DE102014223502A1 - Drive arrangement for a vehicle and vehicle with the drive assembly - Google Patents

Abstract

In electric vehicles, electric axles are often used, starting from an electric motor, a drive torque is optionally guided via a gear change transmission to a transverse differential, which distributes the drive torque to two driven wheels of the axle. It is an object of the present invention to propose a drive arrangement, which is structurally simple. For this purpose, a drive arrangement 1 with an electric motor 4, wherein the electric motor 4 with the rotor shaft 37 defines a first axis 7, with a differential device 8, wherein the differential device 8 defines a second axis 9, wherein the first and the second axis 7,9 parallel with a gear portion 10, wherein the gear portion 10 has at least two gears, wherein the gear portion 10 is arranged in a torque path between the electric motor 4 and the differential device 8 coaxial with one of the axles, with a gear stage portion 13, wherein the gear stage portion 13th an input gear 31 and an output gear 32, wherein the input gear 31 to the first axis 7 and the output gear 32 is arranged coaxially to the second axis 9, wherein the gear stage portion 13 has a Zwischenradeinrichtung 33, wherein the Zwischenradeinrichtung 33 with the input gear 31 and Output wheel 32 is engaged, proposed n, wherein the gear stage section 13 has exactly one input gear 31.

Description

The invention relates to a drive arrangement for a vehicle with an electric motor, wherein the electric motor with the rotor shaft defines a first axis, with a differential device, wherein the differential device defines a second axis, wherein the first and the second axis are arranged offset from each other in parallel, with a A gear portion, wherein the gear portion has at least two gears, said gear portion is arranged in a torque path between the electric motor and the differential device coaxial with one of the axes, with a gear stage portion, wherein the gear stage portion has an input gear and an output gear, wherein the input gear coaxial with the the first axis and the output gear is arranged coaxially with the second axis, wherein the gear stage portion has a Zwischenradeinrichtung, wherein the Zwischenradeinrichtung with the input gear and the output gear is engaged. The invention further relates to a vehicle with this drive arrangement.

In electric powered vehicles, such as Electric vehicles and hybrid vehicles, electric axles are often used, starting from an electric motor, a drive torque is optionally performed via a gear change transmission to a transverse differential, which distributes the drive torque to two driven wheels of the axle.

For example, the document discloses DE 10 2010 024 147 A1 , which is probably the closest prior art, a 2-speed transmission for transmitting a driving torque in a drive train of a vehicle. The 2-speed transmission has an input shaft, a planetary gear and an output shaft, wherein the input shaft and the output shaft are arranged offset parallel to each other. Furthermore, the 2-speed transmission has a switching device for switching over two operating modes of the planetary gear, so that the two gears are realized. In the 7 The document is an embodiment shown, wherein the drive torque is translated in dependence on the selected gear in a downstream transmission stage.

It is an object of the present invention to propose a drive arrangement, which is structurally simple. This object is achieved by a drive arrangement with the features of claim 1 and by a vehicle having the features of claim 10. Preferred or advantageous embodiments of the invention will become apparent from the dependent claims, the following description and the accompanying drawings.

In the context of the invention, a drive arrangement is proposed, which is suitable and / or designed for a vehicle. In particular, the drive arrangement is formed as part of a drive train of the vehicle. In particular, the drive arrangement forms an electrical axis, wherein the drive arrangement is designed to drive two wheels of the electrical axis. The axle may be a front axle or a rear axle of the vehicle.

The drive assembly includes an electric motor, wherein the electric motor generates a drive torque for the vehicle. Preferably, the electric motor is the only torque generator for driving the vehicle of the drive assembly. In particular, the drive arrangement is designed for an electric vehicle. The electric motor defines a first axis with the rotor shaft. In particular, the first axis is designed as a drive axle. Alternatively, the drive arrangement may be formed as part of a hybrid drive.

Furthermore, the drive arrangement has a differential device, wherein the differential device distributes the drive torque of the electric motor, optionally the translated or reduced drive torque of the electric motor, to two outputs, in particular to the two wheels of the driven axle.

