DE102023004067A1 - Electric drive system for a motor vehicle - Google Patents

Abstract

The invention relates to an electric drive system (1) for a motor vehicle having two electric machines (M1, M2), each with a rotor (R1, R2). The rotors (R1, R2) can be coupled or are coupled to a respective output shaft (A1, A2) in a torque-transmitting manner. The output shafts (A1, A2) are arranged coaxially to one another and to a common output axis of rotation (AA).
According to the invention, it is provided that
- a first rotor rotation axis (RA1) of the first rotor (R1) is arranged parallel and offset from a second rotor rotation axis (RA2) of the second rotor (R2),
- the output axis of rotation (AA) is arranged parallel and offset to both rotor axes of rotation (RA1, RA2), and
- a first intermediate shaft (Z1) and a second intermediate shaft (Z2) are provided, which are arranged parallel and axially offset from one another and parallel and axially offset both to the rotor axes of rotation (RA1, RA2) and to the output axis of rotation (AA), wherein with regard to a torque flow emanating from the first rotor (R1), the first intermediate shaft (Z1) is arranged between the first rotor (R1) and the first output shaft (A1) and with regard to a torque flow emanating from the second rotor (R2), the second intermediate shaft (Z2) is arranged between the second rotor (R2) and the second output shaft (A2).

Description

The invention relates to an electric drive system for a motor vehicle according to the features of the preamble of claim 1.

The state of the art is, as described in the DE 10 2019 107 538 A1 described, a torque vectoring transmission for a motor vehicle is known, comprising a first drive shaft which is connected in a rotationally fixed manner to a first sun gear of a spur gear differential, and a second drive shaft which is connected in a rotationally fixed manner to a second sun gear of the spur gear differential. The first sun gear engages with at least one first planet gear in a first toothing plane. The second sun gear engages with at least one second planet gear in a second toothing plane. The first planet gear engages with a first ring gear in the first toothing plane. The second planet gear engages with a second ring gear in the second toothing plane. The first planet gear engages with the second planet gear. A first transmission stage is formed on the first ring gear, which engages with a first output gear in a third toothing plane. A second transmission stage is formed on the second ring gear, which engages with a second output gear in a fourth toothing plane. The first output gear is rotationally fixed to a first output shaft and the second output gear is rotationally fixed to a second output shaft.

The invention is based on the object of providing an electric drive system for a motor vehicle which is improved compared to the prior art.

The object is achieved according to the invention by an electric drive system for a motor vehicle having the features of claim 1.

Advantageous embodiments of the invention are the subject of the subclaims.

• - eine erste elektrische Maschine, die einen ersten Rotor aufweist,
• - eine zweite elektrische Maschine, die einen zweiten Rotor aufweist,
• - eine erste Abtriebswelle, wobei der erste Rotor drehmomentübertragend mit der ersten Abtriebswelle koppelbar oder gekoppelt ist, und
• - eine koaxial zur ersten Abtriebswelle angeordnete zweite Abtriebswelle, wobei der zweite Rotor drehmomentübertragend mit der zweiten Abtriebswelle koppelbar oder gekoppelt ist, und wobei die erste Abtriebswelle und die zweite Abtriebswelle koaxial zu einer gemeinsamen Abtriebsdrehachse angeordnet sind.

An electric drive system for a motor vehicle has the following:

• - a first electric machine having a first rotor,
• - a second electric machine having a second rotor,
• - a first output shaft, wherein the first rotor is coupled or can be coupled to the first output shaft in a torque-transmitting manner, and
• - a second output shaft arranged coaxially to the first output shaft, wherein the second rotor can be coupled or is coupled to the second output shaft in a torque-transmitting manner, and wherein the first output shaft and the second output shaft are arranged coaxially to a common output axis of rotation.

According to the invention, a first rotor rotation axis of the first rotor is arranged parallel to and axially offset from a second rotor rotation axis of the second rotor. According to the invention, the output rotation axis is arranged parallel to and axially offset from both rotor rotation axes. According to the invention, the electric drive system has a first intermediate shaft and a second intermediate shaft, which are arranged parallel to and axially offset from one another and parallel to and axially offset from both the rotor rotation axes and the output rotation axis, wherein with regard to a torque flow emanating from the first rotor, the first intermediate shaft is arranged between the first rotor and the first output shaft and with regard to a torque flow emanating from the second rotor, the second intermediate shaft is arranged between the second rotor and the second output shaft.

In one possible embodiment, in a sectional plane perpendicular to the rotor rotation axes, the first rotor rotation axis, the second rotor rotation axis, a first intermediate shaft rotation axis, and a second intermediate shaft rotation axis mark the vertices of a trapezoid, and the first intermediate shaft rotation axis, the second intermediate shaft rotation axis, and the output rotation axis mark the vertices of a triangle. The triangle can advantageously be isosceles or nearly isosceles. An isosceles triangle results when both drive sides have exactly the same design with regard to the choice of gear ratios and gear diameters. A nearly isosceles triangle results when both drive sides have slightly different gear ratios or gear diameters.

The described solution enables a particularly compact and modular structure of the electric drive system, in particular a compact, axis-parallel arrangement of all components with a high degree of modularity, and low mechanical construction effort.

The electric drive system is provided, for example, for driving a rear axle of the motor vehicle. In this case, the electric drive system is arranged in the motor vehicle in such a way that the respective rotor rotation axis is arranged in the vehicle longitudinal axis direction, ie in the direction of travel of the motor vehicle, in front of and/or in the vehicle vertical axis direction above the intermediate shaft rotation axis, which lies in the common torque flow, and that the rotor rotation axes and, in particular, the intermediate shaft rotation axes are arranged in front of the output rotation axis in the vehicle's longitudinal axis direction and above the output rotation axis in the vehicle's vertical axis direction. This provides, for example, space for a drive battery of the motor vehicle beneath the two electric motors. The drive battery, in particular a rear end region of the drive battery, can extend, for example, beneath the electric motors and up to an area of gears on the intermediate shafts or gears on the output shafts.

• - eine erste Zahnradpaarung, welche ein drehfest mit dem ersten Rotor verbundenes erstes Zahnrad und ein mit dem ersten Zahnrad in Eingriff stehendes und drehfest mit der ersten Zwischenwelle verbundenes oder verbindbares zweites Zahnrad aufweist,
• - eine zweite Zahnradpaarung, welche ein drehfest mit dem zweiten Rotor verbundenes drittes Zahnrad und ein mit dem dritten Zahnrad in Eingriff stehendes und drehfest mit der zweiten Zwischenwelle verbundenes oder verbindbares viertes Zahnrad aufweist,
• - eine dritte Zahnradpaarung, welche ein drehfest mit der ersten Zwischenwelle verbundenes oder verbindbares fünftes Zahnrad und ein mit dem fünften Zahnrad in Eingriff stehendes und drehfest mit der ersten Abtriebswelle verbundenes sechstes Zahnrad aufweist, und
• - eine vierte Zahnradpaarung, welche ein drehfest mit der zweiten Zwischenwelle verbundenes oder verbindbares siebtes Zahnrad und ein mit dem siebten Zahnrad in Eingriff stehendes und drehfest mit der zweiten Abtriebswelle verbundenes achtes Zahnrad aufweist.

