Electric drive system for a motor vehicle, in particular for a car, as well as motor vehicle

Abstract

Electric drive system (10) for a motor vehicle, comprising: - an electric machine (18) which has a stator (20) and a rotor (22); - a multi-stage transmission (28) which has a first planetary gear set (30) which has: ◯ a first wave (32); ◯ a second shaft (34), which is designed as a first planet carrier, on which first planet gears (42) are rotatably mounted; and ◯ a third wave (36); and - a differential gear (46) which has: ◯ a differential planetary carrier (48) as differential input shaft; ◯ a first differential sun gear (52) as the first differential output shaft; ◯ a second differential sun gear (54) as a second differential output shaft; ◯ first differential differential gears (74), which are rotatably arranged on the differential planetary carrier (48) and mesh with the first differential sun gear (52); and ◯ second differential differential gears (76), which are rotatably arranged on the differential planetary carrier (48) and mesh with the second differential sun gear (54), wherein: ▪ each of the first differential compensating gears (74) meshes with one of the second differential compensating gears (76); ▪ viewed along an 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 can be coupled to the first shaft (32) in such a way that torques available from the rotor (22) can be introduced into the first planetary gear set (30) at the first shaft (32) bypassing the differential gear (46): wherein: - a first switching unit (SE1) is configured to connect the third shaft (36) rotationally fixedly to a housing (26) of the electric drive system (10); and - a second switching unit (SE2) is designed to lock the first planet gear set (30), characterized in that the first planet carrier is rotationally fixed to the differential planet carrier (48), one of the first planet gears (42) and one of the first differential differential gears (74) are arranged coaxially to each other and the first switching unit (SE1) is arranged axially overlapping and radially surrounding the differential gear (46).

Description

[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. Furthermore, the invention relates to a motor vehicle, in particular a car.

[0002] DE 10 2018 008 939 B3 discloses an electric drive device as known, comprising a housing and a first planetary gear set arranged in the housing. Furthermore, DE 10 2018 128 836 B3 discloses a transmission device for a motor vehicle.

[0003] DE 10 2017 111 049 A1 discloses a drive device comprising an electric machine, a first planetary gear set, and a planetary differential, wherein a planet carrier of the first planetary gear set is coupled to a planet carrier of the planetary differential, and wherein a rotor of the electric machine is coupled to a ring gear of the first planetary gear set. WO 2018 / 019 324 A1 also discloses a system comprising an electric machine, a first planetary gear set, and a planetary differential, wherein in this case the rotor of the electric machine, the first planetary gear set, and the planetary differential are all arranged coaxially with respect to each other.

[0004] The object of the present invention is to create an electric drive system for a motor vehicle and a motor vehicle with such an electric drive system, so that a particularly compact and lightweight design can be achieved.

[0005] This problem is solved by an electric drive system with the features of claim 1 and by a motor vehicle with the features of claim 7. Advantageous embodiments with expedient further developments of the invention are specified in the remaining claims.

[0006] The starting point is an electric drive system for a motor vehicle, particularly a passenger car, also referred to as an electric drive device or designed as such. This means that the motor vehicle, also simply called a vehicle, in its fully manufactured state, has the electric drive system and can be driven, in particular purely electrically, by means of the electric drive system. For this purpose, the electric drive system includes an electric machine, which has a stator and a rotor. The rotor can be driven by means of the stator and is thus rotatable, for example, about a machine axis of rotation relative to the stator. The electric drive system can provide torques for driving the motor vehicle via the rotor.The motor vehicle, in its fully manufactured state, has, for example, at least or exactly two axles arranged consecutively and thus one behind the other in the longitudinal direction of the vehicle. Each axle has at least or exactly two wheels. The wheels of each axle are located on opposite sides of the vehicle in the transverse direction. The wheels are ground contact elements by which the vehicle can be supported or is supported downwards against the ground. When the vehicle is driven along the ground while supported downwards by the ground contact elements, the wheels roll along the ground, in particular directly.For example, the vehicle wheels of at least one or exactly one of the vehicle axles can be driven by the electric drive system, in particular by the electric machine and especially by the rotor. When the vehicle wheels are mentioned below, unless otherwise specified, this refers to the vehicle wheels that can be driven by the drive unit.

[0007] The electric drive system features a multi-stage gearbox comprising a first planetary gear set. The first planetary gear set includes a first shaft, a second shaft, and a third shaft. The second shaft serves as the first planet carrier of the first planetary gear set, with the first planet gears rotatably mounted on this carrier. The first planet carrier is referred to as the first web. The first shaft, the second shaft, and the third shaft are also referred to as the first gear elements of the first planetary gear set. Specifically, the first gear elements are arranged coaxially with each other. The electric drive system includes a housing, in which, for example, the first planetary gear set is at least partially located.Particularly when the respective first gear element is not rotationally fixed to the housing, it is rotatable about a first planetary gear set axis of rotation relative to the housing. Especially when the first gear elements are arranged coaxially, the first planetary gear set axis of rotation can, for example, be a common axis of rotation for the first gear element. The first gear elements are also referred to as planetary gear set elements, with the first planetary gear set element being the second shaft and thus the first planet carrier of the first planetary gear set. A second planetary gear set element comprises, for example, a first sun gear of the first planetary gear set. Furthermore, it is conceivable that a third planetary gear set element comprises a first ring gear of the first planetary gear set.In this process, for example, the respective first planet gear meshes, especially simultaneously, with both the first sun gear and the first ring gear of the first planet gear set.

[0008] Within the context of the present disclosure, ordinal words such as "first", "first", "first", "second", "second", "second", etc. are not necessarily used to indicate a number of elements to which the ordinal words refer, but rather to be able to refer unambiguously to the elements to which the ordinal words refer.

[0009] The electric drive system also features a differential gear, which has a differential planetary carrier as its differential input shaft. The differential planetary carrier is also referred to as the second planetary carrier or second web. The respective torque provided or available from the rotor is also referred to as the drive torque. Whenever the respective torque is mentioned before and below, unless otherwise specified, it refers to the respective torque provided or available from the rotor. For example, the respective drive torque provided or available from the rotor, or any further torque resulting from the respective drive torque, can be introduced into the differential gear via the differential input shaft, thereby driving the differential gear.The differential gear is, for example, assigned to or part of the vehicle axle, whose wheels can be driven by the drive system. The driven wheels are also referred to as drive wheels. In particular, the rotor can drive the vehicle wheels (drive wheels) via the differential gear. The differential gear has, for example, a function well known from the prior art, such as allowing different rotational speeds of the drive wheels when the vehicle is cornering, specifically such that the outer drive wheel rotates, or can rotate, at a higher speed than the inner drive wheel.Furthermore, the differential gear serves, for example, to divide or distribute the respective drive torque introduced into the differential gear, or the respective additional torque resulting from the respective drive torque and introduced into the differential gear, to the drive wheels, so that, for example, the drive wheels can be driven or are driven by the rotor, while the drive wheels rotate at different speeds, for example, during the aforementioned cornering maneuver.

