Drive unit for a vehicle axle

Abstract

The invention relates to a drive unit (100) for a vehicle axle with a first wheel (R1) and a second wheel (R2), comprising an electric machine (EM) and a transmission with at least two planetary gear sets (PS1, PS2) which are arranged coaxially to the electric machine (EM), and a connecting shaft (W) which is arranged axially parallel to the electric machine (EM) and is designed to connect the second wheel (R2), characterized in that one of the two planetary gear sets (PS1, PS2) is designed to unequally distribute a torque fed in by the electric machine (EM) via a sun shaft of the same planetary gear set between a carrier shaft and a ring gear shaft of the same planetary gear set.

Description

[0001] The invention relates to a drive unit for a vehicle axle, wherein the drive unit has an electric machine and a transmission with at least two planetary gear sets.

[0002] For example, DE 298 00 582 U1 discloses a drive unit for buses. The drive unit has a drive machine designed as a transverse flux machine, comprising at least one rotor and one stator; wherein the transverse flux machine is assigned to at least two wheels arranged on a common geometric axis. Furthermore, the transverse flux machine is assigned a device for dividing and transmitting the power to the two wheels, wherein the device for dividing and transmitting the power has at least one input which is at least indirectly coupled to the rotor of the electric motor and at least two outputs. The first output can be coupled at least indirectly to the wheel drive shaft of the first wheel, and the second output can be coupled at least indirectly to the wheel drive shaft of the second wheel via a transmission shaft arranged parallel to the rotor axis of the transverse flux machine.

[0003] The object of the present invention is to provide an alternative drive unit for a vehicle, wherein the drive unit is to be designed in a particularly compact and energy-efficient manner. This object is achieved by a drive unit having the features of independent patent claim 1. Advantageous embodiments are the subject of the dependent claims, the following description, and the figures.

[0004] A drive unit according to the invention for a vehicle axle with a first wheel and a second wheel comprises an electric machine and a transmission with at least two planetary gear sets arranged coaxially to the electric machine, as well as a connecting shaft arranged axially parallel to the electric machine and configured to connect the second wheel, wherein one of the two planetary gear sets is configured to unequally distribute a torque fed in by the electric machine via a sun shaft of the same planetary gear set between a carrier shaft and a ring gear shaft of the same planetary gear set. Thus, the transmission implements a differential function and unequally distributes the drive torque of the electric machine between the carrier shaft and the ring gear shaft of the planetary gear set, which is configured to unequally distribute the drive torque.The drive torque is transferred to the differential via the sun gear of the planetary gear set, which is designed to distribute the drive torque unevenly. The drive axle is designed as an electric drive axle and is intended for the vehicle's electric drive.

[0005] According to one embodiment, the drive unit comprises exactly three planetary gear sets coupled to one another, which are arranged coaxially to the electric machine, • wherein the first planetary gear set comprises a first sun shaft, a first ring gear shaft and a first carrier shaft and is configured as a pre-transmission, • wherein the second planetary gear set comprises a second sun shaft, a second ring gear shaft and a second carrier shaft and is designed to unequally distribute a torque received from the first planetary gear set between the second carrier shaft and the second ring gear, • wherein the third planetary gear set comprises a third sun shaft, a third ring gear shaft and a third carrier shaft and is configured to align a torque and a direction of rotation of the third ring gear shaft with a torque and a direction of rotation of the second carrier shaft, • the first solar shaft is designed to connect the electrical machine, • wherein the second web shaft is designed to drive the first wheel of the vehicle axle, • wherein the third ring gear shaft has an external toothing which meshes with a first spur gear and forms a first spur gear stage, wherein the first spur gear is connected to a second spur gear via the connecting shaft, wherein the second spur gear meshes with a third spur gear and forms a second spur gear stage, wherein the third spur gear is connected in a rotationally fixed manner to a second output shaft for driving the second wheel of the vehicle axle.

[0006] For this purpose, reference is made to the embodiments according to Fig. 1 and Fig. 2 and the corresponding figure description.

[0007] The first wheel is therefore driven via the second carrier shaft, and the second wheel is driven via the third ring gear and the spur gear chain with the connecting shaft arranged in between. The first planetary gear set serves as the first transmission. The second and third planetary gear sets form an integral differential. An “integral differential” is understood to be a differential with two planetary gear sets, in this case the second and third planetary gear sets. The second planetary gear set is connected on the one hand to the first planetary gear set, and on the other hand to the third planetary gear set and at least indirectly to the first output shaft, which is to be understood as the first differential output shaft. The third planetary gear set is also at least indirectly connected to the second output shaft, which is to be understood as the second differential output shaft, and is further supported on a stationary component, in particular a housing component.By means of such an integral differential, the input torque introduced into the integral differential can be changed and distributed in a defined ratio between the two differential output shafts.

[0008] At identical output speeds of the differential output shafts, the integral differential has no gears rotating in the block or rotating without a rolling motion. Therefore, regardless of the output speeds of the output shafts, there is always a relative movement of the meshing components of the integral differential. With an integral differential, the sum of both wheel torques is not combined or summarized into a common axle torque in one component; instead, the drive power is divided in the integral differential and transmitted to the connected differential output shaft according to the design of its two planetary gear sets. This allows the components of the integral differential to be designed more slenderly due to the respective, comparatively low torque. Furthermore, a reduction in the number of components and weight savings are achieved.Using such an integral differential, the two functions of torque conversion and torque distribution, which are usually performed by two separate assemblies, can be implemented by a single integral assembly. The integral differential is thus a combined transmission and differential gear that, on the one hand, realizes torque conversion and, on the other hand, torque distribution to the differential output shafts. Furthermore, the first planetary gear set pre-transmits the torque fed into the integral differential.

[0009] The first spur gear stage has a gear ratio iG1 and connects the third ring gear shaft to the connecting shaft. For example, the connecting shaft can be designed as a rigid shaft or a propeller shaft. The second spur gear stage has a gear ratio of 1 / iG1 and connects the connecting shaft to the second output shaft. The reciprocal of the gear ratio is necessary to ensure identical speeds and torques at both wheels of the drive axle. The input shaft and the two output shafts are arranged on a common rotational axis with the electric machine, with the connecting shaft arranged parallel to the axis.

[0010] For the purposes of the invention, a “shaft” is understood to be a rotatable component of the transmission via which associated components of the transmission are connected to one another in a rotationally fixed manner or via which such a connection can be established upon actuation of one of the shift elements. The respective shaft can connect the components axially or radially, or even both axially and radially. For example, the respective shaft can also be in the form of an intermediate piece via which a respective component is connected radially, for example. The term “shaft” does not exclude the possibility that the components to be connected can be designed as a single piece. In particular, two or more shafts connected to one another in a rotationally fixed manner can be designed as a single piece.

[0011] The input shaft is configured to connect the electric motor to the transmission. The first output shaft is configured to connect the first gear, and the second output shaft is configured to connect the second gear. The second carrier shaft is rotationally fixed to the first output shaft, and the third spur gear is rotationally fixed to the second output shaft.

[0012] According to a further embodiment, the drive unit comprises exactly three planetary gear sets coupled to one another, which are arranged coaxially to the electric machine, • wherein the first planetary gear set comprises a first sun shaft, a first ring gear shaft and a first carrier shaft and is configured as a pre-transmission, • wherein the second planetary gear set comprises a second sun shaft, a second ring gear shaft and a second carrier shaft and is designed to unequally distribute a torque received from the first planetary gear set between the second carrier shaft and the second ring gear, • wherein the third planetary gear set comprises a third sun shaft, a third ring gear shaft and a third carrier shaft and is configured to align a torque and a direction of rotation of the third ring gear shaft with a torque and a direction of rotation of the second carrier shaft, • the first sun shaft is connected to the electric machine via a drive shaft, • wherein the third ring gear shaft is connected in a rotationally fixed manner to a first output shaft for driving the first wheel, • wherein the second web shaft is connected in a rotationally fixed manner to a first spur gear, wherein the first spur gear meshes with a second spur gear and forms a first spur gear stage, wherein the second spur gear is connected via at least one connecting shaft to a third spur gear, wherein the third spur gear meshes with a fourth spur gear and forms a second spur gear stage, wherein the fourth spur gear is connected in a rotationally fixed manner to a second output shaft for driving the second gear.

[0013] For this purpose, reference is made to the embodiment according to Fig. 3 and the corresponding figure description. In this embodiment, the second and third planetary gear sets also form an integral differential. The output from the integral differential toward the second gear is transmitted through the electric motor. This can generate advantages in the arrangement of the transmission components.

