Electric drive system for motor vehicle, in particular for motor vehicle, and motor vehicle

Abstract

The invention relates to an electric drive system (10) for a motor vehicle, comprising an electric machine (18) having a stator (20) and a rotor (22); the electric drive system has a multi-stage gear arrangement (28) with a first planetary gear set (30) which in turn has: a first shaft (32); a second shaft (34) designed as a first planet carrier on which the first planet gear (42) is rotatably mounted; and a third shaft (36); the electric drive system has a differential gear arrangement (46) which in turn has: a differential planet carrier (48) as a differential input shaft; a first differential sun gear (52) as a first differential output shaft; a second differential sun gear (54) as a second differential output shaft; a first differential compensation wheel (74) which is rotatably arranged on the differential planet carrier (48) and which meshes with the first differential sun gear (52); and a second differential compensation gear (76), which is rotatably arranged on the differential planet carrier (48) and meshes with the second differential sun gear (54).

Description

Technical Field

[0001] The invention relates to an electric drive system for a motor vehicle, in particular for a car, according to the preamble of claim 1. The invention also relates to a motor vehicle, in particular a car. Background Art

[0002] DE 10 2018 008 939 B3 discloses an electric drive having a housing and a first planetary gear set arranged in the housing. DE 10 2018 128 836 B3 also discloses a transmission for a motor vehicle.

[0003] DE 10 2017 111 049 A1 shows a drive device having an electric motor, a first planetary gear set, and a planetary differential gearing, wherein the planet carrier of the first planetary gear set is coupled to the planet carrier of the planetary differential gearing, and wherein the rotor of the electric motor is coupled to the ring gear of the first planetary gear set. WO 2018 / 019 324 A1 also shows a system having an electric motor, a first planetary gear set, and a planetary differential gearing, wherein in this case, the rotor of the electric motor, the first planetary gear set, and the planetary differential gearing are all arranged coaxially with one another. Summary of the Invention

[0004] The object of the present invention is to provide an electric drive system for a motor vehicle and a motor vehicle having such an electric drive system, which allows a particularly compact and weight-effective construction.

[0005] This object is achieved by an electric drive system having the features of claim 1 and a motor vehicle having the features of claim 7. Advantageous embodiments with suitable developments of the invention are specified in the remaining claims.

[0006] The starting point is an electric drive system for a motor vehicle, particularly an automobile, and particularly a passenger car, also referred to as an electric drive unit or designed as an electric drive unit. This means that the motor vehicle (also simply referred to as a vehicle) in its fully manufactured state has an electric drive system and can be driven electrically, particularly purely electrically, by means of the electric drive system. To this end, the electric drive system includes an electric motor having a stator and a rotor. The rotor can be driven by the stator and can therefore rotate relative to the stator, for example, about a machine axis of rotation. The electric drive system can provide torque via the rotor to drive the motor vehicle. For example, in its fully manufactured state, the motor vehicle has at least or exactly two axles, also simply referred to as axles, arranged one behind the other in the longitudinal direction of the motor vehicle. Each axle has at least or exactly two wheels, also simply referred to as wheels. The wheels of each axle are arranged on opposite sides of the motor vehicle in the transverse direction of the motor vehicle. Wheels are ground-contacting elements by which the motor vehicle can be supported downward in the vertical direction of the motor vehicle or supported on the ground. If a motor vehicle is driven along the ground while being supported downwardly on the ground by ground-contacting elements in the vertical direction of the vehicle, the wheels roll, in particular directly on the ground. In this case, the wheels of at least one or exactly one of the axles can be driven, for example, by an electric drive system, in particular by an electric motor, and most particularly by a rotor. Therefore, hereinafter, when referring to wheels, unless otherwise specified, this should be understood to mean wheels that can be driven by a drive.

[0007] An electric drive system includes a multi-stage gear arrangement having a first planetary gear set. The first planetary gear set includes a first shaft, a second shaft, and a third shaft. The second shaft is configured as a first planetary carrier of the first planetary gear set, wherein the first planetary gears are rotatably supported on the first planetary carrier of the first planetary gear set. The first planetary carrier is referred to as a first carrier. The first, second, and third shafts are also referred to as first gear elements of the first planetary gear set. In particular, the first gear elements are arranged coaxially with one another. The electric drive system includes a housing, wherein the first planetary gear set is, for example, at least partially arranged in the housing. In particular, if the respective first gear elements are not connected to the housing in a rotationally fixed manner, the respective first gear elements can rotate relative to the housing about the first planetary gear set axis of rotation. In particular, if the first gear elements are coaxially arranged, the first planetary gear set axis of rotation can, for example, be a common first planetary gear set axis of rotation for the first gear elements. The first gear element is also referred to as a planetary gear set element, wherein the first of the planetary gear set elements is the second shaft and, therefore, the first planetary carrier of the first planetary gear set. The second planetary gear set element of the planetary gear set comprises, for example, the first sun gear of the first planetary gear set. Furthermore, it is conceivable that the third planetary gear set element of the planetary gear set comprises the first ring gear of the first planetary gear set. In this case, the corresponding first planetary gears mesh, for example, with both the first sun gear and the first ring gear of the first planetary gear set, in particular simultaneously.

[0008] Within the scope of the present disclosure, ordinal numbers (also called sequential numbers), such as "first", "second", etc., are not necessarily used to indicate the number of the elements to which the ordinal numbers refer, but are only used to clearly indicate the elements to which the ordinal numbers refer.

[0009] The electric drive system also includes a differential gearing system having a differential planetary carrier as a differential input shaft. This differential planetary carrier is also referred to as a second planetary carrier or second carrier. The corresponding torque provided or capable of being provided by the rotor is also referred to as driving torque. When referring to a corresponding torque above and below, unless otherwise specified, it should be understood to refer to the corresponding torque provided or capable of being provided by the rotor. For example, the corresponding driving torque provided or capable of being provided by the rotor, or a corresponding further torque generated from this corresponding driving torque, can be introduced into the differential gearing system via the differential input shaft, thereby driving the differential gearing system. The differential gearing system is, for example, assigned to or is a component of an axle, the wheels of which can be driven by the drive system. Driven wheels are also referred to as drive wheels. In particular, the rotor can drive the wheels (drive wheels) via the differential gearing system. The differential gearing system has functions common in the prior art, such as allowing different rotational speeds of the drive wheels when a motor vehicle turns, particularly allowing the drive wheels on the outside of the curve to rotate or be able to rotate at a higher speed than the drive wheels on the inside of the curve. In addition, the differential gear device is used, for example, to divide or distribute the corresponding driving torque introduced into the differential gear device or the corresponding other torque generated from the corresponding driving torque and introduced into the differential gear device to the drive wheels, so that these drive wheels are driven or can be driven by the rotor, for example, while the drive wheels rotate at different speeds, for example during the above-mentioned turn.

[0010] The differential gear arrangement also includes a first differential sun gear as a first differential output shaft. The first differential sun gear is also referred to as a second sun gear. Furthermore, the differential gear arrangement includes a second differential sun gear as a second differential output shaft, wherein the second differential sun gear is also referred to as a third sun gear. For example, a first of the drive wheels can be driven by the first differential output shaft, and for example, a second of the drive wheels can be driven by the second differential output shaft. A corresponding drive torque introduced into the differential gear arrangement, or a corresponding other torque introduced into the differential gear arrangement, or a corresponding third torque generated from the corresponding drive torque introduced into the differential gear arrangement, or from the other torque introduced into the differential gear arrangement, can be transmitted to or at the corresponding drive wheel via the corresponding differential output shaft. The corresponding drive wheel can be driven by the corresponding differential output shaft, thereby driving or driving the drive wheel.