[0010] The differential gear also features a first differential sun gear as the first differential output shaft. The first differential sun gear is also referred to as the second sun gear. Furthermore, the differential gear features a second differential sun gear as the second differential output shaft, with the second differential sun gear also being referred to as the third sun gear. For example, one of the drive wheels is driven by the first differential output shaft, and another of the drive wheels is driven by the second differential output shaft.The respective drive torque introduced into the differential gear, or the respective additional torque introduced into the differential gear, or a respective third torque resulting from the respective drive torque introduced into the differential gear, or from the additional torque introduced into the differential gear, can be transmitted via the respective differential output shaft to or to the respective drive wheel, which can be driven by the respective differential output shaft, thereby enabling the drive wheels to be driven or being driven.

[0011] The first differential sun gear is rotatable about a first sun gear axis of rotation relative to the housing, and the second differential sun gear is rotatable about a second sun gear axis of rotation relative to the housing. In particular, it is conceivable that the differential sun gears are arranged coaxially with each other, so that the sun gear axes of rotation preferably coincide. The differential planetary carrier is rotatable about a planetary carrier axis of rotation relative to the housing. It is particularly provided that the differential planetary carrier is arranged coaxially with the first differential sun gear and coaxially with the second differential sun gear, so that the planetary carrier axis of rotation preferably coincides with the first sun gear axis of rotation and with the second sun gear axis of rotation.In particular, it is conceivable that the differential planetary carrier, the first differential sun gear, and the second differential sun gear constitute the second gear elements of the differential gear, whereby, for example, the second gear elements can be rotatable relative to each other about their respective sun gear axis or planetary carrier axis. It is conceivable that the first planetary gear set axis of rotation coincides with the machine axis of rotation, so that, for example, the first planetary gear set is arranged coaxially with the electric machine, and thus coaxially with the rotor. Alternatively or additionally, it is conceivable that the differential gear is arranged coaxially with the electric machine, so that the planetary carrier axis of rotation or the sun gear axis of rotation coincides with the machine axis of rotation.Furthermore, it is conceivable that the first planetary gear set is arranged coaxially to the differential gear, so that, for example, the first planetary gear axis of rotation coincides with the respective sun gear axis of rotation or with the planet carrier axis of rotation.

[0012] The differential gear comprises first differential differential gears, which are rotatably mounted on the differential planetary carrier, in particular by bearings. Each first differential differential gear meshes with the first differential sun gear and, for example, not with the second differential sun gear. The differential gear also comprises second differential differential gears, which are rotatably mounted on the differential planetary carrier and mesh with the second differential sun gear. Thus, each second differential differential gear meshes with the second differential sun gear, but preferably not with the first differential sun gear. For example, each first differential differential gear is rotatable about a respective first differential gear axis of rotation relative to the differential planetary carrier, wherein, for example, the first differential gear axes of rotation run parallel to each other in pairs and are spaced apart in pairs.Furthermore, the respective first differential gear axis of rotation runs parallel to the planet carrier axis of rotation, and is spaced apart from the planet carrier axis of rotation. In particular, the first differential gear axes of rotation are spaced apart from each other in the circumferential direction of the differential gear around the planet carrier axis of rotation and are arranged in an evenly spaced manner.

[0013] For example, each second differential gear is rotatable about a second differential gear axis of rotation relative to the differential planetary carrier, wherein, for example, the second differential gear axes of rotation run parallel to each other in pairs and are spaced apart from each other and from the first differential gear axes of rotation. Furthermore, each second differential gear axis of rotation runs parallel to the planetary carrier axis of rotation, and is spaced apart from the planetary carrier axis of rotation. In particular, the second differential gear axes of rotation are spaced apart from each other in the circumferential direction of the differential gear around the planetary carrier axis of rotation and are arranged in a particularly evenly distributed manner. It is specifically provided that each second differential gear axis of rotation runs parallel to and is spaced apart from the first differential gear axes of rotation.

[0014] Furthermore, it is provided, for example, that each first planet gear is rotatable about its respective first planet gear axis relative to the first planet carrier. The first planet gear axes run parallel to each other in pairs, and are spaced apart from each other in pairs. In addition, each first planet gear axis is spaced apart from the first planet gear set axis of rotation, and runs parallel to the first planet gear set axis of rotation. The first planet gear axes of rotation are spaced apart from each other in the circumferential direction of the first planet gear set around the first planet gear set axis of rotation, and are arranged in a particularly even distribution. Specifically, the first planet gear axis of rotation is arranged on a first circle whose center lies on the first planet gear set axis of rotation.For example, the first compensating gear axes are arranged on a second circle whose center lies on the planet carrier axis of rotation. For example, the second compensating gear axes are arranged on a third circle whose center lies on the planet carrier axis of rotation. It is particularly provided that the first circle has a first diameter, the second circle a second diameter, and the third circle a third diameter. In particular, it is provided that the second diameter and the third diameter differ from each other, especially such that the second diameter is smaller or larger than the third diameter.

[0015] In the electric drive system, it is further provided that one of the first differential compensating gears meshes, in particular directly, with, in particular exactly, one of the second differential compensating gears.

[0016] Viewed along an axial direction of the electric drive system, whose axial direction coincides with or runs along the planet gear set's axis of rotation, the first planet gear set, the first differential sun gear, and the second differential sun gear are arranged in the aforementioned order, that is, in the order in which they are named, one after the other, so that, viewed along the axial direction of the electric drive system, the first planet gear set, the first differential sun gear, and the second differential sun gear are arranged in the following order, that is, consecutively: the first planet gear set - the first differential sun gear - the second differential sun gear.In other words, viewed axially in the electric drive system, the first differential sun gear follows the first planetary gear set, and the second differential sun gear follows the first differential sun gear. This allows for a particularly compact and lightweight design of the electric drive system, enabling the vehicle to be driven with exceptional efficiency. In particular, this allows for a particularly long electric range of the vehicle. Furthermore, the invention enables a particularly compact design of the, preferably switchable, multi-stage transmission, which, for example, can be configured as a switchable multi-speed transmission.

