Drive unit for one vehicle axle

Abstract

Drive unit (100) for a vehicle axle with a first wheel (R1) and a second wheel (R2), comprising an electric machine (EM) and a gearbox with exactly three planetary sets (PS1, PS2, PS3) arranged coaxially to the electric machine (EM), • wherein the first planetary set (PS1) has a first sun gear shaft (SO1), a first ring gear shaft (HR1) and a first bridge shaft (ST1) and is configured as a pre-reduction gear, • wherein the second planetary gear set (PS2) has a second sun shaft (SO2), a second ring gear shaft (HR2) and a second bridge shaft (ST2) and is designed to distribute a torque received from the first planetary gear set (PS1) unequally between the second bridge shaft (ST2) and the second ring gear shaft (HR2), • wherein the third planetary set (PS3) has a third sun shaft (SO3), a third ring gear shaft (HR3) and a third bridge shaft (ST3) and is arranged to match a torque and direction of rotation of the third ring gear shaft (HR3) to a torque and direction of rotation of the second bridge shaft (ST2), • wherein the first solar wave (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) for driving the first wheel (R1) is non-rotatably connected to a first output shaft (2), • wherein the second spur shaft (ST2) is non-rotatably 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), wherein the second spur gear (S2) is connected via at least one connecting shaft (W) arranged axially parallel to the electric machine (EM) to a third spur gear (S3), 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 non-rotatably connected to a second output shaft (3) for driving the second gear (R2).

Description

[0001] The invention relates to a drive unit for a vehicle axle, wherein the drive unit comprises 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 comprises a drive machine designed as a transverse flux machine, comprising at least one rotor and one stator; the transverse flux machine is associated with at least two wheels arranged on a common geometric axis. Furthermore, the transverse flux machine is associated with a device for distributing and transmitting power to the two wheels, wherein the device for distributing and transmitting 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] Furthermore, the publications DE 10 2021 208 545 A1, DE 10 2013 210 312 A1, DE 10 2013 215 879 A1, DE 10 2013 218 502 A1 and DE 10 2021 115 680 A1 disclose further drive units for vehicles.

[0004] The object of the present invention is to provide an alternative drive unit for a vehicle, wherein the drive unit is to be particularly compact and energy-efficient. This object is achieved by a respective drive unit with the features of the independent claims. Advantageous embodiments are the subject of the dependent claims, the following description, and the figures.

[0005] A drive unit according to the invention for a vehicle axle with a first wheel and a second wheel comprises an electric motor and a transmission with at least two planetary gear sets arranged coaxially to the electric motor, as well as a connecting shaft arranged parallel to the axis of the electric motor and configured for connecting the second wheel, wherein one of the two planetary gear sets is configured for the unequal distribution of a torque supplied by the electric motor via a sun gear shaft of that planetary gear set to a splined shaft and a ring gear shaft of that planetary gear set. Thus, the transmission implements a differential function and distributes the drive torque of the electric motor unequally to the splined shaft and the ring gear shaft of the planetary gear set configured for the unequal distribution of the drive torque.The drive torque is transmitted to the differential via the solar shaft of the planetary gear set, which is designed for unequal distribution of the drive torque. The drive axle is designed as an electric drive axle and is intended for the electric propulsion of the vehicle.

[0006] According to a non-inventive embodiment, the drive unit comprises exactly three interconnected planetary sets arranged coaxially to the electric machine, • wherein the first planetary set comprises a first sun gear shaft, a first ring gear shaft and a first bridge shaft and is configured as a pre-reduction gear, • wherein the second planetary set has a second sun shaft, a second ring gear shaft and a second bridge shaft and is designed to distribute a torque received from the first planetary set unequally between the second bridge shaft and the second ring gear, • wherein the third planetary set comprises a third sun shaft, a third ring gear shaft and a third bridge shaft and is arranged to match a torque and direction of rotation of the third ring gear shaft to a torque and direction of rotation of the second bridge shaft, • where the first solar wave is set up to connect the electric machine, • wherein the second axle shaft is designed to drive the first wheel of the vehicle axle, • wherein the third 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 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 non-rotatably connected to a second output shaft for driving the second wheel of the vehicle axle.

[0007] For this purpose, reference is made to the embodiments according to Fig. 1 and Fig. 2 and the corresponding character description are referenced.

[0008] Thus, the first wheel is driven via the second shaft, and the second wheel is driven via the third ring gear and the spur gear chain with the connecting shaft between them. The first planetary gear set serves as a reduction gear. 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. The second planetary gear set is connected to the first planetary gear set, and also to the third planetary gear set, as well as at least indirectly to the first output shaft, which can be understood as the first differential output shaft. The third planetary gear set is also connected, at least indirectly, to the second output shaft, which can be understood as the second differential output shaft, and is further supported by 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 divided between the two differential output shafts in a defined ratio.

[0009] The integral differential, when the differential output shafts have identical output speeds, does not have gears that rotate within a block or without rolling motion. Therefore, regardless of the output shaft speeds, the components of the integral differential that mesh with each other always exhibit relative motion. With an integral differential, the sums of the torques from both wheels are not combined or summarized into a single axle torque within a single component. Instead, the drive power is divided within the integral differential and transmitted to the corresponding differential output shafts according to the design of its two planetary gear sets. This allows the components of the integral differential to be designed more compactly due to the comparatively low torque of each individual shaft. Furthermore, this results in a reduction in the number of components and a weight saving.Using such an integral differential, the two functions of torque conversion and torque distribution, which are usually handled by two separate components, can be represented by a single integral component. The integral differential is thus a combined transmission and differential gear that performs both torque conversion and torque distribution to the differential output shafts. Furthermore, the first planetary gear set provides a pre-transmission of the torque fed into the integral differential.

[0010] The first spur gear stage has a gear ratio of iG1 and connects the third ring gear shaft to the connecting shaft. The connecting shaft can be a rigid shaft or a cardan shaft, for example. 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 rotational speeds and torques at both gears of the drive axle. The input shaft and the two output shafts are arranged on a common axis of rotation with the electric motor, with the connecting shaft running parallel to this axis.

