Electric drive train for motor vehicle, in particular for motor vehicle

Abstract

The invention relates to an electric drive train (10) for a motor vehicle, comprising: a first electric machine (16) having a first rotor (20); a second electric machine (18) having a second rotor (22); a planetary gear (42) having a first shaft (W1), a second shaft (W2), a third shaft (W3), a fourth shaft (W4) and a fifth shaft (W5); a first wheel (12); the electric machine (16, 18) is arranged upstream of the planetary gear (42) with respect to a torque flow emitted from the electric machine (16, 18) and running towards the wheels (12, 14), and wherein the planetary gear (42) is arranged upstream of the wheels (12, 14) in the torque flow. According to the invention, a first shift element (S1) is provided, which is configured to connect the second rotor (22) to the first shaft (W1).

Description

Technical Field

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

[0002] US 9 494 218 B2 discloses a power unit for driving two drive components for driving a vehicle. Summary of the invention

[0003] It is an object of the present invention to provide an electric powertrain for a motor vehicle which makes it possible to achieve particularly advantageous drivability properties.

[0004] This object is achieved by an electric drive train having the features of claim 1. Advantageous embodiments with suitable developments of the invention are specified in the remaining claims.

[0005] The invention relates to an electric drive train for a motor vehicle (also referred to as vehicle for short). This means that the motor vehicle, which is preferably configured as a car, in particular a passenger car, has an electric drive train in its fully manufactured state and can be driven by means of the electric drive train. The electric drive train comprises a first electric machine with a first rotor. For example, the first electric machine has a first stator, by means of which the first rotor can be driven and can therefore be rotated in particular relative to the first stator about a first machine rotation axis. For example, the first electric machine can provide a first drive torque for driving the motor vehicle by means of its first rotor. The electric drive train comprises a second electric machine with a second rotor. For example, the second electric machine has a second stator, by means of which the second rotor can be driven and can therefore be rotated in particular relative to the second stator about a second machine rotation axis. It is conceivable that the electric machines are arranged coaxially relative to each other so that the machine rotation axes coincide. The second electric machine can provide a second drive torque for driving the motor vehicle by means of its second rotor. In particular, the motor vehicle can be driven by means of the electric machine, in particular purely electrically, so that the motor vehicle is preferably configured as an electric vehicle, in particular a battery electric vehicle (BEV). The corresponding electric machine is preferably designed as a high-voltage component, whose voltage, in particular the electrical operating voltage or nominal voltage, is preferably greater than 50 volts, in particular greater than 60 volts, and very preferably amounts to several hundred volts.

[0006] The electric powertrain further comprises a planetary gear transmission, which comprises a first shaft, a second shaft, a third shaft, a fourth shaft and a fifth shaft. For example, the electric powertrain has a housing, wherein, for example, the planetary gear transmission is at least partially arranged in the housing. The first shaft, the second shaft, the third shaft, the fourth shaft and the fifth shaft are five shafts of the planetary gear transmission. Preferably, the planetary gear transmission has exactly five shafts, namely the first shaft, the second shaft, the third shaft, the fourth shaft and the fifth shaft. In particular, the corresponding shafts can rotate relative to the housing around the shaft rotation axis. In particular, it is conceivable that the first motor and / or the second motor are arranged coaxially with the planetary gear transmission, so that the first machine rotation axis and / or the second machine rotation axis coincide with the shaft rotation axis.

[0007] In particular, it is conceivable that the planetary gear transmission has six transmission components. The first transmission component is, for example, the first sun gear, the second transmission component is, for example, the first planet carrier, the third transmission component is, for example, the first ring gear, the fourth transmission component is, for example, the second sun gear, the fifth transmission component is, for example, the second planet carrier, and the sixth transmission component is, for example, the second ring gear. The planetary gear transmission has at least or exactly six transmission components and at least or exactly five shafts, in particular because, for example, two transmission components are, in particular, permanently and rotationally connected to each other. In particular, for example, the first planet carrier is permanently and rotationally connected to the second planet carrier. In this case, it is conceivable that the transmission components that are connected to each other rotationally are constructed separately from each other and are, in particular, permanently and rotationally connected to each other, or that the transmission components that are connected to each other rotationally are constructed integrally with each other, thus formed from a single piece, thus formed from an integral body or constructed as an integral body. The term "integral" refers to a body that is manufactured as a whole, i.e. a body that is manufactured as a whole, and therefore is an integral body, so that, for example, the transmission components that are connected to each other rotationally are formed by a body that is manufactured as a whole, and therefore do not consist of parts that are constructed separately from each other and connected to each other.

[0008] The electric drive train has a first wheel and a second wheel. A wheel is a ground contact element by which the drive train and therefore the motor vehicle as a whole is supported or can be supported on the ground in the vehicle vertical direction of the motor vehicle. If the motor vehicle is driven along the ground while the motor vehicle is supported downwards on the ground in the vehicle vertical direction by the ground contact element, the wheel rolls, in particular directly on the ground. In particular, the wheel is part of the same axis of the motor vehicle, also called axle. For example, in its fully manufactured state, the motor vehicle has at least or exactly two axles, which are arranged one after the other in the vehicle longitudinal direction of the motor vehicle, thus one after the other, namely the aforementioned axle as the first axle and the second axle. The wheel is, for example, the wheel of the first axle. The first axle can have at least or exactly two wheels, namely the first wheel and the second wheel. The second axle can have, for example, at least or exactly two further wheels, namely the third wheel and the fourth wheel, wherein the previous and following statements about the first wheel and the second wheel can also be easily transferred to the third wheel and the fourth wheel. If wheels are mentioned below, unless otherwise specified, they are understood to include the first wheel and the second wheel. In particular, the electric machine can drive the wheels electrically, in particular purely electrically, whereby the motor vehicle can be driven electrically, in particular purely electrically. The wheels of the respective axles are arranged, for example, on opposite sides of the motor vehicle in a vehicle transverse direction of the motor vehicle.

[0009] Regarding the torque flow from the electric machine, that is, in particular from the corresponding rotor and running toward the wheels, the electric machine is arranged in the torque flow upstream of the planetary gear transmission, and the planetary gear transmission is arranged in the torque flow upstream of the wheels, so that the wheels can be driven by the electric machine via the planetary gear transmission.

[0010] The electric drive train has a first shifting element, which is configured to connect the second rotor to the first shaft in such a way that a corresponding second drive torque that can be provided or provided by the second electric machine via the second rotor can be introduced into the first shaft, in particular into the planetary gear via the first shaft. In other words, by means of the first shifting element, the second rotor can be connected to the first shaft in a torque-transmitting manner, in particular in a torque-proof manner. In other words, the first shifting element is configured to connect the second rotor to the first shaft in such a way that a torque starting from the second rotor can be introduced into the planetary gear at the first shaft.

[0011] The electric drive train also includes a second shifting element, which is provided in addition to the first shifting element. The second shifting element is designed as a power-shifting shifting element, in particular a friction clutch, in particular a multi-disk clutch, wherein a friction clutch is also referred to as a friction clutch. In this case, the friction element of the power-shifting shifting element can be flat or conical, for example in the case of classic synchronization.

[0012] The second shift element can also be designed in two stages. Two stages here means that the second shift element is designed as a friction lock in the first actuation stage and as a form lock in the second actuation stage (as in the case of known shift elements with synchronized form lock). Thus, a friction lock can be generated in the first actuation stage in order to perform a power shift, while a form lock can be generated in the second actuation stage in order to be able to transmit torque via the second shift element without using actuation energy. In an advantageous embodiment, the second shift element can be designed so that in the friction lock actuation stage, when the clutch is closed and opened, a torque transmission can be ensured.