[0017] The rotor of the electric machine is coupled or can be coupled to the first shaft in such a way that the torques provided or that can be provided by the rotor can be introduced into the first planetary gear set via the first shaft, bypassing the differential gear. The characteristic that the respective torque provided or that can be provided by the rotor can be introduced into the first planetary gear set via the first shaft, bypassing the differential gear, means that the respective torque provided or that can be provided by the rotor bypasses the differential gear on its way from the rotor to the first shaft; that is, it does not flow from the rotor to the first shaft via the differential gear.In other words, the respective torque that can be provided or is provided by the rotor can be transmitted along a torque flow from the rotor to or onto the first shaft, wherein the differential gear is not located in the torque flow from the second shaft to the rotor and the first shaft, in particular such that the differential gear is located outside the torque flow, which, for example, begins at the rotor and ends at the first shaft. In particular, the rotor can be coupled or connected to the first shaft in a torque-transmitting manner, and especially in a rotationally fixed manner. It is also conceivable that the rotor is permanently connected to the first shaft in a torque-transmitting manner, and especially in a rotationally fixed manner.

[0018] To achieve a particularly compact and lightweight design or construction of the electric drive system, as well as particularly efficient operation of the drive system, it is provided, in a manner known per se, that the electric drive system has a first switching unit which is 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 switching unit. The first switching unit can thus be switched between a first coupling state and a first decoupling state. In the first coupling state, the third shaft is connected to the housing in a rotationally fixed manner by means of the first switching unit, thereby preventing relative rotations of the third shaft and the housing about the planetary gear set's axis of rotation.In the first decoupling state, the first switching unit releases the third shaft for rotations around the planetary gear set axis and relative to the housing, so that in the first decoupling state the third shaft can be rotated around the planetary gear set axis relative to the housing.

[0019] The electric drive system also features a second switching unit, designed to lock the first planetary gear set, in a manner known per se. This enables a particularly compact and lightweight design as well as highly efficient operation of the drive system. The switching unit can be switched between a second coupling state and a second decoupling state. In the second coupling state, the first planetary gear set is locked by means of the second switching unit. In other words, in the second coupling state of the second switching unit, the locking of the first planetary gear set is activated. In the second decoupling state, the locking of the first planetary gear set is deactivated, i.e., removed.The locking of the first planetary gear set means that, in the second coupling state of the second switching unit, two of the shafts of the first planetary gear set are rotationally fixed to each other by means of the second switching unit. This ensures that when the first planetary gear set is driven, the entire planetary gear set—that is, the first gear elements or the shafts of the first planetary gear set—rotates as a single unit and thus together, i.e., at the same angular velocity. Consequently, they rotate together, or simultaneously, at the same angular velocity around the first planetary gear set's axis of rotation relative to the housing. In the second decoupling state, the second switching unit allows relative rotations of the shafts around the planetary gear set's axis of rotation. In this second coupling state, the shafts are rotationally fixed to each other by means of the second switching unit.

[0020] According to the invention, the first planet carrier is permanently and rotationally fixed to the differential planet carrier. Furthermore, according to the invention, one of the first planet gears and, in particular, one of the first differential differential gears are arranged coaxially to each other. Thus, it is particularly provided that the first diameter and the second diameter are the same. For example, the first diameter corresponds to the second diameter. Therefore, for example, the respective first planet gear and the respective first differential differential gear arranged coaxially to the respective first planet gear form a gear pair.

[0021] In order to achieve a particularly compact and space-saving design as well as a particularly efficient operation of the drive system, it is further provided according to the invention that the first switching unit is arranged axially overlapping and radially surrounding the differential gear.In particular, the feature that the first switching unit is arranged radially surrounding the differential gear means, for example, that at least a length of the differential gear in the circumferential direction of the drive system extending around the axial direction of the drive system is at least partially, in particular at least predominantly and thus at least more than half or completely, surrounded by the first switching element, so that the first switching element, for example, in the circumferential direction of the electric drive system, runs at least partially, in particular at least predominantly and thus at least more than half or completely, around the said length.

[0022] Unless otherwise specified, the terms "axial" and "radial" refer to the planetary gear set's axis of rotation, which is also referred to as the main axis of rotation. The first transmission elements, namely the first shaft, the second shaft, and the third shaft of the first planetary gear set, are arranged coaxially with the main axis of rotation. In particular, the differential gear is arranged coaxially with the main axis of rotation, such that preferably the first differential gear axis of rotation, the second differential gear axis of rotation, and the planet carrier axis of rotation coincide with the main axis of rotation. The term or feature "radially within" means that an element, particularly one rotatably mounted, is arranged radially within another rotatably mounted element when it is located within a region of smaller radii.Thus, for example, the largest radius of the radially inner element is smaller than the smallest radius of the radially outer element. Accordingly, the term or feature "radially outer" means that an element, particularly one rotatably mounted, is arranged radially outer from another element, particularly one rotatably mounted, if it is located in an area of ​​larger radii, such that the smallest radius of the radially outer element is larger than the largest radius of the radially inner element. Furthermore, the term or feature "axially overlapping" means that two elements are arranged in an axially overlapping manner, particularly with respect to each other, if they are at least partially located in the same axial area.In other words, two elements are arranged axially overlapping, particularly with respect to each other, if the two elements have at least partially the same coordinates with respect to a reference axis extending, in particular, in the axial direction of the electrical drive system. The term "coaxial" means that two rotatably mounted elements are arranged coaxially with respect to each other if they are rotatable about the same axis of rotation, in particular relative to each other and / or relative to the housing.

[0023] Within the scope of this disclosure, the feature that two components are rotationally fixed to one another is understood to mean that the components connected in such a rotationally fixed manner are arranged coaxially to one another and, in particular when the components are driven, rotate together or simultaneously about a common axis of rotation, such as the planetary gear set axis of rotation, at the same angular velocity, especially relative to the housing. The feature that two components are connected to one another in a torque-transmitting manner is understood to mean that the components are coupled or connected to one another in such a way that torques can be transmitted between the components, wherein, if the components are connected in a rotationally fixed manner, they are also connected to one another in a torque-transmitting manner.

[0024] The characteristic that two components are permanently connected to each other in a torque-transmitting manner means that there is no switching element that can be switched between a coupled state connecting the components in a torque-transmitting manner and a decoupling state in which no torque can be transmitted between the components via the switching element. Rather, the components are always and therefore permanently torque-transmitting, meaning they are connected to each other via the switching element in such a way that torque can be transmitted between them. Thus, for example, one component can be driven by the other, and vice versa.In particular, the feature that components are permanently and rotationally fixed to one another means that a switching element is not provided which can be switched between a coupling state that connects the components rotationally fixed to one another and a decoupling state in which the components are decoupled from each other and rotatable relative to each other, so that no torques can be transmitted between the components via the switching element. Rather, the components are always, i.e., permanently and rotationally fixed to one another. The feature that two components can be connected or coupled to one another in a rotationally fixed or torque-transmitting manner means, in particular, that the components are assigned a switching element which can be switched between at least one coupling state and at least one decoupling state.In the coupled state, the components are connected to each other in a rotationally fixed or torque-transmitting manner via the switching element. In the decoupling state, the components are decoupled from each other, so that in the decoupling state the components can rotate relative to each other, particularly about a component rotation axis, such as the aforementioned common axis of rotation of the components, and in particular so that no torques can be transmitted between the components via the switching element. Put another way, the characteristic "rotationally fixed" means the following: Two rotatably mounted elements are rotationally fixed to each other if they are arranged coaxially and connected in such a way that they rotate at the same angular velocity.