In one possible embodiment, the electric drive system comprises the following:

• - a first gear pair comprising a first gear connected in a rotationally fixed manner to the first rotor and a second gear meshing with the first gear and connected or connectable in a rotationally fixed manner to the first intermediate shaft,
• - a second gear pair comprising a third gear connected in a rotationally fixed manner to the second rotor and a fourth gear meshing with the third gear and connected or connectable in a rotationally fixed manner to the second intermediate shaft,
• - a third gear pair comprising a fifth gear connected or connectable in a rotationally fixed manner to the first intermediate shaft and a sixth gear meshing with the fifth gear and connected in a rotationally fixed manner to the first output shaft, and
• - a fourth gear pair comprising a seventh gear connected or connectable in a rotationally fixed manner to the second intermediate shaft and an eighth gear meshing with the seventh gear and connected in a rotationally fixed manner to the second output shaft.

The first gear is, in particular, rotationally fixedly connected to a first rotor shaft, which is rotationally fixedly connected to the first rotor. The third gear is, in particular, rotationally fixedly connected to a second rotor shaft, which is rotationally fixedly connected to the second rotor.

In particular, it is provided that the first gear pair and the second gear pair are arranged in an axially overlapping manner.

In particular, it is provided that the first gear pair and the second gear pair are arranged in the axial direction between the third gear pair and the fourth gear pair.

In one possible embodiment, the first rotor, the third gear pair, the first gear pair, the fourth gear pair and the second rotor are arranged one after the other in the axial direction in the order mentioned.

In one possible embodiment, the first rotor, the fourth gear pair, the first gear pair, the third gear pair, and the second rotor are arranged one after the other in the axial direction in the order mentioned. In this embodiment, the torque flows intersect, i.e., the first output shaft is arranged on a side of the electric drive system opposite the first electric machine, and the second output shaft is also arranged on a side of the electric drive system opposite the second electric machine.

In one possible embodiment, the electric drive system has a first rotor shaft bearing for supporting the first rotor shaft and a first output shaft bearing for supporting the first output shaft. In particular, in the embodiment in which the first rotor, the fourth gear pair, the first gear pair, the third gear pair, and the second rotor are arranged one after the other in the axial direction in the stated order, the first rotor shaft bearing is arranged in the axial direction between the first rotor and the fourth gear pair, and the first output shaft bearing is arranged in the axial direction between the third gear pair and the second rotor. This enables axial support of the torque flow coming from the first electric machine on a side of a housing opposite the first electric machine, for example on a housing wall of this housing, by the first output shaft bearing. The first output shaft bearing is arranged in particular on and/or in this housing, in particular on and/or in this housing wall of the housing.

The first output shaft bearing is designed in particular as a tapered roller bearing.

It is particularly provided that the electric drive system has a second rotor shaft bearing for supporting the second rotor shaft and a second output shaft bearing for supporting the second output shaft. In particular, in the embodiment in which the first rotor, the fourth gear pair, the first gear pair, the third gear pair and the second rotor are arranged one after the other in the axial direction in the order mentioned, the second rotor shaft bearing is arranged in the axial direction between the second rotor and the third gear pairing, and the second output shaft bearing is arranged in the axial direction between the fourth gear pairing and the first rotor. This enables axial support of the torque flow coming from the second electric machine on a side of the housing opposite the second electric machine, for example, on a housing wall of this housing, by the second output shaft bearing. The second output shaft bearing is arranged in particular on and/or in this housing, in particular on and/or in this housing wall of the housing.

The second output shaft bearing is designed in particular as a tapered roller bearing.

In one possible embodiment, it can be provided that the fourth gear pair is arranged in the axial direction between the first gear pair and second gear pair on the one hand and the third gear pair on the other hand.

In one possible embodiment, it can be provided that the first rotor, the first gear pair, the fourth gear pair, the third gear pair and the second rotor are arranged one after the other in the axial direction in the order mentioned.

In one possible embodiment, it can be provided that the first rotor, the third gear pair, the fourth gear pair, the first gear pair and the second rotor are arranged one after the other in the axial direction in the order mentioned.

In one possible embodiment, it can be provided that the third gear pair is arranged in the axial direction between the first gear pair and second gear pair on the one hand and the fourth gear pair on the other hand.

In one possible embodiment, it can be provided that the first rotor, the first gear pair, the third gear pair, the fourth gear pair and the second rotor are arranged one after the other in the axial direction in the order mentioned.

In one possible embodiment, it can be provided that the first rotor, the fourth gear pair, the third gear pair, the first gear pair and the second rotor are arranged one after the other in the axial direction in the order mentioned.

In one possible embodiment, the electric drive system comprises a first parking lock gear that is or can be connected in a rotationally fixed manner to the first intermediate shaft, and a second parking lock gear that is or can be connected in a rotationally fixed manner to the second intermediate shaft. In particular, it is provided that all gear pairs are arranged in the axial direction between the two parking lock gears.

In one possible embodiment, the electric drive system has a first separating clutch which is designed to connect the fifth gear and/or the second gear in a rotationally fixed manner to the first intermediate shaft.

In one possible embodiment, the electric drive system has a hollow shaft arranged coaxially to the first intermediate shaft, which is connected in a rotationally fixed manner to the fifth gear and in a rotationally fixed manner to the first parking lock gear.

In one possible embodiment, the electric drive system has a second separating clutch which is designed to connect the fourth gear and/or the seventh gear in a rotationally fixed manner to the second intermediate shaft.

To implement the first separating clutch, it is provided, in particular, that the first separating clutch has a first gear toothing, a second gear toothing, and a first sliding sleeve. In particular, it is provided that the second gear toothing is connected in a rotationally fixed manner to the first intermediate shaft.

To implement the second separating clutch, it is particularly provided that the second separating clutch has a third gearing, a fourth gearing, and a second sliding sleeve. In particular, it is provided that the fourth gearing is connected in a rotationally fixed manner to the second intermediate shaft.

In one possible embodiment, the respective intermediate shaft is supported by means of a fixed bearing and a loose bearing.

In one possible embodiment, the first output shaft is mounted relative to the second output shaft by means of a shaft bearing. In particular, it is provided that the first output shaft is rotatably mounted directly relative to the second output shaft by means of the shaft bearing. The shaft bearing comprises, in particular, an axial bearing and a radial bearing, each of which is designed, in particular, as a rolling bearing, for example, as a needle bearing.