[0014] According to a further embodiment, the drive unit comprises exactly three planetary gear sets coupled to one another, which are arranged coaxially to the electric machine, • wherein the first planetary gear set comprises a first sun shaft, a first ring gear shaft and a first carrier shaft and is designed to unequally distribute a torque received from the electric machine between the first carrier shaft and the first ring gear shaft, • wherein the second planetary gear set comprises a second sun shaft, a second ring gear shaft and a second carrier shaft, • wherein the third planetary gear set comprises a third sun shaft, a third ring gear shaft and a third carrier shaft and is configured to align a torque and a direction of rotation of the third carrier shaft with a torque and a direction of rotation of the second ring gear shaft, • the first sun shaft is connected to the electric machine via a drive shaft, • wherein the third web shaft for driving the first wheel is connected in a rotationally fixed manner to a first output shaft, • wherein the second ring gear shaft has an external toothing which meshes with a first spur gear and forms a first spur gear stage, wherein the first spur gear is connected to a second spur gear via at least one connecting shaft, wherein the second spur gear meshes with a third spur gear and forms a second spur gear stage, wherein the third spur gear is connected in a rotationally fixed manner to a second output shaft for driving the second gear.

[0015] For this purpose, reference is made to the embodiment according to Fig. 4 and the corresponding figure description. In this embodiment, the second and third planetary gear sets also form an integral differential. In this embodiment, no explicit pre-ratio is provided; the overall ratio is generated by the three planetary gear sets. This can result in efficiency advantages due to the torques and speeds in the planetary gear sets.

[0016] According to a further embodiment, the drive unit comprises exactly three planetary gear sets coupled to one another, which are arranged coaxially to the electric machine, • wherein the first planetary gear set comprises a first sun shaft, a first ring gear shaft and a first carrier shaft and is designed to unequally distribute a torque received from the electric machine between the first carrier shaft and the first ring gear shaft, • wherein the second planetary gear set comprises a second sun shaft, a second ring gear shaft and a second carrier shaft, • wherein the third planetary gear set comprises a third sun shaft, a third ring gear shaft and a third carrier shaft and is configured to align a torque and a direction of rotation of the third carrier shaft with a torque and a direction of rotation of the second ring gear shaft, • the first sun shaft is connected to the electric machine via a drive shaft, • wherein the second ring gear shaft is connected in a rotationally fixed manner to a first output shaft for driving the first wheel, • wherein the third web shaft is connected in a rotationally fixed manner to a first spur gear, wherein the first spur gear meshes with a second spur gear and forms a first spur gear stage, wherein the second spur gear is connected to a third spur gear via at least one connecting shaft, wherein the third spur gear meshes with a fourth spur gear and forms a second spur gear stage, wherein the fourth spur gear is connected in a rotationally fixed manner to a second output shaft for driving the second gear.

[0017] For this purpose, reference is made to the embodiment according to Fig. 5 and the associated figure descriptions. In this embodiment, the second and third planetary gear sets also form an integral differential. In this embodiment, no explicit pre-transmission ratio is provided; the overall transmission ratio is generated by the three planetary gear sets. This can result in efficiency advantages due to the torques and speeds in the planetary gear sets. The output from the integral differential toward the second wheel occurs through the electric motor. This can generate advantages in the arrangement of the transmission components.

[0018] According to a further embodiment, the drive unit comprises exactly two planetary gear sets coupled to one another, a third planetary gear set designed as a wheel head gear for arrangement within the first wheel of the vehicle axle and a fourth planetary gear set designed as a wheel head gear for arrangement within the second wheel of the vehicle axle, wherein the four planetary gear sets are arranged coaxially to the electric machine, • wherein the first planetary gear set comprises a first sun shaft, a first ring gear shaft and a first carrier shaft and is designed to unequally distribute a torque received from the electric machine between the first carrier shaft and the first ring gear shaft, • wherein the second planetary gear set comprises a second sun shaft, a second ring gear shaft and a second carrier shaft and is configured to align a torque and a direction of rotation of the second ring gear shaft with a torque and a direction of rotation of the first carrier shaft, • the third planetary gear set has a third sun shaft, a third ring gear shaft and a third carrier shaft, • the fourth planetary gear set has a fourth sun shaft, a fourth ring gear shaft and a fourth carrier shaft, • the first sun shaft is connected to the electric machine via a drive shaft, • wherein the first web shaft is connected to the third sun shaft in a rotationally fixed manner and the third web shaft is connected to a first output shaft in a rotationally fixed manner for driving the first wheel, • wherein the second ring gear shaft has an external toothing which meshes with a first spur gear and forms a first spur gear stage, wherein the first spur gear is connected to a second spur gear via a connecting shaft, wherein the second spur gear meshes with a third spur gear and forms a second spur gear stage, wherein the fourth sun shaft is connected in a rotationally fixed manner to the third spur gear and the fourth web shaft for driving the second gear is connected in a rotationally fixed manner to a second output shaft.

[0019] For this purpose, reference is made to the embodiment according to Fig. 6 and the corresponding figure description. In this embodiment, the first and second planetary gear sets form an integral differential. Because the drive unit has final gears in the wheel heads, a lower gear ratio is required in the differential. This results in particular in advantages in terms of installation space.

[0020] According to a further embodiment, the drive unit comprises exactly two planetary gear sets coupled to one another, a third planetary gear set designed as a wheel-end gear for arrangement within a first wheel of the vehicle axle and a fourth planetary gear set designed as a wheel-end gear for arrangement within a second wheel of the vehicle axle, wherein the four planetary gear sets are arranged coaxially to the electric machine, • wherein the first planetary gear set comprises a first sun shaft, a first ring gear shaft and a first carrier shaft and is designed to unequally distribute a torque received from the electric machine between the first carrier shaft and the first ring gear shaft, • wherein the second planetary gear set comprises a second sun shaft, a second ring gear shaft and a second carrier shaft and is configured to align a torque and a direction of rotation of the second ring gear shaft with a torque and a direction of rotation of the first carrier shaft, • the third planetary gear set has a third sun shaft, a third ring gear shaft and a third carrier shaft, • the fourth planetary gear set has a fourth sun shaft, a fourth ring gear shaft and a fourth carrier shaft, • the first sun shaft is connected to the electric machine via a drive shaft, • wherein the second ring gear shaft is connected to the third sun shaft in a rotationally fixed manner and the third web shaft is connected to a first output shaft in a rotationally fixed manner for driving the first wheel, • wherein the first carrier shaft is connected in a rotationally fixed manner to a first spur gear, wherein the first spur gear meshes with a second spur gear and forms a first spur gear stage, wherein the second spur gear is connected via a connecting shaft to a third spur gear, wherein the third spur gear meshes with a fourth spur gear and forms a second spur gear stage, wherein the fourth sun shaft is connected in a rotationally fixed manner to the fourth spur gear and the fourth carrier shaft is connected in a rotationally fixed manner to a second output shaft for driving the second gear.

[0021] For this purpose, reference is made to the embodiment according to Fig. 7 and the corresponding figure description. In this embodiment, the first and second planetary gear sets form an integral differential. Because the drive unit has final gears in the wheel heads, a lower gear ratio is required in the differential. This results in particular in advantages in terms of installation space.

[0022] Preferably, one of the aforementioned drive units has a clutch designed as a differential lock. Such a clutch is to be understood as a switching element, i.e. as a switchable device, which, in a closed state, connects two shafts to one another in a rotationally fixed manner and, in an open state, decouples the two shafts from one another. Two shafts can rotate relative to one another in the decoupled state. For example, the differential lock connects the third ring gear shaft to the second carrier shaft in order to deactivate the differential function. For example, the differential lock connects the third carrier shaft to the second ring gear shaft in order to deactivate the differential function. For example, the differential lock connects the second ring gear shaft to the first carrier shaft in order to deactivate the differential function.