[0011] For the purposes of this invention, a "shaft" is understood to be a rotatable component of the transmission by which the respective components of the transmission are connected to one another in a rotationally fixed manner, or by which such a connection can be established when one of the switching elements is actuated. The shaft can connect the components axially or radially, or both. The shaft can also serve as an intermediate piece by which a component is connected, for example, radially. The term "shaft" does not preclude the possibility that the components to be connected may be manufactured as a single piece. In particular, two or more shafts connected in a rotationally fixed manner can be manufactured as a single piece.

[0012] The input shaft is configured to connect the electric motor to the gearbox. 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 splined shaft is non-rotatably connected to the first output shaft, and the third spur gear is non-rotatably connected to the second output shaft.

[0013] According to an embodiment of the invention, the drive unit comprises exactly three interconnected planetary sets, which are arranged coaxially to the electric machine, • wherein the first planetary set comprises a first sun gear shaft, a first ring gear shaft and a first bridge shaft and is configured as a pre-reduction gear, • wherein the second planetary set has a second sun shaft, a second ring gear shaft and a second bridge shaft and is designed to distribute a torque received from the first planetary set unequally between the second bridge shaft and the second ring gear, • wherein the third planetary set comprises a third sun shaft, a third ring gear shaft and a third bridge shaft and is arranged to match a torque and direction of rotation of the third ring gear shaft to a torque and direction of rotation of the second bridge shaft, • wherein the first solar wave is connected to the electric machine via a drive shaft in a rotationally fixed manner, • wherein the third ring gear shaft for driving the first wheel is non-rotatably connected to a first output shaft, • wherein the second web shaft is non-rotatably connected 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 non-rotatably connected to a second output shaft for driving the second gear.

[0014] For this purpose, reference is made to the embodiment according to Fig. Reference is made to Figure 3 and the corresponding figure description. In this embodiment as well, the second and third planetary gear sets form an integral differential. The output from the integral differential towards the second wheel passes through the electric motor. This allows for advantages in the arrangement of the transmission components.

[0015] According to a further embodiment not in accordance with the invention, the drive unit comprises exactly three interconnected planetary sets, which are arranged coaxially to the electric machine, • wherein the first planetary set comprises a first sun shaft, a first ring gear shaft and a first bridge shaft and is arranged to distribute a torque supplied by the electric machine unequally between the first bridge shaft and the first ring gear shaft, • wherein the second planetary set has a second sun shaft, a second ring gear shaft and a second bridge shaft, • wherein the third planetary set comprises a third sun shaft, a third ring gear shaft and a third bridge shaft and is arranged to match a torque and direction of rotation of the third bridge shaft to a torque and direction of rotation of the second ring gear shaft, • wherein the first solar wave is connected to the electric machine via a drive shaft in a rotationally fixed manner, • wherein the third web shaft for driving the first wheel is non-rotatably connected to a first output shaft, • wherein the second 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 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 non-rotatably connected to a second output shaft for driving the second gear.

[0016] For this purpose, reference is made to the embodiment according to Fig. Reference is made to Figure 4 and the corresponding figure description. In this embodiment as well, the second and third planetary gear sets form an integral differential. In this embodiment, no explicit pre-transmission is provided, with the overall transmission ratio being generated by the three planetary gear sets. Efficiency advantages may result from the torques and rotational speeds in the planetary gear sets.

[0017] According to a further embodiment of the invention, the drive unit comprises exactly three interconnected planetary sets, which are arranged coaxially to the electric machine, • wherein the first planetary set comprises a first sun shaft, a first ring gear shaft and a first bridge shaft and is arranged to distribute a torque supplied by the electric machine unequally between the first bridge shaft and the first ring gear shaft, • wherein the second planetary set has a second sun shaft, a second ring gear shaft and a second bridge shaft, • wherein the third planetary set comprises a third sun shaft, a third ring gear shaft and a third bridge shaft and is arranged to match a torque and direction of rotation of the third bridge shaft to a torque and direction of rotation of the second ring gear shaft, • wherein the first solar wave is connected to the electric machine via a drive shaft in a rotationally fixed manner, • wherein the second ring gear shaft for driving the first wheel is non-rotatably connected to a first output shaft, • wherein the third web shaft is non-rotatably connected 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 non-rotatably connected to a second output shaft for driving the second gear.

[0018] For this purpose, reference is made to the embodiment according to Fig. Reference is made to Figure 5 and the corresponding figure description. In this embodiment as well, the second and third planetary gear sets form an integral differential. In this embodiment, no explicit pre-reduction gear is provided, with the overall gear ratio being generated by the three planetary gear sets. Efficiency advantages can result from the torques and speeds in the planetary gear sets. The output from the integral differential towards the second wheel passes through the electric motor. This allows for advantages in the arrangement of the transmission components.

[0019] According to a further embodiment not in accordance with the invention, the drive unit comprises exactly two coupled planetary sets, a third planetary set designed as a wheel head gear for arrangement within the first wheel of the vehicle axle, and a fourth planetary set designed as a wheel head gear for arrangement within the second wheel of the vehicle axle, wherein the four planetary sets are arranged coaxially to the electric machine. • wherein the first planetary set comprises a first sun shaft, a first ring gear shaft and a first bridge shaft and is arranged to distribute a torque supplied by the electric machine unequally between the first bridge shaft and the first ring gear shaft, • wherein the second planetary set comprises a second sun shaft, a second ring gear shaft and a second bridge shaft and is arranged to match a torque and direction of rotation of the second ring gear shaft to a torque and direction of rotation of the first bridge shaft, • wherein the third planetary set has a third sun shaft, a third ring gear shaft and a third bridge shaft, • wherein the fourth planetary set includes a fourth solar shaft, a fourth ring gear shaft and a fourth bridge shaft, • wherein the first solar wave is connected to the electric machine via a drive shaft in a rotationally fixed manner, • wherein the first web shaft is non-rotatably connected to the third sun shaft and the third web shaft is non-rotatably connected to a first output shaft for driving the first wheel, • wherein the second 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 forms a second spur gear stage, wherein the fourth sun shaft is non-rotatably connected to the third spur gear and the fourth web shaft for driving the second gear is non-rotatably connected to a second output shaft.