[0011] The first differential sun gear is, for example, rotatable relative to the housing about the first sun gear axis of rotation, and the second differential sun gear is, for example, rotatable relative to the housing about the second sun gear axis of rotation. It is particularly conceivable that the differential sun gears are arranged coaxially with one another, such that the sun gear axes of rotation preferably coincide. The differential planet carrier is, for example, rotatable relative to the housing about the planet carrier axis of rotation. In particular, it is provided that the differential planet carrier is arranged coaxially with the first differential sun gear and coaxially with the second differential sun gear, such that the planet carrier axis of rotation preferably coincides with the first and second sun gear axes of rotation. It is particularly conceivable that the differential planet carrier, the first differential sun gear, and the second differential sun gear constitute second gear elements of the differential gear arrangement, wherein the second gear elements may, for example, be rotatable relative to one another about the respective sun gear axes of rotation or about the planet carrier axis of rotation. It is also conceivable that the first planetary gearset axis of rotation coincides with the machine axis of rotation, such that the first planetary gearset is, for example, arranged coaxially with the electric machine, i.e., the rotor. Alternatively or additionally, it is conceivable that the differential gearing is arranged coaxially with the electric machine, such that the planetary carrier axis of rotation or the sun gear axis of rotation coincides with the machine axis of rotation. It is also conceivable that the first planetary gear set is arranged coaxially with the differential gearing, such that the first planetary gear axis of rotation coincides, for example, with the corresponding sun gear axis of rotation or with the planetary carrier axis of rotation.

[0012] The differential gear device has a first differential compensation wheel These first differential compensating gears are rotatably arranged, in particular, supported on the differential planet carrier. The respective first differential compensating gears mesh with the first differential sun gear, rather than, for example, the second differential sun gear. The differential gear arrangement further comprises second differential compensating gears, which are rotatably arranged, in particular, supported on the differential planet carrier, and mesh with the second differential sun gear. Thus, the respective second differential compensating gears mesh with the second differential sun gear, but preferably do not mesh with the first differential sun gear. For example, the respective first differential compensating gears are rotatable relative to the differential planet carrier about the respective first compensating gear rotational axis, wherein the first compensating gear rotational axes extend, for example, parallel to one another in pairs and are spaced apart from one another in pairs. Furthermore, the respective first compensating gear rotational axes extend parallel to the planet carrier rotational axis, wherein the respective first compensating gear rotational axes are spaced apart from the planet carrier rotational axis. In particular, the first compensating gear rotational axes are spaced apart from one another in a circumferential direction of the differential gear arrangement extending about the planet carrier rotational axis and are particularly evenly distributed.

[0013] For example, the respective second differential compensating gears can rotate relative to the differential planetary carrier about respective second compensating gear rotation axes, wherein the second compensating gear rotation axes extend, for example, in pairs, parallel to one another and spaced apart from the first compensating gear rotation axis. Furthermore, the respective second compensating gear rotation axes extend parallel to the planetary carrier rotation axis, wherein the respective second compensating gear rotation axes are spaced apart from the planetary carrier rotation axis. In particular, the second compensating gear rotation axes are spaced apart from one another in a circumferential direction of the differential gear arrangement extending about the planetary carrier rotation axis and are particularly arranged in a uniformly distributed manner. In particular, it is provided that the respective second compensating gear rotation axes extend parallel to the first compensating gear rotation axis and are spaced apart from the first compensating gear rotation axis.

[0014] Furthermore, for example, it is provided that the respective first planetary gears are rotatable relative to the first planetary carrier about the respective first planetary gear rotational axis. The first planetary gear rotational axes extend parallel to each other in pairs and are spaced apart from each other in pairs. Furthermore, the respective first planetary gear rotational axes are spaced apart from the first planetary gear set rotational axis and extend parallel to the first planetary gear set rotational axis. The first planetary gear rotational axes are spaced apart from each other in a circumferential direction of the first planetary gear set extending about the first planetary gear set rotational axis and are, in particular, arranged in a uniform distribution. For example, the first planetary gear rotational axes are arranged on a first circle, the center of which lies on the first planetary gear set rotational axis. For example, the first compensating gear rotational axis is arranged on a second circle, the center of which lies on the planetary carrier rotational axis. For example, the second compensating gear rotational axis is arranged on a third circle, the center of which lies on the planetary carrier rotational axis. It is particularly provided that the first circle has a first diameter, the second circle has a second diameter, and the third circle has a third diameter. It is particularly provided that the second and third diameters differ from each other, in particular, that the second diameter is smaller or larger than the third diameter.

[0015] In the electric drive system, it is further provided that each of the first differential compensating wheels meshes, in particular directly, with, in particular precisely one corresponding differential compensating wheel of the second differential compensating wheels.

[0016] Viewed in the axial direction of the electric drive system, which coincides with or extends along the axis of rotation of the planetary gear sets, the first planetary gear set, the first differential sun gear, and the second differential sun gear are arranged in the sequence described, i.e., in the order in which they are mentioned, such that, viewed in the axial direction of the electric drive system, the first planetary gear set, the first differential sun gear, and the second differential sun gear are arranged sequentially, i.e., one after the other, in the following order: first planetary gear set - first differential sun gear - second differential sun gear. In other words, viewed in the axial direction of the electric drive system, the first differential sun gear follows the first planetary gear set, and, viewed in the axial direction of the electric drive system, the second differential sun gear follows the first differential sun gear. This allows for a particularly compact and weight-efficient design of the electric drive system, enabling particularly efficient driving of the motor vehicle. In particular, this allows for a particularly long electric range of the motor vehicle. Furthermore, the present invention favors a particularly compact design of a shiftable multi-stage gear arrangement, wherein the multi-stage gear arrangement can be designed, for example, as a particularly shiftable multi-speed gear arrangement.

[0017] The rotor of the electric machine is coupled or can be coupled to a first shaft such that a torque provided or capable of being provided by the rotor can bypass the differential gearing to the first shaft and thus be introduced into the first planetary gearset via the first shaft, thereby allowing the torque to be introduced. The characteristic "a corresponding torque provided or capable of being provided by the rotor can bypass the differential gearing to the first shaft and thus be introduced into the first planetary gearset via the first shaft" should be understood to mean that the corresponding torque provided or capable of being provided by the rotor bypasses the differential gearing on its way from the rotor to the first shaft, i.e., does not flow or be conducted from the rotor to the first shaft via the differential gearing. In other words, the corresponding torque provided or capable of being provided by the rotor can be transmitted along a torque flow from the rotor to or on the first shaft, wherein the differential gearing is not located in the torque flow between the rotor and the first shaft, in particular, the differential gearing is located outside the torque flow, which, for example, begins at the rotor and ends at the first shaft. In particular, the rotor is coupled or can be coupled to the first shaft, for example, in a torque-transmitting manner, in particular, in a torsionally fixed manner. In particular, it is conceivable that the rotor is permanently connected to the first shaft in a torque-transmitting manner, in particular permanently in a rotationally fixed manner.