[0023] According to a further embodiment, the drive unit comprises exactly one first planetary gear set, a second planetary gear set designed as a wheel-end gear for arrangement within a first wheel of the vehicle axle and a third planetary gear set designed as a wheel-end gear for arrangement within a second wheel of the vehicle axle, wherein the three planetary gear sets are arranged coaxially to the electric machine, • wherein the first planetary gear set comprises a first sun shaft, a first ring gear shaft and a first carrier shaft and is designed to unequally distribute a torque received from the electric machine between the first carrier shaft and the first ring gear shaft, • wherein the second planetary gear set comprises a second sun shaft, a second ring gear shaft and a second carrier shaft, • the third planetary gear set has a third sun shaft, a third ring gear shaft and a third carrier shaft, • the first sun shaft is connected to the electric machine via a drive shaft, • wherein the first carrier shaft is connected in a rotationally fixed manner to the second sun shaft and the second carrier shaft is connected in a rotationally fixed manner to a first output shaft for driving the first wheel, • wherein the first ring gear shaft has external teeth which mesh with a first spur gear and form a first spur gear stage, wherein the first spur gear is connected to a second spur gear via a connecting shaft, wherein the second spur gear meshes with a third spur gear and form a second spur gear stage, wherein the third spur gear meshes with a fourth spur gear and form a third spur gear stage, wherein the third sun shaft is connected in a rotationally fixed manner to the fourth spur gear and the third web shaft for driving the second gear is connected in a rotationally fixed manner to a second output shaft.

[0024] For this purpose, reference is made to the embodiment according to Fig. 8 and the corresponding figure description. In this embodiment of the drive unit, the torque and direction of rotation of the second output shaft are aligned with the torque and direction of rotation of the first output shaft not via planetary gear sets, but via the spur gear chain, in particular via the three spur gear stages.

[0025] According to a further embodiment, the drive unit comprises exactly one first planetary gear set, a second planetary gear set designed as a wheel-end gear for arrangement within a first wheel of the vehicle axle and a third planetary gear set designed as a wheel-end gear for arrangement within a second wheel of the vehicle axle, wherein the three planetary gear sets are arranged coaxially to the electric machine, • wherein the first planetary gear set comprises a first sun shaft, a first ring gear shaft and a first carrier shaft and is designed to unequally distribute a torque received from the electric machine between the first carrier shaft and the first ring gear shaft, • wherein the second planetary gear set comprises a second sun shaft, a second ring gear shaft and a second carrier shaft, • the third planetary gear set has a third sun shaft, a third ring gear shaft and a third carrier shaft, • the first sun shaft is connected to the electric machine via a drive shaft, • wherein the first ring gear shaft is connected in a rotationally fixed manner to the second sun shaft and the second web shaft is connected in a rotationally fixed manner to a first output shaft for driving the first wheel, • wherein the first carrier shaft is connected in a rotationally fixed manner to a first spur gear, wherein the first spur gear meshes with a second spur gear and forms a first spur gear stage, wherein the second spur gear is connected to a third spur gear via a connecting shaft, wherein the third spur gear meshes with a fourth spur gear and forms a second spur gear stage, wherein the fourth spur gear meshes with a fifth spur gear and forms a third spur gear stage, wherein the third sun shaft is connected in a rotationally fixed manner to the fifth spur gear and the third carrier shaft is connected in a rotationally fixed manner to a second output shaft for driving the second gear.

[0026] For this purpose, reference is made to the embodiment according to Fig. 9 and the corresponding figure description. In this embodiment of the drive unit, the torque and direction of rotation of the second output shaft are aligned with the torque and direction of rotation of the first output shaft not via planetary gear sets, but via the spur gear chain, in particular via the three spur gear stages.

[0027] According to a further embodiment, the drive unit comprises exactly one first planetary gear set and a second planetary gear set designed as a wheel head gear for arrangement within a first wheel of the vehicle axle, wherein the two planetary gear sets are arranged coaxially to the electric machine, • wherein the first planetary gear set comprises a first sun shaft, a first ring gear shaft and a first carrier shaft and is designed to unequally distribute a torque received from the electric machine between the first carrier shaft and the first ring gear shaft, • wherein the second planetary gear set comprises a second sun shaft, a second ring gear shaft and a second carrier shaft, • the first sun shaft is connected to the electric machine via a drive shaft, • wherein the first carrier shaft is connected in a rotationally fixed manner to the second sun shaft and the second carrier shaft is connected in a rotationally fixed manner to a first output shaft for driving the first wheel, • wherein the first ring gear shaft has external teeth which mesh with a first spur gear and form a first spur gear stage, wherein the first spur gear is connected to a second spur gear via a connecting shaft, wherein the second spur gear meshes with a third spur gear and form a second spur gear stage, wherein the third spur gear meshes with a fourth spur gear and form a third spur gear stage, wherein the fourth spur gear is connected in a rotationally fixed manner to a second output shaft for driving the second gear.

[0028] For this purpose, reference is made to the embodiment according to Fig. 10 and the corresponding figure description. The spur gear chain with three spur gear stages produces such a high gear ratio that the gearhead in the second gear can be eliminated. This can result in efficiency advantages and cost reduction.

[0029] According to a further embodiment, the drive unit comprises exactly one electric machine, a first planetary gear set and a second planetary gear set designed as a wheel head gear for arrangement within a first wheel of the vehicle axle, wherein the two planetary gear sets are arranged coaxially to the electric machine, • wherein the first planetary gear set comprises a first sun shaft, a first ring gear shaft and a first carrier shaft and is designed to unequally distribute a torque received from the electric machine between the first carrier shaft and the first ring gear shaft, • wherein the second planetary gear set comprises a second sun shaft, a second ring gear shaft and a second carrier shaft, • the first sun shaft is connected to the electric machine via a drive shaft, • wherein the first ring gear shaft is connected in a rotationally fixed manner to the second sun shaft and the second web shaft is connected in a rotationally fixed manner to a first output shaft for driving the first wheel, • wherein the first web shaft is connected in a rotationally fixed manner to a first spur gear, wherein the first spur gear meshes with a second spur gear and forms a first spur gear stage, wherein the second spur gear is connected via a connecting shaft to a third spur gear, wherein the third spur gear meshes with a fourth spur gear and forms a second spur gear stage, wherein the fourth spur gear meshes with a fifth spur gear and forms a third spur gear stage, wherein the fifth spur gear is connected in a rotationally fixed manner to a second output shaft for driving the second gear.

[0030] For this purpose, reference is made to the embodiment according to Fig. 11 and the corresponding figure description. The spur gear chain with three spur gear stages produces such a high gear ratio that the gearhead in the second gear can be eliminated. This can result in efficiency advantages and cost reduction.

[0031] The connecting shaft is preferably configured to connect a first section of the drive unit to a second section of the drive unit, with a space for accommodating passengers and / or cargo being arranged axially between the two sections of the drive unit. Thus, the connecting shaft bridges an unobstructed space. For example, the connecting shaft can be designed as a rigid shaft or a cardan shaft. Thus, the two axle sides of the drive unit are connected either via a cardan shaft or a rigid shaft. Multiple shafts can also be connected to one another in a rotationally fixed manner or as a single piece to form the connecting shaft.

[0032] A vehicle according to the invention comprises at least one drive unit according to the invention. The above definitions as well as explanations regarding technical effects, advantages, and advantageous embodiments of the drive unit according to the invention also apply mutatis mutandis to the vehicle according to the invention. In particular, the vehicle is designed as a low-floor vehicle and has space for accommodating passengers and / or freight. For example, the vehicle is a bus. Preferably, the vehicle is an electric vehicle, i.e., an electrically powered vehicle.

[0033] Advantageous embodiments of the invention, which are explained below, are illustrated in the drawings, wherein identical or similar elements are provided with the same reference numerals. They show: Fig. 1 a highly abstracted schematic view of a drive unit according to the invention according to a first embodiment; Fig. 2 a highly abstracted schematic view of a drive unit according to the invention according to a second embodiment; Fig. 3 a highly abstracted schematic view of a drive unit according to the invention according to a third embodiment; Fig. 4 a highly abstracted schematic view of a drive unit according to the invention according to a fourth embodiment; Fig. 5 a highly abstracted schematic view of a drive unit according to the invention according to a fifth embodiment; Fig. 6 a highly abstracted schematic view of a drive unit according to the invention according to a sixth embodiment; Fig. 7 a highly abstracted schematic view of a drive unit according to the invention according to a seventh embodiment; Fig. 8 is a highly abstracted schematic view of a drive unit according to the invention according to an eighth embodiment; Fig. 9 a highly abstracted schematic view of a drive unit according to the invention according to a ninth embodiment; Fig. 10 is a highly abstracted schematic view of a drive unit according to the invention according to a tenth embodiment; Fig. 11 a highly abstracted schematic view of a drive unit according to the invention according to an eleventh embodiment and Fig. 12 a highly abstracted schematic view of a vehicle with a drive unit according to the invention.