In one possible embodiment, an intermediate wall is arranged axially, i.e. in the axial direction of the output shafts, between the sixth gear and the eighth gear.

In one possible embodiment, one of the output shafts, in particular the second output shaft, is mounted opposite the intermediate wall by means of an additional bearing. This additional bearing is designed, in particular, as a rolling bearing, for example, as a needle bearing.

In one possible embodiment, the electric drive system comprises a first housing part and a second housing part. The two housing parts are detachably connected to one another, in particular along a flange plane, and form the housing.

In one possible embodiment, the first electrical machine is arranged in a first machine housing, which is detachably connected to the first housing part, and/or the second electrical machine is arranged in a second machine housing, which is detachably connected to the second housing part. In this embodiment, the respective electrical machine is thus advantageously designed as a closed unit and can thus be easily connected to and detached from the respective housing part. In this embodiment, the respective electrical machine, in particular its machine housing, forms in particular an end cover for the respective housing part, i.e. the respective housing part has an opening that is or can be closed by the respective electrical machine, in particular its machine housing. In one possible embodiment, the respective machine housing has a bearing plate on both sides of the rotor in the axial direction, in particular for supporting the rotor and/or the rotor shaft.

As already mentioned above with regard to one embodiment of the electric drive system, the electric drive system can be designed such that the torque flows cross, i.e., the first output shaft is arranged on a side of the electric drive system opposite the first electric machine, and the second output shaft is also arranged on a side of the electric drive system opposite the second electric machine. This is the case, for example, in the embodiment described above, in which the first rotor, the fourth gear pair, the first gear pair, the third gear pair, and the second rotor are arranged one after the other in the axial direction in the order mentioned. The advantage of this design of the electric drive system is that the gears of the intermediate shafts, in particular the fifth gear of the first intermediate shaft and the seventh gear of the second intermediate shaft, can be arranged near a shaft bearing of the respective intermediate shaft, i.e., in each case in particular near the fixed bearing or the floating bearing of the respective intermediate shaft, with which the respective intermediate shaft is mounted in the respective end region, in particular on the housing. This prevents excessive shaft deflection of the respective intermediate shaft and excessive bearing load.

Without the torque crossover, in particular the fifth gear of the first intermediate shaft and the seventh gear of the second intermediate shaft are arranged more towards the middle of the respective intermediate shaft, resulting in greater shaft deflection and greater bearing load.

A further advantage of designing the electric drive system in such a way that the torque flows cross is the resulting shorter design of the hollow shaft arranged coaxially to the first intermediate shaft, particularly in conjunction with the first separating clutch and the first parking lock gear. Without the crossing torque flows, the hollow shaft section on the first intermediate shaft is longer because the first parking lock gear is advantageously arranged in an end region of the first intermediate shaft and thus close to the housing. However, longer hollow shafts mean more weight. The crossing torque flows and the resulting shorter hollow shaft thus achieve a weight reduction.

In the context of the present application, the term “rotatably fixed” means: two rotatably mounted elements are connected to each other in a rotationally fixed manner if they are arranged coaxially to each other and are connected to each other in such a way that they rotate at the same angular speed.

In the context of the present application, the term "axially fixed" means: two rotatably mounted elements are axially fixed to one another if they are arranged coaxially to one another and are connected in such a way that they cannot be displaced relative to one another in the axial direction; axially fixedly connected elements do not have to be connected to one another in a rotationally fixed manner at the same time.

In the context of the present application, the terms "axial" and "axial direction" refer in particular to the first and/or second rotor shaft and/or to the first and/or second intermediate shaft and/or to the first and/or second output shaft and/or to the first and/or second rotor rotation axis and/or to the first and/or second intermediate shaft rotation axis and/or to the output rotation axis. Since the aforementioned components are aligned in particular parallel to one another, they have the same axial direction.

Embodiments of the invention are explained in more detail below with reference to drawings.

• 1 schematisch eine Ausführungsform eines elektrischen Antriebssystems für ein Kraftfahrzeug,
• 2 schematisch eine zweite Ausführungsform des elektrischen Antriebssystems,
• 3 schematisch eine Anordnung von Rotordrehachsen, Zwischenwellendrehachsen und einer Abtriebsdrehachse des elektrischen Antriebssystems in einer Schnittebene senkrecht zu den Rotordrehachsen,
• 4 schematisch eine dritte Ausführungsform des elektrischen Antriebssystems, und
• 5 schematisch eine vierte Ausführungsform des elektrischen Antriebssystems.

Showing:

• 1 schematically an embodiment of an electric drive system for a motor vehicle,
• 2 schematically shows a second embodiment of the electric drive system,
• 3 schematically an arrangement of rotor rotation axes, intermediate shaft rotation axes and an output rotation axis of the electric drive system in a sectional plane perpendicular to the rotor rotation axes,
• 4 schematically a third embodiment of the electric drive system, and
• 5 schematically shows a fourth embodiment of the electric drive system.

Corresponding parts are provided with the same reference numerals in all figures.

The 1 and 2 show exemplary schematic representations of two embodiments of an electric drive system 1 for a motor vehicle.

The electric drive system 1 comprises a first electric machine M1 with a first rotor R1 and a second electric machine M2 with a second rotor R2. The design of the electric machines M1, M2 is shown by way of example in 4 based on a third embodiment of the electric drive system 1, which will be explained in more detail later. In this example, the electric machines M1, M2 are each designed as an axial flux machine. The respective rotor R1, R2 has an H-shape in the central section, i.e. two rotor parts RT which extend radially outwards from a respective rotor shaft RW1, RW2. A stator S1, S2 of the respective electric machine M1, M2 is arranged in the axial direction of the respective rotor shaft RW1, RW2 between the two rotor parts RT of the respective rotor R1, R2.

The electric drive system 1 further comprises a first output shaft A1, wherein the first rotor R1 is or can be coupled to the first output shaft A1 in a torque-transmitting manner. In addition, the electric drive system 1 comprises a second output shaft A2 arranged coaxially to the first output shaft A1, wherein the second rotor R2 is or can be coupled to the second output shaft A2 in a torque-transmitting manner. The first output shaft A1 and the second output shaft A2 are arranged coaxially to a common output axis of rotation AA. This common output axis of rotation AA is, in particular, a virtual axis that runs through both output shafts A1, A2 and about which both output shafts A1, A2 rotate, i.e., the common output axis of rotation AA is, in particular, not a physically existing axis on which the output shafts A1, A2 are rotatably arranged.