[0013] The second shifting element is designed to connect the third shaft to a sixth shaft in a rotationally fixed manner, in particular a sixth shaft provided in addition to the five shafts of the planetary gear. In other words, the third shaft can be connected to the sixth shaft in a rotationally fixed manner by means of the second shifting element. The sixth shaft is provided in addition to the five shafts of the planetary gear and is not, for example, a component of the planetary gear.

[0014] For example, the first shift element can be switched between a first connected state and a first disconnected state. In the first connected state, the second rotor is connected to the first shaft via the first shift element, in particular in a torque-transmitting manner, so that a corresponding second drive torque that can be provided by the second electric machine via the second rotor can be introduced into the planetary gear at the first shaft. In the first disconnected state, the second rotor and the first shaft are separated from each other, so that torque cannot be transmitted between the second rotor and the first shaft via the first shift element. In particular, it is conceivable that in the first disconnected state, the second rotor and the first shaft can rotate relative to each other about the shaft rotation axis and the second machine rotation axis, respectively. For example, in the first connected state, the second rotor and the first shaft are connected to each other in a torque-proof manner via the first shift element. For example, the first shift element can be moved, in particular translated and / or relative to the housing, between at least one first connected position for realizing the first connected state and at least one first disconnected position for realizing the first disconnected state.

[0015] For example, the second shift element can be switched between a second connection state and a second separation state. In the second connection state, the third shaft is connected to the sixth shaft in a friction-locked or form-locked manner by the second shift element. In the second separation state, the second shift element releases the third shaft to rotate relative to the sixth shaft about the shaft rotation axis, so that in the second separation state, the third shaft and the sixth shaft can rotate relative to each other about the shaft rotation axis, and so that in particular, torque cannot be transmitted between the third shaft and the sixth shaft via the second shift element. For example, the second shift element can be moved between at least one second connection position for achieving the second connection state and at least one second separation position for achieving the second separation state, in particular translationally and / or relative to the housing. In the context of the present disclosure, the feature that two components, such as the two transmission members, are connected to each other in a rotationally fixed manner should be understood as that the components connected to each other in a rotationally fixed manner are arranged coaxially relative to each other and, in particular, when the components are driven, rotate together or simultaneously at the same angular speed, in particular relative to the housing, about a common rotation axis of the components, such as the shaft rotation axis. In other words, the term "rotationally fixed" or "rotationally fixedly connected" is to be understood as meaning that two elements are connected to one another in a torque-fixed manner when they are arranged coaxially relative to one another and rotate with them at the same angular velocity, in particular when they are driven. The feature that two components are connected to one another in a torque-transmitting manner is to be understood as meaning that the components are coupled or connected to one another in such a way that torque can be transmitted between the components, whereby if the components are connected to one another in a torque-fixed manner, they are also connected to one another in a torque-transmitting manner.

[0016] The feature that two components are permanently connected to one another in a torque-transmitting manner is to be understood as meaning, for example, that no shifting element is provided that can be switched between a connection state, in which the components are connected to one another in a torque-transmitting manner, and a decoupled state, in which no torque can be transmitted between the components via the shifting element, but that the components are always or permanently and thus permanently connected to one another in a torque-transmitting manner, i.e. in such a way that torque can be transmitted between the components. Thus, for example, one component can be driven by the respective other component and vice versa. In particular, the feature that two components are permanently connected to one another in a rotationally fixed manner is to be understood as meaning that no shifting element is provided that can be switched between a connection state, in which the components are connected to one another in a torque-transmitting manner, and a decoupled state, in which the components are separated from one another and can rotate relative to one another, so that no torque can be transmitted between the components via the shifting element, but that the components are always or permanently and thus permanently connected or connected in a torque-transmitting manner.

[0017] The feature that two components (e.g., the second rotor and the first shaft) can be connected or coupled to each other in a torque-proof or torque-transmitting manner is to be understood as meaning that a shift element (e.g., a first shift element assigned to the components) can be switched between at least one coupled / connected state and at least one uncoupled / disconnected state. In the connected state, the components are connected to each other in a torque-proof or torque-transmitting manner via the shift element. In the disconnected state, the components are disconnected from each other, so that in the disconnected state the components can rotate relative to each other, in particular about a component rotation axis, such as a shaft rotation axis, and in particular so that torque cannot be transmitted between the components via the shift element.

[0018] For example, the sixth shaft can rotate relative to the housing about the element rotation axis.Preferably, the sixth shaft is arranged coaxially with the five shafts of the planetary gear transmission, so that the element rotation axis coincides with the shaft rotation axis.

[0019] In order to be able to achieve particularly advantageous driving properties of the electric drive train and thus of the motor vehicle as a whole, according to the invention, the electric drive train has a third shift element, which is in particular provided in addition to the first shift element and in addition to the second shift element and is designed as a positive coupling / clutch, in particular a dog clutch. The third shift element is designed to connect the second shaft or the fourth shaft to the sixth shaft in a rotationally fixed manner. In other words, the sixth shaft can be connected to the second shaft in a positively locked manner or to the fourth shaft in a positively locked manner via the third shift element. The second shaft and the fourth shaft are also collectively referred to as connecting shafts. The third shift element can be switched, for example, between a third connected state and a third disconnected state. In the third connected state, the sixth shaft is connected to the connecting shaft in a rotationally fixed manner via the third shift element, ie, in particular, precisely to one of the connecting shafts. In the third disconnected state, the third shift element releases the sixth shaft to rotate about the element rotation axis or respectively about the shaft rotation axis and relative to one of the connecting shafts, so that in the third disconnected state, one of the connecting shafts and the sixth shaft can rotate relative to each other about the element rotation axis or the shaft rotation axis respectively. In particular, for example, the third shift element can be moved, in particular translationally and / or relative to the housing, between at least one third connected position for achieving the third connected state and at least one third disconnected position for achieving the third disconnected state.

[0020] According to the invention, the electric drive train also has a first transmission ratio stage, which is arranged downstream of the planetary gear transmission and upstream of the first wheel with respect to the torque flow in the torque flow, so that the first wheel can be driven by the planetary gear transmission via the first transmission ratio stage. In this case, the fourth shaft is connected or can be connected to the first wheel via the first transmission ratio stage, in particular in a torque-transmitting manner, so that the first wheel can be driven by the fourth shaft via the first transmission ratio stage.

[0021] A second transmission ratio stage is also provided, which is in particular provided in addition to the first transmission ratio stage and is arranged downstream of the planetary gearing and upstream of the second wheel with respect to the torque flow, so that the second wheel can be driven by the planetary gearing via the second transmission ratio stage. A fifth shaft is connected or connectable to the second wheel via the second transmission ratio stage, in particular in a torque-transmitting manner, so that the second wheel can be driven by the fifth shaft via the second transmission ratio stage.

[0022] The first transmission ratio step has a first transmission ratio, in particular from the fourth shaft to the first wheel. The second transmission ratio step has a second transmission ratio, in particular from the fifth shaft towards the second vehicle. It is provided that the first transmission ratio is not equal to the second transmission ratio. In other words, the first transmission ratio is different from the second transmission ratio. In particular, the absolute value of the first transmission ratio is not equal to the absolute value of the second transmission ratio.

[0023] In other words, with respect to the torque flow from the electric machine, the electric machine is arranged upstream, ie upstream of the planetary gear transmission, and the planetary gear transmission is arranged upstream of the torque flow, ie upstream of the wheels.

[0024] With respect to torque flow, a first gear ratio step is located between the planetary gear transmission and the first wheel, and a second gear ratio step is located between the planetary gear transmission and the second wheel.

