the resulting guide shaft 11. The guide shaft is arranged coaxially with the output shaft 15 and is designed to receive the hollow shaft of the output shaft 15. As an alternative to the illustrated embodiment, the traction motor 2 can be arranged on the other side of the torque converter 3, i.e., the opposite side of the pump impeller 7 and the turbine 8. Furthermore, the transmission mechanism 4 can be implemented as a belt drive mechanism instead of a spur gear transmission mechanism.

[0043] Figure 4A schematic diagram of a fourth embodiment of the power unit 1 is shown. Referring to the above description, especially the description of the second embodiment, only the differences are clarified. The difference is that the transmission mechanism 4 is not designed as a spur gear transmission mechanism, but as a planetary gear transmission mechanism. Accordingly, the transmission mechanism has a sun gear 22, a ring gear 23, and a planetary gear carrier 24, on which planetary gears 25 are rotatably supported. The planetary gears 25 mesh not only with the sun gear 22 but also with the ring gear 23. The planetary gear carrier 24 is connected to the differential transmission mechanism 5; in particular, the planetary gear carrier 24 replaces the input gear 16. The ring gear 23 is fixedly positioned and is preferably connected to the housing 12 for this purpose.

[0044] The guide shaft 11 is designed as a hollow shaft and houses one of the branch shafts 18 and 19, in this case, branch shaft 18. Correspondingly, the input shaft 14 also surrounds branch shaft 18. The same applies to the output shaft 15, which is also a hollow shaft and surrounds branch shaft 18. In a modified version of the design shown, the traction motor 2 can be arranged on the opposite side of the torque converter 3 and correspondingly connected to the pump impeller 7 via the connecting shaft 21.

[0045] Figure 5 A fifth embodiment of the power unit 1 is illustrated schematically. Referring to the above embodiments, particularly the fourth embodiment, only the differences are pointed out. The difference is that the traction motor 2 is arranged on the side of the turbine 8 away from the pump wheel 7 and connected to the pump wheel 7 via a connecting shaft 21 bridging the turbine 8. The input shaft 14 is designed as a hollow shaft and surrounds the transmission mechanism 4, which is again a planetary gear transmission mechanism.

[0046] To fix the gear ring 23 in position, a gear ring shaft 26, rigidly connected to the gear ring 23, extends from the input shaft 14 and is correspondingly positioned on the side of the spur gear transmission mechanism 20 opposite to the transmission mechanism 4. The gear ring shaft 26 is fastened to the housing 12 on its side away from the gear ring 23. Preferably, in the axial direction, this fastening overlaps with the traction motor 2. As an alternative to the described design, the arrangement of the pump wheel 7 and the turbine 8 can be interchanged, so that the pump wheel 7 is thus positioned on the side of the turbine 8 facing the traction motor 2.

[0047] Figure 6A schematic diagram of the power unit 1 according to an embodiment of the present invention is shown. Referring to the above description, especially the description of the fifth embodiment, only the differences are pointed out below. The difference is that the spur gear transmission mechanism 20 is omitted, so the traction motor 2 is connected to the torque converter 3 without a transmission mechanism. Here, the traction motor 2 is arranged coaxially with and surrounds the axle 17, especially the split axle 19. Therefore, it is necessary to extend the gear ring shaft 26 so that the gear ring shaft passes through the traction motor 2 and is fastened to the housing 12 on the side of the traction motor 2 away from the transmission mechanism 4.

[0048] Alternatively, the traction motor 2 can be arranged axially between the torque converter 3 and the differential transmission mechanism 5. It is also possible to arrange the traction motor 2 on the opposite side of the torque converter 3, so that the traction motor 2 is correspondingly located on the side of the pump impeller 7 away from the turbine 8. Furthermore, in another design, another transmission mechanism can be present in each of the split shafts 18 and 19, which is implemented, for example, as a spur gear transmission mechanism or a planetary gear transmission mechanism.

[0049] List of reference numerals

[0050] 1 Power unit

[0051] 2 traction motors

[0052] 3 torque converter

[0053] 4. Speed ​​Transmission Mechanism

[0054] 5. Differential transmission mechanism

[0055] 6 drive shafts

[0056] 7 pump wheel

[0057] 8 turbo

[0058] 9 guide wheels

[0059] 10 Freewheels

[0060] 11 guide wheel shaft

[0061] 12 shells

[0062] 13 Lock-up Clutch

[0063] 14 input axes

[0064] 15 output shafts

[0065] 16 input gears

[0066] 17-wheel axle

[0067] 18-inch axle

[0068] 19-inch axle

[0069] 20 Spur Gear Transmission Mechanism

[0070] 21 connecting shaft

[0071] 22 Sun Wheels

[0072] 23 gear ring

[0073] 24 Planetary Gear Carrier

[0074] 25 planetary gears

[0075] 26-tooth ring shaft.

Claims

1. A power unit (1) for a motor vehicle, comprising a traction motor (2), a torque converter (3), a transmission mechanism (4), and a differential transmission mechanism (5), wherein, The traction motor (2) is driven technically connected to the differential transmission mechanism (5) via a torque converter (3) and a transmission mechanism (4) in a given order, wherein the traction motor (2) is driven technically connected to the torque converter (3) via a spur gear transmission mechanism (20) or without a transmission mechanism, wherein the transmission mechanism (4) is designed as a planetary gear transmission mechanism having a sun gear (22), a ring gear (23) and at least one planetary gear (25) rotatably supported on a planetary gear carrier (24) and engaging with the sun gear (22) and the ring gear (23), wherein the sun gear (22) is driven technically arranged on the torque converter (3) side, the planetary gear carrier (24) is driven technically arranged on the differential transmission mechanism (5) side, and the ring gear (23) is fixed, characterized in that the ring gear (23) is fixed by a ring gear shaft (26) that overlaps with the traction motor (2) in an axial direction based on the rotation axis of the traction motor (2).

2. The power unit according to claim 1, characterized in that, The torque converter (3) has a pump wheel (7) located on the side of the traction motor (2) in terms of drive technology, a turbine (8) located on the side of the differential transmission mechanism (5) in terms of drive technology, and a guide wheel (9), wherein the guide wheel (9) is arranged on the guide wheel shaft (11).

3. The power device according to any one of the preceding claims, characterized in that, The guide shaft (11) is received by the input shaft (14) of the torque converter (3), which is designed to be a hollow shaft, or the guide shaft (11) is designed to be a hollow shaft and is received by the output shaft (15) of the torque converter (3) or the differential transmission mechanism (5) located between the torque converter (3) and the transmission mechanism (4) in the drive technology.

4. The power unit according to claim 3, characterized in that, The traction motor (2) is arranged coaxially with the output shaft (15) or eccentrically relative to the output shaft (15).

5. The power unit according to claim 1 or 2, characterized in that, Looking in the axial direction with reference to the rotation axis of the traction motor (2), a lock-up clutch (13) is arranged between the traction motor (2) and the torque converter (3) or on the side of the torque converter (3) away from the traction motor (2).

6. The power unit according to claim 2, characterized in that, In the axial direction with reference to the rotation axis of the traction motor (2), the turbine (8) is arranged on the side of the pump wheel (7) facing the traction motor (2), or in the axial direction with reference to the rotation axis of the traction motor (2), the pump wheel (7) is arranged on the side of the turbine (8) facing the traction motor (2).

7. The power unit according to claim 3, characterized in that, The gear ring shaft (26) is arranged coaxially with the output shaft of the differential transmission mechanism and / or the guide wheel shaft (11).

Images