In particular, the differential device is designed as a transverse differential. The differential device may e.g. be realized as a bevel gear differential means or as a Planetenraddifferenzeinrichtung. The differential device defines either with its input or with its two outputs a second axis. In particular, the second axis is designed as an output axis. It is provided that the first and the second axis are arranged parallel to each other, but offset from each other.

The drive assembly further comprises a passage section, wherein the passage section is in particular formed as a gear change section and has at least two courses. The passage section is arranged in a torque path between the electric motor and the differential device. Thus, the gear portion converts the drive torque generated by the electric motor before being input to the differential device. Preferably, the alternative torque paths in the transmission section of the at least two gears are each form-fitting manner, in particular a frictional engagement in the course of the torque paths in the transmission section is dispensed with. The passage section may have exactly two courses, in less preferred embodiments the passage section has more than two courses. In principle, however, has shown that the choice of two gears for the design of a drive assembly for a vehicle, especially for an electric vehicle, in the field of tension between the design effort and the benefit represents a good compromise. The gang section is arranged coaxially with one of the axles.

Furthermore, the drive arrangement has a gear stage section which has an input gear and an output gear. Particularly preferably, input gear and output gear are each designed as a spur gear. The input gear is coaxial with the first axis and the output gear is coaxial with the second axis. In addition, the gear stage section has a Zwischenradeinrichtung, wherein the Zwischenradeinrichtung with the input gear and the output gear is engaged. In particular, the driving torque of the electric motor is passed through the Zwischenradeinrichtung. In particular, with respect to the torque path input wheel, Zwischenradeinrichtung and output gear are arranged serially to each other.

In the context of the invention is claimed that the gear stage section has exactly one input gear. In particular, it is determined by this demarcation that the gear stage section has no two input gears with different pitch diameters, as in the prior art in the 7 is shown. The gear stage section has in particular a fixed gear ratio. The gear ratio can be chosen equal to 1 in terms of amount, but it can also be realized as a translation or as a reduction.

While in the prior art, a device similar to the Zwischenradeinrichtung is used to form two alternative, parallel torque paths, which are used depending on the selected gear, a simplified construction is proposed according to the invention, wherein the gear stage section has only one input gear, wherein Thus, the Zwischenradeinrichtung is designed as a purely serial and not as a parallel torque path guide.

By Zwischenradeinrichtung is achieved that the center distance between the first and the second axis can be variably adjusted. On the one hand, the variable setting is possible by varying the pitch diameter of the input gear, intermediate gear and output gear. On the other hand, it is possible to vary the axial distance by varying the position of the first axis, the second axis and a Zwischenradachse the Zwischenradeinrichtung. If the first axis, the intermediate wheel axis of the intermediate wheel device and the second axis are arranged in a straight line relative to one another in an axial plan view, a maximum distance between the first axis and the second axis is generated. Alternatively, it is also possible that the first axis, the Zwischenradachse and the second axis are arranged angled to each other, so that the distance between the first axis and the second axis is reduced from the maximum distance.

Furthermore, the pitch circle diameter of the output gear can be reduced. Due to the smaller pitch circle diameter of the output wheel, the mass on the second axis is reduced on the one hand. Due to the reduced mass higher dynamics due to the reduction of the mass to be accelerated can be achieved. Furthermore, the reduced mass allows a better acoustics to be implemented in the region of the second axis. After the second axle preferably forms the wheel axle of the driven wheels, it is further achieved by a possible reduction of the pitch circle diameter of the output wheel that the ground clearance and the installation space for a deflection of PTO shafts from the neutral position is increased. In particular, the required installation space can be reduced in terms of the diameter of the entire assembly about the second axis.

Another advantage is achieved by the three-stage gear stage section that the direction of rotation of the electric motor and the second axis is the same when moving forward. In particular, no torque reversal occurs by the combination of the gear portion and the gear stage portion in comparison between the first and second axes.

In a particularly preferred and simple structural embodiment of the invention, the Zwischenradeinrichtung is designed as an intermediate. In particular, input gear, intermediate gear and output gear are in a common plane, in particular toothing plane, in which they mesh. In this embodiment, in particular the gear stage section in the axial direction can be constructed particularly narrow.