[0025] By means of the invention, a power shift capability of an electric drive train can be achieved, thereby making it possible to achieve particularly high driving dynamics and particularly high driving comfort. The first transmission ratio is also referred to as i1 and the second transmission ratio is also referred to as i2. Since the third shifting element is designed as a positive-locking clutch, the losses can be kept particularly low, so that particularly efficient operation can be achieved. If the first transmission ratio and the second transmission ratio, in particular their absolute values, were identical, it would be difficult or impossible to switch between two different operating modes of the electric drive train, for example, without interrupting the traction force, because, in particular at one end of the shifting sequence for switching from the first operating mode to the second operating mode, the third shifting element, for example designed as a claw shifting element, must be opened. However, a positive-locking shifting element, such as a claw shifting element, can or should be opened, i.e. switched from its connected state to its disengaged state, only when there is no load between the connecting halves of the claw shifting element and therefore between the elements that can be connected to each other in a rotationally fixed manner by means of the claw shifting element. This load-free operation can be achieved by operating the second shifting element, which is designed as a friction clutch, in a sliding manner, for example, only when there is a speed difference during straight-line driving, in particular at the second shifting element, i.e. when there is a speed difference between the input of the second shifting element and the output of the second shifting element, and when during the shifting, the connecting half of the shifting element located downstream in the torque flow has a lower speed than the connecting half located upstream. In the case of equal speeds, if the second shifting element is designed as a positive-locking shifting element, it cannot be engaged at all. The tooth-to-tooth position can only be resolved by the relative speeds between input and output. However, in the case of straight-line driving, the above-mentioned speed differences usually do not occur, in particular because during straight-line driving, the wheels rotate at the same speed and in the same direction of rotation. However, since the planetary gear, also referred to as the connecting gear or used as the connecting gear, is designed asymmetrically in the present invention, when the motor vehicle is driven in a straight line, the above-mentioned speed difference is generated at the second shift element, in particular between the input and the output of the second shift element, whereby a power shift can be achieved, in particular in such a way that the third shift element can be unloaded, so that in the event of a traction interruption, in particular then shifting, in particular opening, while the wheels are driven by at least one or both of the electric machines, wherein the torque is transmitted via the first shift element and the sliding / slipping second shift element. The asymmetrical design of the planetary gear is achieved by an asymmetrical design of the two transmission ratio stages. The asymmetrical design of the transmission ratio stages is achieved by the first transmission ratio and the second transmission ratio, in particular their absolute values ​​being different from each other. In particular, it is conceivable that the second transmission ratio, in particular the absolute value of the second transmission ratio, is greater than the first transmission ratio, in particular the absolute value of the first transmission ratio.

[0026] In this case, the transmission ratios of the two planetary stages and the two ratio stages are proportional to one another in such a way that in the first operating mode, a classic differential operation with a 50:50 torque distribution of the two drive wheels relative to one another is ideally achieved and a corresponding rotational speed compensation can take place at the wheels when cornering.

[0027] In particular, it is thereby possible, for example, to switch from the above-mentioned first operating mode to the above-mentioned second operating mode without interruption of traction force, ie without interruption of traction force.

[0028] In a particularly advantageous embodiment of the invention, the planetary gear transmission has a first planetary gear set and a second planetary gear set. For example, the first planetary gear set comprises a first sun gear, a first planet carrier and a first ring gear. For example, the second planetary gear set comprises a second sun gear, a second planet carrier and a second ring gear. Preferably, the first planet carrier of the first planetary gear set and the second planet carrier of the second planetary gear set are particularly permanently and torsionally connected to each other and form a common planet carrier, which is also referred to as an integral planet carrier. In this case, it is conceivable that the first planet carrier and the second planet carrier are constructed separately from each other and are particularly permanently and torsionally connected to each other, or that the first planet carrier and the second planet carrier are constructed integrally with each other and are thus formed by a single piece. In this case, one of the five shafts of the planetary gear transmission has a common planet carrier and therefore has an integral planet carrier. In other words, one of the five shafts comprises a common planet carrier. In other words, for example, the common planet carrier forms one of the five shafts, so that the common planet carrier is a component of one of the five shafts of the planetary gear transmission. Thus, in particular, it is conceivable that the respective shaft has a respective shaft portion and at least or exactly one transmission member, in particular exactly two transmission members, wherein the respective shaft portion of the respective shaft and the respective transmission member of the respective shaft are connected to each other in a rotationally fixed manner, in particular permanently and rotationally fixedly to each other. Thus, in the above-described embodiment, it is conceivable that one of the five shafts comprises a shaft portion and a common planet carrier, thus comprising a first planet carrier and a second planet carrier, wherein the shaft portion of one of the five shafts is in particular permanently and rotationally fixedly connected to the integral planet carrier. Thus, particularly advantageous driving properties can be provided.

[0029] The asymmetric design of the planetary gear transmission can be specified by selecting the transmission ratios within the first planetary gear set and within the second planetary gear set so that for the torque from the first electric machine, the same torque is generated at the first wheel via the first torque transmission path as at the second wheel via the second torque transmission path.

[0030] In this case, the above-mentioned shafts of the planetary gear transmission are arranged so that the first torque transmission path further reaches the sixth shaft from the first motor, further reaches the second shaft, further reaches the fourth shaft, further reaches the first gear ratio level, and the second torque transmission path further reaches the sixth shaft from the first motor, further reaches the second shaft, further reaches the fifth shaft, and further reaches the second gear ratio level.

[0031] Another embodiment is characterized in that the first shaft comprises a sun gear of the planetary gear, wherein the third shaft comprises a further sun gear of the planetary gear or a ring gear of the planetary gear. Thus, a particularly advantageous shifting capability and thus particularly advantageous driving properties can be achieved.

[0032] In another particularly advantageous embodiment of the invention, a sixth shaft is provided which is or can be connected to the first rotor, in particular in a torque-transmitting manner and in particular in a rotationally fixed manner, and is located in the torque flow between the first rotor and the planetary gear, in particular upstream of the planetary gear and downstream of the first rotor, with respect to the torque flow. As a result, particularly advantageous drive properties can be achieved in a particularly space-saving manner.

[0033] Another embodiment is characterized in that the first shaft has or includes a first sun gear. The third shaft has a second sun gear, wherein the second shafts have or include a common planet carrier. For example, the fifth shaft has a first ring gear and the fourth shaft has a second ring gear. Thus, a particularly advantageous transmission ratio can be achieved in a particularly space-saving manner, as a result of which particularly advantageous driving properties can be provided.

[0034] In another particularly advantageous embodiment of the present invention, the first planetary gear, the second planetary gear and the third planetary gear of the planetary gear transmission are rotatably supported on a common planet carrier. The first planetary gear meshes with the first sun gear and the second planetary gear, and the second planetary gear meshes with the first ring gear and the second sun gear. The third planetary gear meshes with the second planetary gear and the second ring gear. As a result, a particularly advantageous transmission ratio can be achieved, thereby achieving particularly advantageous driving performance.

[0035] In order to be able to provide particularly advantageous driving properties in a particularly space-saving manner, in a further embodiment of the invention a sixth shaft is provided which is in particular permanently and rotationally fixedly connected to the first rotor.

[0036] In another particularly advantageous embodiment of the invention, a sixth shaft is provided, in particular permanently and rotationally fixedly connected to the first input shaft of the first transmission ratio stage and arranged downstream of the planetary gearing with respect to the torque flow in the torque flow, in particular upstream of the first transmission ratio stage. Thus, a particularly advantageous transmission ratio can be achieved in a space-saving manner, thereby achieving particularly advantageous driving properties.