[0025] Preferably, the first switching unit has a freewheel clutch designed to connect the third shaft to the housing in a rotationally fixed manner during a forward pulling movement of the motor vehicle.

[0026] To achieve a particularly lightweight and space-saving design for the drive system, it is preferably provided that the respective first planet gear and the respective first differential gear arranged coaxially to the respective first planet gear, i.e., the respective first planet gear of the respective gear pair and the respective first differential gear of the respective gear pair, are each arranged, particularly rotatably, on a single, one-piece, common planet gear bolt, and preferably mounted on it. Preferably, the respective one-piece, common planet gear bolt is designed as a steel bolt, i.e., made of a single piece of steel. In particular, the feature "one-piece" is to be understood as follows: A component is one-piece, i.e., formed in one piece, if it has no joint, such as a joining point.In other words, the one-piece component, such as the respective one-piece planetary gear bolt, is formed in one piece, meaning it is made from a single piece, so that, for example, the one-piece component, such as the respective one-piece planetary gear bolt, is manufactured by primary forming processes such as casting or forging, so that the one-piece component, such as the one-piece planetary gear bolt, is formed as a casting or as a forging.In other words, a one-piece component, such as a one-piece planetary gear bolt, is formed from a single piece and is therefore a monoblock, meaning it is a single, integrally manufactured body. To put it another way, the one-piece component, such as a one-piece planetary gear bolt, is not composed of several separately manufactured and joined components, but rather is formed from a single piece.

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

[0028] Another embodiment is characterized in that the second switching 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 switching unit. This allows for a particularly advantageous switching capability of the drive system to be achieved in a particularly compact and lightweight manner. In a further, particularly advantageous embodiment of the invention, the second switching 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 switching unit.This allows for a particularly advantageous switching capability of the drive system in a way that is especially economical in terms of weight and installation space, thus enabling a particularly efficient and advantageous operation.

[0029] In order to keep the installation space requirement of the electric drive system particularly low, especially in the axial direction of the drive system and thus along the planetary gear set rotation axis, it is provided in a further embodiment of the invention that the third shaft comprises the third ring gear of the first planetary gear set and the first shaft comprises the first sun gear of the first planetary gear set.

[0030] The second switching unit is preferably designed to connect the first planet carrier to the third shaft in a rotationally fixed manner. To keep the installation space and weight of the drive system to a particularly low level, it is further preferably provided that the second switching unit is arranged on a side of the first switching unit facing away from the first planet gear set, particularly in the axial direction of the drive system.

[0031] Another embodiment features an oil channel. The oil channel is a channel through which oil flows, for example, during operation of the electric drive system. The oil channel is designed to guide and transport oil, also known as hydraulic oil, to an actuating piston of the second switching unit. The oil channel has a first section running within the housing and a second section running within the first planet carrier. This allows for a particularly space-saving and demand-based actuation of the second switching unit. For example, the second coupling state is also referred to as the first state of the second switching unit, and the second decoupling state is also referred to as the second state of the second switching unit.For example, the second switching unit can be switched from one state to the other by means of the hydraulic oil, i.e., by means of the hydraulic oil being guided and thus transported to the actuating piston via the oil channel, for example in such a way that the second switching unit can be switched from the second decoupling state to the second coupling state by means of the hydraulic oil.

[0032] It has proven particularly advantageous if the housing has a housing wall that is arranged or extends perpendicular to the main axis of rotation, i.e., perpendicular to the planetary gear axis of rotation. In other words, the housing wall extends in a plane perpendicular to the main axis of rotation (planetary gear set axis of rotation), with the second switching unit being arranged adjacent to the housing wall, particularly when viewed in the axial direction of the drive system, and preferably with the first section being arranged within the housing wall. This ensures a particularly advantageous supply of hydraulic oil to the actuating piston in a space-saving and weight-efficient manner.

[0033] A second aspect of the invention relates to a motor vehicle, also simply referred to as a vehicle, which is preferably designed as a motor car, in particular a passenger car, and has an electric drive system according to the first aspect of the invention and can be driven electrically by means of the electric drive system, in particular purely electrically. Advantages and advantageous embodiments of the first aspect of the invention are to be regarded as advantages and advantageous embodiments of the second aspect of the invention and vice versa.

[0034] Further advantages, features, and details of the invention will become apparent from the following description of preferred embodiments and from the drawings. The features and combinations of features mentioned above in the description, as well as those mentioned below in the figure description and / or shown in the figures alone, can be used not only in the combinations specified, but also in other combinations or individually, without departing from the scope of the invention.

[0035] The drawing shows in: Fig. 1 a schematic representation of a first embodiment of an electric drive system for a motor vehicle not falling under claim 1; Fig. 2 a schematic representation of a second embodiment of the electric drive system; Fig. 3. Partially a schematic front view of the electric drive system; and Fig. 4 a schematic representation of a third embodiment of the electric drive system.

[0036] In the figures, identical or functionally equivalent elements are provided with the same reference symbols.

[0037] Fig. Figure 1 shows a schematic representation of a first embodiment of an electric drive system 10 for a motor vehicle, not falling under claim 1. This means that the motor vehicle, also referred to simply as the vehicle, which is preferably designed as a motor car, in particular as a passenger car, has the drive system 10 in its fully manufactured state and can be driven electrically by means of the drive system 10, in particular purely. The motor vehicle has, for example, at least or exactly two axles arranged one behind the other in the longitudinal direction of the motor vehicle. Each axle has, for example, at least or exactly two wheels. The electric drive system 10 can drive the wheels of at least one of the axles electrically, in particular purely, thereby enabling the motor vehicle to be driven electrically.The vehicle wheels that can be driven by the drive system are also called drive wheels and are in . Fig. 1 is shown particularly schematically and labelled 12 and 14. The vehicle axle comprising vehicle wheels 12 and 14 is labelled 16.