In an alternative embodiment of the invention, the Zwischenradeinrichtung has an intermediate shaft and an intermediate input gear and an Zwischenausgangsrad, wherein the Zwischeneingangsrad with the input gear and Zwischenausgangsrad with the output gear are engaged and rotatably mounted on the intermediate shaft. In particular, intermediate input gear and Zwischenausgangsrad are arranged coaxially with each other. Due to the design of the Zwischenradeinrichtung with an intermediate shaft, it is possible, the input gear and the output gear with respect to the axial direction to each other. In this way, a possibly structurally predetermined by the vehicle space can be optimally utilized.

In one possible development of the invention, the intermediate output gear has a different pitch circle diameter than the intermediate input gear. In this way, the ratio of the gear stage section can be adjusted. By changing the pitch circle diameter also advantageous effects are to be achieved in terms of space. If the pitch diameter of the Zwischenausgangsrads smaller than the pitch diameter of the Zwischeneingangsrads, the size of the drive assembly is reduced in the radial direction to the Zwischenradachse. If the Zwischenausgangsrad larger than the Zwischeneingangsrad, although the space is nominally increased, but the translation is changed, but the space enlargement only the radius magnification and not the increase in diameter corresponds, so that a ratio change can be implemented space-saving.

In a preferred constructional realization of the invention, the passage section has a planetary gear and a gearbox. Preferably, the planetary gear is designed as a Stirnradplanetengetriebe. The planetary gear has a sun gear, a plurality of planet gears, a planet carrier for supporting the planetary gears. Furthermore, the planetary gear has a ring gear, wherein the planet gears mesh with the sun gear and with the ring gear.

The manual transmission has two inputs and one output, wherein the two inputs for selecting the at least two gears are selectively coupled to the output. The sun gear forms an input in the planetary gear. In addition, the sun gear and the planet carrier each form an output from the planetary gear, wherein the outputs of the planetary gear are operatively connected to the inputs of the gearbox. The ring gear, however, fixed stationary.

In a preferred structural embodiment of the invention, the transmission has a switching element, in particular a sliding sleeve, which is slidably mounted on a Schaltausgangsrad, wherein the Schaltausgangsrad forms the output of the transmission. The inputs of the gearbox are formed by two switching input gears, wherein the switching element is selectively connectable to one of the two shift input gears.

Thus, a first torque path from the sun gear as the first input of the planetary gear to the sun gear as the first output of the planetary gear, wherein the first output of the planetary gear is coupled to a first input of the gearbox and the first input of the gearbox in the first gear to the output of the Gearbox is operatively connected. A second torque path is from the sun gear of the planetary gear as an input of the planetary gear via the planet gears in the planet carrier of the planetary gear as a second output of the planetary gear. The second output of the planetary gear is coupled to the second input of the gearbox. In the second gear, the second input of the gearbox is coupled to the output of the gearbox.

In a preferred embodiment of the invention, the passage portion is arranged coaxially with the first axis. Thus, the output of the gearbox is particularly preferably operatively connected to the input gear, in particular rotatably coupled. Alternatively or additionally, it is preferred that the input of the gear portion is rotatably coupled to the rotor shaft of the electric motor.

This preferred embodiment has the advantage that the passage section is arranged in the region of the first axis and not in the region of the second axis, which forms the output axis. As a result, the second axle with respect to space and weight is significantly relieved.

In preferred embodiments of the invention, the input gear forms in the axial direction to the first axis viewed a central output, wherein the input gear between the planetary gear and the gearbox is arranged. Alternatively, the input gear can form a side exit, wherein the input gear is arranged on the edge side to the planetary gear and the gearbox. Here again two possibilities are to be distinguished, wherein the input wheel is arranged on the axial side facing the electric motor or arranged on the opposite axial side. Each of the three options can offer advantages in certain installation space situations of the vehicle, since the input wheel can be arranged as an interface to the second axis as desired.

In an alternative embodiment of the invention, the passage portion is arranged coaxially with the second axis. In this embodiment, the first axis is relieved in terms of mass and space, so that other space requirements can be considered. It is possible that the output gear is arranged as a central input between the differential device and the passage section or as a side entrance on an axial side of the passage section facing away from the differential device. Also this positioning can be done in Depending on the installation space requirements are selected advantageous.