[0034] According to Fig. 1 to Fig. 11 comprises a drive unit 100 according to the invention for a vehicle axle with a first wheel R1 and a second wheel R2, a single electric machine EM with a housing-fixed stator EMS and a rotatable rotor EMR, and a transmission. The transmission implements a differential function and distributes the drive torque of the electric machine EM unequally between a carrier shaft and a ring gear shaft of a planetary gear set. Thus, the sun shaft of the planetary gear set, which is configured to distribute the drive torque unequally, always serves to introduce the drive torque into the differential. The drive axle is thus designed as an electric drive axle and is intended for the electrical drive of the vehicle.A connecting shaft W is configured to connect a first section of the respective drive unit 100 to a second section of the respective drive unit 100, wherein a space 4 for accommodating passengers is arranged axially between the two sections of the respective drive unit 100.

[0035] According to Fig. 1, the transmission comprises precisely three interconnected planetary gear sets PS1, PS2, PS3, which are arranged coaxially to the electric machine EM. The first planetary gear set PS1 comprises three shafts, namely a first sun gear shaft SO1, a first ring gear shaft HR1, and a first planetary gear shaft ST1. The first planetary gear shaft ST1 carries a plurality of planet gears that mesh with the first sun gear shaft SO1 and the first ring gear shaft HR1. The second planetary gear set PS2 also comprises three shafts, namely a second sun gear shaft SO2, a second ring gear shaft HR2, and a second planetary gear shaft ST2. The second planetary gear shaft ST2 carries a plurality of planet gears that mesh with the second sun gear shaft SO2 and the second ring gear shaft HR2. The third planetary gear set PS3 also comprises three shafts, namely a third sun gear shaft SO3, a third ring gear shaft HR3, and a third planetary gear shaft ST3.The third carrier shaft ST3 carries several planetary gears that mesh with the third sun gear shaft SO3 and the third ring gear shaft HR3. According to an axial sequence, the first planetary gear set PS1 is arranged axially adjacent to the electric machine EM, with the second planetary gear set PS2 being arranged axially adjacent to the first planetary gear set PS1, and the third planetary gear set PS3 being arranged axially adjacent to the second planetary gear set PS2. Thus, the second planetary gear set PS2 is arranged axially between the third planetary gear set PS3 and the first planetary gear set PS1.

[0036] The first sun gear shaft SO1 is designed to connect to the electric machine EM. In this case, the first sun gear shaft SO1 is rotationally fixedly connected to the rotor EMR of the electric machine EM via a drive shaft 1 and can thus be driven by the electric machine EM. The first carrier shaft ST1 is rotationally fixedly connected to the second sun gear shaft SO2. The first ring gear shaft HR1 and the third carrier shaft ST3 are rotationally fixedly connected to a stationary component designed as a housing G and are thus prevented from rotating. The second carrier shaft ST2 is rotationally fixedly connected to a first output shaft 2. The first output shaft 2 is rotationally fixedly connected to the first wheel R1 of the vehicle axle. The second carrier shaft ST2 is therefore rotationally fixedly connected to the first wheel R1 of the vehicle axle. The second ring gear shaft HR2 is rotationally fixedly connected to the third sun gear shaft SO3.

[0037] The first planetary gear set PS1 is configured here as a pre-transmission gear. The second planetary gear set PS2 is configured to unequally distribute the torque received from the electric motor EM via the first planetary gear set PS1 between the second carrier shaft ST2 and the second ring gear shaft HR2. The third planetary gear set PS3 is configured to align the torque and direction of rotation of the third ring gear shaft HR3 with the torque and direction of rotation of the second carrier shaft ST2, whereby the torque and direction of rotation at the third ring gear shaft HR3 and the second carrier shaft ST2 are identical. Thus, the second planetary gear set PS2 and the third planetary gear set PS3 form an integral differential.

[0038] The second wheel R2 of the vehicle axle is drivingly connected to the third ring gear shaft HR3. For this purpose, external teeth are formed on the third ring gear shaft HR3. The third ring gear shaft HR3 therefore has internal teeth on its inner circumferential surface and external teeth on its outer circumferential surface. A first spur gear stage SR1, a second spur gear stage SR2 and a connecting shaft W are arranged in the torque flow between the third ring gear shaft HR3 and the second wheel R2. The connecting shaft W is designed to driveably connect a first section of the drive unit to a second section of the drive unit, with a space 4 for accommodating passengers being arranged axially between the two sections of the drive unit. The connecting shaft W therefore bridges this unobstructed space 4. In the present case, the connecting shaft W is designed as a cardan shaft.

[0039] The external teeth on the third ring gear shaft HR3 mesh with a first spur gear S1. The first spur gear S1 and the external teeth on the third ring gear shaft HR3 form the first spur gear stage SR1. The first spur gear S1 is articulated to a second spur gear S2 via the connecting shaft W. The second spur gear S2 meshes with a third spur gear S3. The second spur gear S2 and the third spur gear S3 form the second spur gear stage SR2. The third spur gear 3 is rotationally fixedly connected to the second wheel R2 of the vehicle axle via a second output shaft 3. Furthermore, the drive unit has a clutch DS designed as a differential lock. When closed, the clutch DS connects the third ring gear shaft HR3 rotationally fixedly to the second carrier shaft ST2 in order to lock the differential and thus override the differential function in accordance with a control command.

[0040] The spur gear ratio of the first spur gear stage SR1 serves to connect the third ring gear shaft HR3 to the cardan shaft, whereby the spur gear ratio of the second spur gear stage SR2 serves to connect the cardan shaft to the second output shaft 3 or the second wheel R2, whereby the spur gear ratio of the second spur gear stage SR2 corresponds to the reciprocal of the spur gear ratio of the first spur gear stage SR1, in order to obtain both identical speeds and identical torques at both wheels R1, R2.

[0041] Fig. 2 shows a second embodiment of a drive unit 100 according to the invention. The drive unit 100 according to Fig. 2 essentially corresponds to the drive unit 100 according to Fig. 1, whereby the difference between these two embodiments lies in the design of the connecting shaft W. In the present case, the connecting shaft W is designed as a rigid shaft, so that the first spur gear S1 is rigidly connected to a second spur gear S2 via the connecting shaft W. Both the articulated connection of the first and second spur gears S1, S2 via the connecting shaft W designed as a cardan shaft, as well as the rigid connection of the first and second spur gears S1, S2 via the connecting shaft W designed as a rigid shaft are rotationally fixed connections that are provided for bridging the unobstructed space 4 between the two axially spaced sections of the drive unit 100. Therefore, in the following embodiments, the connecting shaft W can be designed as a cardan shaft or a rigid shaft. Otherwise, the embodiment according to Fig. 2 the embodiment according to Fig. 1, to which reference is made.

[0042] Fig. 3 shows a third embodiment of a drive unit 100 according to the invention. The drive unit 100 according to Fig. 3 essentially corresponds to the drive unit 100 according to Fig. 2, the difference between these two embodiments being the connection of the second and third planetary gear sets PS2, PS3. In this case, the connecting shaft W, as in Fig. 2, designed as a rigid shaft and can alternatively be designed as a cardan shaft.

[0043] The first planetary gear set PS1 is configured as a pre-transmission, wherein the second planetary gear set PS2 is configured for the unequal distribution of a torque received from the first planetary gear set PS1 to the second carrier shaft ST2 and the second ring gear shaft HR2, wherein the third planetary gear set PS3 is configured for the alignment of a torque and a direction of rotation of the third ring gear shaft HR3 to a torque and a direction of rotation of the second carrier shaft ST2.

[0044] The third ring gear shaft HR3 is designed to drive the first wheel R1 of the vehicle axle and is, for this purpose, connected in a rotationally fixed manner to the first wheel R1 via the first output shaft 2. The second planetary gear shaft ST2 is designed to drive the second wheel R2 of the vehicle axle, with the first spur gear stage SR1, the second spur gear stage SR2 and the connecting shaft W being arranged in the torque flow between the second planetary gear shaft ST2 and the second wheel R2. The second planetary gear shaft ST2 is rotationally fixedly connected to a first spur gear S1. The second planetary gear shaft ST2 or a shaft rotationally fixedly connected thereto extends axially through the electric machine EM and the first and second planetary gear sets PS1, PS2. The first spur gear S1, which is arranged axially between the electric machine EM and the unobstructed space 4, meshes with a second spur gear S2 and forms a first spur gear stage SR1.The second spur gear S2 is connected to a third spur gear S3 via the connecting shaft W. The third spur gear S3 meshes with a fourth spur gear S4 and forms a second spur gear stage SR2. The unobstructed space 4 is arranged axially between the two spur gear stages SR1, SR2. The fourth spur gear S4 is connected in a rotationally fixed manner to the second output shaft 3 and is configured to drive the second wheel R2 of the vehicle axle. Otherwise, the embodiment corresponds to . Fig. 3 the embodiment according to Fig. 2, to which reference is made.