[0018] To achieve a particularly compact and weight-efficient design or configuration of the electric drive system, as well as particularly efficient operation of the drive system, the electric drive system is provided, according to a known method, with a first shifting unit designed to connect the third shaft to the housing in a rotationally fixed manner. This means that the third shaft can be connected to the housing in a rotationally fixed manner by means of the first shifting unit. The first shifting unit can thus be switched between a first coupled state and a first uncoupled state. In the first coupled state, the third shaft is connected to the housing in a rotationally fixed manner by means of the first shifting unit, thereby preventing the second shaft from rotating relative to the third shaft and the housing about the axis of rotation of the planetary gear set. In the first uncoupled state, the first shifting unit releases the third shaft for rotation about the axis of rotation of the planetary gear set and relative to the housing, so that in the first uncoupled state, the third shaft can rotate relative to the housing about the axis of rotation of the planetary gear set.

[0019] Electric drive systems also generally include a second shifting unit designed to lock the first planetary gear set. This allows for a particularly compact and weight-saving design of the drive system, as well as particularly efficient operation. The shifting unit can be switched between a second coupled state and a second decoupled state. In the second coupled state, the first planetary gear set is locked by means of the second shifting unit. In other words, in the second coupled state of the second shifting unit, the locking of the first planetary gear set is activated. In the second decoupled state, the locking of the first planetary gear set is deactivated, i.e., canceled. Locking the first planetary gear set should be understood as meaning that, in the second coupled state of the second shifting unit, two of the shafts of the first planetary gear set are connected to each other in a rotationally fixed manner by means of the second shifting unit, so that when the first planetary gear set is driven, the entire planetary gear set (i.e., the first gear element or the shafts of the first planetary gear set) rotates as a whole and therefore jointly (i.e., at the same angular velocity), i.e., they rotate jointly or simultaneously at the same angular velocity about the first planetary gear set axis of rotation relative to the housing. In the second decoupled state, the second shifting unit allows relative rotation of the shafts about the axis of rotation of the planetary gear set, which shafts are connected to one another in a rotationally fixed manner by means of the second shifting unit in the second coupled state.

[0020] According to the present invention, the first planet carrier is, in particular, permanently connected to the differential planet carrier in a torsionally fixed manner. Furthermore, according to the present invention, each of the first planetary gears and, in particular, exactly one of the first differential compensating gears are arranged coaxially with one another. Therefore, it is particularly provided that the first diameter and the second diameter are identical. That is, the first diameter corresponds, for example, to the second diameter. Thus, for example, a respective first planetary gear and a respective first differential compensating gear arranged coaxially therewith form a respective wheelset.

[0021] In order to achieve a particularly compact and space-saving design of the drive system and particularly efficient operation, the invention further provides that the first shifting unit axially overlaps and is arranged radially around the differential gearing. In particular, the feature "the first shifting unit is arranged radially around the differential gearing" is to be understood as meaning that at least one length region of the differential gearing is at least partially, in particular at least for the most part, and therefore at least more than half or completely, surrounded by the first shifting element in a circumferential direction of the drive system around the axial direction of the drive system, so that the first shifting element, for example, surrounds the length region at least partially, in particular at least for the most part, and therefore at least more than half or completely, in a circumferential direction of the electric drive system.

[0022] Unless otherwise specified, the terms "axial" and "radial" refer to the planetary gear set axis of rotation, also referred to as the main axis of rotation. The first gear element, i.e., the first, second, and third shafts of the first planetary gear set, are arranged coaxially with the main axis of rotation. In particular, the differential gear arrangement is arranged coaxially with the main axis of rotation, such that the first compensator wheel axis of rotation, the second compensator wheel axis of rotation, and the planet carrier axis of rotation preferably coincide with the main axis of rotation. The term "radially inner" or the characteristic "radially inner" should be understood to mean that one element (particularly a rotatably mounted element) is arranged radially inner than another element (particularly a rotatably mounted element) if it is arranged in an area of ​​smaller radius. Thus, the maximum radius of the radially inner element is, for example, smaller than the minimum radius of the radially outer element. Thus, the term "radially outer" or the characteristic "radially outer" should be understood to mean that one element (particularly a rotatably mounted element) is arranged radially outer than another element (particularly a rotatably mounted element) if it is arranged in an area of ​​larger radius, such that the minimum radius of the radially outer element is larger than the maximum radius of the radially inner element. Furthermore, the term or feature "axially overlapping" should be understood as follows: two elements are arranged axially overlapping, in particular, overlapping one another, if they are at least partially arranged in the same axial region. In other words, two elements are arranged axially overlapping, in particular, overlapping one another, if they have at least partially the same coordinates relative to a reference axis, in particular, extending in the axial direction of the electric drive system. The term "coaxial" should be understood as meaning that two rotatably mounted elements are arranged coaxially with one another if they are rotatable about the same axis of rotation, in particular relative to one another and / or relative to the housing.

[0023] In the context of the present disclosure, the characteristic that two components are connected to each other in a torsionally fixed manner is understood to mean that the components connected to each other in a torsionally fixed manner are coaxially arranged with respect to one another and, in particular when the components are driven, rotate jointly or simultaneously about a common axis of rotation of the components, such as the axis of rotation of a planetary gear set, at the same angular speed, in particular relative to a housing. The characteristic that two components are connected to each other in a torque-transmitting manner is understood to mean that the components are coupled or connected to each other in such a way that torque can be transmitted between the components, wherein when the components are connected to each other in a torsionally fixed manner, the components are also connected to each other in a torque-transmitting manner.

[0024] The characteristic that two components are permanently connected to one another in a torque-transmitting manner should be understood to mean that no shifting element is provided that can be switched between a coupled state (the components are torque-transmittingly connected to one another) and a decoupled state (torque cannot be transferred between the components via the shifting element). Instead, the components are always or permanently, and therefore, permanently, connected to one another in a torque-transmitting manner, i.e., via the shifting element, such that torque can be transferred between the components. Thus, for example, one of the components can be driven by the corresponding other component, and vice versa. In particular, the characteristic that the components are permanently connected to one another in a torque-proof manner should be understood to mean that no shifting element is provided that can be switched between a coupled state (the components are torque-proofly connected to one another) and a decoupled state (the components are decoupled from one another and can rotate relative to one another, such that torque cannot be transferred between the components via the shifting element). Instead, the components are always or permanently, i.e., permanently, connected or coupled to one another in a torque-proof manner. The characteristic that two components can be connected or coupled to one another in a torque-proof or torque-transmitting manner should be understood to mean that the components are assigned a shifting element that can be switched between at least one coupled state and at least one decoupled state. In the coupled state, the components are connected to one another in a torsionally fixed or torque-transmitting manner via the switching element. In the uncoupled state, the components are decoupled from one another, such that in the uncoupled state the components can rotate relative to one another, in particular about a component rotation axis, such as the aforementioned common component rotation axis, and in particular, no torque can be transmitted between the components via the switching element. Similarly, in other words, the feature "connected in a torsionally fixed manner" should be understood as follows: if two rotatably mounted elements are arranged coaxially with one another and connected to one another so that they rotate at the same angular velocity, then the two elements are connected to one another in a torsionally fixed manner.

[0025] Preferably, the first shifting unit has a freewheel clutch which is designed to connect the third shaft to the housing in a rotationally fixed manner when the motor vehicle is being towed.