Another object of the invention relates to a vehicle with the drive assembly, as described above or according to one of the preceding claims. In particular, the drive arrangement is designed as an electrical axle in the vehicle for driving the front axle or the rear axle. In a further development of the invention, such a drive arrangement can also be provided for the front axle and for the rear axle.

Further features, advantages and effects of the invention will become apparent from the following description of preferred embodiments of the invention and the accompanying figures. Showing:

1 a schematic representation of a drive arrangement for a vehicle as a first embodiment of the invention;

2 a further embodiments of the drive assembly in the 1 ;

3 a further embodiments of the drive assembly in the 1 ;

4 a further embodiments of the drive assembly in the 1 ;

5 a further embodiments of the drive assembly in the 1 ;

6 a further embodiments of the drive assembly in the 1 ;

7 a further embodiments of the drive assembly in the 1 ;

8th a further embodiments of the drive assembly in the 1 ;

9 a further embodiments of the drive assembly in the 1 ;

10 a further embodiments of the drive assembly in the 1 ,

The 1 shows a schematic representation of a drive assembly 1 for a vehicle 2 as an embodiment of the invention, wherein the vehicle 2 only highly schematic as a block is shown. The drive arrangement 1 is designed as an electrical axis and is used for driving wheels 3 of the vehicle 2 a rear axle or a front axle.

The drive arrangement 1 has an electric motor 4 on, with the electric motor 4 a stator 5 and a rotor 6 includes. A rotor shaft 37 of the rotor 6 defines a first axis 7 in the drive arrangement 1 , The drive arrangement 1 also has a differential device 8th on, with the differential device 8th a second axis 9 Are defined. The second axis 9 is coaxial with the driven axle of the vehicle 2 educated.

The drive arrangement 1 has a passage section 10 on, with the passage section 10 a hallway entrance 11 and a gangway exit 12 having. The passage section 10 is formed, two different gears, so two different translations between the gear input 11 and the passageway exit 12 to switch.

Furthermore, the drive arrangement 1 a gear stage section 13 on, wherein the gear stage section 13 a gear stage input 14 and a gear stage output 15 having. In the embodiment in the 1 is the gearbox input 14 rotatably with the gear output 12 and the gear stage output 15 non-rotatable with the differential input 35 in the differential device 8th connected.

A torque path runs from the electric motor 4 over the passage section 10 , the gear stage section 13 in the differential device 8th and gets up there 2 differential outputs 16a Distributed to the powered wheels 3 to lead.

The passage section 10 has a planetary gear 17 and a manual transmission 18 on. The planetary gear 17 has a sun wheel 19 , a plurality of planetary gears 20 and a planet carrier 21 on. The planet wheels 20 are rotatable on the planet carrier 21 arranged. The axes of rotation of the planet wheels 20 are radially offset and at the same time parallel to the axis of rotation of the sun gear 19 arranged. Furthermore, the planetary gear has 17 a ring gear 22 on, which on a frame or a housing of the drive assembly 1 is arranged stationary or fixed to the frame. The sun wheel 19 forms a planetary gear input 23 , at the same time forms the sun wheel 19 a first planetary gear output 24 , The planet carrier 21 forms a second planetary gear output 25 ,

The manual transmission 18 has two switch inputs, the first switch input acting as a first switch input gear 26 and the second switching input as a second switching input gear 27 are formed. The manual transmission 18 further includes a shift output gear 28 , on which an axially movable sliding sleeve 29 is arranged as a switching element. The sliding sleeve 29 can the switching output 28 optionally with the first Schalteingangsrad 26 or with the second shift input gear 27 couple by axial displacement. The switching output gear 28 forms a switching output 30 from the manual transmission 18 ,

The gear stage section 13 has an input wheel 31 on, which is coaxial with the first axis 7 is arranged. Furthermore, the gear stage section 13 a starting wheel 32 on, which is coaxial with the second axis 9 is arranged. In the moment path between the input wheel 31 and the output gear 32 is a Zwischenradeinrichtung 33 arranged in the embodiment in the 1 as a single idler 34 is trained. The gear stage section 13 forms an operative connection between the first axis formed as a drive axle 7 and the second axis formed as output shaft 9 ,