[0045] Fig. 4 shows a fourth embodiment of a drive unit 100 according to the invention. The drive unit 100 according to Fig. 4 essentially corresponds to the drive unit 100 according to Fig. 1, whereby the difference between these two embodiments is the connection of the three planetary gear sets PS1, PS2, PS3. In this case, the connecting shaft W, as in Fig. 1, is designed as a cardan shaft and can alternatively be designed as a rigid shaft. The first planetary gear set PS1 is designed to unevenly distribute the torque received from the electric machine EM between the first carrier shaft ST1 and the first ring gear shaft HR1, while the third planetary gear set PS3 is designed to align the torque and direction of rotation of the third carrier shaft ST3 with the torque and direction of rotation of the second ring gear shaft HR2. The first ring gear shaft HR1 is rotationally fixedly connected to the third sun gear shaft SO3. The first carrier shaft ST1 is rotationally fixedly connected to the second sun gear shaft SO2. The second carrier shaft ST2 and the third ring gear shaft HR3 are rotationally fixedly connected. The third carrier shaft ST3 is designed to drive the first wheel R1 of the vehicle axle and is rotationally fixedly connected to the first wheel R1 via the first output shaft 2.The second ring gear shaft HR2 has an external toothing and is designed to drive the second wheel R2 of the vehicle axle, wherein in the torque flow between the second ring gear shaft HR2 and the second wheel R2, as in . Fig. 1, the first spur gear stage SR1, the second spur gear stage SR2 and the connecting shaft W are arranged. Furthermore, the clutch DS, in a closed state, connects the second ring gear shaft HR2 in a rotationally fixed manner to the third carrier shaft ST3 in order to lock the differential and thus override the differential function in accordance with a control command. Therefore, in this embodiment, no explicit pre-transmission is provided, with the overall transmission being generated by the three planetary gear sets PS1, PS2, PS3. Efficiency advantages can result due to the prevailing torques and speeds in the planetary gear sets PS1, PS2, PS3. Otherwise, the embodiment according to Fig. 4 the embodiment according to Fig. 1, to which reference is made.

[0046] Fig. 5 shows a fifth embodiment of a drive unit 100 according to the invention. The drive unit 100 according to Fig. 5 essentially corresponds to the drive unit 100 according to Fig. 4, whereby a difference between these two embodiments is the connection of the second and third planetary gear sets PS2, PS3. Furthermore, the connecting shaft W, as in Fig. 2, designed as a rigid shaft and can alternatively be designed as a cardan shaft. The first planetary gear set PS1 is designed for the unequal distribution of a torque received from the electric machine EM between the first carrier shaft ST1 and the first ring gear shaft HR1, wherein the third planetary gear set PS3 is designed to align a torque and a direction of rotation of the third carrier shaft ST3 with a torque and a direction of rotation of the second ring gear shaft HR2. The second ring gear shaft HR2 is designed to drive the first wheel R1 of the vehicle axle and is connected to the first wheel R1 via the first output shaft 2 in a rotationally fixed manner. The third carrier shaft ST3 is designed to drive the second wheel R2 of the vehicle axle, wherein in the torque flow between the third carrier shaft ST3 and the second wheel R2, as in Fig. 2, the first spur gear stage SR1, the second spur gear stage SR2 and the connecting shaft W are arranged. Otherwise, the embodiment according to Fig. 5 the embodiment according to Fig. 4, to which reference is made.

[0047] Fig. 6 shows a sixth embodiment of a drive unit 100 according to the invention. The drive unit 100 according to Fig. 6 comprises two interconnected planetary gear sets PS1, PS2, a third planetary gear set PS3 designed as a gearhead for placement within the first wheel R1 of the vehicle axle, and a fourth planetary gear set PS4 designed as a gearhead for placement within the second wheel R2 of the vehicle axle. The four planetary gear sets PS1-PS4 are arranged coaxially with the electric machine EM.

[0048] The first planetary gear set PS1 comprises three shafts, namely a first sun gear shaft SO1, a first ring gear shaft HR1, and a first spider shaft ST1. The first spider shaft ST1 carries a plurality of planet gears that mesh with the first sun gear shaft SO1 and the first ring gear shaft HR1. The second planetary gear set PS2 also comprises three shafts, namely a second sun gear shaft SO2, a second ring gear shaft HR2, and a second spider shaft ST2. The second spider shaft ST2 carries a plurality of planet gears that mesh with the second sun gear shaft SO2 and the second ring gear shaft HR2. The first planetary gear set PS1 is designed to unequally distribute a torque received from the electric machine EM between the first spider shaft ST1 and the first ring gear shaft HR1. The second planetary gear set PS2 is designed to align a torque and direction of rotation of the second ring gear shaft HR2 with a torque and direction of rotation of the first spider shaft ST1.

[0049] The third planetary gear set PS3 has a third sun gear shaft SO3, a third ring gear shaft HR3, and a third carrier shaft ST3. The third carrier shaft ST3 carries several planetary gears that mesh with the third sun gear shaft SO3 and the third ring gear shaft HR3. The fourth planetary gear set PS4 has a fourth sun gear shaft SO4, a fourth ring gear shaft HR4, and a fourth carrier shaft ST4. The fourth carrier shaft ST4 carries several planetary gears that mesh with the fourth sun gear shaft SO4 and the fourth ring gear shaft HR4.

[0050] The first carrier shaft ST1 is connected in a rotationally fixed manner to the third sun shaft SO3, and the third carrier shaft ST3 is configured to drive the first gear R1. The first ring gear shaft HR1 is connected in a rotationally fixed manner to the second sun shaft SO2. The second carrier shaft ST2, the third ring gear shaft HR3, and the fourth ring gear shaft HR4 are each fixed in a stationary manner to a housing G. The second ring gear shaft HR2 has external teeth that mesh with a first spur gear S1, forming a first spur gear stage SR1. The first spur gear S1 is connected to a second spur gear SR2 via a connecting shaft W. In this case, the connecting shaft W, as shown in Fig. 1, is designed as a cardan shaft and can alternatively be designed as a rigid shaft. The second spur gear S2 meshes with a third spur gear S3, forming a second spur gear stage SR2. The fourth sun gear SO4 is non-rotatably connected to the third spur gear S3, and the fourth carrier shaft ST4 is configured to drive the second gear R2.

[0051] Furthermore, a clutch DS designed as a differential lock is provided. When engaged, the clutch DS connects the second ring gear shaft HR2 to the first carrier shaft ST1 in a rotationally fixed manner, locking the differential and thus overriding the differential function in accordance with a control command. Because the drive unit has final gears in the gear heads, namely the third and fourth planetary gear sets PS3, PS4, a lower gear ratio is required in the differential, i.e., the first and second planetary gear sets PS1, PS2. The use of gear head gears results in particular in space savings.

[0052] Fig. 7 shows a seventh embodiment of a drive unit 100 according to the invention. The drive unit 100 according to Fig. 7 essentially corresponds to the drive unit 100 according to Fig. 6, whereby a difference between these two embodiments lies in the connection of the planetary gear sets PS1, PS2. The first planetary gear set PS1 is designed for the unequal distribution of a torque received from the electric machine EM between the first planetary gear shaft ST1 and the first ring gear shaft HR1. The second planetary gear set PS2 is designed to align a torque and a direction of rotation of the second ring gear shaft HR2 with a torque and a direction of rotation of the first planetary gear shaft ST1. The second ring gear shaft HR2 is rotationally fixedly connected to the third sun gear shaft SO3, and the third planetary gear shaft ST3 is designed to drive the first gear R1. The first planetary gear shaft ST1 is rotationally fixedly connected to a first spur gear S1, wherein the first spur gear S1 meshes with a second spur gear S2 and forms a first spur gear stage SR1. Otherwise, the embodiment according to Fig. 7 the embodiment according to Fig. 6, to which reference is made.

[0053] Fig. Figure 8 shows an eighth embodiment of a drive unit 100 according to the invention. The drive unit 100 according to Fig. 8 comprises a first planetary gear set PS1, a second planetary gear set PS2 designed as a gearhead for arrangement within a first wheel R1 of the vehicle axle, and a third planetary gear set PS3 designed as a gearhead for arrangement within a second wheel R2 of the vehicle axle. The three planetary gear sets PS1-PS3 are arranged coaxially with the electric machine EM.