A first rotor rotation axis RA1 of the first rotor R1 is arranged parallel to and offset from a second rotor rotation axis RA2 of the second rotor R2. The respective rotor rotation axis RA1, RA2 is, in particular, a virtual axis that extends through the respective rotor shaft RW1, RW2 and about which the respective rotor R1, R2, in particular the respective rotor shaft RW1, RW2, rotates. This means that the respective rotor rotation axis RA1, RA2 is, in particular, not a physically existing axis on which the respective rotor shaft RW1, RW2 is rotatably arranged.

The output rotation axis AA is arranged parallel and offset to both rotor rotation axes RA1, RA2.

The electric drive system 1 further comprises a first intermediate shaft Z1 and a second intermediate shaft Z2, which are arranged parallel and axially offset from one another and parallel and axially offset both from the rotor rotational axes RA1, RA2 and from the output rotational axis AA, wherein with regard to a torque flow emanating from the first rotor R1, the first intermediate shaft Z1 is arranged between the first rotor R1 and the first output shaft A1 and with regard to a torque flow emanating from the second rotor R2, the second intermediate shaft Z2 is arranged between the second rotor R2 and the second output shaft A2.

As in 3 As shown schematically, it is particularly provided that in a sectional plane perpendicular to the rotor rotation axes RA1, RA2, the first rotor rotation axis RA1, the second rotor rotation axis RA2, a first intermediate shaft rotation axis ZA1 and a second intermediate shaft rotation axis ZA2 mark the corner points of a trapezoid, and the first intermediate shaft rotation axis ZA1, the second intermediate shaft rotation axis ZA2 and the output rotation axis AA mark the corner points of a triangle. The triangle can advantageously be designed as an isosceles triangle. This arrangement of the rotation axes RA1, RA2, ZA1, ZA2 and AA according to the 3 is the advantageous arrangement of these axes of rotation for all four embodiments.

The respective intermediate shaft rotation axis ZA1, ZA2 is in particular a virtual axis which runs through the respective intermediate shaft Z1, Z2 and around which the respective intermediate shaft Z1, Z2 rotates, ie the respective intermediate shaft rotation axis ZA1, ZA2 is in particular not a physically existing axis on which the respective intermediate shafts Z1, Z2 are rotatably arranged.

• - eine erste Zahnradpaarung ZP1, welche ein drehfest mit dem ersten Rotor R1, insbesondere mit der ersten Rotorwelle RW1, verbundenes erstes Zahnrad ZR1 und ein mit dem ersten Zahnrad ZR1 in Eingriff stehendes und drehfest mit der ersten Zwischenwelle Z1 verbundenes oder verbindbares zweites Zahnrad ZR2 aufweist,
• - eine zweite Zahnradpaarung ZP2, welche ein drehfest mit dem zweiten Rotor R2, insbesondere mit der zweiten Rotorwelle RW2, verbundenes drittes Zahnrad ZR3 und ein mit dem dritten Zahnrad ZR3 in Eingriff stehendes und drehfest mit der zweiten Zwischenwelle Z2 verbundenes oder verbindbares viertes Zahnrad ZR4 aufweist,
• - eine dritte Zahnradpaarung ZP3, welche ein drehfest mit der ersten Zwischenwelle Z1 verbundenes oder verbindbares fünftes Zahnrad ZR5 und ein mit dem fünften Zahnrad ZR5 in Eingriff stehendes und drehfest mit der ersten Abtriebswelle A1 verbundenes sechstes Zahnrad ZR6 aufweist, und
• - eine vierte Zahnradpaarung ZP4, welche ein drehfest mit der zweiten Zwischenwelle Z2 verbundenes oder verbindbares siebtes Zahnrad ZR7 und ein mit dem siebten Zahnrad ZR7 in Eingriff stehendes und drehfest mit der zweiten Abtriebswelle A2 verbundenes achtes Zahnrad ZR8 aufweist.

The electric drive system 1 has in particular the following:

• - a first gear pair ZP1, which has a first gear ZR1 connected in a rotationally fixed manner to the first rotor R1, in particular to the first rotor shaft RW1, and a second gear ZR2 meshing with the first gear ZR1 and connected or connectable in a rotationally fixed manner to the first intermediate shaft Z1,
• - a second gear pair ZP2, which has a third gear ZR3 connected in a rotationally fixed manner to the second rotor R2, in particular to the second rotor shaft RW2, and a fourth gear ZR4 meshing with the third gear ZR3 and connected or connectable in a rotationally fixed manner to the second intermediate shaft Z2,
• - a third gear pair ZP3, which has a fifth gear ZR5 which is connected or connectable in a rotationally fixed manner to the first intermediate shaft Z1 and a sixth gear ZR6 which meshes with the fifth gear ZR5 and is connected in a rotationally fixed manner to the first output shaft A1, and
• - a fourth gear pair ZP4, which has a seventh gear ZR7 which is connected or connectable in a rotationally fixed manner to the second intermediate shaft Z2 and an eighth gear ZR8 which meshes with the seventh gear ZR7 and is connected in a rotationally fixed manner to the second output shaft A2.

In 3 The engagement of the first gear ZR1 with the second gear ZR2 and the engagement of the third gear ZR3 with the fourth gear ZR4 and also the sixth gear ZR6 and the eighth gear ZR8 are also shown schematically. The fifth gear ZR5 and its engagement with the sixth gear ZR6 and the seventh gear ZR7 and its engagement with the eighth gear ZR8 are shown in 3 not shown. Everything that is 3 is stated, applies advantageously to all four embodiments of the 1 , 2 , 4 and 5 .

The first gear ZR1 is particularly connected in a rotationally fixed manner to the first rotor shaft RW1, which is rotationally fixedly connected to the first rotor R1. The third gear ZR3 is particularly connected in a rotationally fixed manner to the second rotor shaft RW2, which is rotationally fixedly connected to the second rotor R2.

Due to the described design, the torque transmissions and thus the power flows from the respective electric machine M1, M2 via the respective intermediate shaft Z1, Z2 to the respective output shaft A1, A2 are completely separated from one another. The first gear pair ZP1 and the third gear pair ZP3 are assigned to the first electric machine M1 and the first output shaft A1, i.e., via these two gear pairs ZP1, ZP3, the torque is transmitted exclusively from the first electric machine M1 and exclusively to the first output shaft A1, and the second gear pair ZP2 and the fourth gear pair ZP4 are assigned to the second electric machine M2 and the second output shaft A2, i.e., via these two gear pairs ZP2, ZP4, the torque is transmitted exclusively from the second electric machine M2 and exclusively to the second output shaft A2.