[0026] In order to create a particularly advantageous design of the drive system in terms of weight and installation space, it is preferably provided that the respective first planetary gear and the first differential compensating gear arranged coaxially therewith, i.e., the respective first planetary gear of the respective wheelset and the respective first differential compensating gear of the respective wheelset, are particularly rotatably arranged, in particular supported, on each, in particular, exactly one, integral common planetary gear pin. Preferably, the respective integral common planetary gear pin is designed as a steel bolt, i.e., manufactured from steel. The term "integral" is to be understood as follows: a component is designed as a single piece, i.e., one-piece, if it has no connection points, such as joints. In other words, a one-piece or one-piece component (e.g., a corresponding one-piece planetary gear pin) is designed as a single piece, i.e., consists of a single part, such that the one-piece or one-piece component (e.g., the corresponding one-piece planetary gear pin) is produced by a forming process, such as casting or forging, and thus the one-piece or one-piece component (e.g., the one-piece planetary gear pin) is designed as a casting or forging. In other words, a one-piece or integral component (e.g., a one-piece planetary gear pin) is composed of a single piece and is therefore designed as a single unit or is composed of a single unit. Therefore, a one-piece component (e.g., a one-piece planetary gear pin) is a one-piece, and therefore, a monolithic object manufactured in one piece. In other words, a one-piece or integral component (e.g., a one-piece planetary gear pin) is not composed of several parts that are manufactured separately and connected to each other, but is composed of a single piece.

[0027] In particular, the present invention makes it possible to design the differential gearing as an integrated differential gearing, in particular an integrated planetary differential gearing, in which the first planetary gear set can serve as a transmission stage of the differential gearing. This allows for a particularly compact design. Furthermore, a particularly weight-optimized design can be achieved, in particular by using a first planet carrier, which can be designed as a one-piece planet carrier. It is particularly possible to design the first planet carrier in aluminum, i.e., to produce it from aluminum or an aluminum alloy.

[0028] Another embodiment is characterized in that the second shifting unit is designed to connect the first planet carrier to the first shaft in a rotationally fixed manner. In other words, it is preferably provided that the first planet carrier can be connected to the first shaft in a rotationally fixed manner by means of the first shifting unit. This allows for particularly advantageous shiftability of the drive system in a particularly compact and weight-saving manner.

[0029] In another particularly advantageous embodiment of the present invention, the second shifting unit is designed to connect the first planet carrier to the third shaft in a rotationally fixed manner. In other words, it is preferably provided that the first planet carrier can be connected to the third shaft in a rotationally fixed manner by means of the second shifting unit. This allows for particularly advantageous shiftability of the drive system in a manner that is particularly advantageous in terms of weight and installation space, resulting in particularly efficient and advantageous operation.

[0030] In order to be able to keep the space requirement of the electric drive system at a particularly low level, in particular in the axial direction of the drive system and therefore viewed along the axis of rotation of the planetary gear set, it is provided in a further embodiment of the invention that the third shaft includes the third ring gear of the first planetary gear set and the first shaft includes the first sun gear of the first planetary gear set.

[0031] The second shifting unit is preferably designed to connect the first planetary carrier to the third shaft in a rotationally fixed manner. In order to be able to keep the space requirement and weight of the drive system particularly low, it is also preferably provided that the second shifting unit is arranged on a side of the first shifting unit that is remote from the first planetary gear set, in particular in the axial direction of the drive system.

[0032] Another embodiment is characterized by an oil channel. An oil channel is a channel through which oil can flow, for example, during operation of the electric drive system. The oil channel is designed to guide oil (also called hydraulic oil) and thus supply it to the actuating piston of the second shifting unit, wherein the oil channel has a first section extending in the housing and a second section extending in the first planetary carrier. This allows the second shifting unit to be actuated as required in a particularly space-saving manner. For example, the second coupled state is also referred to as the first state of the second shifting unit, and for example, the second uncoupled state is also referred to as the second state of the second shifting unit. For example, the second shifting unit can be transferred or switched from one state to another by means of hydraulic oil, i.e., by guiding, i.e., supplying, the hydraulic oil to the actuating piston via the oil channel, so that, for example, the second shifting unit can be switched from the second uncoupled state to the second coupled state by means of hydraulic oil.

[0033] It has proven particularly advantageous for the housing to have a housing wall that is arranged or extends perpendicularly to the main rotational axis, i.e., the planetary gear rotational axes. In other words, the housing wall extends in a plane perpendicular to the main rotational axis (planetary gear set rotational axis), with the second shifting unit being arranged adjacent to the housing wall, particularly when viewed in the axial direction of the drive system, and the first section preferably being arranged within the housing wall. This ensures a particularly advantageous supply of hydraulic oil to the actuating piston in a manner that is particularly advantageous in terms of installation space and weight.

[0034] A second aspect of the present invention relates to a motor vehicle (referred to as a vehicle for short), preferably designed as an automobile, in particular a passenger car, and comprising an electric drive system according to the first aspect of the present invention and capable of being driven electrically, in particular purely electrically, by means of the electric drive system. The advantages and advantageous configurations of the first aspect of the present invention should be considered as those of the second aspect of the present invention, and vice versa.

[0035] Further advantages, features and details of the present invention will become apparent from the following description of preferred embodiments with reference to the accompanying drawings. The above-mentioned features and combinations of features mentioned in the description, as well as the features and combinations of features mentioned in the description of the drawings and / or shown alone in the drawings, may be used not only in the respective combination but also in other combinations or alone without departing from the scope of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0036] In the attached figure:

[0037] Figure 1 A schematic diagram showing a first embodiment of an electric drive system for a motor vehicle not falling within the scope of claim 1 ;

[0038] Figure 2 A schematic diagram showing a second embodiment of an electric drive system;

[0039] Figure 3 a schematic front view partially showing an electric drive system; and

[0040] Figure 4 A schematic diagram of a third embodiment of an electric drive system is shown.

[0041] In the figures, identical or functionally identical elements are provided with the same reference signs. DETAILED DESCRIPTION

[0042] Figure 1 A first embodiment of an electric drive system 10 for a motor vehicle, which does not belong to claim 1, is shown in a schematic diagram. This means that a motor vehicle, referred to simply as vehicle, which is preferably designed as a car, in particular a passenger car, has a drive system 10 in its fully manufactured state and can be driven electrically, in particular purely electrically, by means of the drive system 10. The motor vehicle has, for example, at least or exactly two axles, which are arranged one after the other in the longitudinal direction of the vehicle of the motor vehicle. The respective axles have, for example, at least or exactly two wheels. The electric drive system 10 can drive electrically, in particular purely electrically, the wheels of one of the axles, whereby the motor vehicle can be driven electrically, in particular purely electrically. The wheels that can be driven by means of the drive system 10 are also referred to as drive wheels. Figure 1The wheels 12 and 14 are particularly schematically shown and are respectively referenced 12 and 14. The axle including the wheels 12 and 14 is referenced 16.

[0043] The electric drive system 10 has Figure 1 The motor 18 is particularly schematically shown in FIG. 1 , which has a stator 20 and a rotor 22. The rotor 22 can be driven by the stator 20 and can therefore rotate relative to the stator 20 about a machine rotation axis 24. The motor 18 can provide a drive torque for driving the wheels 12 and 14 via the rotor 22. The drive torque is also referred to as torque or first torque. Figure 1 Also shown is a housing 26 of the drive system 10 , wherein the rotor 22 is rotatable relative to the housing 26 about the machine axis of rotation 24 .