[0054] The first planetary gear set PS1 comprises three shafts, namely a first sun shaft SO1, a first ring gear shaft HR1 and a first carrier shaft ST1. The first carrier shaft ST1 carries several planet gears that mesh with the first sun shaft SO1 and the first ring gear shaft HR1. The second planetary gear set PS2 also comprises three shafts, namely a second sun shaft SO2, a second ring gear shaft HR2 and a second carrier shaft ST2. The second carrier shaft ST2 carries several planet gears that mesh with the second sun shaft SO2 and the second ring gear shaft HR2. The third planetary gear set PS3 also comprises three shafts, namely a third sun shaft SO3, a third ring gear shaft HR3 and a third carrier shaft ST3. The third carrier shaft ST3 carries several planet gears that mesh with the third sun shaft SO3 and the third ring gear shaft HR3.The first planetary gear set PS1 is designed to unequally distribute the torque received from the electric machine EM between the first planetary gear shaft ST1 and the first ring gear shaft HR1. The first sun gear shaft SO1 is designed to connect the electric machine EM. The first planetary gear shaft ST1 is connected in a rotationally fixed manner to the second sun gear shaft SO2, and the second planetary gear shaft ST2 is designed to drive the first gear R1. The first ring gear shaft HR1 has external teeth that mesh with a first spur gear S1 to form a first spur gear stage SR1. The first spur gear S1 is connected to a second spur gear S2 via a connecting shaft W, with the second spur gear S2 meshing with a third spur gear S3 to form a second spur gear stage SR2. The third spur gear S3 meshes with a fourth spur gear S4 to form a third spur gear stage SR3.The third sun shaft SO3 is non-rotatably connected to the fourth spur gear S4, and the third carrier shaft ST3 is configured to drive the second gear R2. In this case, the connecting shaft W is shown in . Fig. 2, designed as a rigid shaft and can alternatively be designed as a cardan shaft.

[0055] According to this embodiment, the alignment of the torques and direction of rotation after the unequal distribution in the first planetary gear set is not achieved via another planetary gear set, but via the spur gear chain, in particular via the first, second, and third spur gear stages SR1, SR2, SR3. This reduces the complexity of the planetary gear set.

[0056] Fig. 9 shows a ninth embodiment of a drive unit 100 according to the invention. The drive unit 100 according to Fig. 9 essentially corresponds to the drive unit 100 according to Fig. 8, whereby a difference between these two embodiments is the connection of the first planetary gear set PS1. Furthermore, the connecting shaft W, as in Fig. 1, designed as a cardan shaft and can alternatively be designed as a rigid shaft. The first planetary gear set PS1 is designed for the unequal distribution of a torque received from the electric machine EM between the first carrier shaft ST1 and the first ring gear shaft HR1. The first ring gear shaft HR1 is rotationally fixedly connected to the second sun gear shaft SO2 and the second carrier shaft ST3 is designed to drive the first gear R1. The first carrier shaft ST1 is rotationally fixedly connected to a first spur gear S1, wherein the first spur gear S1 meshes with a second spur gear S2 and forms a first spur gear stage SR1. Otherwise, the embodiment according to Fig. 9 the embodiment according to Fig. 8, to which reference is made.

[0057] Fig. 10 shows a tenth embodiment of a drive unit 100 according to the invention. The drive unit 100 according to Fig. 10 essentially corresponds to the drive unit 100 according to Fig. 9, whereby a difference between these two embodiments is the connection of the second gear R2. In the present case, the drive unit 100 has only the first and second planetary gear sets, so that the third planetary gear set PS3 according to Fig. 9 is omitted. As a result, the second gear R2 is connected directly via the fifth spur gear S5. Consequently, the fifth spur gear S5 is connected to the second gear R2 in a rotationally fixed manner. In particular, the gear ratios in the spur gear chain, particularly in the first, second, and third spur gear stages SR1, SR2, SR3, can be increased to such an extent that the second gearhead gear becomes obsolete, which can result in efficiency advantages and cost reductions. Otherwise, the embodiment according to Fig. 10 the embodiment according to Fig. 9, to which reference is made.

[0058] Fig. 11 shows an eleventh embodiment of a drive unit 100 according to the invention. The drive unit 100 according to Fig. 11 essentially corresponds to the drive unit 100 according to Fig. 10, whereby a difference between these two embodiments is the connection of the first planetary gear set PS1. The first ring gear shaft HR1 has an external toothing and is designed to drive the second wheel R2 of the vehicle axle, wherein in the torque flow between the first ring gear shaft HR1 and the second wheel R2, as in Fig. 10, the first spur gear stage SR1, the second spur gear stage SR2, the third spur gear stage SR3 and the connecting shaft W are arranged. Otherwise, the embodiment according to Fig. 11 the embodiment according to Fig. 10, to which reference is made.

[0059] Fig. 12 shows a vehicle according to the invention with a drive unit 100 according to Fig. 1. The vehicle is designed as a bus and intended for passenger transport. For this purpose, the vehicle has a compartment 4 for accommodating passengers. This compartment extends essentially over the entire length of the vehicle. The vehicle is thus designed as a low-floor vehicle. The first and second wheels R1, R2 of the vehicle axle are drivingly connected to one another via the drive unit 100, with a differential function being implemented in the drive unit 100. Furthermore, the vehicle has a third and fourth wheel R3, R4 on a non-driven axle. Reference symbol 1 drive shaft 2 output shaft 3 Output shaft 4 rooms EM electric machine EMS stator EMR Rotor PS1 first planetary set SO1 first solar wave HO1 first ring gear shaft ST1 first bridge wave PS2 second planetary gear set SO2 second solar wave HO2 second ring gear shaft ST2 second web wave PS3 third planetary set SO3 third solar wave HO3 third ring gear shaft ST3 third web wave PS4 fourth planet set SO4 fourth solar wave HO4 fourth ring gear shaft ST4 fourth bridge wave W wave SR1 first spur gear stage SR2 second spur gear stage SR3 third spur gear stage S1 first spur gear S2 second spur gear S3 third spur gear S4 fourth spur gear S5 fifth spur gear DS clutch G Housing R1 first wheel R2 second wheel R3 third wheel R4 fourth wheel QUOTES CONTAINED IN THE DESCRIPTION

[0000] This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions. Cited patent literature

[0000] DE 298 00 582 U1

[0002]