[0020] For this purpose, reference is made to the embodiment according to Fig. Reference is made to Figure 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 hubs, a lower gear ratio is required in the differential. This results in particular space savings.

[0021] According to a further embodiment of the invention, the drive unit comprises exactly two coupled planetary sets, a third planetary set designed as a wheel head gear for arrangement within a first wheel of the vehicle axle, and a fourth planetary set designed as a wheel head gear for arrangement within a second wheel of the vehicle axle, wherein the four planetary sets are arranged coaxially to the electric machine. • wherein the first planetary set comprises a first sun shaft, a first ring gear shaft and a first bridge shaft and is arranged to distribute a torque supplied by the electric machine unequally between the first bridge shaft and the first ring gear shaft, • wherein the second planetary set comprises a second sun shaft, a second ring gear shaft and a second bridge shaft and is arranged to match a torque and direction of rotation of the second ring gear shaft to a torque and direction of rotation of the first bridge shaft, • wherein the third planetary set has a third sun shaft, a third ring gear shaft and a third bridge shaft, • wherein the fourth planetary set includes a fourth solar shaft, a fourth ring gear shaft and a fourth bridge shaft, • wherein the first solar wave is connected to the electric machine via a drive shaft in a rotationally fixed manner, • wherein the second ring gear shaft is non-rotatably connected to the third sun gear shaft and the third web shaft is non-rotatably connected to a first output shaft for driving the first gear, • wherein the first web shaft is non-rotatably connected 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 sun shaft is non-rotatably connected to the fourth spur gear and the fourth web shaft is non-rotatably connected to a second output shaft for driving the second gear.

[0022] For this purpose, reference is made to the embodiment according to Fig. Reference is made to Figure 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 hubs, a lower gear ratio is required in the differential. This results in particular space savings.

[0023] Preferably, one of the aforementioned drive units has a coupling designed as a differential lock. Such a coupling is to be understood as a switching element, i.e., a switchable device, which, in a closed state, connects two shafts in a rotationally fixed manner and, in an open state, decouples the two shafts from each other. In the decoupled state, the two shafts can rotate relative to each other. For example, the differential lock connects the third ring gear shaft to the second carrier shaft to deactivate the differential function. For example, the differential lock connects the third carrier shaft to the second ring gear shaft to deactivate the differential function. For example, the differential lock connects the second ring gear shaft to the first carrier shaft to deactivate the differential function.

[0024] According to a further embodiment of the invention, the drive unit comprises exactly a first planetary gear set, a second planetary gear set designed as a wheel head gear set for arrangement within a first wheel of the vehicle axle, and a third planetary gear set designed as a wheel head gear set 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 set comprises a first sun shaft, a first ring gear shaft and a first bridge shaft and is arranged to distribute a torque supplied by the electric machine unequally between the first bridge shaft and the first ring gear shaft, • wherein the second planetary set has a second sun shaft, a second ring gear shaft and a second bridge shaft, • wherein the third planetary set has a third sun shaft, a third ring gear shaft and a third bridge shaft, • wherein the first solar wave is connected to the electric machine via a drive shaft in a rotationally fixed manner, • wherein the first web shaft is non-rotatably connected to the second sun shaft and the second web shaft is non-rotatably connected 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 forms a second spur gear stage, wherein the third spur gear meshes with a fourth spur gear and forms a third spur gear stage, wherein the third sun shaft is non-rotatably connected to the fourth spur gear and the third web shaft for driving the second gear is non-rotatably connected to a second output shaft.

[0025] For this purpose, reference is made to the embodiment according to Fig. Reference is made to Figure 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 not aligned with the torque and direction of rotation of the first output shaft via planetary gear sets, but rather via the spur gear chain, in particular via the three spur gear stages.

[0026] According to a further embodiment of the invention, the drive unit comprises exactly a first planetary gear set, a second planetary gear set designed as a wheel head gear set for arrangement within a first wheel of the vehicle axle, and a third planetary gear set designed as a wheel head gear set 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 set comprises a first sun shaft, a first ring gear shaft and a first bridge shaft and is arranged to distribute a torque supplied by the electric machine unequally between the first bridge shaft and the first ring gear shaft, • wherein the second planetary set has a second sun shaft, a second ring gear shaft and a second bridge shaft, • wherein the third planetary set has a third sun shaft, a third ring gear shaft and a third bridge shaft, • wherein the first solar wave is connected to the electric machine via a drive shaft in a rotationally fixed manner, • wherein the first ring gear shaft is non-rotatably connected to the second sun gear shaft and the second web shaft for driving the first gear is non-rotatably connected to a first output shaft, • wherein the first web shaft is non-rotatably connected 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 non-rotatably connected to the fifth spur gear and the third web shaft is non-rotatably connected to a second output shaft for driving the second gear.

[0027] For this purpose, reference is made to the embodiment according to Fig. Reference is made to Figure 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 not aligned with the torque and direction of rotation of the first output shaft via planetary gear sets, but rather via the spur gear chain, in particular via the three spur gear stages.

[0028] According to a further embodiment of the invention, the drive unit comprises exactly a first planetary gear set and a second planetary gear set designed as a wheel head gear set 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 set comprises a first sun shaft, a first ring gear shaft and a first bridge shaft and is arranged to distribute a torque supplied by the electric machine unequally between the first bridge shaft and the first ring gear shaft, • wherein the second planetary set has a second sun shaft, a second ring gear shaft and a second bridge shaft, • wherein the first solar wave is connected to the electric machine via a drive shaft in a rotationally fixed manner, • wherein the first web shaft is non-rotatably connected to the second sun shaft and the second web shaft is non-rotatably connected 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 forms a second spur gear stage, wherein the third spur gear meshes with a fourth spur gear and forms a third spur gear stage, wherein the fourth spur gear is non-rotatably connected to a second output shaft for driving the second gear.

[0029] For this purpose, reference is made to the embodiment according to Fig. Reference is made to Figure 10 and the corresponding figure description. The spur gear chain with the three spur gear stages generates such a high gear ratio that the wheel head gear in the second wheel can be omitted. This can result in efficiency gains and cost reductions.