[0037] Another embodiment is characterized in that the first shaft comprises the first sun gear of the planetary gear, wherein the second shaft comprises the first ring gear of the planetary gear. The third shaft has the second ring gear of the planetary gear, and the fourth shaft has the second sun gear of the planetary gear. The fifth shaft has a common planet carrier. As a result, particularly advantageous transmission ratios and thus particularly advantageous driving properties can be achieved in a particularly space-saving manner.

[0038] Finally, in order to achieve particularly advantageous driving performance, it has proven particularly advantageous if the first, second and third planetary gears are rotatably supported on a common planetary carrier, wherein the first planetary gear meshes with the first sun gear and the first ring gear, wherein the second planetary gear meshes with the second sun gear and the first planetary gear, and wherein the third planetary gear meshes with the second planetary gear and the second ring gear.

[0039] In the context of the present disclosure, the terms "axial" and "axial direction" refer to the axis of rotation of the shaft of the planetary gear, also referred to as the axis of rotation. The planetary gear sets are advantageously arranged coaxially with one another. The electric machine and the transmission ratio stage are advantageously arranged coaxially with the planetary gear and thus coaxially with the axis of rotation of the shaft.

[0040] It is conceivable that the respective transmission ratio step is designed as a respective further planetary gear set provided in addition to the planetary gear, whereby a particularly advantageous transmission ratio and thus a particularly good driving performance can be achieved in a particularly space-saving manner. BRIEF DESCRIPTION OF THE DRAWINGS

[0041] Further advantages, features and details of the invention will become apparent from the following description of preferred embodiments with reference to the drawings. The features and feature combinations mentioned above in the description and the features and feature combinations mentioned below in the description of the drawings and / or shown individually in the drawings can be used not only in the combination specified in each case but also in other combinations or alone without departing from the scope of the invention.

[0042] In the attached picture:

[0043] Figure 1 shows a schematic diagram of a first embodiment of an electric powertrain for a motor vehicle;

[0044] Figure 2 shows a schematic diagram of a second embodiment of an electric powertrain; and

[0045] Figure 3 A schematic diagram of a third embodiment of an electric powertrain is shown.

[0046] In the figures, identical or functionally identical elements are provided with the same reference symbols. DETAILED DESCRIPTION

[0047] Figure 1 A first embodiment of an electric drive train 10 for a motor vehicle (also referred to as vehicle for short) is shown in a schematic perspective view. This means that the motor vehicle in the fully manufactured state has an electric drive train 10 and can be driven by the electric drive train 10. The motor vehicle, which is preferably designed as a car, in particular a passenger car, has at least or exactly two axles in its fully manufactured state, which are arranged one behind the other in the longitudinal direction of the vehicle and are therefore also simply referred to as axles. The respective axles have at least or exactly two wheels, also referred to as wheels for short. The respective wheels of the respective axles are arranged on sides of the motor vehicle that are opposite each other in the transverse direction of the motor vehicle. In this case, the electric drive train 10 comprises at least or exactly one axle and therefore at least or exactly two wheels of at least or exactly one axle of the electric drive train 10. The wheels of the electric drive train 10 are arranged in a longitudinal direction of the vehicle. Figure 1 1 and 14. In this case, wheel 12 is also referred to as a first wheel and wheel 14 is also referred to as a second wheel. The wheels of a motor vehicle are ground-contacting elements, by means of which the motor vehicle can be supported downwardly on the ground in a vehicle vertical direction of the motor vehicle. If the motor vehicle is driven along the ground while the motor vehicle is supported downwardly on the ground in a vehicle vertical direction by the ground-contacting elements, the wheels of the motor vehicle roll, in particular directly on the ground.

[0048] The electric drive train 10 comprises a first electric machine 16 and a second electric machine 18, wherein the wheels 12 and 14 can be driven, in particular purely electrically, by means of the electric machines 16 and 18. Thus, the motor vehicle can be driven electrically, in particular purely electrically.

[0049] The first motor 16 has a first rotor 20 and can provide a first driving torque for driving the wheels 12 and 14 through the first rotor 20. The second motor 18 has a second rotor 22 and can provide a second driving torque for driving the wheels 12 and 14 through the second rotor 22.

[0050] The first electric machine 16 has a first stator 24, by means of which the first rotor 20 can be driven so as to be relatively stable relative to the first stator 24 and relative to the first rotor 20. Figure 1 The housing 28 of the electric drive train 10, which is particularly schematically shown in FIG. 1 , rotates about the first machine rotation axis 26. The second electric machine 18 has a second stator 30, by means of which the second rotor 22 can be driven so as to rotate relative to the stator 30 and relative to the housing 28 about a second machine rotation axis 32. Figure 1In the first embodiment shown, the electric machines 16 and 18 are arranged coaxially relative to each other, so that the machine axes of rotation 26 and 32 coincide.

[0051] from Figure 1 It can be seen that the respective electric machine 16, 18 is designed as an axial flux machine. In this case, the respective rotor 20, 22 has two rotor elements 34 and 36 and 38 and 40, respectively, which are designed as rotor disks, for example. The respective rotor elements 34 and 36 and 38 and 40 of the respective electric machine 16, 18 are spaced apart from one another in the axial direction of the respective electric machine 16, 18, thus viewed along the respective machine axis of rotation 26, 32. In this case, the respective sub-region of the respective stator 24, 30 of the respective electric machine 16, 18 is arranged in the axial direction of the respective electric machine 16, 18 between the respective rotor elements 34 and 36 or 38 and 40, so that the respective rotor element 34, 36, 38, 40 of the respective electric machine 16, 18 is at least partially overlapped or covered by the respective sub-region of the respective stator 24, 30 of the respective electric machine 16, 18 in a direction extending in the axial direction of the respective electric machine 16, 18 and pointing to the respective other rotor element 36, 34, 40, 38.

[0052] The electric drive train 10 has a planetary gear 42, which in particular has at least or exactly five shafts, namely a first shaft W1, a second shaft W2, a third shaft W3, a fourth shaft W4 and a fifth shaft W5. The respective shafts W1, W2, W3, W4, W5 can rotate relative to the housing 28 about the respective shaft rotation axis 44. In a first embodiment, the planetary gear 42 is arranged coaxially with the respective electric machine 16, 18, so that the shaft rotation axis 44 coincides with the machine rotation axis 26 and the machine rotation axis 32. In particular, the planetary gear 42 is at least partially arranged in the housing 28.

[0053] Regarding the torque flow emitted from the motors 16 and 18 and extending to the wheels 12 and 14, along which, for example, the corresponding drive torque can be or is being transmitted from the corresponding motors 16, 18 to the corresponding wheels 12, 14, thereby driving the corresponding wheels 12, 14, the motors 16 and 18 are arranged upstream of the planetary gear transmission 42 in the torque flow, so that the wheels 12 and 14 can be driven by the motors 16 and 18 via the planetary gear transmission 42, in particular by the rotors 20 and 22.

[0054] The electric drive train 10 has a first shift element S1, which is configured to connect the second rotor 22 to the first shaft W1 in such a way, in particular in a torque-transmitting manner, and very particularly in a torque-proof manner, so that a corresponding second drive torque provided or can be provided by the second electric machine 18 via the second rotor 22 can be introduced into the first shaft W1 and via the first shaft W1 into the planetary gear transmission 42.

[0055] The electric drive train 10 also has a second shifting element S2, which is designed as a power-shifting clutch, in particular a friction clutch, in particular a multi-disk clutch or a multi-disk brake. The second shifting element S2 can be formed in two stages, including a friction-locking part, such as a cone clutch as a synchronization element, and a positive-locking part, such as a dog clutch as a positive-locking element.