[0044] In this example, the electric machine 18 is designed as an axial flux machine (AFM), for example. The rotor 22 has two rotor elements 21 and 23 that are spaced apart from one another in the axial direction of the electric machine 18, which coincides with the machine axis of rotation 24. The rotor 22 is arranged at least partially between the rotor elements 21 and 23 in the axial direction of the electric machine 18, so that the rotor element 21 is at least partially overlapped, i.e., covered, by the stator 20 in the axial direction of the electric machine 18 toward the rotor element 23, and the rotor element 23 is at least partially overlapped, i.e., covered, by the stator 20 in the axial direction of the electric machine 18 toward the rotor element 23, and the rotor element 23 is at least partially overlapped, i.e., covered, by the stator 20 in the axial direction of the electric machine 18 toward the rotor element 21. For example, the rotor elements 21 and 23 are rotor disks. In particular, the rotor elements 21 and 23 are permanently connected to one another in a rotationally fixed manner.

[0045] The electric drive system 10 has a multi-stage gear arrangement 28, which is arranged at least partially in a housing 26, for example. The multi-stage gear arrangement 28 has a first planetary gear set 30, which has a first shaft 32, a second shaft 34 and a third shaft 36. In a first embodiment, the third shaft 36 includes a first sun gear 38 of the first planetary gear set 30. In addition, the first shaft 32 includes a first ring gear 40 of the first planetary gear set 30. The second shaft 34 is designed as a first planet carrier of the first planetary gear set 30, which is also referred to as a first carrier. The first planetary gears are supported on the first planet carrier in a rotatable manner. Figure 1The first of these first planetary gears can be seen in FIG, which is referenced by 42. The respective first planetary gears 42 can rotate relative to the first planet carrier about the respective first planetary gear rotational axis, wherein the first planetary gear rotational axes are parallel to each other in pairs and are parallel to each other in pairs and are spaced apart from each other in pairs. Furthermore, the first planetary gear rotational axes are spaced apart in pairs from the first planetary gear set rotational axis of the first planetary gear set 30. The respective shafts 32, 34, 36 of the first planetary gear set 30 can rotate about the respective first planetary gear axis of rotation, in particular when the respective shafts 32, 34 and 36 of the first planetary gear set 30 are not connected to the housing 26 in a rotationally fixed manner. Figure 1 The first planetary gear set axis of rotation, designated 49 in the figure, rotates relative to the housing 26, wherein the first planetary gear set axis of rotation 49 is also referred to as the main axis of rotation. It can be seen that in the first embodiment, the main axis of rotation coincides with the machine axis of rotation 24, so that in the first embodiment, the first planetary gear set 30 is arranged coaxially with the electric machine 18, in particular coaxially with the rotor 22. The first planetary gear axes of rotation are spaced apart from the main axis of rotation in pairs. In particular, the first planetary gear axes of rotation are spaced apart from each other in a circumferential direction around the main axis of rotation of the electric drive system 10 and are arranged in a particularly uniformly distributed manner, the axial direction of the electric drive system coinciding with this main axis of rotation, i.e., with the first planetary gear set axis of rotation 49, in particular so that the first planetary gear axes of rotation are arranged on a first circle whose center lies on the main axis of rotation (first planetary gear set axis of rotation 49).

[0046] Each first planet gear 42 is assigned a corresponding first planet gear pin 44, also referred to as a first pin for short. In particular, the corresponding first planet gear pin 44 is a component of the first planet carrier. The corresponding first planet gear 42 is rotatably arranged, in particular, mounted on the corresponding first planet gear pin 44 assigned to the corresponding first planet gear 42, in particular such that the corresponding first planet gear 42 can rotate about the corresponding first planet gear axis of rotation relative to the corresponding first planet gear pin 44 assigned to the corresponding first planet gear 42. Particularly preferably, the corresponding first planet gear pin 44 is designed as a single piece, i.e., as a single piece, such that the corresponding first planet gear pin 44 is preferably formed from a single part.

[0047] The electric drive system 10 further comprises a differential gear 46, which in the first embodiment is designed as a planetary differential. The differential gear 46 (simply referred to as a differential) has a differential planet carrier 48 as a differential input shaft. The differential planet carrier 48 is also referred to as a second planet carrier or a second carrier. Figure 1As can be seen in FIG, wheels 12 and 14 can be driven by rotor 22 via differential gearing 46, wherein differential gearing 46 can be driven by rotor 22 via first planetary gear set 30. A corresponding drive torque provided or capable of being provided by rotor 22, or a corresponding second torque generated therefrom, can be provided by first planetary gear set 30 and thus transmitted via first planetary gear set 30 to or onto differential gearing 46, in particular to differential planet carrier 48, and thus introduced via differential planet carrier 48 into differential gearing 46, thereby being able to drive differential gearing 46. Differential planet carrier 48 is rotatable relative to housing 26 about a planet carrier axis of rotation 50, wherein in this case, planet carrier axis of rotation 50 coincides with the main axis of rotation and therefore also with the machine axis of rotation 24.

[0048] The differential gear device 46 has a first differential sun gear 52 as a first differential output shaft and a second differential sun gear 54 as a second differential output shaft. Figure 1 As can be seen in FIG, wheel 12 can be driven by a first differential sun gear 52, and wheel 14 can be driven by a second differential sun gear 54. Differential sun gear 52 is also referred to as the second sun gear, and differential sun gear 54 is also referred to as the third sun gear. The second and third sun gears (differential sun gears 52 and 54) are arranged coaxially with one another and can rotate relative to housing 26 about respective sun gear rotation axes 51. The respective sun gear rotation axes 51 coincide with the planet carrier rotation axis 50 and therefore with the main rotation axis, and in this case also with the machine rotation axis 24.

[0049] The torque introduced or capable of being introduced into the differential gear arrangement 46, whether the corresponding driving torque or the corresponding second torque, is also referred to as the corresponding input torque. The differential gear arrangement 46 can provide the corresponding input torque or the corresponding output torque generated from the corresponding input torque via the corresponding differential output shaft and thereby drive the corresponding wheels 12, 14. The corresponding wheel torque for driving the wheels 12, 14 is Figure 1 5 and 6. The corresponding wheel torque is, for example, the corresponding output torque or a third torque generated from the output torque.

[0050] from Figure 1As can be seen, the first differential sun gear 52 is assigned, for example, a first sideshaft 58, which can be driven by the differential sun gear 52. For example, the sideshaft 58, or at least one length region of the sideshaft 58, is permanently connected to the differential sun gear 52 in a rotationally fixed manner. A second sideshaft 60 is assigned to the differential sun gear 52, which can be driven by the differential sun gear 52. For example, the sideshaft 60, or at least one length region of the sideshaft 60, is permanently connected to the differential sun gear 54 in a rotationally fixed manner. It can be seen that the wheels 12 can be driven by the differential sun gear 52 via the sideshaft 58, which can drive the sideshaft 58. It can also be seen that the wheels 14 can be driven by the differential sun gear 54 via the sideshaft 60, which can drive the sideshaft 60.