[0030] According to a further embodiment of the invention, 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 set comprises a first sun shaft, a first ring gear shaft and a first bridge shaft and is arranged to distribute a torque supplied by the electric machine unequally between the first bridge shaft and the first ring gear shaft, • wherein the second planetary set has a second sun shaft, a second ring gear shaft and a second bridge shaft, • wherein the first solar wave is connected to the electric machine via a drive shaft in a rotationally fixed manner, • wherein the first ring gear shaft is non-rotatably connected to the second sun gear shaft and the second web shaft for driving the first gear is non-rotatably connected to a first output shaft, • wherein the first web shaft is non-rotatably connected 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 fifth spur gear is non-rotatably connected to a second output shaft for driving the second gear.

[0031] For this purpose, reference is made to the embodiment according to Fig. Reference is made to Figure 11 and the corresponding figure description. The spur gear chain with the three spur gear stages generates such a high gear ratio that the wheel head gear in the second wheel can be omitted. This can result in efficiency gains and cost reductions.

[0032] Preferably, the connecting shaft is configured to connect a first section of the drive unit with a second section of the drive unit, with a space for accommodating passengers and / or cargo 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. The connection between the two axle sides of the drive unit is therefore achieved either via a cardan shaft or a rigid shaft. Several shafts can also be connected together in a rotationally fixed manner or as a single unit to form the connecting shaft.

[0033] A vehicle according to the invention comprises at least one drive unit according to the invention. The above definitions, as well as descriptions of the 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.

[0034] Advantageous embodiments are shown in the drawings, where identical or similar elements are designated with the same reference numeral. They show: Fig. 1 a highly abstracted schematic view of a drive unit not according to the invention, according to a first embodiment; Fig. 2 a highly abstracted schematic view of a drive unit not according to the invention, according to a second embodiment; Fig. 3 a highly abstracted schematic view of a drive unit according to a first embodiment of the invention; Fig. 4 a highly abstracted schematic view of a drive unit not according to the invention, according to a third embodiment; Fig. 5 a highly abstracted schematic view of a drive unit according to a second embodiment of the invention; Fig. 6 a highly abstracted schematic view of a drive unit not according to the invention, according to a fourth embodiment; Fig. 7 a highly abstracted schematic view of a drive unit according to a third embodiment of the invention; Fig. 8 a highly abstracted schematic view of a drive unit according to a fourth embodiment of the invention; Fig. 9 a highly abstracted schematic view of a drive unit according to the invention in a fifth embodiment; Fig. 10 a highly abstracted schematic view of a drive unit according to a sixth embodiment according to the invention; Fig. 11 a highly abstracted schematic view of a drive unit according to the invention in a seventh embodiment and Fig. 12 a highly abstracted schematic view of a vehicle with a drive unit according to the invention.

[0035] According to Fig. 1 to Fig. Section 11 comprises a drive unit 100 for a vehicle axle with a first wheel R1 and a second wheel R2, a single electric machine EM with a housing-mounted stator EMS and a rotatable rotor EMR, and a gearbox. The gearbox implements a differential function and distributes the drive torque of the electric machine EM unequally between a splined shaft and a ring gear shaft of a planetary gear set. Thus, the sun gear shaft of the planetary gear set, which is designed for the unequal distribution of the drive torque, always serves to introduce the drive torque into the differential. The drive axle is therefore designed as an electric drive axle and intended for the electric propulsion of the vehicle.A connecting shaft W is arranged to connect a first section of the respective drive unit 100 with 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.

[0036] According to Fig. The gearbox comprises exactly three interconnected planetary gear sets PS1, PS2, and PS3, arranged coaxially with the electric machine EM. The first planetary gear set, PS1, includes three shafts: a first sun gear 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 gear shaft SO1 and the first ring gear shaft HR1. The second planetary gear set, PS2, also includes three shafts: a second sun gear 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 gear shaft SO2 and the second ring gear shaft HR2. The third planetary gear set, PS3, also includes three shafts: a third sun gear shaft SO3, a third ring gear shaft HR3, and a third carrier shaft ST3.The third shaft ST3 carries several planet gears that mesh with the third sun gear SO3 and the third ring gear 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.

[0037] The first solar shaft SO1 is configured to connect the electric machine EM. In this configuration, the first solar shaft SO1 is non-rotatably connected to the rotor EMR of the electric machine EM via a drive shaft 1 and can therefore be driven by the electric machine EM. The first connecting shaft ST1 is non-rotatably connected to the second solar shaft SO2. The first ring gear shaft HR1 and the third connecting shaft ST3 are non-rotatably connected to a stationary component designed as a housing G and are thus prevented from rotating. The second connecting shaft ST2 is non-rotatably connected to a first output shaft 2. The first output shaft 2 is non-rotatably connected to the first wheel R1 of the vehicle axle. Therefore, the second connecting shaft ST2 is non-rotatably connected to the first wheel R1 of the vehicle axle. The second ring gear shaft HR2 is non-rotatably connected to the third solar shaft SO3.

[0038] The first planetary gear set PS1 is configured as a pre-transmission. The second planetary gear set PS2 is configured to unequally distribute a torque received from the electric machine EM via the first planetary gear set PS1 to the second splined 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 splined shaft ST2, thus making the torque and direction of rotation at the third ring gear shaft HR3 and the second splined shaft ST2 identical. Therefore, the second planetary gear set PS2 and the third planetary gear set PS3 form an integral differential.

[0039] The second wheel R2 of the vehicle axle is effectively connected to the third ring gear shaft HR3. For this purpose, the third ring gear shaft HR3 has external teeth. Thus, the third ring gear shaft HR3 has internal teeth on its inner circumferential surface and external teeth on its outer circumferential surface. In the torque path between the third ring gear shaft HR3 and the second wheel R2, a first spur gear stage SR1, a second spur gear stage SR2, and a connecting shaft W are arranged. The connecting shaft W is designed to effectively connect a first section of the drive unit to a second section of the drive unit, with a space 4 for accommodating passengers arranged axially between the two sections of the drive unit. Thus, the connecting shaft W bridges this unobstructed space 4. In this case, the connecting shaft W is designed as a cardan shaft.