Claims

[1] Drive unit (100) for a vehicle axle with a first wheel (R1) and a second wheel (R2), comprising an electric machine (EM) and a transmission with at least two planetary gear sets (PS1, PS2) arranged coaxially to the electric machine (EM), and a connecting shaft (W) arranged axially parallel to the electric machine (EM) and designed to connect the second wheel (R2), characterized by that one of the two planetary gear sets (PS1, PS2) is designed for the unequal distribution of a torque fed in by the electric machine (EM) via a sun shaft of the same planetary gear set to a carrier shaft and a ring gear shaft of the same planetary gear set. [2] Drive unit (100) according to claim 1, comprising exactly three planetary gear sets (PS1, PS2, PS3) coupled to one another, which are arranged coaxially to the electric machine (EM), • wherein the first planetary gear set (PS1) has a first sun shaft (SO1), a first ring gear shaft (HR1) and a first carrier shaft (ST1) and is set up as a pre-transmission, • wherein the second planetary gear set (PS2) has a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2) and is designed to unequally distribute a torque received from the first planetary gear set (PS1) between the second carrier shaft (ST2) and the second ring gear shaft (HR2), • wherein the third planetary gear set (PS3) comprises a third sun shaft (SO3), a third ring gear shaft (HR3) and a third carrier shaft (ST3) and is designed to align a torque and a direction of rotation of the third ring gear shaft (HR3) with a torque and a direction of rotation of the second carrier shaft (ST2), • wherein the first sun shaft (SO1) is connected to the electric machine (EM) via a drive shaft (1) in a rotationally fixed manner, • wherein the second carrier shaft (ST2) for driving the first wheel (R1) is connected in a rotationally fixed manner to a first output shaft (2), • wherein the third ring gear shaft (HR3) has an external toothing which meshes with a first spur gear (S1) and forms a first spur gear stage (SR1), wherein the first spur gear (S1) is connected to a second spur gear (S2) via the connecting shaft (W), wherein the second spur gear (S2) meshes with a third spur gear (S3) and forms a second spur gear stage (SR2), wherein the third spur gear (S3) is connected in a rotationally fixed manner to a second output shaft (3) for driving the second gear (R2). [3] Drive unit (100) according to claim 1, comprising exactly three planetary gear sets (PS1, PS2, PS3) coupled to one another, which are arranged coaxially to the electric machine (EM), • wherein the first planetary gear set (PS1) has a first sun shaft (SO1), a first ring gear shaft (HR1) and a first carrier shaft (ST1) and is set up as a pre-transmission, • wherein the second planetary gear set (PS2) has a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2) and is designed to unequally distribute a torque received from the first planetary gear set (PS1) between the second carrier shaft (ST2) and the second ring gear shaft (HR2), • wherein the third planetary gear set (PS3) comprises a third sun shaft (SO3), a third ring gear shaft (HR3) and a third carrier shaft (ST3) and is designed to align a torque and a direction of rotation of the third ring gear shaft (HR3) with a torque and a direction of rotation of the second carrier shaft (ST2), • wherein the first sun shaft (SO1) is connected to the electric machine (EM) via a drive shaft (1) in a rotationally fixed manner, • wherein the third ring gear shaft (HR3) is connected in a rotationally fixed manner to a first output shaft (2) for driving the first wheel (R1), • wherein the second carrier shaft (ST2) is connected in a rotationally fixed manner to a first spur gear (S1), wherein the first spur gear (S1) meshes with a second spur gear (S2) and forms a first spur gear stage (SR1), wherein the second spur gear (S2) is connected to a third spur gear (S3) via at least one connecting shaft (W), wherein the third spur gear (S3) meshes with a fourth spur gear (S4) and forms a second spur gear stage (SR2), wherein the fourth spur gear (S4) is connected in a rotationally fixed manner to a second output shaft (3) for driving the second gear (R2). [4] Drive unit (100) according to claim 1, comprising exactly three planetary gear sets (PS1, PS2, PS3) coupled to one another, which are arranged coaxially to the electric machine (EM), • wherein the first planetary gear set (PS1) has a first sun shaft (SO1), a first ring gear shaft (HR1) and a first carrier shaft (ST1) and is designed to unequally distribute a torque received from the electric machine (EM) between the first carrier shaft (ST1) and the first ring gear shaft (HR1), • wherein the second planetary gear set (PS2) has a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2), • wherein the third planetary gear set (PS3) comprises a third sun shaft (SO3), a third ring gear shaft (HR3) and a third carrier shaft (ST3) and is configured to align a torque and a direction of rotation of the third carrier shaft (ST3) with a torque and a direction of rotation of the second ring gear shaft (HR2), • wherein the first sun shaft (SO1) is connected to the electric machine (EM) via a drive shaft (1) in a rotationally fixed manner, • wherein the third carrier shaft (ST3) for driving the first wheel (R1) is connected in a rotationally fixed manner to a first output shaft (2), • wherein the second ring gear shaft (HR2) has an external toothing which meshes with a first spur gear (S1) and forms a first spur gear stage (SR1), wherein the first spur gear (S1) is connected to a second spur gear (S2) via at least one connecting shaft (W), wherein the second spur gear (S2) meshes with a third spur gear (S3) and forms a second spur gear stage (SR2), wherein the third spur gear (S3) is connected in a rotationally fixed manner to a second output shaft (3) for driving the second gear (R2). [5] Drive unit (100) according to claim 1, comprising exactly three planetary gear sets (PS1, PS2, PS3) coupled to one another, which are arranged coaxially to the electric machine (EM), • wherein the first planetary gear set (PS1) has a first sun shaft (SO1), a first ring gear shaft (HR1) and a first carrier shaft (ST1) and is designed to unequally distribute a torque received from the electric machine (EM) between the first carrier shaft (ST1) and the first ring gear shaft (HR1), • wherein the second planetary gear set (PS2) has a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2), • wherein the third planetary gear set (PS3) comprises a third sun shaft (SO3), a third ring gear shaft (HR3) and a third carrier shaft (ST3) and is configured to align a torque and a direction of rotation of the third carrier shaft (ST3) with a torque and a direction of rotation of the second ring gear shaft (HR2), • wherein the first sun shaft (SO1) is connected to the electric machine (EM) via a drive shaft (1) in a rotationally fixed manner, • wherein the second ring gear shaft (HR2) is connected in a rotationally fixed manner to a first output shaft (2) for driving the first wheel (R1), • wherein the third carrier shaft (ST3) is connected in a rotationally fixed manner to a first spur gear (S1), wherein the first spur gear (S1) meshes with a second spur gear (S2) and forms a first spur gear stage (SR1), wherein the second spur gear (S2) is connected to a third spur gear (S3) via at least one connecting shaft (W), wherein the third spur gear (S3) meshes with a fourth spur gear (S4) and forms a second spur gear stage (SR2), wherein the fourth spur gear (S4) is connected in a rotationally fixed manner to a second output shaft (3) for driving the second gear (R2). [6] Drive unit (100) according to claim 1, comprising exactly two planetary gear sets (PS1, PS2) coupled to one another, a third planetary gear set (PS3) designed as a wheel-end gear for arrangement within the first wheel (R1) of the vehicle axle and a fourth planetary gear set (PS4) designed as a wheel-end gear for arrangement within the second wheel (R2) of the vehicle axle, wherein the four planetary gear sets (PS1-PS4) are arranged coaxially to the electric machine (EM), • wherein the first planetary gear set (PS1) has a first sun shaft (SO1), a first ring gear shaft (HR1) and a first carrier shaft (ST1) and is designed to unequally distribute a torque received from the electric machine (EM) between the first carrier shaft (ST1) and the first ring gear shaft (HR1), • wherein the second planetary gear set (PS2) comprises a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2) and is configured to align a torque and a direction of rotation of the second ring gear shaft (HR2) with a torque and a direction of rotation of the first carrier shaft (ST1), • the third planetary gear set (PS3) has a third sun shaft (SO3), a third ring gear shaft (HR3) and a third carrier shaft (ST3), • the fourth planetary gear set (PS4) has a fourth sun shaft (SO4), a fourth ring gear shaft (HR4) and a fourth carrier shaft (ST4), • wherein the first sun shaft (SO1) is connected to the electric machine (EM) via a drive shaft (1) in a rotationally fixed manner, • wherein the first carrier shaft (ST1) is connected in a rotationally fixed manner to the third sun shaft (SO3) and the third carrier shaft (ST3) is connected in a rotationally fixed manner to a first output shaft (2) for driving the first wheel (R1), • wherein the second ring gear shaft (HR2) has external teeth which mesh with a first spur gear (S1) and form a first spur gear stage (SR1), wherein the first spur gear (S1) is connected to a second spur gear (SR2) via a connecting shaft (W), wherein the second spur gear (S2) meshes with a third spur gear (S3) and form a second spur gear stage (SR2), wherein the fourth sun shaft (SO4) is connected in a rotationally fixed manner to the third spur gear (S3) and the fourth web shaft (ST4) for driving the second gear (R2) is connected in a rotationally fixed manner to a second output shaft (3). [7] Drive unit (100) according to claim 1, comprising exactly two planetary gear sets (PS1, PS2) coupled to one another, a third planetary gear set (PS3) designed as a wheel-end gear for arrangement within a first wheel (R1) of the vehicle axle and a fourth planetary gear set (PS4) designed as a wheel-end gear for arrangement within a second wheel (R2) of the vehicle axle, wherein the four planetary gear sets (PS1-PS4) are arranged coaxially to the electric