[0051] In the first embodiment, the wheels 12 can be driven by the sideshaft 58 via the first transmission unit 62, and the wheels 14 can be driven by the sideshaft 60 via the second transmission unit 64. In the first embodiment, the respective transmission units 62, 64 are designed as respective planetary gear sets, which have a respective further sun gear 66, a respective further planet carrier 68 and a respective further ring gear 70. In addition, the respective further planetary gear set has further planetary gears, Figure 1 , another of these additional planetary gears, designated 72, can be seen. The respective other planetary gear 72 of the respective other planetary gear set (transmission unit 62, 64) is rotatably supported on the respective other planet carrier 68. In the first embodiment, the respective other sun gear 66 represents the respective input of the respective other planetary gear set, which can be driven by the respective sideshaft 58, 60 via its respective input. Furthermore, the respective other planet carrier 68 represents the respective output of the respective planetary gear set, which can drive the respective wheels 12, 14 via its respective output. Thus, the respective wheel 12 can be driven by the respective other planet carrier 68 and, via the respective other planet carrier 68, by the respective other sun gear 66. Furthermore, the respective other ring gear 70 is, for example, permanently connected to the housing 26 in a rotationally fixed manner. For example, the first planetary gear set 30 and / or the differential gear arrangement 46 are each at least partially situated in the housing 26. For example, alternatively or additionally, the respective further planetary gear set or the respective transmission unit 62 , 64 is at least partially arranged in the housing 26 .

[0052] The differential gear device 46 has a first differential compensation wheel. Figure 1The first of these first differential compensating gears, designated 74, can be seen in FIG. The first differential compensating gears 74 are rotatably arranged on the differential planet carrier 48 such that they can rotate relative to the differential planet carrier 48 about their respective first compensating gear rotational axis. Furthermore, the respective first differential compensating gears 74 mesh directly with the first differential sun gear 52 but not with the differential sun gear 54. The first compensating gear rotational axes are spaced apart in pairs and parallel to one another. Furthermore, the respective first compensating gear rotational axes are parallel to the main rotational axis and spaced apart from the main rotational axis. The first compensating gear rotational axes are arranged sequentially and spaced apart from one another in a circumferential direction of the electric drive system 10 about the axial direction of the electric drive system 10 and, therefore, about the main rotational axis. They are particularly evenly distributed, particularly such that the first compensating gear rotational axes are arranged on a second circle whose center lies on the main rotational axis.

[0053] The differential gear device 46 has a second differential compensation wheel. Figure 1 Among these second differential compensating gears, a second differential compensating gear designated 76 can be seen in FIG. The second differential compensating gears 76 are rotatably arranged on the differential planet carrier 48 such that the respective second differential compensating gear 76 can rotate relative to the differential planet carrier 48 about the respective second compensating gear rotation axis. Furthermore, the respective second differential compensating gears 76 mesh directly with the second differential sun gear 54 but not with the differential sun gear 52. The second compensating gear rotation axes are spaced apart in pairs and parallel to one another. Furthermore, the respective second compensating gear rotation axes are parallel to the main rotation axis and spaced apart from the main rotation axis. The second compensating gear rotation axes are arranged sequentially and spaced apart from one another in a circumferential direction of the electric drive system 10 about the axial direction of the electric drive system 10 and, therefore, about the main rotation axis. They are particularly evenly distributed, particularly such that the second compensating gear rotation axes are arranged on a third circle whose center lies on the main rotation axis. The first circle has a first diameter, the second circle has a second diameter, and the third circle has a third diameter. In this example, the second diameter and the third diameter are different from each other, in particular such that the third diameter is, for example, smaller than the second diameter.

[0054] Each of the first differential output wheels 74 meshes with, in particular, exactly one corresponding second differential compensating wheel among the second differential compensating wheels 76. In addition, each of the first planetary gears 42 is coaxially arranged with, in particular, exactly one corresponding first differential compensating wheel among the first differential compensating wheels 74, so that the corresponding planetary gear 42 and the first differential compensating wheel 74 coaxially arranged with the corresponding planetary gear 42 constitute a corresponding wheel pair. The first planetary gears 42, the first differential compensating wheel 74 and the second differential compensating wheel 76, as well as the sun gear 40, the sun gear 38, the differential sun gear 52 and the differential sun gear 54, the sun gear 66, the planetary gears 72 and the ring gear 70 are all gears. Figure 1 As can be seen in the figure, the respective gears of the respective wheelset are rotatably arranged, in particular, mounted, on the respective one-piece first planetary gear pin 44, which is assigned to the respective first planetary gear 42. Thus, the first circle and the second circle have, for example, the same diameter. That is, the first diameter and the second diameter are, for example, identical. The respective second differential compensating gear 76 is, for example, assigned a respective second pin, which can also be designed as a single piece or a single piece. The respective second differential compensating gear 76 is, for example, rotatably arranged on the respective second pin assigned to the respective second differential compensating gear 76, so that the respective second differential compensating gear 76 rotates about the respective second differential compensating gear axis of rotation relative to the respective second pin assigned to the respective second differential compensating gear 76. Thus, it can be seen that the respective first planetary gear pin 44 is a common pin for the respective gears of the respective wheelset, and that both gears of the respective wheelset are rotatably arranged, in particular, mounted, on this common pin.

[0055] When viewed in the axial direction of the electric drive system 10 and therefore along the main rotation axis, the first planetary gear set 30, the first differential sun gear 52 and the second differential sun gear 54 are arranged in the order described, i.e. in the order in which they are mentioned, one after the other, so that when viewed in the axial direction of the drive system 10 and therefore along the main rotation axis (planetary gear set rotation axis 49), the first planetary gear set 30, the first differential sun gear 52 and the second differential sun gear 54 are arranged one after the other in the following order: first planetary gear set 30—first differential sun gear 52—second differential sun gear 54.

[0056] Furthermore, it is provided that the rotor 22 is coupled or can be coupled to the first shaft 32 , so that a corresponding first torque provided or provided by the rotor 22 can be introduced into the first planetary gear set 30 at the first shaft 32 , bypassing the differential gear arrangement 46 .

[0057] To achieve a particularly space-saving and weight-efficient design of the drive system 10, the drive system 10 includes a first shifting unit SE1, which is designed to connect the third shaft 36, and thus, in this example, the sun gear 38, to the housing 26 in a rotationally fixed manner. Furthermore, the drive system 10, also referred to as the drive device, includes a second shifting unit SE2, which is designed to lock the first planetary gear set 30. In the first embodiment, the second shifting unit SE2 is designed to connect the third shaft 36 to the first shaft 32 in a rotationally fixed manner, so that the first sun gear 38 can be connected to the first ring gear 40 in a rotationally fixed manner via the second shifting unit SE2. For example, the second shifting unit SE2 is designed as a friction-locking and therefore force-locking shifting unit and, in this case, as a friction clutch, in particular a multi-plate clutch. Furthermore, in the first embodiment, it is provided, for example, that the first shifting unit SE1 includes a freewheel clutch, which is designed to connect the third shaft 36 to the housing 26 in a rotationally fixed manner when the motor vehicle is being towed. In particular, the traction of the motor vehicle is understood to mean that the rotor 22 provides a torque, in particular a positive torque, in particular in the form of a corresponding drive torque, so that the motor vehicle is driven by the drive torque provided by the rotor 22 and thus moves forward. It can be seen that in the first embodiment, the wheels 12 and 14 are driven via the ring gear 40 of the multi-stage gear arrangement 28. Preferably, a parallel arrangement of the axes of the drive system 10, in particular with respect to the wheels 12 and 14, is provided, wherein alternatively a coaxial arrangement of the drive system 10, in particular with respect to the wheels 12 and 14, in particular as Figure 1 As shown. Figure 1 It can be seen that the first planet carrier of the first planetary gear set 30 , ie the second shaft 34 , is in particular permanently connected in a rotationally fixed manner to the differential planet carrier 48 .