[0040] 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 S3 is non-rotatably connected to the second wheel R2 of the vehicle axle via a second output shaft S3. Furthermore, the drive unit includes a clutch DS designed as a differential lock. In its engaged state, the clutch DS non-rotatably connects the third ring gear shaft HR3 to the second connecting shaft ST2 to lock the differential and thus disengage the differential function according to an actuating command.

[0041] The spur gear ratio of the first spur gear stage SR1 serves to connect the third ring gear shaft HR3 to the cardan shaft, wherein 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, wherein 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, so that identical speeds and identical torques are obtained at both wheels R1, R2.

[0042] Fig. Figure 2 shows a second embodiment of a drive unit 100 not according to the invention. The drive unit 100 according to Fig. 2 essentially corresponds to drive unit 100 according to Fig. 1, the difference between these two embodiments being the design of the connecting shaft W. In the present embodiment, 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, which is designed as a cardan shaft, and the rigid connection of the first and second spur gears S1, S2 via the connecting shaft W, which is designed as a rigid shaft, are rotationally fixed connections intended to bridge 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 either a cardan shaft or a rigid shaft. Otherwise, the embodiment corresponds to the following. Fig. 2 according to the exemplary embodiment Fig. 1, which is referred to.

[0043] Fig. Figure 3 shows a first embodiment of a drive unit 100 according to the invention. The drive unit 100 according to Fig. 3 essentially corresponds to drive unit 100 according to Fig. 2, the difference between these two embodiments being the connection of the second and third planetary sets PS2 and PS3. In the present case, the connecting shaft W is as shown in Fig. 2, designed as a rigid shaft and can alternatively be designed as a cardan shaft.

[0044] The first planetary gear set PS1 is configured as a pre-transmission, wherein the second planetary gear set PS2 is configured to distribute a torque received from the first planetary gear set PS1 unequally to the second web shaft ST2 and the second ring gear shaft HR2, wherein the third planetary gear set PS3 is configured to match a torque and direction of rotation of the third ring gear shaft HR3 to a torque and direction of rotation of the second web shaft ST2.

[0045] The third ring gear shaft HR3 is configured 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 second connecting shaft ST2 is configured 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 arranged in the torque path between the second connecting shaft ST2 and the second wheel R2. The second connecting shaft ST2 is rotationally fixed to a first spur gear S1. The second connecting shaft ST2, or a shaft rotationally fixed to it, extends axially through the electric machine EM and the first and second planetary gear sets PS1 and 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, forming a second spur gear stage SR2. The unobstructed space 4 is arranged axially between the two spur gear stages SR1 and SR2. The fourth spur gear S4 is rotationally fixed to the second output shaft 3 and is configured to drive the second wheel R2 of the vehicle axle. Otherwise, the embodiment corresponds to the following. Fig. 3 according to the exemplary embodiment Fig. 2, which is referenced.

[0046] Fig. Figure 4 shows a third embodiment of a drive unit 100 not according to the invention. The drive unit 100 according to Fig. 4 essentially corresponds to drive unit 100 according to Fig. 1, wherein a difference between these two embodiments lies in the connection of the three planetary sets PS1, PS2, PS3. In the present case, the connecting shaft W is as shown in Fig. 1. The first planetary gear set, PS1, is designed as a cardan shaft and can alternatively be designed as a rigid shaft. It is configured to unequally distribute a torque input from the electric machine, EM, between the first splined shaft, ST1, and the first ring gear shaft, HR1. The third planetary gear set, PS3, is configured to align the torque and direction of rotation of the third splined shaft, ST3, with the torque and direction of rotation of the second ring gear shaft, HR2. The first ring gear shaft, HR1, is non-rotatably connected to the third sun gear shaft, SO3. The first splined shaft, ST1, is non-rotatably connected to the second sun gear shaft, SO2. The second splined shaft, ST2, and the third ring gear shaft, HR3, are non-rotatably connected. The third splined shaft, ST3, is configured to drive the first wheel, R1, of the vehicle axle and is therefore non-rotatably connected to the first wheel, R1, via the first output shaft, 2.The second ring gear shaft HR2 has external teeth and is designed to drive the second wheel R2 of the vehicle axle, with the torque flow between the second ring gear shaft HR2 and the second wheel R2 as shown in . Fig. 1, the first spur gear stage SR1, the second spur gear stage SR2, and the connecting shaft W are arranged. Furthermore, in a closed state, the coupling DS connects the second ring gear shaft HR2 to the third web shaft ST3 in a rotationally fixed manner to lock the differential and thus disable the differential function according to an actuating command. Therefore, in this embodiment, no explicit pre-reduction is provided, with the overall gear ratio being generated by the three planetary gear sets PS1, PS2, and PS3. Efficiency advantages may result from the prevailing torques and speeds in the planetary gear sets PS1, PS2, and PS3. Otherwise, the embodiment corresponds to the above. Fig. 4 according to the exemplary embodiment Fig. 1, which is referred to.

[0047] Fig. Figure 5 shows a second embodiment of a drive unit 100 according to the invention. The drive unit 100 according to Fig. 5 essentially corresponds to drive unit 100 according to Fig. 4, wherein a difference between these two embodiments lies in the connection of the second and third planetary sets PS2 and PS3. Furthermore, the connecting shaft W is as shown in Fig. 2, designed as a rigid shaft and can alternatively be designed as a cardan shaft. The first planetary gear set PS1 is configured to unequally distribute a torque input from the electric machine EM to the first splined shaft ST1 and the first ring gear shaft HR1, wherein the third planetary gear set PS3 is configured to match the torque and direction of rotation of the third splined shaft ST3 to the torque and direction of rotation of the second ring gear shaft HR2. The second ring gear shaft HR2 is configured to drive the first wheel R1 of the vehicle axle and is therefore non-rotatably connected to the first wheel R1 via the first output shaft 2. The third splined shaft ST3 is configured to drive the second wheel R2 of the vehicle axle, wherein the torque flow between the third splined shaft ST3 and the second wheel R2 is as shown 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 corresponds to the following. Fig. 5 according to the exemplary embodiment Fig. 4, which is referenced.