machine (EM), • wherein the first planetary gear set (PS1) has a first sun shaft (SO1), a first ring gear shaft (HR1) and a first carrier shaft (ST1) and is designed to unequally distribute a torque received from the electric machine (EM) between the first carrier shaft (ST1) and the first ring gear shaft (HR1), • wherein the second planetary gear set (PS2) comprises a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2) and is configured to align a torque and a direction of rotation of the second ring gear shaft (HR2) with a torque and a direction of rotation of the first carrier shaft (ST1), • the third planetary gear set (PS3) has a third sun shaft (SO3), a third ring gear shaft (HR3) and a third carrier shaft (ST3), • the fourth planetary gear set (PS4) has a fourth sun shaft (SO4), a fourth ring gear shaft (HR4) and a fourth carrier shaft (ST4), • wherein the first sun shaft (SO1) is connected to the electric machine (EM) via a drive shaft (1) in a rotationally fixed manner, • wherein the second ring gear shaft (HR2) is connected in a rotationally fixed manner to the third sun shaft (SO3) and the third web shaft (ST3) is connected in a rotationally fixed manner to a first output shaft (2) for driving the first wheel (R1), • wherein the first carrier shaft (ST1) is connected in a rotationally fixed manner to a first spur gear (S1), wherein the first spur gear (S1) meshes with a second spur gear (S2) and forms a first spur gear stage (SR1), wherein the second spur gear (S2) is connected via a connecting shaft (W) to a third spur gear (SR3), wherein the third spur gear (S3) meshes with a fourth spur gear (S4) and forms a second spur gear stage (SR2), wherein the fourth sun shaft (SO4) is connected in a rotationally fixed manner to the fourth spur gear (S4) and the fourth carrier shaft (ST4) is connected in a rotationally fixed manner to a second output shaft (3) for driving the second gear (R2). [8] Drive unit (100) according to one of the preceding claims, further comprising a clutch (DS) designed as a differential lock. [9] Drive unit (100) according to claim 1, comprising exactly one first planetary gear set (PS1), a second planetary gear set (PS2) designed as a wheel-end gear for arrangement within a first wheel (R1) of the vehicle axle and a third planetary gear set (PS3) designed as a wheel-end gear for arrangement within a second wheel (R2) of the vehicle axle, wherein the three planetary gear sets (PS1-PS3) are arranged coaxially to the electric machine (EM), • wherein the first planetary gear set (PS1) has a first sun shaft (SO1), a first ring gear shaft (HR1) and a first carrier shaft (ST1) and is designed to unequally distribute a torque received from the electric machine (EM) between the first carrier shaft (ST1) and the first ring gear shaft (HR1), • wherein the second planetary gear set (PS2) has a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2), • the third planetary gear set (PS3) has a third sun shaft (SO3), a third ring gear shaft (HR3) and a third carrier shaft (ST3), • wherein the first sun shaft (SO1) is connected to the electric machine (EM) via a drive shaft (1) in a rotationally fixed manner, • wherein the first carrier shaft (ST1) is connected in a rotationally fixed manner to the second sun shaft (SO2) and the second carrier shaft (ST2) is connected in a rotationally fixed manner to a first output shaft (2) for driving the first wheel (R1), • wherein the first ring gear shaft (HR1) has external teeth which mesh with a first spur gear (S1) and form a first spur gear stage (SR1), wherein the first spur gear (S1) is connected to a second spur gear (S2) via a connecting shaft (W), wherein the second spur gear (S2) meshes with a third spur gear (S3) and form a second spur gear stage (SR2), wherein the third spur gear (S3) meshes with a fourth spur gear (S4) and form a third spur gear stage (SR3), wherein the third sun shaft (SO3) is connected in a rotationally fixed manner to the fourth spur gear (S4) and the third web shaft (ST3) is connected in a rotationally fixed manner to a second output shaft (3) for driving the second gear (R2). [10] Drive unit (100) according to claim 1, comprising exactly one first planetary gear set (PS1), a second planetary gear set (PS2) designed as a wheel-end gear for arrangement within a first wheel (R1) of the vehicle axle and a third planetary gear set (PS3) designed as a wheel-end gear for arrangement within a second wheel (R2) of the vehicle axle, wherein the three planetary gear sets (PS1-PS3) are arranged coaxially to the electric machine (EM), • wherein the first planetary gear set (PS1) has a first sun shaft (SO1), a first ring gear shaft (HR1) and a first carrier shaft (ST1) and is designed to unequally distribute a torque received from the electric machine (EM) between the first carrier shaft (ST1) and the first ring gear shaft (HR1), • wherein the second planetary gear set (PS2) has a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2), • the third planetary gear set (PS3) has a third sun shaft (SO3), a third ring gear shaft (HR3) and a third carrier shaft (ST3), • wherein the first sun shaft (SO1) is connected to the electric machine (EM) via a drive shaft (1) in a rotationally fixed manner, • wherein the first ring gear shaft (HR1) is connected in a rotationally fixed manner to the second sun shaft (SO2) and the second web shaft (ST2) is connected in a rotationally fixed manner to a first output shaft (2) for driving the first wheel (R1), • wherein the first carrier shaft (ST1) is connected in a rotationally fixed manner to a first spur gear (S1), wherein the first spur gear (S1) meshes with a second spur gear (S2) and forms a first spur gear stage (SR1), wherein the second spur gear (S2) is connected to a third spur gear (SR3) via a connecting shaft (W), wherein the third spur gear (S3) meshes with a fourth spur gear (S4) and forms a second spur gear stage (SR2), wherein the fourth spur gear (S4) meshes with a fifth spur gear (S5) and forms a third spur gear stage (SR3), wherein the third sun shaft (SO3) is connected in a rotationally fixed manner to the fifth spur gear (S5) and the third carrier shaft (ST3) is connected in a rotationally fixed manner to a second output shaft (3) for driving the second gear (R2). [11] Drive unit (100) according to claim 1, comprising exactly one first planetary gear set (PS1) and a second planetary gear set (PS2) designed as a wheel head gear for arrangement within a first wheel (R1) of the vehicle axle, wherein the two planetary gear sets (PS1, PS2) are arranged coaxially to the electric machine (EM), • wherein the first planetary gear set (PS1) has a first sun shaft (SO1), a first ring gear shaft (HR1) and a first carrier shaft (ST1) and is designed to unequally distribute a torque received from the electric machine (EM) between the first carrier shaft (ST1) and the first ring gear shaft (HR1), • wherein the second planetary gear set (PS2) has a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2), • wherein the first sun shaft (SO1) is connected to the electric machine (EM) via a drive shaft (1) in a rotationally fixed manner, • wherein the first carrier shaft (ST1) is connected in a rotationally fixed manner to the second sun shaft (SO2) and the second carrier shaft (ST2) is connected in a rotationally fixed manner to a first output shaft (2) for driving the first wheel (R1), • wherein the first ring gear shaft (HR1) has external teeth which mesh with a first spur gear (S1) and form a first spur gear stage (SR1), wherein the first spur gear (S1) is connected to a second spur gear (S2) via a connecting shaft (W), wherein the second spur gear (S2) meshes with a third spur gear (S3) and form a second spur gear stage (SR2), wherein the third spur gear (S3) meshes with a fourth spur gear (S4) and form a third spur gear stage (SR3), wherein the fourth spur gear (S4) is connected in a rotationally fixed manner to a second output shaft (3) for driving the second gear (R2). [12] Drive unit (100) according to claim 1, comprising exactly one electric machine (EM), a first planetary gear set (PS1) and a second planetary gear set (PS2) designed as a wheel head gear for arrangement within a first wheel (R1) of the vehicle axle, wherein the two planetary gear sets (PS1, PS2) are arranged coaxially to the electric machine (EM), • wherein the first planetary gear set (PS1) has a first sun shaft (SO1), a first ring gear shaft (HR1) and a first carrier shaft (ST1) and is designed to unequally distribute a torque received from the electric machine (EM) between the first carrier shaft (ST1) and the first ring gear shaft (HR1), • wherein the second planetary gear set (PS2) has a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2), • wherein the first sun shaft (SO1) is connected to the electric machine (EM) via a drive shaft (1) in a rotationally fixed manner, • wherein the first ring gear shaft (HR1) is connected in a rotationally fixed manner to the second sun shaft (SO2) and the second web shaft (ST2) is connected in a rotationally fixed manner to a first output shaft (2) for driving the first wheel (R1), • wherein the first carrier shaft (ST1) is connected in a rotationally fixed manner to a first spur gear (S1), wherein the first spur gear (S1) meshes with a second spur gear (S2) and forms a first spur gear stage (SR1), wherein the second spur gear (S2) is connected to a third spur gear (S3) via a connecting shaft (W), wherein the third spur gear (S3) meshes with a fourth spur gear (S4) and forms a second spur gear stage (SR2), wherein the fourth spur gear (S4) meshes with a fifth spur gear (S5) and forms a third spur gear stage (SR3), wherein the fifth spur gear (S5) is connected in a rotationally fixed manner to a second output shaft (3) for driving the second gear (R2). [13] Drive unit (100) according to one of the preceding claims, wherein the connecting shaft (W) is adapted to connect a first section of the drive unit (100) to a second section of the drive unit (100), wherein a space (4) for accommodating passengers and / or cargo is arranged axially between the two sections of the drive unit (100). [14] Drive unit (100) according to one of the preceding claims, wherein the connecting shaft (W) is designed as a rigid shaft or a cardan shaft. [15] Vehicle with a drive unit (100) according to one of the preceding claims.

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