It is particularly provided that the first gear pair ZP1 and the second gear pair ZP2 are arranged axially overlapping, as shown in the 1 and 2 by the reference arrows of the first gear pair ZP1 and the second gear pair ZP2. The first and second gears ZR1, ZR2 of the first gear pair ZP1 are arranged opposite the third and fourth gears ZR3, ZR4 of the second gear pair ZP2 in the 1 and 2 shown schematically slightly axially offset for reasons of clarity. Furthermore, in the 1 , 2 and 4 For reasons of clarity, the second intermediate shaft Z2 is shown schematically in a position different from the actual position, because in reality the first and second intermediate shafts Z1, Z2 are arranged one above the other, as can be seen from 3 , in which the intermediate shaft rotation axes ZA1, ZA2 of the two intermediate shafts Z1, Z2 are shown in the correct position. The present engagement of the seventh gear ZR7 with the eighth gear ZR8 is therefore in the 1 , 2 and 4 each shown schematically by a dashed connecting line between the seventh gear ZR7 and the eighth gear ZR8.

As in the 1 , 2 As shown, it is particularly provided that the first gear pair ZP1 and the second gear pair ZP2 are arranged in the axial direction between the third gear pair ZP3 and the fourth gear pair ZP4. The third embodiment according to 4 is designed in this way.

In the first embodiment according to 1 In the axial direction, the first rotor R1, the third gear pair ZP3, the first gear pair ZP1, the fourth gear pair ZP4 and the second rotor R2 are arranged one after the other in the order mentioned. The third embodiment according to 4 is designed in this way.

In this embodiment of the electric drive system 1, the first electric machine M1 and the first output shaft A1 which can be coupled or is coupled to the first rotor R1 of the first electric machine M1 in a torque-transmitting manner are arranged on one side of the electric drive system 1, and the second electric machine M2 and the second output shaft A2 which can be coupled or is coupled to the second rotor R2 of the second electric machine M2 in a torque-transmitting manner are arranged on the other side of the electric drive system 1.

In the second embodiment according to 2 In the axial direction, the first rotor R1, the fourth gear pair ZP4, the first gear pair ZP1, the third gear pair ZP3, and the second rotor R2 are arranged one after the other in the stated order. In this embodiment of the electric drive system 1, the torque flows cross, i.e. the first output shaft A1 is arranged on a side of the electric drive system 1 opposite the first electric machine M1, and the second output shaft A2 is also arranged on a side of the electric drive system 1 opposite the second electric machine M2.

As in the 1 and 2 As shown, it is provided in particular that the electric drive system 1 has a first rotor shaft bearing RL1 for supporting the first rotor shaft RW1, a second rotor shaft bearing RL2 for supporting the second rotor shaft R2, a first output shaft bearing AL1 for supporting the first output shaft A1, and a second output shaft bearing AL2 for supporting the second output shaft A2. The respective output shaft bearing AL1, AL2 is designed in particular as a tapered roller bearing.

In the second embodiment according to 2 , in which the first rotor R1, the fourth gear pair ZP4, the first gear pair ZP1, the third gear pair ZP3 and the second rotor R2 are arranged one after the other in the axial direction in the order mentioned, the first rotor shaft bearing RL1 is arranged in the axial direction between the first rotor R1 and the fourth gear pair ZP4 and the first output shaft bearing AL1 is arranged in the axial direction between the third gear pair ZP3 and the second rotor R2. This enables axial support with regard to the torque flow coming from the first electrical machine M1 on a side of a housing opposite the first electrical machine M1, for example on a housing wall of this housing, by the first output shaft bearing AL1. The first output shaft bearing AL1 is arranged in particular on and/or in this housing, in particular on and/or in this housing wall of the housing.

Accordingly, in this second embodiment according to 2 It is also provided that the second rotor shaft bearing RL2 is arranged in the axial direction between the second rotor R2 and the third gear pair ZP3, and the second output shaft bearing AL2 is arranged in the axial direction between the fourth gear pair ZP4 and the first rotor R1. This enables axial support with regard to the torque flow coming from the second electric machine M2 on a side of the housing opposite the second electric machine M2, for example on a housing wall of this housing, by the second output shaft bearing AL2. The second output shaft bearing AL2 is arranged in particular on and/or in this housing, in particular on and/or in this housing wall of the housing.

In an embodiment not shown, it can be provided that the fourth gear pair ZP4 is arranged in the axial direction between the first gear pair ZP1 and second gear pair ZP2 on the one hand and the third gear pair ZP3 on the other hand.

In an embodiment not shown, it can be provided that the first rotor R1, the first gear pair ZP1, the fourth gear pair ZP4, the third gear pair ZP3 and the second rotor R2 are arranged one after the other in the axial direction in the order mentioned.

In an embodiment not shown, it can be provided that the first rotor R1, the third gear pair ZP3, the fourth gear pair ZP4, the first gear pair ZP1 and the second rotor R2 are arranged one after the other in the axial direction in the order mentioned.

In an embodiment not shown, it can be provided that the first rotor R1, the first gear pair ZP1, the third gear pair ZP3, the fourth gear pair ZP4 and the second rotor R2 are arranged one after the other in the axial direction in the order mentioned.

In an embodiment not shown, it can be provided that the first rotor R1, the fourth gear pair ZP4, the third gear pair ZP3, the first gear pair ZP1 and the second rotor R2 are arranged one after the other in the axial direction in the order mentioned.

As in the 1 and 2 As shown, it is particularly provided that the first intermediate shaft Z1 is mounted by means of a first intermediate shaft bearing ZL1. The first intermediate shaft bearing ZL1 is particularly designed as a fixed bearing. As shown in the 1 and 2 As shown, it is further provided in particular that the first intermediate shaft Z1 is supported by a second intermediate shaft bearing ZL2. The second intermediate shaft bearing ZL2 is designed in particular as a floating bearing.

As in the 1 and 2 As shown, it is particularly provided that the second intermediate shaft Z2 is supported by a third intermediate shaft bearing ZL3. The third intermediate shaft bearing ZL3 is particularly designed as a fixed bearing. As shown in the 1 and 2 As shown, it is further provided in particular that the second intermediate shaft Z2 is supported by a fourth intermediate shaft bearing ZL4. The fourth intermediate shaft bearing ZL4 is designed in particular as a floating bearing.

In an embodiment not shown, the first output shaft A1 is mounted relative to the second output shaft A2 by means of a shaft bearing. In particular, it is provided that the first output shaft A1 is rotatably mounted directly relative to the second output shaft A2 by means of the shaft bearing. The shaft bearing has, in particular, an axial bearing and a radial bearing, each of which is designed, in particular, as a rolling bearing, for example, as a needle bearing.

In an embodiment not shown, an intermediate wall is arranged axially, i.e. in the axial direction of the output shafts A1, A2, between the sixth gear ZR6 and the eighth gear ZR8.

In an embodiment not shown, one of the output shafts A1, A2, in particular the second output shaft A2, is mounted relative to the intermediate wall by means of a further bearing. This further bearing is designed in particular as a rolling bearing, for example as a needle bearing.