[0038] The electric drive system 10 has a Fig. Figure 1 shows a particularly schematic representation of an electric machine 18, which has a stator 20 and a rotor 22. The rotor 22 can be driven by means of the stator 20 and is thus rotatable about a machine axis of rotation 24 relative to the stator 20. Via the rotor 22, the electric machine 18 can provide drive torques for driving the vehicle wheels 12 and 14. The drive torques are also referred to as torques or first torques. Particularly schematic representation in Fig. Figure 1 also shows a housing 26 of the drive system 10, wherein the rotor 22 is rotatable about the machine axis of rotation 24 relative to the housing 26.

[0039] In the present case, the electric machine 18 is designed, for example, as an axial flux machine (AFM). The rotor 22 comprises two rotor elements 21 and 23, which are spaced apart from each other in the axial direction of the electric machine 18, whose axial direction coincides with the machine's axis of rotation 24. The rotor 22 is arranged, at least partially, in the axial direction of the electric machine 18 between the rotor elements 21 and 23, such that the rotor element 21 overlaps, and thus is covered, at least partially by the stator 20 in the axial direction of the electric machine 18 towards the rotor element 23. For example, the rotor elements 21 and 23 are rotor disks. In particular, the rotor elements 21 and 23 are permanently and rotationally fixedly connected to each other.

[0040] The electric drive system 10 has a multi-stage transmission 28, which is, for example, at least partially arranged in the housing 26. The multi-stage transmission 28 has a first planetary gear set 30, which comprises a first shaft 32, a second shaft 34, and a third shaft 36. In the first embodiment, the third shaft 36 includes a first sun gear 38 of the first planetary gear set 30. The first shaft 32 also 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, the first planet carrier of which is also referred to as the first web. First planet gears are rotatably mounted on the first planet carrier. Of the first planet gears, Fig. 1. A first planet gear is identifiable and designated 42. The respective first planet gear 42 is rotatable about a respective first planet gear axis of rotation relative to the first planet carrier, wherein the first planet gear axes of rotation run parallel to each other in pairs and are spaced apart from each other in pairs. Furthermore, the first planet gear axes of rotation are spaced apart in pairs from a first planet gear set axis of rotation of the first planet gear set 30. The respective shaft 32, 34, 36 of the first planet gear set 30 is, in particular, when the respective shaft 32, 34 and 36 of the first planet gear set 30 is not rotationally fixed to the housing 26, in order to Fig. The first planetary gear set axis of rotation, designated 49, is rotatable relative to the housing 26, and this axis of rotation 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 with the rotor 22. The first planetary gear sets are spaced apart from the main axis of rotation in pairs.In particular, the first planet gear axes of rotation in the circumferential direction of the electric drive system 10, whose axial direction coincides with the main axis of rotation, and thus with the first planet gear set axis of rotation 49, are spaced apart from one another and are arranged in a particularly even distribution, especially such that the first planet gear axes of rotation are arranged on a first circle whose center lies on the main axis of rotation (first planet gear set axis of rotation 49).

[0041] Each first planet gear 42 is associated with a corresponding first planet gear bolt 44, which is also simply referred to as the first bolt. In particular, the corresponding first planet gear bolt 44 is a component of the first planet carrier. The corresponding first planet gear 42 is rotatably mounted on the corresponding first planet gear bolt 44, and in particular, is supported such that the corresponding first planet gear 42 is rotatable about its axis of rotation relative to the corresponding first planet gear bolt 44. Most preferably, the corresponding first planet gear bolt 44 is formed in one piece, i.e., as a single component.

[0042] The electric drive system 10 also includes a differential gear 46, which in the first embodiment is designed as a planetary differential. The differential gear 46, also simply referred to as the differential, has a differential planet carrier 48 as the differential input shaft. The differential planet carrier 48 is also referred to as the second planet carrier or second web. Fig. It can be seen from Figure 1 that the vehicle wheels 12 and 14 can be driven by the rotor 22 via the differential gear 46, the differential gear 46 being driven by the rotor 22 via the first planetary gear set 30. The respective drive torque provided or available by the rotor 22, or a respective second torque resulting from the respective drive torque, can be provided by the first planetary gear set 30 and thereby transmitted via the first planetary gear set 30 to or onto the differential gear 46, in particular to or onto the differential planetary carrier 48, and thereby introduced into the differential gear 46 via the differential planetary carrier 48, thus enabling the differential gear 46 to be driven.The differential planetary carrier 48 is rotatable about a planetary carrier rotation axis 50 relative to the housing 26, whereby the planetary carrier rotation axis 50 coincides with the main rotation axis and thus also with the machine rotation axis 24.

[0043] The differential gear 46 has a first differential sun gear 52 as the first differential output shaft and a second differential sun gear 54 as the second differential output shaft. Fig. Figure 1 shows that the vehicle wheel 12 is driven by the first differential sun gear 52 and the vehicle wheel 14 by the second differential sun gear 54. The differential sun gear 52 is also referred to as the second sun gear and the differential sun gear 54 as the third sun gear. The second and third sun gears (differential sun gears 52 and 54) are arranged coaxially and are rotatable about a respective sun gear axis of rotation 51 relative to the housing 26. The respective sun gear axis of rotation 51 coincides with the planet carrier axis of rotation 50 and thus with the main axis of rotation and, in this case, also with the machine axis of rotation 24.

[0044] The torque introduced or that can be introduced into the differential gear 46, be it the respective drive torque or the respective secondary torque, is also referred to as the respective input torque. The differential gear 46 can provide the respective input torque or a respective output torque resulting from the respective input torque via the respective differential output shaft and thereby drive the respective vehicle wheel 12, 14. A respective wheel torque for driving the vehicle wheel 12, 14 is in Fig. 1 illustrated by a respective arrow 55, 56. For example, the respective wheel torque is the respective output torque or a respective third torque resulting from the output torque.

[0045] Out of Fig. Figure 1 shows that, for example, a first differential sun gear 52 is associated with a first side shaft 58, which can be driven by the differential sun gear 52. For example, the side shaft 58, or at least a section of its length, is permanently connected to the differential sun gear 52 in a rotationally fixed manner. A second side shaft 60 is associated with the differential sun gear 52, which can be driven by the differential sun gear 52. For example, the side shaft 60, or at least a section of its length, is permanently connected to the differential sun gear 54 in a rotationally fixed manner. It is apparent that the vehicle wheel 12 can be driven via the side shaft 58 by the differential sun gear 52, which in turn can drive the side shaft 58. It is also apparent that the vehicle wheel 14 can be driven via the side shaft 60 by the differential sun gear 54, which in turn can drive the side shaft 60.