[0058] Figure 2A schematic diagram illustrates a second embodiment of the drive system 10 according to the present invention. In this second embodiment, the first shaft 32 includes the first sun gear 38 of the first planetary gear set 30. Furthermore, in this second embodiment, the third shaft 36 includes the second ring gear 40 of the first planetary gear set 30. Thus, in this second embodiment, the wheels 12 and 14 are driven via the first sun gear 38 (also referred to simply as sun) of the first planetary gear set 30 or the multi-stage gear arrangement 28. In this second embodiment, a parallel or coaxial arrangement of the axes of the drive system 10, particularly with respect to the wheels 12 and 14, is also possible. In this second embodiment, the first shifting unit SE1 is designed to connect the third shaft 36 to the housing 26 in a rotationally fixed manner. In this second embodiment, the second shifting unit SE2 is also designed to lock the first planetary gear set 30. In the second embodiment, the first planetary carrier of the first planetary gear set 30 and therefore the second shaft 34 and the third shaft 36 and therefore the first ring gear 40 of the first planetary gear set 30 can be connected to each other in a torsionally fixed manner by means of the second shifting unit SE2, in this case enabling the second shaft 34 to be connected to the shaft 36 in a torsionally fixed manner by means of the second shifting unit SE2 under the mediation of the differential planetary carrier 48.

[0059] The difference between the first embodiment and the second embodiment lies in that, in the first embodiment, the first shaft 32 includes a first ring gear 40, while in the second embodiment, the first shaft 32 includes a first sun gear 38. Figure 1 In the first variant of the first embodiment shown, the first planetary gear set 30 can be locked by means of the second shifting unit SE2, so that the shaft 36 and therefore the sun gear 38 can be connected in a rotationally fixed manner to the shaft 32 and therefore the ring gear 40 by means of this shifting unit SE2, bypassing the differential carrier 48. In a second variant of the first embodiment not shown in the figures, the first planetary gear set 30 can be locked by means of the second shifting unit SE2, for example, so that the shaft 36 and therefore the sun gear 38 can be connected in a rotationally fixed manner to the first shaft 34 and therefore the first planet carrier of the first planetary gear set 30 by means of the second shifting unit SE2, bypassing the differential carrier 48. In a third variant of the first embodiment not shown in the figures, the first planetary gear set 30 can be locked by means of the second shifting unit SE2, so that the shaft 34 and therefore the first planet carrier of the first planet carrier 30 can be connected in a rotationally fixed manner to the shaft 32 and therefore the ring gear 40 by means of the second shifting unit SE2 through the intermediary of the differential carrier 48.

[0060] exist Figure 2In the first variant of the second embodiment shown, the first planetary gear set 30 can be locked by means of the second shifting unit SE2, so that the shaft 34, and therefore the first planet carrier of the first planetary gear set 30, can be connected in a rotationally fixed manner to the shaft 36, and therefore the ring gear 40, by means of the second shifting unit SE2 through the intermediary of the differential carrier 48. In a second variant of the second embodiment not shown in the figures, the first planetary gear set 30 can be locked by means of the shifting unit SE2, for example, so that the shaft 32, and therefore the sun gear 38, can be connected in a rotationally fixed manner to the shaft 34, and therefore the first planet carrier of the first planetary gear set 30, by means of the second shifting unit SE2, bypassing the differential carrier 48. In a third variant of the second embodiment not shown in the figures, the first planet carrier can be locked by means of the shifting unit SE2, so that the shaft 32, and therefore the sun gear 38, can be connected in a rotationally fixed manner to the shaft 36, and therefore the ring gear 40, by means of the second shifting unit SE2, bypassing the differential carrier 48.

[0061] The corresponding transmission units 62 , 64 are also referred to as final drives, and the final drives are also referred to as Final Drive (FD).

[0062] Figure 3 A second embodiment of a drive system 10 is shown in a schematic front view. Figure 3 It can be seen particularly clearly that the sun gear 38 meshes with the planetary gears 42, which mesh with the ring gear 40. The first differential compensation gear 74 meshes with the differential sun gear 52, and the differential compensation gear 76 meshes with the differential sun gear 54. It can also be seen that each of the differential compensation gears 74 meshes with, in particular, exactly one of the differential compensation gears 76. Figure 3 It can be seen particularly clearly in Figure 3 The wheelsets are designated 78 in FIG. 1 , and it can also be seen that the first gear of the gears of the respective wheelset is one of the first planetary gears 42, and the second gear of the gears of the respective wheelset 78 is one of the first differential compensating gears 74. It can also be seen particularly clearly that the gears of the respective wheelset 78 are arranged coaxially with one another, so that each of the first planetary gear rotation axes coincides with, in particular, exactly one of the first compensating gear rotation axes. The respective gears of the respective wheelset 78 are supported not only on the common first planetary carrier or differential carrier 48 or on the first planetary carrier or differential carrier, but also on the corresponding common first planetary gear pin 44.

[0063] at last, Figure 4 The schematic diagram shows a third embodiment of the electric drive system 10 according to the invention. In the third embodiment, the first shifting unit SE1 is arranged axially overlapping and radially around the differential gear arrangement. Figure 4 In FIG, the corresponding drive torque provided or available by the rotor 22 is indicated by arrow 80 , which drive torque can be introduced or available at the shaft 32 and via the shaft 32 into the first planetary gear set 30 bypassing the differential carrier 48 in this example.

[0064] In the third embodiment, the second shifting unit SE2 is designed to connect the first planet carrier to the shaft 36 in a rotationally fixed manner, particularly through the intermediary of the differential planet carrier 48. In the third embodiment, the electric drive system 10 has an oil channel 82 through which oil can flow, where the oil is also referred to as hydraulic oil. The oil channel 82 has a first section A1 that passes through the housing 26. The oil channel 82 also has a second section A2 that extends in the first planet carrier of the first planetary gear set 30, or as otherwise described. Figure 4 As in the case of the differential planetary carrier 48, the hydraulic oil flowing through the oil channel 82 can be guided, ie delivered, to the actuating piston of the second shifting unit SE2, wherein the second shifting unit SE2 includes the actuating piston. Figure 4 , the oil flow through the oil channel 82 to the actuating piston is indicated by arrow 84. The actuating piston and thus the second shifting unit SE2 can be actuated by means of hydraulic oil, wherein, for example, by actuating the second shifting unit SE2, the first planetary gear set 30 can be locked by means of the shifting unit SE2.