In an embodiment not shown, the electric drive system 1 has a first housing part and a second housing part. The two housing parts are detachably connected to one another, in particular along a flange plane, and form the housing. The flange plane is arranged, in particular, in the axial direction between the two electric machines M1, M2 and perpendicular to the rotor shafts RW1, RW2. It is provided, in particular, that the first rotor shaft bearing RL1, the first output shaft bearing AL1, the second intermediate shaft bearing ZL2, and the third intermediate shaft bearing ZL3 are arranged in the first housing part, and the second rotor shaft bearing RL2, the second output shaft bearing AL2, the first intermediate shaft bearing ZL1, and the fourth intermediate shaft bearing ZL4 are arranged in the second housing part.

In an embodiment not shown, the first electrical machine M1 is arranged in a first machine housing, which is detachably connected to the first housing part, and/or the second electrical machine M2 is arranged in a second machine housing, which is detachably connected to the second housing part. In this embodiment, the respective electrical machine M1, M2 is thus advantageously designed as a closed unit and can thus be easily connected to and detached from the respective housing part. In this embodiment, the respective electrical machine M1, M2, in particular its machine housing, forms in particular an end cover for the respective housing part, i.e., the respective housing part has an opening that is or can be closed by the respective electrical machine M1, M2, in particular its machine housing. In one possible embodiment, the respective machine housing has a bearing plate on both sides of the rotor R1, R2 in the axial direction, in particular for supporting the rotor R1, R2 and/or the rotor shaft RW1, RW2.

The electric drive system 1 comprises, for example, a first parking lock gear P1 which is connected or connectable in a rotationally fixed manner to the first intermediate shaft Z1 and a second parking lock gear P2 which is connected or connectable in a rotationally fixed manner to the second intermediate shaft Z2, as shown in the 1 , 2 and 4 shown.

The first parking lock gear P1 is arranged in the axial direction in particular between one of the two intermediate shaft bearings ZL1, ZL2 of the first intermediate shaft Z1 on the one hand and both gear wheels ZR2, ZR5 of the first intermediate shaft Z1 on the other hand, in particular close to the intermediate shaft bearing ZL1, ZL2. In the embodiment according to 1 the first parking lock gear P1 is arranged in the axial direction between the second intermediate bearing ZL2 and the fifth gear ZR5. In the embodiment according to 2 the first parking lock gear P1 is arranged in the axial direction between the second intermediate bearing ZL2 and the second gear ZR2.

The second parking lock gear P2 is arranged in the axial direction in particular between one of the two intermediate shaft bearings ZL3, ZL4 of the second intermediate shaft Z2 on the one hand and both gears ZR4, ZR7 of the second intermediate shaft Z2 on the other hand, in particular close to the intermediate shaft bearing ZL3, ZL4. In the embodiment according to 1 the second parking lock gear P2 is arranged in the axial direction between the fourth intermediate bearing ZL4 and the seventh gear ZR7. In the embodiment according to 2 the second parking lock gear P2 is arranged in the axial direction between the fourth intermediate bearing ZL4 and the fourth gear ZR4.

In particular, it is provided that all gear pairs ZP1, ZP2, ZP3, ZP4 are arranged in the axial direction between the two parking lock gears P1, P2.

In one possible embodiment, the electric drive system 1 has a first separating clutch T1, which is designed to engage the fifth gear ZR5, as shown in 4 shown, and/or in other embodiments, to connect the second gear ZR2 in a rotationally fixed manner to the first intermediate shaft Z1.

In a possible embodiment, the electric drive system 1 has a second separating clutch T2, which is designed to engage the fourth gear ZR4, as in 4 shown, and/or in other embodiments, to connect the seventh gear ZR7 in a rotationally fixed manner to the second intermediate shaft Z2.

In one possible embodiment, the electric drive system 1 has a hollow shaft 2 arranged coaxially to the first intermediate shaft Z1, which is connected in a rotationally fixed manner to the fifth gear ZR5 and in a rotationally fixed manner to the first parking lock gear P1, as shown in 4 shown.

The respective separating clutch T1, T2 can separate the respective electric motor M1, M2 from the respective output shaft A1, A2, thus preventing torque transmission. This is particularly useful when the motor vehicle is to roll without transmitting torque to the respective electric motor M1, M2, for example, for so-called coasting operation of the motor vehicle, in which the motor vehicle is to roll as far as possible without any braking effect, in particular without engine braking and without recuperation.

In the example shown according to 4 When the first separating clutch T1 is closed, the hollow shaft 2 and thus the fifth gear ZR5, which is connected in a rotationally fixed manner to the hollow shaft 2, is connected in a rotationally fixed manner to the first intermediate shaft Z1, and when the second separating clutch T2 is closed, the fourth gear ZR4 is connected in a rotationally fixed manner to the second intermediate shaft Z2.

When the first separating clutch T1 is opened, the hollow shaft 2 and thus the fifth gear ZR5, which is connected in a rotationally fixed manner to the hollow shaft 2, is decoupled from the first intermediate shaft Z1, i.e. is no longer connected in a rotationally fixed manner to the first intermediate shaft Z1, and when the second separating clutch T2 is opened, the fourth gear ZR4 is decoupled from the second intermediate shaft Z2, i.e. is no longer connected in a rotationally fixed manner to the second intermediate shaft Z2. As a result, when the separating clutches T1, T2 are open and the vehicle is rolling, only the two output shafts A1, A2, the sixth gear ZR6 which is connected in a rotationally fixed manner to the first output shaft A1, the eighth gear ZR8 which is connected in a rotationally fixed manner to the second output shaft A2, the fifth gear ZR5 which is in engagement with the sixth gear ZR6, the seventh gear ZR7 which is in engagement with the eighth gear ZR8, the hollow shaft 2 which is connected in a rotationally fixed manner to the fifth gear ZR5, the first parking lock gear P1 which is connected in a rotationally fixed manner to the hollow shaft 2, the second intermediate shaft Z2 which is connected in a rotationally fixed manner to the seventh gear ZR7 and the second parking lock gear P2 which is connected in a rotationally fixed manner to the second intermediate shaft Z2.

The first intermediate shaft Z1, which is no longer rotationally connected to the hollow shaft 2 when the first separating clutch T1 is open, and the fourth gear ZR4, which is no longer rotationally connected to the second intermediate shaft Z2 when the second separating clutch T2 is open, do not rotate. This also applies to the second gear ZR2, which is rotationally connected to the first intermediate shaft Z1, to the first gear ZR1 meshing therewith, to the first rotor shaft RW1, which is rotationally connected therewith, and to the first rotor R1 of the first electrical machine M1, which is rotationally connected therewith, as well as to the third gear ZR3, which is meshing with the fourth gear ZR4, to the second rotor shaft RW2, which is rotationally connected therewith, and to the second rotor R2 of the second electrical machine M2, i.e. these components do not rotate either.