[0056] The second shifting element S2 is designed to connect the third shaft W3 to the sixth shaft W6 in a frictional or non-positive manner during the module change between the first operating mode and the second operating mode, which is provided in addition to the five shafts W1, W2, W3, W4 and W5 of the planetary gear 42, in particular in a torque-transmitting manner and, in particular, in a rotationally fixed manner at the end of the shifting operation. Figure 1 In the first embodiment shown, the sixth shaft W6 is, in particular, permanently and rotationally connected to the first rotor 20 so that a corresponding first drive torque, which can be provided or provided by the first electric machine 16 via the first rotor 20 , can be introduced into the planetary gear 42 at the third shaft W3 and via the third shaft W3 .

[0057] The electric drive train 10 further comprises a third shifting element S3 which is designed as a positive-locking clutch, in particular a dog clutch or a dog shifting element. In a first embodiment, the third shifting element S3 is designed to connect the second shaft W2 to the sixth shaft W6 in a positive-locking and rotationally fixed manner.

[0058] Furthermore, the electric drive train 10 has a first transmission ratio stage 46 which is arranged downstream of the planetary gear 42 and upstream of the first wheel 12 with respect to the torque flow in the torque flow, wherein the fourth shaft W4 is connected to the first wheel 12, in particular in a torque-transmitting manner and very particularly in a permanent torque-transmitting manner, via the first transmission ratio stage 46. Thus, the first wheel 12 can be driven by the fourth shaft W4 via the first transmission ratio stage 46.

[0059] The electric powertrain 10 further comprises a second transmission ratio stage 48 which is arranged upstream of the wheel 14 and downstream of the planetary gearing 42 with respect to the torque flow in the torque flow. As a result, the second wheel 14 can be driven by the planetary gearing 42 via the second transmission ratio stage 48. The fifth shaft W5 is connected to the second wheel 14 via the second transmission ratio stage 48, in particular in a torque-transmitting manner and very particularly in a permanent torque-transmitting manner, so that the second wheel 14 can be driven by the fifth shaft W5 via the second transmission ratio stage 48. The first transmission ratio stage 46 has a first transmission ratio, in particular with a first absolute magnitude. The second transmission ratio stage 48 has a second transmission ratio, in particular with a second absolute magnitude. In this case, the transmission ratio, in particular the absolute magnitude of the transmission ratio, is such that, for example, the second transmission ratio, in particular the absolute magnitude of the second transmission ratio, is greater or less than the first transmission ratio, in particular the absolute magnitude of the first transmission ratio. The planetary gearing 42 forms or is a coupling / connecting gear, or is also referred to as a coupling / connecting gear. For example, the shift elements S2 and S3 form a switchable device, since by means of the shift elements S2 and S3 advantageous shiftability or switchability can be achieved, in particular between at least two operating modes (a first operating mode and a second operating mode of the electric drive train 10 ).

[0060] The planetary gear transmission 42 has a first planetary gear set 50, which has a first sun gear 52, a first planet carrier 54 and a first ring gear 56. The planetary gear transmission 42 also includes a second planetary gear set 58 having a second sun gear 60, a second planet carrier 62 and a second ring gear 64. The planet carriers 54 and 62 are also called webs, wherein the planet carrier 54 is also called the first web and the planet carrier 62 is also called the second web. In a first embodiment, the planet carriers 54 and 62 are connected to each other in a rotationally fixed manner, for example, the planet carriers 54 and 62 are constructed separately from each other and connected to each other in a rotationally fixed manner, or for example, the planet carriers 54 and 62 are constructed integrally with each other, that is, formed by a single piece. In particular, the planet carriers 54 and 62 are permanently and rotationally connected to each other. Therefore, the planet carriers 54 and 62 form a common planet carrier 63, which is also called an integral planet carrier. In this case, the integral planet carrier forms one of the five shafts W1, W2, W3, W4 and W5 of the planetary gear transmission 42. In other words, one of the five shafts W1, W2, W3, W4 and W5 of the planetary gear 42 has an integral planet carrier. Figure 1 In the first embodiment shown, one of the five shafts W1, W2, W3, W4 and W5 of the planetary gear transmission 42 is the second shaft W2, so that in the first embodiment, the second shaft W2 has an integral planet carrier. In other words, in the first embodiment, the integral planet carrier forms the second shaft W2. This means that in the first embodiment, the integral planet carrier is a component of the second shaft W2.

[0061] For example, the corresponding shafts W1, W2, W3, W4, W5 of the planetary gear transmission 42 have corresponding shaft portions, and the corresponding shafts W1, W2, W3, W4, W5 of the planetary gear transmission 42 are, for example, at least indirectly rotatably supported on the housing 28. In addition, the corresponding shafts W1, W2, W3, W4, W5 of the planetary gear transmission 42, for example, have corresponding component parts, in particular component parts arranged in addition to the corresponding shaft parts, which are constructed or used as corresponding transmission components of the planetary gear transmission 42, in particular corresponding transmission components of the corresponding planetary gear sets 50, 58. In the first embodiment, with respect to the second shaft W2, the component part of the second shaft W2 is a planet carrier part, which includes or forms an integral planet carrier or is formed by an integral planet carrier. The planet carrier part will be explained in more detail below. In other words, the planet carrier part of the shaft W2 is formed by the planet carriers 54 and 62 or includes the planet carriers 54 and 62. Sun gears 52 and 60, planet carriers 54 and 62, and ring gears 56 and 64 are transmission components of the planetary gear 42, in particular, transmission components of the corresponding planetary gear sets 50, 58. The corresponding transmission components can rotate relative to the housing 28 about the shaft rotation axis 44.

[0062] Since two of the six transmission elements of the planetary gear 42, in particular exactly two transmission elements, in the present case the planet carriers 54 and 62, are connected to each other in a rotationally fixed, in particular permanently, rotationally fixed manner, the six transmission elements of the planetary gear 42 form five shafts W1, W2, W3, W4 and W5 of the planetary gear 42. In particular, the five shafts W1, W2, W3, W4 and W5 of the planetary gear 42 can rotate relative to each other in pairs about the axis of rotation 44.

[0063] In the first embodiment, the first shaft W1 has a first sun gear 52, so that in the first embodiment, the component part of the first shaft W1 has the sun gear 52 or is formed by the sun gear 52. In the first embodiment, the third shaft W3 has a second sun gear 60, so that the component part of the third shaft W3 has the second sun gear 60 or is formed by the second sun gear 60. In the first embodiment, the sixth shaft W6 is connected to the first rotor 20, in particular permanently and rotationally fixedly, so that it is connected, wherein, with respect to the torque flow, the sixth shaft W6 is located in the torque flow between the first rotor 20 and the planetary gear 42, in particular downstream of the first rotor 20 and upstream of the planetary gear 42, so that the planetary gear 42 can be driven by the first rotor 20 via the sixth shaft W6. In the first embodiment, the fifth shaft W5 has a first ring gear 56, so that the component part of the fifth shaft W5 has the ring gear 56 or is formed by the ring gear 56. In the first embodiment, the fourth shaft W4 has a second ring gear 64, so that the component part of the fourth shaft W4 is formed by the second ring gear 64 or has the second ring gear 64.