[0046] In the first embodiment, the vehicle wheel 12 is driven from the side shaft 58 via a first transmission unit 62, and the vehicle wheel 14 is driven from the side shaft 60 via a second transmission unit 64. In the first embodiment, the respective transmission units 62 and 64 are designed as planetary gear sets, each comprising a further sun gear 66, a further planet carrier 68, and a further ring gear 70. Furthermore, each further planetary gear set comprises additional planet gears, of which in Fig. 1. A further planet gear, designated 72, is identifiable. The respective further planet gear 72 of the respective further planet gear set (transmission unit 62, 64) is rotatably mounted on the respective further planet carrier 68. In the first embodiment, the respective further sun gear 66 is a respective input of the respective further planet gear set, which can be driven via its respective input by the respective side shaft 58, 60. Furthermore, the respective further planet carrier 68 is a respective output of the respective planet gear set, which can drive the respective vehicle wheel 12, 14 via its respective output. Thus, the respective vehicle wheel 12 can be driven by the respective further planet carrier 68 and, via the respective further planet carrier 68, by the respective further sun gear 66. In addition, for example, the respective further ring gear 70 is, in particular, permanently and rotationally fixed to the housing 26.For example, the first planetary gear set 30 and / or the differential gear 46 is each at least partially arranged in the housing 26. 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.

[0047] The differential gear 46 has first differential compensating gears, of which in Fig. 1. A first differential differential gear, designated 74, is identifiable. The first differential differential gears 74 are rotatably mounted on the differential planetary carrier 48 such that each first differential differential gear is rotatable about a respective first differential gear axis of rotation relative to the differential planetary carrier 48. Furthermore, each first differential differential gear 74 meshes, in particular directly, with the first differential sun gear 52, but not with the differential sun gear 54. The first differential gear axes of rotation are spaced apart from each other in pairs, and the first differential gear axes of rotation run parallel to each other in pairs. Furthermore, each first differential gear axis of rotation runs parallel to the main axis of rotation, and each first differential gear axis of rotation is spaced apart from the main axis of rotation.The first compensating wheel axes of rotation are arranged successively and thus spaced apart from one another in the circumferential direction of the electrical drive system 10 which runs around the axial direction of the electrical drive system 10 and thus around the main axis of rotation, and in particular are arranged in an equally distributed manner, especially such that the first compensating wheel axes of rotation are arranged on a second circle whose center lies on the main axis of rotation.

[0048] The differential gear 46 has two differential compensating gears, one of which is in Fig. 1. A second differential differential gear, designated 76, is identifiable. The second differential differential gears 76 are rotatably mounted on the differential planetary carrier 48 such that each second differential differential gear 76 is rotatable about a respective second differential gear axis of rotation relative to the differential planetary carrier 48. Furthermore, each second differential differential gear 76 meshes, in particular directly, with the differential sun gear 54, but not with the differential sun gear 52. The second differential gear axes of rotation are spaced apart from each other in pairs, and the second differential gear axes of rotation run parallel to each other in pairs. Furthermore, each second differential gear axis of rotation runs parallel to the main axis of rotation and is spaced apart from the main axis of rotation.The second compensating wheel axes are arranged successively and thus spaced apart from one another in the circumferential direction of the electric drive system 10, which extends around the axial direction and thus around the main axis of rotation, and are in particular arranged in an equally distributed manner, such that the second compensating wheel axes are arranged on a third circle whose center lies on the main axis of rotation. The first circle has a first diameter, the second circle has a second diameter, and the third circle has a third diameter. In this case, the second diameter and the third diameter differ from each other, in particular such that, for example, the third diameter is smaller than the second diameter.

[0049] Each of the first differential output gears 74 meshes with, in particular, one of the second differential differential gears 76. Furthermore, each of the first planet gears 42 is arranged coaxially with, in particular, one of the first differential differential gears 74, such that the respective planet gear 42 and the respective first differential differential gear 74, arranged coaxially with the respective planet gear 42, form a gear pair. The first planet gears 42, the first differential differential gears 74, and the second differential differential gears 76, as well as the sun gear 40, the sun gear 38, the differential sun gear 52, and the differential sun gear 54, and also the sun gears 66, the planet gears 72, and the ring gears 70, are gears. Fig. As can be seen from Figure 1, the respective gears of each gear pair are rotatably arranged, in particular mounted, on the respective one-piece first planet gear pin 44, which is assigned to the respective first planet gear 42. Thus, for example, the first circle and the second circle have the same diameter. Therefore, for example, the first diameter and the second diameter are equal.Each second differential differential gear 76 is associated with a second bolt, which may also be formed in one piece or as a single component. The second differential differential gear 76 is rotatably mounted on the second bolt associated with it, such that the second differential differential gear 76 is oriented about its second axis of rotation relative to the second bolt. It is thus evident that the first planet gear bolt 44 is a common bolt for both gears of the respective gear pair, on which both gears of the respective gear pair are rotatably mounted, in particular supported.

[0050] Viewed in the axial direction of the electric drive system 10 and thus along the main axis of rotation, the first planetary gear set 30, the first differential sun gear 52 and the second differential sun gear 54 are arranged in the aforementioned order, that is, in the order in which they are named, one after the other and thus consecutively, so that, viewed in the axial direction of the drive system 10 and thus along the main axis of rotation (planetary gear set axis of rotation 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 and thus consecutively in the following order: the first planetary gear set 30 - the first differential sun gear 52 - the second differential sun gear 54.

[0051] Furthermore, it is provided that the rotor 22 is coupled or can be coupled to the first shaft 32 in such a way that the respective first torque provided or 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 gear 46.

[0052] To achieve a particularly space-saving and lightweight design for the drive system 10, the drive system 10 comprises a first switching unit SE1, which is configured to connect the third shaft 36, and thus in this case 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, comprises a second switching unit SE2, which is configured to lock the first planetary gear set 30. In the first embodiment, the second switching unit SE2 is configured to connect the third shaft 36 to the first shaft 32 in a rotationally fixed manner, so that in the first embodiment, the first sun gear 38 can be connected to the first ring gear 40 in a rotationally fixed manner by means of the second switching unit SE2. For example, the second switching unit SE2 is designed as a friction-based and thus force-fit switching unit, and in particular as a friction clutch, especially a multi-plate clutch.Furthermore, in the first embodiment, for example, the first switching unit SE1 is provided with a freewheel clutch designed to connect the third shaft 36 to the housing 26 in a rotationally fixed manner during forward traction of the vehicle. Forward traction of the vehicle is understood to mean, in particular, that the rotor 22 provides a torque, especially a positive torque, particularly in the form of the respective drive torque, so that the vehicle is driven and thus propelled forward by means of the drive torque provided by the rotor 22. It is evident that in the first embodiment, the vehicle wheels 12 and 14 are driven via the ring gear 40 of the multi-stage transmission 28.Preferably, an axially parallel arrangement of the drive system 10 is provided, particularly with regard to the vehicle wheels 12 and 14, wherein alternatively a coaxial arrangement of the drive system 10 may be provided, particularly with regard to the vehicle wheels 12 and 14, as is particularly shown in . Fig. 1 is shown. From Fig. 1 it can be seen that the first planet carrier of the first planet gear set 30, and thus the second shaft 34, is permanently and rotationally fixed to the differential planet carrier 48.