To implement the first separating clutch T1, it is provided in particular that the first separating clutch T1 has a first shift toothing SZ1, a second shift toothing SZ2 and a first sliding sleeve SM1.

To implement the second separating clutch T2, it is provided in particular that the second separating clutch T2 has a third shift toothing SZ3, a fourth shift toothing SZ4 and a second sliding sleeve SM2.

In the embodiment according to 4 the first gear teeth SZ1 of the first separating clutch T1 is connected in a rotationally fixed manner to the hollow shaft 2 and thus also in a rotationally fixed manner to the fifth gear ZR5, and the second gear teeth SZ2 of the first separating clutch T1 is connected in a rotationally fixed manner to the first intermediate intermediate shaft Z1. The first sliding sleeve SM1 is in engagement with the second gear teeth SZ2. To engage the first separating clutch T1, the first sliding sleeve SM1 can be displaced axially in the direction of the first gear teeth SZ1, so that it engages with the first gear teeth SZ1, but remains in engagement with the second gear teeth SZ2. As a result, the hollow shaft 2 and, via it, the fifth gear ZR5 are connected in a rotationally fixed manner to the first intermediate shaft Z1 via the first gear teeth SZ1, the first sliding sleeve SM1, and the second gear teeth SZ2.

In the embodiment according to 4 the third shift toothing SZ3 of the second separating clutch T2 is connected in a rotationally fixed manner to the fourth gearwheel ZR4, for example formed laterally thereon, and the fourth shift toothing SZ4 of the second separating clutch T2 is connected in a rotationally fixed manner to the second intermediate shaft Z2. The second sliding sleeve SM2 is in engagement with the fourth shift toothing SZ4. To close the second separating clutch T2, the second sliding sleeve SM2 can be moved axially in the direction of the third shift toothing SZ3 so that it comes into engagement with the third shift toothing SZ3, but still remains in engagement with the fourth shift toothing SZ4. As a result, the fourth gearwheel ZR4 is connected in a rotationally fixed manner to the second intermediate shaft Z2 via the third shift toothing SZ3, the second sliding sleeve SM2 and the fourth shift toothing SZ4.

In one of 4 In a different embodiment not shown, the first separating clutch T1 is designed to connect the second gearwheel ZR2 in a rotationally fixed manner to the first intermediate shaft Z1. In this embodiment, the electric drive system 1 does not have a hollow shaft 2 arranged coaxially to the first intermediate shaft Z1. In this embodiment, the fifth gearwheel ZR5 and the first parking lock gear P1 are connected in a rotationally fixed manner to the first intermediate shaft Z1. In this embodiment, when the first separating clutch T1 is closed, the second gearwheel ZR2 is connected in a rotationally fixed manner to the first intermediate shaft Z1. When the first separating clutch T1 is open, the second gearwheel ZR2 is decoupled from the first intermediate shaft Z1, i.e. is no longer connected in a rotationally fixed manner to the first intermediate shaft Z1. To implement the first separating clutch T1 for this embodiment, the first shifting toothing SZ1 of the first separating clutch T1 is connected in a rotationally fixed manner to the second gearwheel ZR2, for example formed laterally thereon, and the second shifting toothing SZ2 of the first separating clutch T1 is connected in a rotationally fixed manner to the first intermediate shaft Z1. The first sliding sleeve SM1 engages with the second shifting toothing SZ2. To engage the first separating clutch T1, the first sliding sleeve SM1 can be displaced axially in the direction of the first shifting toothing SZ1 so that it engages with the first shifting toothing SZ1, but still remains engaged with the second shifting toothing SZ2. As a result, the second gearwheel ZR2 is connected in a rotationally fixed manner to the first intermediate shaft Z1 via the first shifting toothing SZ1, the first sliding sleeve SM1 and the second shifting toothing SZ2.

In one of 4 In a different embodiment not shown, the second separating clutch T2 is designed to connect the seventh gear ZR7 in a rotationally fixed manner to the second intermediate shaft Z2. In this embodiment, the electric drive system 1 has a hollow shaft arranged coaxially to the second intermediate shaft Z2, which is rotationally fixedly connected to the seventh gear ZR7 and to the second parking lock gear P2. In this embodiment, the fourth gear ZR4 is rotationally fixedly connected to the second intermediate shaft Z2. In this embodiment, when the second separating clutch T2 is closed, the hollow shaft and thus the seventh gear ZR7, which is rotationally fixedly connected to the hollow shaft, is rotationally fixedly connected to the second intermediate shaft Z2. In this embodiment, when the second separating clutch T2 is open, the hollow shaft and thus the seventh gear ZR7, which is rotationally fixedly connected to the hollow shaft, is decoupled from the second intermediate shaft Z2, i.e. is no longer rotationally fixedly connected to the second intermediate shaft Z2. To implement the second separating clutch T2 in this embodiment, the third shift toothing SZ3 of the second separating clutch T2 is connected in a rotationally fixed manner to the hollow shaft and thus also in a rotationally fixed manner to the seventh gear ZR7, and the fourth shift toothing SZ4 of the second separating clutch T2 is connected in a rotationally fixed manner to the second intermediate shaft Z2. The second sliding sleeve SM2 engages with the fourth shift toothing SZ4. To close the second separating clutch T2, the second sliding sleeve SM2 can be moved axially in the direction of the third shift toothing SZ3 so that it engages with the third shift toothing SZ3, but still remains engaged with the fourth shift toothing SZ4. As a result, the hollow shaft and, via it, the seventh gear ZR7 are connected in a rotationally fixed manner to the second intermediate shaft Z2 via the third shift toothing SZ3, the second sliding sleeve SM2 and the fourth shift toothing SZ4.

5 shows a fourth embodiment of the electric drive system 1. This fourth embodiment differs from the first embodiment of the 1 only in the detail that the third gear pair ZP3 is arranged in the axial direction between the first gear pair ZP1 and second gear pair ZP2 on the one hand and the fourth gear pair ZP4 on the other hand. This creates a particular advantage of the fourth exemplary embodiment: the sixth gear ZR6, which is non-rotatably connected to the first output shaft A1, and the eighth gear ZFR8, which is non-rotatably connected to the second output shaft A2, are arranged directly adjacent to one another in the axial direction. This allows the first output shaft A1 and the second output shaft A2 to be designed as side shafts with small bending angles, which in turn has the advantage that greater spring travel of a chassis suspension can be realized in the motor vehicle, making the fourth exemplary embodiment particularly suitable for use in off-road vehicles.