[0064] In a first embodiment, the planetary gear 42 has a first planetary gear P1, a second planetary gear P2 and a third planetary gear P3. The planetary gears P1, P2 and P3 are rotatably supported on an integral planet carrier. In a first embodiment, it is provided that the component part of the shaft W2 has an integral planet carrier or is formed by an integral planet carrier, wherein the planetary gears P1, P2 and P3 are rotatably supported on the integral planet carrier and thus rotatably supported on the component part of the second shaft W2. The first planetary gear P1 meshes with the first sun gear 52 and the second planetary gear P2, in particular with the first toothing of the second planetary gear P2. The second planetary gear P2 meshes with the first ring gear 56 and the second sun gear 60, in particular in such a way that the corresponding first toothing of the second planetary gear P2 meshes with the ring gear 56 and the corresponding second toothing of the planetary gear P2 meshes with the sun gear 60. In this case, it is particularly conceivable that the corresponding first toothing and the corresponding second toothing of the corresponding second planetary gear P2 are arranged one after another in the axial direction of the corresponding second planetary gear P2, that is, arranged one after another. For example, the respective first toothing of the respective second planetary gear P2 is formed by the respective first teeth of the respective second planetary gear P2, wherein, for example, the respective second toothing of the respective second planetary gear P2 is formed by the respective second teeth of the respective second planetary gear P2. The third planetary gear P3 meshes with the second gear ring 64 and the second planetary gear P2, in particular with the second toothing of the second planetary gear P2. The first toothing preferably has a first rolling pitch circle diameter and a first pitch circle diameter. The second toothing has a second rolling pitch circle diameter and a second pitch circle diameter. Preferably, the first pitch circle diameter and the second pitch circle diameter are different from each other. Alternatively or additionally, the first rolling pitch circle diameter and the second rolling pitch circle diameter are different from each other.

[0065] In a first embodiment, for example, the second pitch circle diameter or the second rolling pitch circle diameter is greater than the first pitch circle diameter or the first rolling pitch circle diameter. Thus, for example, the corresponding second planetary gear P2 is configured as a stepped / stepped planetary gear, also called a stepped planetary gear. In particular, the first tooth and the second tooth are in particular permanently and rotationally connected to each other. For example, the first tooth and the second tooth are formed integrally with each other, i.e., are formed from a single piece. In summary, it can be seen that in the first embodiment, the planetary gear P1 meshes with the first sun gear 52 and the second planetary gear P2, in particular with the first toothing of the second planetary gear P2, wherein the planetary gear P1 does not mesh with the first ring gear 56, the second ring gear 64, the second sun gear 60 and the third planetary gear P3. The second planetary gear P2, in particular the second toothing, meshes with the third planetary gear P3, and the second planetary gear P2, in particular the second toothing, meshes with the second sun gear 60. The second planetary gear P2, in particular the first toothing, meshes with the first ring gear 56, and the second planetary gear P2, in particular the first toothing, meshes with the first planetary gear P1. The second planetary gear P2 does not mesh with the first sun gear 52 and the second ring gear 64. The third planetary gear P3 meshes with the second planetary gear P2, in particular with the second toothing, and the third planetary gear P3 meshes with the second ring gear 64. The third planetary gear P3 does not mesh with the first sun gear 52, the first ring gear 56, the second sun gear 60 and the first planetary gear P1. Furthermore, in the first embodiment, the sixth shaft W6 is in particular permanently and rotationally fixedly connected to the first rotor 20.

[0066] The respective transmission ratio steps 46, 48 are designed as respective further planetary gear sets 66, 68 in addition to the planetary gear 42 and therefore in addition to the planetary gear sets 50 and 58. The respective further planetary gear sets 66, 68 have respective further sun gears 70, 72, respective further planet carriers 74, 76 and respective further ring gears 78, 80. In a first embodiment, the respective sun gears 70, 72 are designed as respective inputs of the respective transmission ratio steps 46, 48, so that the sun gear 70 is connected or can be connected to the fourth shaft W4 in a torque-transmitting manner, in particular in a rotationally fixed manner, and so that the sun gear 72 is connected or can be connected to the fifth shaft W5 in a torque-transmitting manner, in particular in a rotationally fixed manner. In the first embodiment, the sun gear 70 is connected to the fourth shaft W4 in a permanent torque-transmitting manner, in particular permanently and rotationally fixedly connected, and in the first embodiment, the sun gear 72 is connected to the fifth shaft W5 in a permanent torque-transmitting manner, in particular permanently and rotationally fixedly connected. The respective planet carrier 74, 78 is the respective output of the respective transmission ratio stage 46, 48, in this case so that the wheel 12 can be driven by the planet carrier 74 and the wheel 14 can be driven by the planet carrier 76. In particular, the wheel 12 can be connected or connected to the planet carrier 74 in a torque-transmitting manner, in particular in a permanent torque-transmitting manner, and the wheel 14 is connected or can be connected to the planet carrier 76 in particular in a permanent torque-transmitting manner. The respective ring gear 78, 80 can be connected or connected to the housing 28 in a rotationally fixed manner. In a first embodiment, the respective ring gear 78, 80 is permanently and rotationally connected to the housing 28. The respective further planetary gear set 66, 68 has a respective further planet gear 82, 84, which is rotatably held on the planet carrier 74 and which is rotatably held on the planet carrier 76. The planet gear 82 meshes simultaneously with the sun gear 70 and the ring gear 78, and the planet gear 84 meshes simultaneously with the sun gear 72 and the ring gear 80.

[0067] Figure 2A second embodiment of the electric drive train 10 is shown in a schematic diagram. In the second embodiment, the sixth shaft W6 is, in particular, permanently and rotationally connected to the first input shaft 86 of the first transmission ratio stage 46, wherein it is conceivable that the sixth shaft W6 and the first input shaft 86 are formed integrally with one another, thus from a single piece. The first input shaft 86 has a sun gear 70, so that the sun gear 70 is or forms an element part of the input shaft 86. For example, the first input shaft 86 is at least indirectly rotatably supported on the housing 28 via its shaft section. With respect to the torque flow in the torque flow, the sixth shaft W6 is arranged downstream of the planetary gear 42 and upstream of the sun gear 70 or the first input shaft 86, respectively. In the second embodiment, the first shaft W1 has a first sun gear 52 and the second shaft W2 has a first ring gear 56. Therefore, in the second embodiment, the element part of the first shaft W1 is formed by the sun gear 52 and the element part of the shaft W2 is formed by the ring gear 56. The third shaft W3 has a second ring gear 64 and the fourth shaft W4 has a second sun gear 60. In the second embodiment, the fifth shaft W5 has a common planet carrier 63 (integrated planet carrier).

[0068] In the second embodiment, the planetary gears P1 and P2 are rotatably held on an integral planet carrier. In the second embodiment, there is no third planetary gear. The first planetary gear P1, in particular the corresponding first toothing of the first planetary gear P1, meshes with the first sun gear 52 and the first ring gear 56. The second planetary gear P2 meshes with the second sun gear 60 and the first planetary gear P1, in particular with the corresponding second toothing of the first planetary gear P1 and the second ring gear 64. In summary, it can be seen that the first planetary gear P1, in particular the first toothing of the first planetary gear P1, meshes with the first sun gear 52 and the first ring gear 56, and the first planetary gear P1, in particular the second toothing of the planetary gear P1, meshes with the second planetary gear P2. In particular, it is conceivable that the first toothing and the second toothing or the first tooth and the second tooth have the same rolling pitch diameter or pitch diameter, so that, for example, in the second embodiment, the first rolling pitch diameter and the second rolling pitch diameter or the first pitch diameter and the second pitch diameter are the same. The second planetary gears P2 mesh with the second sun gear 60 , the second ring gear 64 , and the first planetary gears P1 , and in particular mesh with the second toothing of the first planetary gears P1 .

[0069] The second planetary gears P2 do not mesh with the first sun gear 52 and the first ring gear 56 .