[0053] Fig. Figure 2 shows a schematic representation of a second embodiment of the drive system 10 according to the invention. In the second embodiment, the first shaft 32 comprises the first sun gear 38 of the first planetary gear set 30. Furthermore, in the second embodiment, the third shaft 36 comprises the second ring gear 40 of the first planetary gear set 30. Thus, in the second embodiment, the vehicle wheels 12 and 14 are driven via the first sun gear 38 of the first planetary gear set 30, or of the multi-stage transmission 28, which is also simply referred to as the sun gear. In the second embodiment, an axially parallel or coaxial arrangement of the drive system 10 is also possible, particularly with respect to the vehicle wheels 12 and 14. In the second embodiment, the first switching unit SE1 is also configured to connect the third shaft 36 to the housing 26 in a rotationally fixed manner.In the second embodiment, the second switching unit SE2 is also configured to lock the first planetary gear set 30. In the second embodiment, the first planet carrier of the first planetary gear set 30, and thus the second shaft 34 and the third shaft 36, and thus the first ring gear 40 of the first planetary gear set 30, can be connected to each other in a rotationally fixed manner by means of the second switching unit SE2, specifically such that the second shaft 34 can be connected to the shaft 36 in a rotationally fixed manner by means of the second switching unit SE2 via the differential planetary carrier 48.

[0054] The first embodiment and the second embodiment differ from each other in particular in that, in the first embodiment, the first shaft 32 comprises the first ring gear 40, and in the second embodiment, the first shaft 32 comprises the first sun gear 38. In a Fig. In the first variant of the first embodiment shown in Figure 1, the first planetary gear set 30 can be locked by means of the second switching unit SE2 such that the shaft 36, and thus the sun gear 38, can be connected to the shaft 32, and thus the ring gear 40, in a rotationally fixed manner by means of the switching unit SE2, bypassing the differential planetary 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 switching unit SE2 such that the shaft 36, and thus the sun gear 38, can be connected to the shaft 34, and thus to the first planetary carrier of the first planetary gear set 30, in a rotationally fixed manner by means of the second switching unit SE2, bypassing the differential planetary carrier 48.In a third variant of the first embodiment, not shown in the figures, the first planet gear set 30 can be locked by means of the second switching unit SE2 in such a way that the shaft 34 and thus the first planet carrier of the first planet gear set 30 can be connected to the shaft 32 and thus to the ring gear 40 in a rotationally fixed manner by means of the second switching unit SE2 via the differential planet carrier 48.

[0055] During a Fig. In the first variant of the second embodiment shown in Figure 2, the first planetary gear set 30 can be locked by means of the second switching unit SE2 such that the shaft 34, and thus the first planet carrier of the first planetary gear set 30, can be connected to the shaft 36, and thus the ring gear 40, in a rotationally fixed manner by means of the second switching unit SE2 via the differential planet 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 switching unit SE2 such that the shaft 32, and thus the sun gear 38, can be connected to the shaft 34, and thus to the first planet carrier of the first planetary gear set 30, in a rotationally fixed manner by means of the second switching unit SE2, by bypassing the differential planet 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 switching unit SE2 in such a way that the shaft 32 and thus the sun gear 38 can be connected to the shaft 36 and thus to the ring gear 40 in a rotationally fixed manner by means of the second switching unit SE2, bypassing the differential planet carrier 48.

[0056] The respective translation unit 62, 64 is also referred to as the final translation, which is also called the Final Drive (FD).

[0057] Fig. Figure 3 shows a schematic front view of the second embodiment of the drive system 10. It looks particularly good Fig. Figure 3 shows that the sun gear 38 meshes with the planet gears 42, which mesh with the ring gear 40. The first differential differential gears 74 mesh with the differential sun gear 52, and the differential differential gears 76 mesh with the differential sun gear 54. It is also evident that each of the differential differential gears 74 meshes with, in particular, one of the differential differential gears 76. This is especially clear from... Fig. 3 are recognizable in Fig. Three pairs of gears designated 78 are shown, and it is also apparent that a first gear of each pair is one of the first planet gears 42, and that a second gear of each pair 78 is one of the first differential gears 74. It is also particularly evident that the gears of each pair 78 are arranged coaxially with each other, such that one of the first planet gear axes of rotation coincides with, in particular, precisely with one of the first differential gear axes of rotation. The respective gears of each pair 78 are mounted not only on or at the common first planet carrier or differential planet carrier 48, but also on the respective common first planet gear pin 44.

[0058] Finally, it shows Fig. Figure 4 shows a schematic view of a third embodiment of the electric drive system 10 according to the invention. In the third embodiment, the first switching unit SE1 is arranged axially overlapping and radially surrounding the differential gear. Fig. Figure 4 shows the respective drive torque provided or available by the rotor 22, which in this case can be introduced or is introduced at the shaft 32 and via the shaft 32 bypassing the differential planetary carrier 48 into the first planetary gear set 30.

[0059] In the third embodiment, the second switching unit SE2 is configured to connect the first planet carrier to the shaft 36 in a rotationally fixed manner, particularly via the differential planet carrier 48. In the third embodiment, the electric drive system 10 has an oil channel 82 through which oil flows, the oil also being referred to as hydraulic oil. The oil channel 82 has a first section A1, which runs in the housing 26. Furthermore, the oil channel 82 has a second section A2, which is located in the first planet carrier of the first planet gear set 30 or, as shown in Fig. 4 is the case, in which the differential planetary carrier 48 runs. By means of the oil channel 82, the hydraulic oil flowing through the oil channel 82 can be guided, and thus transported, to an actuating piston of the second switching unit SE2, the second switching unit SE2 comprising the actuating piston. In Fig. Figure 4 shows an arrow 84 illustrating the flow of oil through the oil channel 82 towards the actuating piston. The actuating piston, and thus the second switching unit SE2, can be actuated by means of the hydraulic oil, whereby, for example, the first planetary gear set 30 can be locked by actuating the second switching unit SE2 using the switching unit SE2.