[0065] exist Figure 4 As can be seen in FIG, a shaft seal 88 is arranged between the housing 26, in particular between the housing wall 86 of the housing 26 and the differential planet carrier 48, which is arranged in particular in the radial direction of the drive system 10, in particular between the housing wall 86 and the differential planet carrier 48. The radial direction of the drive system is perpendicular to the axial direction of the drive system 10. As an alternative or in addition to the shaft seal 88 being designed as a shaft sealing ring, a sealed shaft bearing is conceivable. The transfer of hydraulic oil from section A1 to section A2 can be compared, for example, Figure 4 The oil transfer occurs radially further outward. In this case, a seal is also advantageous, for example, for the transfer from the housing wall 86 or the housing 26 to the differential carrier 48. This transfer of hydraulic oil is possible, in particular, because the multi-plate carrier of the second shifting unit SE2, designed as a multi-plate clutch, is permanently and non-rotatably connected to the differential carrier 48 or its carrier shaft. The detailed descriptions above and below regarding the differential carrier 48, especially with respect to the oil channels 82, can also be easily transferred to the first carrier of the first planetary gear set 30, and vice versa. Advantageously, the differential carrier 48 or the first carrier (in which the second section A2 extends) is a slowly rotating shaft.

[0066] In addition, from Figure 4Bearings 90a-90c can be seen in the figure. For example, the respective bearings 90a-90c are designed as rolling bearings or sliding bearings. The respective first planetary gear 42 is rotatably supported on the first planetary gear pin 44, in particular on the first planetary gear pin, via the respective bearing 90a. The respective first differential compensating gear 74 is rotatably supported on the first planetary gear pin 44, in particular on the first planetary gear pin, via the respective bearing 90b. The respective second differential compensating gear 76 is rotatably supported on the respective second pin 92 of the differential carrier 48, in particular on the second pin, via the respective bearing 90c. It is particularly provided that the respective second pin 92 is provided in addition to the first planetary gear pin 44 and is designed independently of the first planetary gear pin 44.

[0067] It is particularly conceivable that the respective transmission units 62, 64, arranged downstream of the respective sideshafts 58, 60, in particular between the respective sideshafts 58, 60 and the respective wheels 12, 14, could be designed as simple spur gear stages, for example with an axis offset. It can be seen that the housing wall 86 is arranged perpendicular to the main rotation axis, i.e., perpendicular to the axial direction of the electric drive system 10. In other words, the housing wall 86 is perpendicular to the main rotation axis. In other words, the housing wall 86 extends in a plane perpendicular to the main rotation axis. Here, the first section A1 extends in the housing wall 86.

[0068] Reference Signs List

[0069] 10 Electric Drive System

[0070] 12 wheels

[0071] 14 wheels

[0072] 16 axles

[0073] 18 Motor

[0074] 20 stator

[0075] 21 rotor elements

[0076] 22 rotors

[0077] 23 rotor elements

[0078] 24 Machine rotation axis

[0079] 26 housing

[0080] 28 Multi-stage gear unit

[0081] 30 First planetary gear set

[0082] 32 First axis

[0083] 34 Second axis

[0084] 36 Third Axis

[0085] 38 First sun gear

[0086] 40 First ring gear

[0087] 42 First planetary gear

[0088] 44 First planetary gear pin

[0089] 46 Differential gear unit

[0090] 48 differential planetary carrier

[0091] 49 First planetary gear set rotation axis 50 Planet carrier rotation axis

[0092] 51 Sun gear rotation axis

[0093] 52 First differential sun gear

[0094] 54 Second differential sun gear 55 Arrow

[0095] 56 Arrow

[0096] 58 side shaft

[0097] 60 side shaft

[0098] 62 transmission unit

[0099] 64 transmission unit

[0100] 66 Another sun gear

[0101] 68 Another planetary carrier

[0102] 70 Another ring gear

[0103] 72 Another planetary gear 74 First differential compensation wheel 76 Second differential compensation wheel 78 Wheel set

[0104] 80 Arrow

[0105] 82 oil channel

[0106] 84 Arrow

[0107] 86 Shell wall

[0108] 88 Shaft seal

[0109] 90a-c Bearing 92 Second pin A1 First section

[0110] A2 Second section SE1 First shifting unit SE2 Second shifting unit

Claims

1. An electric drive system (10) for a motor vehicle, comprising: an electric motor (18) having a stator (20) and a rotor (22); A multi-stage gear arrangement (28) having a first planetary gear set (30) comprising: ○First axis (32); a second shaft (34) configured as a first planetary carrier, the first planetary gear (42) being rotatably supported on the first planetary carrier; and ○Third axis (36); and - a differential gear device (46), said differential gear device comprising: ○ A differential planet carrier (48) serving as a differential input shaft; ○ A first differential sun gear (52) serving as a first differential output shaft; ○ A second differential sun gear (54) serving as a second differential output shaft; a first differential compensating wheel (74), which is rotatably arranged on the differential planet carrier (48) and meshes with the first differential sun gear (52); and a second differential compensating wheel (76), which is rotatably arranged on the differential planet carrier (48) and meshes with the second differential sun wheel (54), wherein: ● meshing each of the first differential compensating wheels (74) with a corresponding one of the second differential compensating wheels (76); When viewed in the axial direction, the first planetary gear set (30), the first differential sun gear (52), and the second differential sun gear (54) are arranged in the following order: the first planetary gear set (30)—the first differential sun gear (52)—the second differential sun gear (54); and The rotor (22) is coupled or couplable to the first shaft (32) such that torque that can be provided by the rotor (22) can be introduced into the first planetary gear set (30) at the first shaft (32) bypassing the differential gearing (46): in: - the first shifting unit (SE1) is designed to connect the third shaft (36) to the housing (26) of the electric drive system (10) in a rotationally fixed manner; and - a second shifting unit (SE2) is designed to lock the first planetary gear set (30), It is characterized by: The first planet carrier is connected to the differential planet carrier (48) in a torsionally fixed manner, each of the first planetary gears (42) and a corresponding first differential compensation gear (74) are arranged coaxially with each other, and the first shifting unit (SE1) is axially overlapped and radially arranged around the differential gear device (46).

2. The electric drive system (10) according to claim 1, It is characterized by: The second shifting unit (SE2) is designed to connect the first planetary carrier to the first shaft (32) in a rotationally fixed manner and thus to lock the first planetary gear set (30).

3. The electric drive system (10) according to claim 1, It is characterized by: The second shifting unit (SE2) is designed to connect the first planetary carrier to the third shaft (36) in a rotationally fixed manner and thus to lock the first planetary gear set (30).

4. The electric drive system (10) according to claim 3, It is characterized by: - the third shaft (36) comprises the first ring gear (40) of the first planetary gear set (30); - the first shaft (32) includes the first sun gear (38) of the first planetary gear set (30); The second shifting unit (SE2) is arranged axially on a side (S1) of the first shifting unit (SE1) facing away from the first planetary gear set (30).

5. The electric drive system (10) according to any one of the preceding claims, It is characterized by: An oil channel (82) is designed to convey hydraulic oil for actuating the second shifting unit (SE2) to an actuating piston of the second shifting unit (SE2), wherein the oil channel (82) has a first section (A1) extending in the housing (26) and a second section (A2) extending in the first planet carrier or the differential planet carrier (48).

6. The electric drive system (10) according to claim 5, It is characterized by: The housing (26) has a housing wall (86) arranged perpendicular to a main rotation axis of the electric drive system (10), wherein the second shifting unit (SE2) is arranged adjacent to the housing wall (86), and wherein the first section (A1) is arranged within the housing wall (86).

7. A motor vehicle having an electric drive system (10) according to any one of the preceding claims.

Images