[0070] In the third embodiment, the sixth shaft W6 is connected to the first rotor 20 in a torque-transmitting manner, in particular permanently, in particular rotationally fixedly, i.e., with respect to the torque flow, in the torque flow, between the first rotor 20 and the planetary gear 42. In the third embodiment, the planetary gear 42 has at least or exactly three planetary gear sets, namely the first planetary gear set 50, the second planetary gear set 58 and the third planetary gear set 88, the third planetary gear set 88 having, in addition to the planetary gear sets 50 and 58, also in addition to the transmission ratio stages 46 and 48. The third planetary gear set 88 has a third sun gear 90, a third planet carrier 92 (also called a third web) and a third ring gear 94. Thus, the planetary gear 42, in particular, has at least or exactly nine transmission components, namely the sun gears 52, 60 and 90, the planet carriers 54, 62 and 92 and the ring gears 56, 64 and 94. In the third embodiment, the planetary gear 42 also has, in particular, at least or exactly five shafts, namely the shafts W1, W2, W3, W4 and W5. This is because, on the one hand, in the third embodiment, the planet carriers 54 and 62 are in particular permanently and rotationally connected to each other, so that in the third embodiment, the shaft W5 is formed. Therefore, in the third embodiment, the shaft W5 includes a common planet carrier 63 (integral planet carrier). In other words, in the third embodiment, the component part of the fifth shaft W5 includes or is formed by an integral planet carrier. In addition, in the third embodiment, the ring gear 94 is in particular permanently and rotationally connected to the sun gear 52, so that the ring gear 94 and the sun gear 52 form the shaft W1. In other words, the shaft W1 has the sun gear 52 and the ring gear 94, so that the first component part of the shaft W1 is the sun gear 52 or includes the sun gear 52 or is formed by the sun gear 52, and so that the second component part of the shaft W1 is the ring gear 94 or includes the ring gear 94 or is formed by the ring gear 94. In addition, in the third embodiment, the sun gear 90 is in particular permanently and rotationally connected to the sun gear 60, so that the sun gears 90 and 60 form the third shaft W3. In other words, shaft W3 has sun gears 60 and 90, so that the first component part of shaft W3 is or comprises sun gear 60 or is formed by sun gear 60, and so that the second component part of shaft W3 is or comprises sun gear 90 or is formed by sun gear 90. In addition, ring gears 64 and 56 are, in particular, permanently and rotationally connected to one another, as a result of which ring gears 64 and 56 form shaft W4. In other words, shaft W4 has ring gears 64 and 56. It is therefore provided that the first component part of shaft W4 is or comprises ring gear 64 or is formed by ring gear 64, and the second component part of shaft W4 is or comprises ring gear 56 or is formed by ring gear 56. Shaft W2 has a third planet carrier 92, so that the component part of shaft W2 has planet carrier 92 or is formed by planet carrier 92. In summary, it can be seen that shaft W1 comprises sun gear 52 and ring gear 94, which are, in particular, permanently and rotationally connected to one another. Shaft W2 has a planet carrier 92.The shaft W3 has sun gears 60 and 90, which are particularly permanently and non-rotatably connected to one another. The shaft W4 has ring gears 56 and 64, which are particularly permanently and non-rotatably connected to one another. The shaft W5 has a common planet carrier 63, and therefore planet carriers 54 and 62, which are particularly permanently and non-rotatably connected to one another. In a third embodiment, the shaft W4 is particularly permanently connected to the input of the transmission ratio stage 46, and thus to the sun gear 70 of the planetary gear set 66, so as to be torque-transmitting, particularly non-rotatably connected. The shaft W5 is particularly permanently connected to the input of the transmission ratio stage 48, and thus to the sun gear 72 of the planetary gear set 68, so as to be torque-transmitting, particularly non-rotatably connected. In a second embodiment, the shaft W5 is particularly permanently connected to the input of the transmission ratio stage 48, and thus to the sun gear 72 of the planetary gear set 68, so as to be torque-transmitting, particularly non-rotatably connected. In the first embodiment, the shaft W4 is particularly permanently connected to the input of the transmission ratio stage 46 and thus to the sun gear 70 of the planetary gear set 66 in a torque-transmitting manner, in particular in a rotationally fixed manner. In the first embodiment, the shaft W5 is particularly permanently connected to the input of the transmission ratio stage 48 and thus to the sun gear 72 of the planetary gear set 68 in a torque-transmitting manner, in particular in a rotationally fixed manner. In the third embodiment, the shaft W1 can be connected to the second rotor 22 of the second electric machine 18 in a torque-transmitting manner by means of the shift element S1, in particular in a rotationally fixed manner. The sixth shaft W6 can be connected to the third shaft W3 by means of the second shift element S2. The second shaft W2 can be connected to the sixth shaft W6 by means of the shift element S3 and thus to the first rotor 20. In the second embodiment, the fourth shaft W4 can be connected to the sixth shaft W6 in a rotationally fixed manner by means of the shift element S3. In the embodiment, the transmission ratio stages 46 and 48 are arranged coaxially relative to each other, coaxially relative to the planetary gear 42, and coaxially relative to the electric machines 16 and 18. In the third embodiment, the third planetary gear set 88 is arranged coaxially with the planetary gear sets 50 and 58, also coaxially with the gear ratio stages 46 and 48, and coaxially with the motors 16 and 18. The sun gear 90, the planet carrier 92 and the ring gear 94 can rotate relative to the housing 28 about the shaft rotation axis 44 as additional transmission elements.

[0071] In the third embodiment, the planetary gear 42 also has planetary gears P1, P2 and P3. In addition, the planetary gear 42 has a fourth planetary gear P4, which is in particular a planetary gear of the third planetary gear set 88. The fourth planetary gear P4 is rotatably held on the planet carrier 92. The first planetary gear P1 meshes with the first sun gear 52 and the second planetary gear P2. The first planetary gear P1 does not mesh with the first ring gear 56, the third planetary gear P3, the second sun gear 60, the second ring gear 64, the third sun gear 90, the fourth planetary gear P4 and the third ring gear 94. The second planetary gear P2 meshes with the first planetary gear P1 and the first ring gear 56. The second planetary gear P2 does not mesh with the first sun gear 52, the third planetary gear P3, the second sun gear 60, the second ring gear 64, the third sun gear 90, the fourth planetary gear P4 and the third ring gear 94. The third planetary gear P3 meshes with the second sun gear 60 and the second ring gear 64. The third planetary gear P3 is not meshed with the first sun gear 52, the first planetary gear P1, the first ring gear 56, the second planetary gear P2, the third sun gear 90, the fourth planetary gear P4, and the third ring gear 94. The fourth planetary gear P4 is meshed with the third sun gear 90 and the third ring gear 94. The fourth planetary gear P4 is not meshed with the first sun gear 52, the first planetary gear P1, the first ring gear 56, the third planetary gear P3, the second sun gear 60, the second planetary gear P2, and the second ring gear 64.

[0072] from Figure 3 It can also be seen that, viewed in the axial direction of the transmission system 10, the third planetary gear set 88 is arranged between the motors 16 or 18, and therefore along the shaft rotation axis 44, in particular in such a way that the planetary gear set 88 is arranged on the side of the motor 16 facing the motor 18 in the axial direction of the transmission system 10, and the planetary gear set 88 is arranged on the side of the motor 18 facing the motor 16 in the axial direction of the transmission system 10 and away from the planetary gear sets 50 and 58. Therefore, the planetary gear sets 50 and 58 are arranged on the side of the motor 18 in the axial direction of the transmission system 10 away from the third planetary gear set 88.