The entrance wheel 31 , the intermediate wheel 34 and the output gear 32 lie in a common gearing plane. This is the gear stage section 13 very narrow in axial extent. The intermediate wheel device 33 and in the embodiment in the 1 the intermediate wheel 34 define in the axis of rotation a Zwischenradachse 36 ,

The gear stage section 13 is thus formed in three stages. This implements a number of advantages:
Due to the three-stage structure, the ratio of the gear stage section 13 be better adjusted. In particular, the pitch circle diameter of the output gear 32 kept small. This leads to a space advantages, since the reduction of the pitch circle diameter of the output gear 32 the required space for the differential device 8th as "Final Drive" can be kept lower. Furthermore, the masses are at the final drive and / or at the differential device 8th reduced so that the dynamics and the acoustics are improved. By reducing the output wheel 32 Any occurring axial forces and / or tilting moments are also applied to the differential device 8th through the exit wheel 32 downsized, since the leverage of the output gear 32 is weakened due to the reduction of the pitch circle diameter. The space reduction in the area of the Final Drive also leads to more space for the deflection of cardan shafts in the neutral position and to an increase in ground clearance.

It is also possible, the center distance between the first axis 7 and the second axis 9 adjust variably by the first axis 7 , the intermediate wheel axle 36 and the second axis 9 viewed in axial plan view in a line or any angle to each other can be employed. For example, the angle may be the first axis 7 - Intermediate wheel axle 36 - second axis 9 take an angle smaller than 270 degrees.

In addition, the differential device 8th near the center of the vehicle 2 be positioned along the longitudinal axis. This allows equally long differential outputs 16a , b, the same stiffness and thus allow better control of vehicle dynamics.

In the structural design of the drive assembly 1 in the 1 is the corridor entrance 11 with a rotor shaft 37 of the rotor 6 rotatably connected. At the corridor exit 12 closes immediately the gear stage section 13 on, with the gear output 12 with the input wheel 31 rotatably connected. The gear stage section 13 forms the operative connection between the first axis 7 and the second axis 9 , The output wheel 32 forms the gear stage output 15 and is non-rotatable with the differential input 35 , which is formed in this example as a differential cage connected.

In operation, depending on the switching position of the sliding sleeve 29 a first or second gear are selected. The differential device 8th is formed in this embodiment as a bevel gear, wherein a bevel gear 38a respectively. 38b the differential output 16a respectively. 16b forms. Instead of a bevel gear differential designed as a differential device 8th can also be used a planetary gear differential. The entrance wheel 31 forms a side exit, this being arranged so that the passage section 10 between the electric motor 4 and the input wheel 31 is arranged.

In the 2 an alternative embodiment is shown, which is characterized by the formation of the Zwischenradeinrichtung 33 different. In the embodiment in the 2 has the Zwischenradeinrichtung 33 an intermediate wave 39 , a Zwischenausgangsrad 40 and an intermediate input gear 41 on. The intermediate shaft 39 is coaxial with the Zwischenradachse 36 arranged. The intermediate input gear 41 combs with the input wheel 31 , the Zwischenausgangsrad 40 meshes with the output gear 32 , Zwischenausgangsrad 40 and intermediate input gear 41 are arranged coaxially with each other. In the illustration shown have the Zwischenausgangsrad 40 and the intermediate input gear 41 the same pitch circle diameter. By using the intermediate shaft 39 can the output gear 32 relative to the input wheel 31 be offset in the axial direction. This makes it possible to design space requirements of the vehicle 2 enter into.

In the 3 is shown a further embodiment of the invention, wherein the axial Order of planetary gear 17 , Manual transmission 18 and gear stage section 13 were swapped. In the embodiment in the 3 is the input wheel 31 designed as a hollow shaft through which the rotor shaft 37 is carried out. Further, the sun wheel forms 19 again at the same time an input and an output of the planetary gear 17 , wherein, however, input and output on one axial side of the planetary gear 17 lie and the first shift input gear 26 between the electric motor 4 and the planetary gear 17 is arranged. The intermediate wheel device 33 is in the 3 as an intermediate 34 educated.