[0060] In Fig. As can be seen in Figure 4, a shaft seal 88 is arranged between the housing 26, in particular between a housing wall 86 of the housing 26, and the differential planetary carrier 48. This shaft seal is arranged, in particular in the radial direction of the drive system 10, whose radial direction is perpendicular to the axial direction of the drive system 10, between the housing 26, in particular the housing wall 86, and the differential planetary carrier 48. Alternatively or additionally to the shaft seal 88 designed as a shaft sealing ring, a sealed shaft bearing is conceivable. A transfer of the hydraulic oil from section A1 to section A2 can, for example, be compared to Fig. 4 radially further outwards. In this case, too, a seal for the transfer from the housing wall 86 or the housing 26 to the differential planetary carrier 48 is advantageous. In particular, this transfer of the hydraulic oil is possible because, for example, a plate carrier of the second switching unit SE2, designed, for example, as a multi-plate clutch, is permanently and rotationally fixed to the differential planetary carrier 48 or to its web shaft. Particularly with regard to the oil channel 82, the preceding and following descriptions of the differential planetary carrier 48 can readily be transferred to the first planetary carrier of the first planetary gear set 30 and vice versa. It is advantageous if the differential planetary carrier 48 or the first planetary carrier, in which the second section A2 runs, is a slow-rotating shaft.

[0061] Furthermore, from Fig.Four bearings 90a-c are identifiable. For example, each bearing 90a-c is designed as a rolling bearing or as a plain bearing. The respective first planet gear 42 is rotatably mounted on, in particular onto, the first planet gear pin 44 via the respective bearing 90a. The respective first differential differential gear 74 is rotatably mounted on, in particular onto, the first planet gear pin 44 via the respective bearing 90b. The respective second differential differential gear 76 is rotatably mounted on, in particular onto, a respective second pin 92 of the differential planet carrier 48 via the respective bearing 90c. It is specifically provided that the respective second pin 92 is provided in addition to the first planet gear pin 44 and is designed separately from the first planet gear pin 44.

[0062] It is conceivable, in particular, that the respective transmission unit 62, 64, arranged after the respective side shaft 58, 60, and especially between the respective side shaft 58, 60 and the respective vehicle wheel 12, 14, can be designed as a simple spur gear stage, for example with an offset axis. It can be seen that the housing wall 86 is arranged perpendicular to the main axis of rotation, and thus to the axial direction of the electric drive system 10. In other words, the housing wall 86 extends perpendicular to the main axis of rotation. Put another way, the housing wall 86 extends in a plane that is perpendicular to the main axis of rotation. The first section A1 runs within the housing wall 86. Reference symbol list 10 electric drive system 12 vehicle wheel 14 vehicle wheel 16 vehicle axle 18 electric machine 20 Stator 21 Rotor element 22 Rotor 23 Rotor element 24 Machine rotary axis 26 cases 28 multi-stage gearboxes 30 first planetary gear set 32 first wave 34 second wave 36 third wave 38 first sun wheel 40 first ring gear 42 first planetary wheel 44 first planetary wheel bolt 46 Differential gears 48 Differential planetary support 49 first planetary gear set pivot axis 50 Planetary carrier rotation axis 51 Sun gear pivot axis 52 first differential sun gear 54 second differential sun gear 55 Arrow 56 Arrow 58 Side shaft 60 Side shaft 62 translation units 64 translation units 66 more sun wheel 68 more planetary carriers 70 more hollow gear 72 more planetary gears 74 first differential gear 76 second differential gear 78 wheel pairs 80 Arrow 82 Oil channel 84 Arrow 86 Housing wall 88 Shaft seal 90a-c bearing 92 second bolt A1 first section A2 second section SE1 first switching unit SE2 second switching unit

Claims

[1] Electric drive system (10) for a motor vehicle, comprising: - an electrical machine (18) having a stator (20) and a rotor (22); - a multi-stage transmission (28) having a first planetary gear set (30) comprising: ◯ a first wave (32); ◯ a second shaft (34) which is designed as a first planet carrier on which first planet gears (42) are rotatably mounted; and ◯ a third wave (36); and - a differential gear (46) comprising: ◯ a differential planetary carrier (48) as a differential input shaft; ◯ a first differential sun gear (52) as the first differential output shaft; ◯ a second differential sun gear (54) as a second differential output shaft; ◯ first differential pinions (74) rotatably mounted on the differential planetary carrier (48) and meshing with the first differential sun gear (52); and ◯ second differential gears (76) rotatably mounted on the differential planetary carrier (48) and meshing with the second differential sun gear (54), wherein: ▪ one of the first differential gears (74) meshes with one of the second differential gears (76); ▪ viewed along an axial direction, 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: 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 can be coupled to the first shaft (32) in such a way that torques that can be provided by the rotor (22) can be introduced into the first planetary gear set (30) bypassing the differential gear (46) on the first shaft (32): where: - a first switching unit (SE1) is designed to connect the third shaft (36) in a rotationally fixed manner to a housing (26) of the electric drive system (10); and - a second switching unit (SE2) is designed to block the first planetary gear set (30), characterized by in that the first planet carrier is connected in a rotationally fixed manner to the differential planet carrier (48), one of the first planet gears (42) and one of the first differential gears (74) are arranged coaxially to one another and the first switching unit (SE1) is arranged axially overlapping and radially surrounding the differential gear (46). [2] Electric drive system (10) according to claim 1, characterized bythat the second switching unit (SE2) is designed to connect the first planet carrier in a rotationally fixed manner to the first shaft (32) and thereby to block the first planetary gear set (30). [3] Electric drive system (10) according to claim 1, characterized by that the second switching unit (SE2) is designed to connect the first planet carrier in a rotationally fixed manner to the third shaft (36) and thereby to block the first planetary gear set (30). [4] Electric drive system (10) according to claim 3, characterized by , that: - the third shaft (36) comprises a first ring gear (40) of the first planetary gear set (30); - the first shaft (32) comprises a first sun gear (38) of the first planetary gear set (30); - the second switching unit (SE2) is arranged axially on a side (S1) of the first switching unit (SE1) facing away from the first planetary gear set (30). [5] Electric drive system (10) according to one of the preceding claims, characterized by an oil channel (82) which is designed to transport hydraulic oil for actuating the second switching unit (SE2) to an actuating piston of the second switching unit (SE2), wherein the oil channel (82) has a first section (A1) running in the housing (26) and a second section (A2) running in the first planet carrier or in the differential planet carrier (48). [6] Electric drive system (10) according to claim 5, characterized by in that the housing (26) has a housing wall (86) arranged perpendicular to a main axis of rotation of the electric drive system (10), wherein the second switching unit (SE2) is arranged adjacent to the housing wall (86), and wherein the first section (A1) is arranged within the housing wall (86). [7] Motor vehicle, comprising an electric drive system (10) according to one of the preceding claims.

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