[0048] Fig. Figure 6 shows a fourth embodiment of a drive unit 100 not according to the invention. The drive unit 100 according to Fig. Assembly 6 comprises two coupled planetary gear sets PS1 and PS2, a third planetary gear set PS3 designed as a wheel-head gear for arrangement within the first wheel R1 of the vehicle axle, and a fourth planetary gear set PS4 designed as a wheel-head gear for arrangement within the second wheel R2 of the vehicle axle. The four planetary gear sets PS1-PS4 are arranged coaxially with the electric machine EM.

[0049] The first planetary gear set PS1 comprises three shafts: a first sun gear 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 gear shaft SO1 and the first ring gear shaft HR1, i.e., they are in tooth mesh. The second planetary gear set PS2 also comprises three shafts: a second sun gear 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 gear shaft SO2 and the second ring gear shaft HR2. The first planetary gear set PS1 is configured to distribute a torque input from the electric machine EM unequally between the first carrier shaft ST1 and the first ring gear shaft HR1. The second planetary gear set PS2 is configured to match the torque and direction of rotation of the second ring gear shaft HR2 to the torque and direction of rotation of the first carrier shaft ST1.

[0050] 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 planet 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 planet gears that mesh with the fourth sun gear shaft, SO4, and the fourth ring gear shaft, HR4.

[0051] The first splined shaft ST1 is non-rotatably connected to the third sun shaft SO3, and the third splined shaft ST3 is configured to drive the first gear R1. The first ring gear shaft HR1 is non-rotatably connected to the second sun shaft SO2. The second splined shaft ST2, the third ring gear shaft HR3, and the fourth ring gear shaft HR4 are each fixed 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 S2 via a connecting shaft W. In this case, the connecting shaft W is as shown in Fig. 1. The first gear 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 to form a second spur gear stage SR2. The fourth sun shaft SO4 is rotationally fixed to the third spur gear S3, and the fourth web shaft ST4 is designed to drive the second gear R2.

[0052] Furthermore, a clutch DS designed as a differential lock is provided. In its closed state, the clutch DS connects the second ring gear shaft HR2 to the first carrier shaft ST1 in a rotationally fixed manner, thus locking the differential and disabling its function according to an actuating command. Because the drive unit incorporates final gears in the wheel hubs, namely the third and fourth planetary gear sets PS3 and PS4, a lower gear ratio is required in the differential, i.e., in the first and second planetary gear sets PS1 and PS2. The use of wheel hub gears offers particular advantages in terms of installation space.

[0053] Fig. Figure 7 shows a third embodiment of a drive unit 100 according to the invention. The drive unit 100 according to Fig. 7 essentially corresponds to drive unit 100 according to Fig. 6, wherein a difference between these two embodiments lies in the connection of the planetary gear sets PS1 and PS2. The first planetary gear set PS1 is configured to distribute a torque input from the electric machine EM unequally between the first splined shaft ST1 and the first ring gear shaft HR1. The second planetary gear set PS2 is configured to match the torque and direction of rotation of the second ring gear shaft HR2 to the torque and direction of rotation of the first splined shaft ST1. The second ring gear shaft HR2 is non-rotatably connected to the third sun gear shaft SO3, and the third splined shaft ST3 is configured to drive the first gear R1. The first splined shaft ST1 is non-rotatably connected to a first spur gear S1, wherein the first spur gear S1 meshes with a second spur gear S2, forming a first spur gear stage SR1. Otherwise, the embodiment corresponds to the above. Fig. 7 according to the exemplary embodiment Fig. 6, which is referenced.

[0054] Fig. Figure 8 shows a fourth embodiment of a drive unit 100 according to the invention. The drive unit 100 according to Fig. Assembly 8 comprises a first planetary gear set PS1, a second planetary gear set PS2 designed as a wheel-head gear for arrangement within a first wheel R1 of the vehicle axle, and a third planetary gear set PS3 designed as a wheel-head gear 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.

[0055] The first planetary gear set, PS1, comprises three shafts: a first sun gear 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 gear shaft, SO1, and the first ring gear shaft, HR1. The second planetary gear set, PS2, also comprises three shafts: a second sun gear 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 gear shaft, SO2, and the second ring gear shaft, HR2. The third planetary gear set, PS3, also comprises three shafts: 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 planet gears that mesh with the third sun gear shaft, SO3, and the third ring gear shaft, HR3.The first planetary gear set PS1 is configured to unequally distribute the torque input from the electric machine EM to the first carrier shaft ST1 and the first ring gear shaft HR1. The first sun gear shaft SO1 is configured to connect the electric machine EM. The first carrier shaft ST1 is rotationally fixed to the second sun gear shaft SO2, and the second carrier shaft ST2 is configured to drive the first gear R1. The first ring gear shaft HR1 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 via a connecting shaft W to a second spur gear S2, 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, thereby forming a third spur gear stage SR3.The third sun gear SO3 is rotationally fixed to the fourth spur gear S4, and the third web shaft ST3 is configured to drive the second gear R2. The connecting shaft W is as shown in [reference]. Fig. 2, designed as a rigid shaft and can alternatively be designed as a cardan shaft.

[0056] According to this embodiment, the equalization of torques and direction of rotation after the unequal distribution in the first planetary gear set is not achieved via a further 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.

[0057] Fig. Figure 9 shows a fifth embodiment of a drive unit 100 according to the invention. The drive unit 100 according to Fig. 9 essentially corresponds to drive unit 100 according to Fig. 8, wherein a difference between these two embodiments lies in the connection of the first planetary set PS1. Furthermore, the connecting shaft W is as shown in Fig. 1, designed as a cardan shaft and can alternatively be designed as a rigid shaft. The first planetary gear set PS1 is configured to distribute a torque input from the electric machine EM unequally between the first carrier shaft ST1 and the first ring gear shaft HR1. The first ring gear shaft HR1 is non-rotatably connected to the second sun gear shaft SO2, and the second carrier shaft ST3 is configured to drive the first gear R1. The first carrier shaft ST1 is non-rotatably connected to a first spur gear S1, wherein the first spur gear S1 meshes with a second spur gear S2, forming a first spur gear stage SR1. Otherwise, the embodiment corresponds to the Fig. 9 according to the exemplary embodiment Fig. 8, to which reference is made.