In the 4 is a variation of the drive assembly 1 in the 3 shown, with Zwischenradeinrichtung 33 instead of as an intermediate 34 as an assembly as in the 2 comprising the intermediate shaft 39 , Zwischenausgangsrad 40 and intermediate input gear 41 is trained.

Both in the embodiment in the 3 as well as in the embodiment in the 4 forms the entrance wheel 31 a side entrance and is between the electric motor 4 and the passage section 10 arranged. By using the assembly as Zwischenradeinrichtung 33 can be the axial position of the output wheel 32 relative to the input wheel 31 be set.

In the embodiment of the drive assembly 1 in the 5 forms the entrance wheel 31 a center input, with the input gear 31 between the planetary gears 17 and the manual transmission 18 is arranged. In this embodiment, the planet carrier 21 and / or the second shift input gear 27 formed as a hollow shaft through which the extension of the rotor shaft 37 and / or the connection between sun gear 19 and first shift input gear 26 is performed. Further, the input wheel 31 also formed as a hollow shaft, which is radially outside of and concentric with the rotor shaft 37 is arranged. In the embodiment in the 5 is the Zwischenradeinrichtung 33 as an intermediate 34 educated.

The 6 shows a further embodiment, which differs from the embodiment in the 5 characterized in that the Zwischenradeinrichtung 33 again as an assembly comprising the intermediate shaft 39 , the Zwischenausgangsrad 40 and the intermediate input gear 41 , is trained.

In the 7 a further embodiment of the invention is shown, wherein the passage section 10 coaxial with the second axis 9 is arranged. In this embodiment, the rotor shaft 37 rotatably with the input gear 31 connected. The intermediate wheel device 33 is as an intermediate 34 educated. The output wheel 32 is designed as a hollow shaft and is on the one hand rotationally fixed to the sun gear 19 and over the sun wheel 19 rotatably with the first shift input 26 connected. The second shift input gear 27 will be as before by the planet carrier 21 educated. The switching output gear 28 is non-rotatable with the differential input 35 connected. In this embodiment, the space is about the first axis 7 significantly reduced.

In the 8th is an alternative to the embodiment in the 7 shown, wherein the Zwischenradeinrichtung 33 again as an assembly comprising the intermediate shaft 39 , the Zwischenausgangsrad 40 and the intermediate input gear 41 , is trained.

The 9 shows a further embodiment of the invention, wherein as in the previous embodiments in the 7 and 8th the passage section 10 coaxial with the second axis 9 is arranged. While in the embodiments in the 7 and 8th the output wheel 32 has formed a side exit, wherein the side exit on one of the differential device 8th is arranged on the opposite side, so viewed in the axial direction, the differential device 8th , the passage section 10 and the output gear 32 was lined up. In contrast, in the 9 an embodiment shown, wherein the output wheel 32 again forms a side exit, the side exit, however, between the differential device 8th and the passage section 10 is arranged. In this embodiment, adjacent to the output wheel 32 the planetary gear 17 arranged. Axially outside is the manual transmission 18 positioned. The intermediate wheel device 33 is as an intermediate 34 educated.

In the 10 on the other hand is an embodiment as in the 9 shown, wherein the Zwischenradeinrichtung 33 again as an assembly, comprising intermediate shaft 39 , Zwischenausgangsrad 40 and intermediate input gear 41 , is trained.

LIST OF REFERENCE NUMBERS

1

 drive arrangement

2

 vehicle

3

 Wheels of the vehicle

4

 electric motor

5

 stator

6

 rotor

7

 first axis

8th

 differential device

9

 second axis

10

 transition section

11

 Response input

12

 gear output

13

 Transmission step portion

14

 Gear stage input

15

 Gear stage output

16a,

 b Differential outputs

17

 planetary gear

18

 manual transmission

19

 sun

20

 planetary gears

21

 planet carrier

22

 ring gear

23

 Planetary gear input

24

 first planetary gear output

25

 second planetary gear output

26

 first shift input gear

27

 second shift input gear

28

 Schaltausgangsrad

29

 sliding sleeve

30

 switching output

31

 input gear

32

 output gear

33

 Zwischenradeinrichtung

34

 idler

35

 differential input

36

 intermediate gear

37

 rotor shaft

38a,

 b bevel gear

39

 intermediate shaft

40

 Zwischenausgangsrad

41

 Zwischeneingangsrad

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The 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 102010024147 A1 [0003]