[0073] Reference numerals list

[0074] 10 Electric Powertrain

[0075] 12 First Wheel

[0076] 14 Second Wheel

[0077] 16 First Motor

[0078] 18 Second Motor

[0079] 20 First rotor

[0080] 22 Second rotor

[0081] 24 First stator

[0082] 26 First machine axis of rotation

[0083] 28 Shell

[0084] 30 Second stator

[0085] 32 Second machine rotation axis

[0086] 34 Rotor elements

[0087] 36 Rotor elements

[0088] 38 Rotor Components

[0089] 40 Rotor elements

[0090] 42 Planetary gear transmission

[0091] 44 Axis of rotation

[0092] 46 First gear ratio stage

[0093] 48 Second gear ratio stage

[0094] 50 First planetary gear set

[0095] 52 First sun gear

[0096] 54 First planet carrier

[0097] 56 First gear ring

[0098] 58 Second planetary gear set

[0099] 60 Second sun gear

[0100] 62 Second planet carrier

[0101] 63 Public planet carrier

[0102] 64 Second gear ring

[0103] 66 Planetary gear set

[0104] 68 Planetary gear set

[0105] 70 Sun gear

[0106] 72 Sun gear

[0107] 74 Planet carrier

[0108] 76 Planet carrier

[0109] 78 Ring gear

[0110] 80 Ring gear

[0111] 82 Planetary gear

[0112] 84 Planetary gear

[0113] 86 First input shaft

[0114] 88 Third planetary gear set

[0115] 90 Third sun gear

[0116] 92 Third planet carrier

[0117] 94 Third gear ring

[0118] P1 First planetary gear

[0119] P2 Second planetary gear

[0120] P3 Third planetary gear

[0121] P4 Fourth planetary gear

[0122] S1 First shift element

[0123] S2 Second shift element

[0124] S3 Third shift element

[0125] W1 First axis

[0126] W2 Second axis

[0127] W3 Third Axis

[0128] W4 Fourth Axis

[0129] W5 Fifth Axis

[0130] W6 Sixth Axis

Claims

1. An electric powertrain (10) for a motor vehicle, comprising: - a first electric machine (16) having a first rotor (20); - a second electric machine (18) having a second rotor (22); - a planetary gear transmission (42), the planetary gear transmission having a first shaft (W1), a second shaft (W2), a third shaft (W3), a fourth shaft (W4) and a fifth shaft (W5); - a first wheel (12); - a second wheel (14), wherein, with respect to a torque flow from the motor (16, 18) and running toward the wheel (12, 14), the motor (16, 18) is arranged upstream of the planetary gear transmission (42) in the torque flow, and the planetary gear transmission (42) is arranged upstream of the wheel (12, 14) in the torque flow; a first shifting element (S1) which is configured to connect the second rotor (22) to the first shaft (W1) in such a way that a torque which can be provided by the second electric machine (18) via the second rotor (22) can be introduced into the planetary gear (42) at the first shaft (W1); and a second shifting element (S2) which is designed as a powershifting shifting element and which is designed to connect the third shaft (W3) to the sixth shaft (W6) in a rotationally fixed manner; It is characterized in that a third shifting element (S3) which is designed as a positive-locking clutch and which is designed to connect the second shaft (W2) or the fourth shaft (W4) of the drive train (10) to the sixth shaft (W6) in a rotationally fixed manner; a first transmission ratio stage (46) which is arranged downstream of the planetary gear (42) and upstream of the first wheel (12) with respect to the torque flow in the torque flow, wherein the fourth shaft (W4) is connected or connectable to the first wheel (12) via the first transmission ratio stage (46); and - a second transmission ratio stage (48), which is arranged downstream of the planetary gear (42) and upstream of the second wheel (14) with respect to the torque flow in the torque flow, wherein the fifth shaft (W5) is connected or can be connected to the second wheel (14) via the second transmission ratio stage (48), and wherein the first transmission ratio of the first transmission ratio stage (46) is not equal to the second transmission ratio of the second transmission ratio stage (48).

2. The electric powertrain (10) according to claim 1, It is characterized in that The planetary gear transmission (42) comprises a first planetary gear set (50) and a second planetary gear set (58), wherein a first planet carrier (54) of the first planetary gear set (50) and a second planet carrier (62) of the second planetary gear set (58) are connected to each other in a rotationally fixed manner and form a common planet carrier (63), wherein one of the five shafts (W1, W2, W3, W4, W5) of the planetary gear transmission (42) has a common planet carrier (63).

3. The electric powertrain (10) according to claim 2, It is characterized in that The first shaft (W1) includes one of the sun gears (52, 60, 90) of the planetary gear transmission (42), wherein the third shaft (W3) includes another of the sun gears (52, 60, 90) of the planetary gear transmission (42) or one of the ring gears (56, 64, 94) of the planetary gear transmission (42).

4. The electric powertrain (10) according to claim 3, It is characterized in that The sixth shaft (W6) is connected or connectable to the first rotor (20) and is arranged between the first rotor (20) and the planetary gear transmission (42) with respect to the torque flow in the torque flow.

5. The electric powertrain (10) according to claim 4, It is characterized in that - the first shaft (W1) has a first sun gear among the sun gears (52, 60, 90); - the third shaft (W3) has a second sun gear among the sun gears (52, 60, 90); - the second shaft (W2) has the common planet carrier (63); - the fifth shaft (W5) has a first ring gear of the ring gears (56, 64, 94) of the planetary gear transmission (42); and The fourth shaft (W4) has a second ring gear of the ring gear (56, 64, 94) of the planetary gear (42).

6. The electric powertrain (10) according to claim 5, It is characterized in that - the first planetary gear (P1), the second planetary gear (P2) and the third planetary gear (P3) of the planetary gear transmission (42) are rotatably supported on the common planet carrier (63); - the first planetary gear (P1) meshes with the first sun gear (52) and the second planetary gear (P2); - the second planetary gear (P2) meshes with the first ring gear (56) and the second sun gear (60); and The third planetary gear (P3) meshes with the second planetary gear (P2) and the second ring gear (64).

7. An electric powertrain (10) according to any one of claims 4 to 6, It is characterized in that The sixth shaft (W6) is connected to the first rotor (20) in a rotationally fixed manner.

8. The electric powertrain (10) according to claim 3, It is characterized in that The sixth shaft (W6) is connected in a rotationally fixed manner to the first input shaft (86) of the first transmission ratio stage (46) and is arranged downstream of the planetary gear (42) with respect to the torque flow in the torque flow.

9. The electric powertrain (10) according to claim 8, It is characterized in that - the first shaft (W1) has a first sun gear of the sun gears (52, 60, 90) of the planetary gear (42); - the second shaft (W2) has a first ring gear of the ring gear (56, 64, 94) of the planetary gear (42); The third shaft (W3) has a second ring gear of the ring gear (56, 64, 94) of the planetary gear (42); - the fourth shaft (W4) has a second sun gear of the sun gears (52, 60, 90) of the planetary gear (42); and - said fifth shaft (W5) has said common planet carrier (63).

10. The electric powertrain (10) according to claim 9, It is characterized in that - the first planetary gear (P1), the second planetary gear (P2) and the third planetary gear (P3) are rotatably supported on the common planet carrier (63); - the first planetary gear (P1) meshes with the first sun gear (52) and the first ring gear (56); - the second planetary gear (P2) meshes with the second sun gear (60) and the first planetary gear (P1); and The third planetary gear (P3) meshes with the second planetary gear (P2) and the second ring gear (64).

11. The electric powertrain (10) according to claim 2, It is characterized in that The gear ratios in the first planetary gear set (50) and the second planetary gear set (58) are selected so that the torque from the first motor (16) to the first wheel (12) via the first torque transmission path and the torque acting on the first wheel (12) is the same as the torque from the first motor (16) to the second wheel (14) via the second torque transmission path and the torque acting on the second wheel (14), wherein the first torque transmission path is from the first motor (16) further via the sixth shaft (W6), further via the second shaft (W2), further via the fourth shaft (W4), further via the first gear ratio stage (46) to the first wheel (12), The second torque transmission path is from the first motor (16) further via the sixth shaft (W6), further via the second shaft (W2), further via the fifth shaft (W5), and further via the second gear ratio stage (48) to the second wheel (14).

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