[0058] Fig. Figure 10 shows a sixth 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, a difference between these two embodiments being the connection of the second wheel R2. In the present case, the drive unit 100 only has the first and second planetary gear sets, so that the third planetary gear set PS3 according to Fig. Figure 9 is omitted. This results in the second wheel R2 being connected directly via the fifth spur gear S5. Consequently, the fifth spur gear S5 is non-rotatably connected to the second wheel R2. In particular, the gear ratios in the spur gear chain, especially in the first, second, and third spur gear stages SR1, SR2, SR3, can be increased to such an extent that the second gear head drive becomes obsolete, potentially leading to efficiency gains and cost reductions. Otherwise, the embodiment corresponds to the following. Fig. 10 according to the exemplary embodiment Fig. 9, to which reference is made.

[0059] Fig. Figure 11 shows a seventh 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, wherein a difference between these two embodiments lies in the connection of the first planetary gear set PS1. The first ring gear shaft HR1 has external teeth and is configured 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 corresponds to the following. Fig. 11 according to the exemplary embodiment Fig. 10, which is referenced.

[0060] Fig. Figure 12 shows a vehicle according to the invention with a drive unit 100 according to Fig. 3. The vehicle is designed as a bus and intended for passenger transport. For this purpose, the vehicle has a passenger compartment 4. This compartment extends essentially over the entire length of the vehicle. The vehicle is therefore designed as a low-floor vehicle. The first and second wheels R1, R2 of the vehicle axle are connected to each other via the drive unit 100, which incorporates a differential function. Furthermore, the vehicle has a third and fourth wheel R3, R4, on a non-driven axle. Reference sign 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 hollow gear shaft ST1 first bridge wave PS2 second planetary set SO2 second solar wave HO2 second hollow gear shaft ST2 second bridge shaft PS3 third planetary set SO3 third solar wave HO3 third hollow gear shaft ST3 third bridge wave PS4 fourth planetary set SO4 fourth solar wave HO4 fourth hollow gear shaft ST4 fourth bridge shaft 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