Claims (10)

Drive arrangement ( 1 ) with an electric motor ( 4 ), wherein the electric motor ( 4 ) with the rotor shaft ( 37 ) a first axis ( 7 ), with a differential device ( 8th ), wherein the differential device ( 8th ) a second axis ( 9 ), the first and second axes ( 7 . 9 ) are offset parallel to each other, with a transition section ( 10 ), wherein the passage section ( 10 ) has at least two courses, wherein the passage section ( 10 ) in a torque path between the electric motor ( 4 ) and the differential device ( 8th ) coaxial with one of the axes ( 7 . 9 ) is arranged, with a gear stage section ( 13 ), wherein the gear stage section ( 13 ) an input wheel ( 31 ) and an output wheel ( 32 ), wherein the input wheel ( 31 ) coaxial with the first axis ( 7 ) and the output wheel ( 32 ) coaxial with the second axis ( 9 ) is arranged, wherein the gear stage section ( 13 ) a Zwischenradeinrichtung ( 33 ), wherein the intermediate wheel device ( 33 ) with the input wheel ( 31 ) and the output wheel ( 32 ) is engaged, characterized in that the gear stage section ( 13 ) exactly one input wheel ( 31 ) having. Drive arrangement ( 1 ) according to claim 1, characterized in that the intermediate wheel device ( 33 ) as an intermediate wheel ( 34 ) is trained. Drive arrangement ( 1 ) according to claim 1, characterized in that the intermediate wheel device ( 33 ) an intermediate wave ( 39 ) with an intermediate input gear ( 41 ) and an intermediate exit wheel ( 40 ), wherein the intermediate input wheel ( 41 ) with the input wheel ( 31 ) and the Zwischenausgangsrad ( 40 ) with the output wheel ( 32 ) and wherein the intermediate input gear ( 41 ) and the Zwischenausgangsrad ( 40 ) rotatably on the intermediate shaft ( 39 ) are arranged. Drive arrangement ( 1 ) according to one of the preceding claims, characterized in that the Zwischenausgangsrad ( 40 ) a different pitch circle diameter than the intermediate input gear ( 41 ) having. Drive arrangement ( 1 ) according to one of the preceding claims, characterized in that the passage section ( 10 ) a planetary gear ( 17 ) and a manual transmission ( 18 ), wherein the planetary gear ( 17 ) a sun wheel ( 19 ), a plurality of planetary gears ( 20 ), a planet carrier ( 21 ) for supporting the planetary gears ( 20 ) and wherein the manual transmission ( 18 ) has two inputs and one output, wherein the two inputs for selecting the at least two gears are coupled to the output, wherein the sun gear ( 19 ) an input in the planetary gear ( 17 ) and the sun wheel ( 19 ) and the planet carrier ( 21 ) two outputs of the planetary gear ( 17 ), wherein the outputs of the planetary gear ( 17 ) with the inputs of the gearbox ( 18 ) are operatively connected. Drive arrangement ( 1 ) according to one of the preceding claims, characterized in that the passage section ( 10 ) coaxial with the first axis ( 7 ) is trained. Drive arrangement ( 1 ) according to claim 6, characterized in that in the axial direction to the first axis ( 7 ) the input wheel ( 31 ) forms a central output, wherein the input wheel ( 31 ) between the planetary gear ( 17 ) and the manual transmission ( 18 ), or forms a side exit, wherein the input wheel ( 31 ) at the edge of the planetary gear ( 17 ) and the manual transmission ( 18 ) is arranged. Drive arrangement ( 1 ) according to one of claims 1 to 4, characterized in that the passage section ( 10 ) coaxial with the second axis ( 9 ) is arranged. Drive arrangement ( 1 ) according to claim 8, characterized in that the output wheel ( 32 ) forms a side exit, the edge of the passage section ( 10 ) is arranged. Vehicle ( 2 ) with the drive arrangement ( 1 ) according to one of the preceding claims, characterized in that the drive arrangement ( 1 ) as the electrical axis in the vehicle ( 2 ) is trained.

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