List of reference symbols

1

drive system

2

hollow shaft

A1, A2

Output shaft

AA

Output rotary axis

AL1, AL2

Output shaft bearing

M1, M2

machine

P1, P2

Parking lock gear

R1, R2

rotor

RA1, RA2

Rotor rotation axis

RL1, RL2

Rotor shaft bearing

RT

Rotor part

RW1, RW2

rotor shaft

S1, S2

stator

SM1, SM2

Sliding sleeve

SZ1, SZ2, SZ3, SZ4

Gearshift teeth

T1, T2

Separating clutch

Z1, Z2

intermediate shaft

ZA1, ZA2

Intermediate shaft rotation axis

ZL1, ZL2, ZL3, ZL4

Intermediate shaft bearing

ZP1, ZP2, ZP3, ZP4

Gear pairing

ZR1, ZR2, ZR3, ZR4, ZR5, ZR6, ZR7, ZR8

gear

QUOTES CONTAINED IN THE DESCRIPTION

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

Cited patent literature

• DE 10 2019 107 538 A1 [0002]

Claims (13)

Electric drive system (1) for a motor vehicle, comprising: - a first electric machine (M1) having a first rotor (R1), - a second electric machine (M2) having a second rotor (R2), - a first output shaft (A1), wherein the first rotor (R1) is coupled or can be coupled to the first output shaft (A1) in a torque-transmitting manner, and - a second output shaft (A2) arranged coaxially to the first output shaft (A1), wherein the second rotor (R2) is coupled or can be coupled to the second output shaft (A2) in a torque-transmitting manner, and wherein the first output shaft (A1) and the second output shaft (A2) are arranged coaxially to a common output rotational axis (AA), characterized in that - a first rotor rotational axis (RA1) of the first rotor (R1) is parallel to and axially offset from a second rotor rotational axis (RA2) of the second rotor (R2), - the output rotational axis (AA) is arranged parallel and axially offset to both rotor rotational axes (RA1, RA2), and - a first intermediate shaft (Z1) and a second intermediate shaft (Z2) are provided, which are arranged parallel and axially offset to one another and parallel and axially offset both to the rotor rotational axes (RA1, RA2) and to the output rotational axis (AA), wherein with regard to a torque flow emanating from the first rotor (R1), the first intermediate shaft (Z1) is arranged between the first rotor (R1) and the first output shaft (A1) and with regard to a torque flow emanating from the second rotor (R2), the second intermediate shaft (Z2) is arranged between the second rotor (R2) and the second output shaft (A2). Electric drive system (1) according to Claim 1 , characterized in that in a sectional plane perpendicular to the rotor axes of rotation (RA1, RA2), the first rotor axis of rotation (RA1), the second rotor axis of rotation (RA2), a first intermediate shaft axis of rotation (ZA1) and a second intermediate shaft axis of rotation (ZA2) mark the corner points of a trapezoid and the first intermediate shaft axis of rotation (ZA1), the second intermediate shaft axis of rotation (ZA2) and the output axis of rotation (AA) mark the corner points of a triangle. Electric drive system (1) according to one of the preceding claims, characterized by - a first gear pair (ZP1), which has a first gear (ZR1) connected in a rotationally fixed manner to the first rotor (R1) and a second gear (ZR2) which is in engagement with the first gear (ZR1) and is connected or connectable in a rotationally fixed manner to the first intermediate shaft (Z1), - a second gear pair (ZP2), which has a third gear (ZR3) connected in a rotationally fixed manner to the second rotor (R2) and a fourth gear (ZR4) which is in engagement with the third gear (ZR3) and is connected or connectable in a rotationally fixed manner to the second intermediate shaft (Z2), - a third gear pair (ZP3), which has a fifth gear (ZR5) which is connected or connectable in a rotationally fixed manner to the first intermediate shaft (Z1) and a fifth gear (ZR5) which is in engagement with the fifth gear (ZR5) and is connected or connectable in a rotationally fixed manner to the first Output shaft (A1) connected sixth gear (ZR6), and - a fourth gear pair (ZP4) which has a seventh gear (ZR7) which is or can be connected in a rotationally fixed manner to the second intermediate shaft (Z2) and an eighth gear (ZR8) which meshes with the seventh gear (ZR7) and is rotationally fixedly connected to the second output shaft (A2), wherein the first gear pair (ZP1) and the second gear pair (ZP2) are arranged in the axial direction between the third gear pair (ZP3) and the fourth gear pair (ZP4). Electric drive system (1) according to Claim 3 , characterized in that in the axial direction the first rotor (R1), the third gear pair (ZP3), the first gear pair (ZP1), the fourth gear pair (ZP4) and the second rotor (R2) are arranged one after the other in the order mentioned. Electric drive system (1) according to Claim 3 , characterized in that in the axial direction the first rotor (R1), the fourth gear pair (ZP4), the first gear pair (ZP1), the third gear pair (ZP3) and the second rotor (R2) are arranged one after the other in the order mentioned. Electric drive system (1) according to one of the Claims 3 until 5 , characterized in that the first gear pair (ZP1) and the second gear pair (ZP2) are arranged axially overlapping. Electric drive system (1) according to Claim 5 or 6 , characterized by a first rotor shaft bearing (RL1) for supporting a first rotor shaft (RW1) and a first output shaft bearing (AL1) for supporting the first output shaft (A1), wherein the first rotor shaft bearing (RL1) is arranged in the axial direction between the first rotor (R1) and the fourth gear pair (ZP4) and the first output shaft bearing (AL1) is arranged in the axial direction between the third gear pair (ZP3) and the second rotor (R2). Electric drive system (1) according to one of the preceding claims, characterized by a first parking lock gear (P1) which is or can be connected in a rotationally fixed manner to the first intermediate shaft (Z1) and a second parking lock gear (P2) which is or can be connected in a rotationally fixed manner to the second intermediate shaft (Z2). Electric drive system (1) according to one of the Claims 3 until 8 , characterized by a first separating clutch (T1) which is designed to connect the fifth gear (ZR5) and/or the second gear (ZR2) in a rotationally fixed manner to the first intermediate shaft (Z1). Electric drive system (1) according to Claim 8 or 9 , characterized by a hollow shaft (2) arranged coaxially to the first intermediate shaft (Z1), wherein the hollow shaft (2) is connected in a rotationally fixed manner to the fifth gear wheel (ZR5) and in a rotationally fixed manner to the first parking lock wheel (P1). Electric drive system (1) according to one of the Claims 3 until 10 , characterized by a second separating clutch (T2) which is designed to connect the fourth gear (ZR4) and/or the seventh gear (ZR7) in a rotationally fixed manner to the second intermediate shaft (Z2). Electric drive system (1) according to one of the preceding claims, characterized in that the respective intermediate shaft (Z1, Z2) is mounted by means of a fixed bearing and a loose bearing. Electric drive system (1) according to Claim 3 , characterized in that in the axial direction the first rotor (R1), the first gear pair (ZP1), the third gear pair (ZP3), the fourth gear pair (ZP4) and the second rotor (R2) are arranged one after the other in the order mentioned.

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