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 gearbox with exactly three planetary sets (PS1, PS2, PS3) arranged coaxially to the electric machine (EM), • wherein the first planetary set (PS1) has a first sun gear shaft (SO1), a first ring gear shaft (HR1) and a first bridge shaft (ST1) and is configured as a pre-reduction gear, • wherein the second planetary gear set (PS2) has a second sun shaft (SO2), a second ring gear shaft (HR2) and a second bridge shaft (ST2) and is designed to distribute a torque received from the first planetary gear set (PS1) unequally between the second bridge shaft (ST2) and the second ring gear shaft (HR2), • wherein the third planetary set (PS3) has a third sun shaft (SO3), a third ring gear shaft (HR3) and a third bridge shaft (ST3) and is arranged to match a torque and direction of rotation of the third ring gear shaft (HR3) to a torque and direction of rotation of the second bridge shaft (ST2), • wherein the first solar wave (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) for driving the first wheel (R1) is non-rotatably connected to a first output shaft (2), • wherein the second spur shaft (ST2) is non-rotatably 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), wherein the second spur gear (S2) is connected via at least one connecting shaft (W) arranged axially parallel to the electric machine (EM) to a third spur gear (S3), 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 non-rotatably connected to a second output shaft (3) for driving the second gear (R2). [2] Drive unit (100) for a vehicle axle with a first wheel (R1) and a second wheel (R2), comprising an electric machine (EM) and a gearbox with exactly three planetary sets (PS1, PS2, PS3) arranged coaxially to the electric machine (EM), • wherein the first planetary set (PS1) comprises a first sun shaft (SO1), a first ring gear shaft (HR1) and a first bridge shaft (ST1) and is configured to distribute a torque received from the electric machine (EM) unequally between the first bridge shaft (ST1) and the first ring gear shaft (HR1), • wherein the second planetary set (PS2) has a second sun shaft (SO2), a second ring gear shaft (HR2) and a second bridge shaft (ST2), • wherein the third planetary set (PS3) has a third sun shaft (SO3), a third ring gear shaft (HR3) and a third bridge shaft (ST3) and is arranged to match a torque and direction of rotation of the third bridge shaft (ST3) to a torque and direction of rotation of the second ring gear shaft (HR2), • wherein the first solar wave (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) for driving the first wheel (R1) is non-rotatably connected to a first output shaft (2), • wherein the third spur shaft (ST3) is non-rotatably 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), wherein the second spur gear (S2) is connected to a third spur gear (S3) via at least one connecting shaft (W) arranged axially parallel to the electric machine (EM), 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 non-rotatably connected to a second output shaft (3) for driving the second gear (R2). [3] 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 having exactly two coupled planetary sets (PS1, PS2), a third planetary set (PS3) designed as a wheel head transmission for arrangement inside the first wheel (R1) of the vehicle axle and a fourth planetary set (PS4) designed as a wheel head transmission for arrangement inside the second wheel (R2) of the vehicle axle, wherein the four planetary sets (PS1-PS4) are arranged coaxially with the electric machine (EM), • wherein the first planetary set (PS1) comprises a first sun shaft (SO1), a first ring gear shaft (HR1) and a first bridge shaft (ST1) and is configured to distribute a torque received from the electric machine (EM) unequally between the first bridge shaft (ST1) and the first ring gear shaft (HR1), • wherein the second planetary set (PS2) has a second sun shaft (SO2), a second ring gear shaft (HR2) and a second bridge shaft (ST2) and is arranged to match a torque and direction of rotation of the second ring gear shaft (HR2) to a torque and direction of rotation of the first bridge shaft (ST1), • wherein the third planetary set (PS3) has a third sun shaft (SO3), a third ring gear shaft (HR3) and a third bridge shaft (ST3), • wherein the fourth planetary set (PS4) has a fourth sun shaft (SO4), a fourth ring gear shaft (HR4) and a fourth bridge shaft (ST4), • wherein the first solar wave (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 non-rotatably connected to the third sun shaft (SO3) and the third web shaft (ST3) is non-rotatably connected to a first output shaft (2) for driving the first wheel (R1), • wherein the first splined shaft (ST1) is non-rotatably 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), wherein the second spur gear (S2) is connected via a connecting shaft (W) arranged axially parallel to the electric machine (EM) to a third spur gear (S3), 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 non-rotatably connected to the fourth spur gear (S4) and the fourth splined shaft (ST4) is non-rotatably connected to a second output shaft (3) for driving the second gear (R2). [4] Drive unit (100) according to one of the preceding claims, further comprising a clutch (DS) designed as a differential lock. [5] 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 comprising exactly a first planetary set (PS1), a second planetary set (PS2) designed as a wheel head transmission for arrangement within the first wheel (R1) of the vehicle axle and a third planetary set (PS3) designed as a wheel head transmission for arrangement within the second wheel (R2) of the vehicle axle, wherein the three planetary sets (PS1-PS3) are arranged coaxially with the electric machine (EM), • wherein the first planetary set (PS1) comprises a first sun shaft (SO1), a first ring gear shaft (HR1) and a first bridge shaft (ST1) and is configured to distribute a torque received from the electric machine (EM) unequally between the first bridge shaft (ST1) and the first ring gear shaft (HR1), • wherein the second planetary set (PS2) has a second sun shaft (SO2), a second ring gear shaft (HR2) and a second bridge shaft (ST2), • wherein the third planetary set (PS3) has a third sun shaft (SO3), a third ring gear shaft (HR3) and a third bridge shaft (ST3), • wherein the first solar wave (SO1) is connected to the electric machine (EM) via a drive shaft (1) in a rotationally fixed manner, • wherein the first web shaft (ST1) is non-rotatably connected to the second sun shaft (SO2) and the second web shaft (ST2) is non-rotatably connected 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) arranged axially parallel to the electric machine (EM), 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) meshes with a fourth spur gear (S4) and forms a third spur gear stage (SR3), wherein the third sun shaft (SO3) is non-rotatably connected to the fourth spur gear (S4) and the third web shaft (ST3) is non-rotatably connected to a second output shaft (3) for driving the second gear (R2). [6] 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 comprising exactly a first planetary set (PS1), a second planetary set (PS2) designed as a wheel head transmission for arrangement within the first wheel (R1) of the vehicle axle and a third planetary set (PS3) designed as a wheel head transmission for arrangement within the second wheel (R2) of the vehicle axle, wherein the three planetary sets (PS1-PS3) are arranged coaxially with the electric machine (EM), • wherein the first planetary set (PS1) comprises a first sun shaft (SO1), a first ring gear shaft (HR1) and a first bridge shaft (ST1) and is configured to distribute a torque received from the electric machine (EM) unequally between the first bridge shaft (ST1) and the first ring gear shaft (HR1), • wherein the second planetary set (PS2) has a second sun shaft (SO2), a second ring gear shaft (HR2) and a second bridge shaft (ST2), • wherein the third planetary set (PS3) has a third sun shaft (SO3), a third ring gear shaft (HR3) and a third bridge shaft (ST3), • wherein the first solar wave (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 non-rotatably connected to the second sun gear shaft (SO2) and the second web shaft (ST2) is non-rotatably connected to a first output shaft (2) for driving the first gear (R1), • wherein the first splined shaft (ST1) is non-rotatably 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), wherein the second spur gear (S2) is connected via a connecting shaft (W) arranged axially parallel to the electric machine (EM) to a third spur gear (S3), 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 non-rotatably connected to the fifth spur gear (S5) and the third splined shaft (ST3) is non-rotatably connected to a second output shaft (3) for driving the second gear (R2). [7] 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 comprising exactly a first planetary set (PS1) and a second planetary set (PS2) designed as a wheel head transmission for arrangement inside the first wheel (R1) of the vehicle axle, wherein the two planetary sets (PS1, PS2) are arranged coaxially with the electric machine (EM), • wherein the first planetary set (PS1) comprises a first sun shaft (SO1), a first ring gear shaft (HR1) and a first bridge shaft (ST1) and is configured to distribute a torque received from the electric machine (EM) unequally between the first bridge shaft (ST1) and the first ring gear shaft (HR1), • wherein the second planetary set (PS2) has a second sun shaft (SO2), a second ring gear shaft (HR2) and a second bridge shaft (ST2), • wherein the first solar wave (SO1) is connected to the electric machine (EM) via a drive shaft (1) in a rotationally fixed manner, • wherein the first web shaft (ST1) is non-rotatably connected to the second sun shaft (SO2) and the second web shaft (ST2) is non-rotatably connected 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) which is arranged parallel to the axis of the electric machine (EM), 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) meshes with a fourth spur gear (S4) and forms a third spur gear stage (SR3), wherein the fourth spur gear (S4) is non-rotatably connected to a second output shaft (3) for driving the second gear (R2). [8] 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 comprising a first planetary set (PS1) and a second planetary set (PS2) designed as a wheel head transmission for arrangement inside the first wheel (R1) of the vehicle axle, wherein the two planetary sets (PS1, PS2) are arranged coaxially with the electric machine (EM), • wherein the first planetary set (PS1) comprises a first sun shaft (SO1), a first ring gear shaft (HR1) and a first bridge shaft (ST1) and is configured to distribute a torque received from the electric machine (EM) unequally between the first bridge shaft (ST1) and the first ring gear shaft (HR1), • wherein the second planetary set (PS2) has a second sun shaft (SO2), a second ring gear shaft (HR2) and a second bridge shaft (ST2), • wherein the first solar wave (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 non-rotatably connected to the second sun gear shaft (SO2) and the second web shaft (ST2) is non-rotatably connected to a first output shaft (2) for driving the first gear (R1), • wherein the first spur shaft (ST1) is non-rotatably 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), wherein the second spur gear (S2) is connected via a connecting shaft (W) arranged parallel to the axis of the electric machine (EM) to a third spur gear (S3), 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 non-rotatably connected to a second output shaft (3) for driving the second gear (R2). [9] Drive unit (100) according to one of the preceding claims, wherein the connecting shaft (W) is configured to connect a first section of the drive unit (100) with 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). [10] 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. [11] Vehicle with a drive unit (100) according to one of the preceding claims.

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