Drive arrangement with direction-controlled two-speed transmission for a vehicle and vehicle with the drive arrangement

Abstract

Drive arrangement (2) for a vehicle (1) with an input shaft (4), wherein the input shaft (4) can be coupled to an electric motor (3), with an output shaft (5), wherein the output shaft (5) forms an output of the drive arrangement (2), wherein the drive arrangement (2) comprises a first and a second freewheel device (6,7), furthermore comprehensive a first torque path (100) for transmitting a first drive torque with a first drive direction of rotation from the input shaft (4) to the output shaft (5), and by a second torque path (200) for transmitting a second drive torque with a second drive direction of rotation from the input shaft (4) to the output shaft (5), wherein the second drive direction of rotation is opposite to the first drive direction of rotation, wherein the first and the second torque paths (100, 200) implement different gear ratios and / or different gears, wherein the first freewheel device (6) is arranged in the first torque path (100) such that it is in a transmission state during the first drive torque with the first drive direction of rotation and in a freewheel state during the second drive torque with the second drive direction of rotation and wherein the second freewheel device (7) is arranged in the second torque path (200) such that it is in a transmission state during the second drive torque with the second drive direction of rotation and in a freewheel state during the first drive torque with the first drive direction of rotation, characterized in that the freewheel devices (6, 7) are arranged coaxially and / or concentrically to each other and that the first freewheel device (6) has a first freewheel outer ring (10) and a first freewheel inner ring (9) and that the second freewheel device (7) has a second freewheel outer ring (18) and a second freewheel inner ring (17), wherein the first freewheel outer ring (10) and the second freewheel outer ring (18) are coupled in a rotationally fixed manner and are connected in a rotationally fixed manner to the output shaft (5).

Description

[0001] The invention relates to a drive arrangement for a vehicle having the features of the preamble of claim 1. The invention also relates to a vehicle with this drive arrangement.

[0002] In electromobility, the enhanced characteristics of electric motors not only lead to a change in the drive source itself, but also to a change in the transmissions within the drive trains. Therefore, different transmission concepts are being sought for electric vehicles that utilize the special characteristics of electric motors.

[0003] For example, German patent application DE 100 56 597 A1, which probably represents the closest prior art, discloses a high-reduction gearbox for a bicycle with an electric motor, enabling switching between two output speeds. It is equipped with a housing-fixed internal gear, a first drive gear connected to a drive shaft via a first freewheel clutch that can be engaged and disengaged, a second drive state connected to the drive shaft (19) via a second freewheel, and at least two planetary gears, each having at least two, preferably three, external gears rotationally fixed to one another, wherein a first external gear is in mesh with the first drive gear and an output-side internal gear, and a second external gear is in mesh with the second drive gear.and a housing-fixed internal gear is in engagement with, for example, a third external gear, wherein the gear ratio from the first drive gear to the first external gear is greater than from the second drive gear to the second external gear, and the number of teeth of the two internal gears are different and / or the number of teeth of the first and third external gears are different.

[0004] US 2011 / 0 177 902 A1 describes a bicycle gear shifter with bidirectional input and setup output.

[0005] US 2011 / 0 185 849 A1 describes an integrated planetary gear unit with bidirectional input and one-way output.

[0006] CN 1 01 968 103 A describes a shift mechanism for forward and reverse gears with full range. The object of the present invention is to propose a drive arrangement for a vehicle which is designed to be particularly user-friendly.

[0007] This problem is solved by a drive arrangement having the features of claim 1 and by a vehicle having the drive arrangement having the features of claim 7. Preferred or advantageous embodiments of the invention will become apparent from the dependent claims, the following description, and the accompanying figures.

[0008] The invention relates to a drive arrangement suitable and / or designed for use in a vehicle. The drive arrangement is particularly designed as a drive train within the vehicle. Specifically, the drive arrangement has an input interface for connecting an electric motor and an output interface for connecting at least one driven wheel of the vehicle. Particularly preferably, and resulting from the special characteristics of the drive arrangement, the vehicle is designed as a single-track vehicle. For example, the vehicle is designed as a two-wheeled bicycle, particularly a cargo bike, for transporting loads.

[0009] The drive assembly has an input shaft, which forms the input interface and can be coupled to and / or is coupled to the electric motor. The input shaft and a rotor shaft of the electric motor can be coaxial and / or formed as a single unit. Alternatively, an intermediate gearbox, a deflection gearbox, or other transmission components are arranged between the input shaft and the electric motor.

[0010] The drive assembly has an output shaft, which forms the output interface and / or a driven element of the drive assembly. The output shaft is, in particular, operatively connected to and / or functionally linked with the at least one driven wheel. Optionally, further transmission components, such as a final drive, a deflection drive, or other transmission components, can be arranged between the output shaft and the driven wheel.

[0011] The drive arrangement comprises a first and a second freewheel device. The freewheel device is also implemented as an overrunning clutch. Specifically, in a first direction of rotation, the freewheel device can assume a transmission state in which a drive torque is transmitted from the input of the freewheel device to the output of the freewheel device. Furthermore, the freewheel device can assume a freewheel state in which no drive torque can be transmitted from the input of the freewheel device to the output and / or the input and output are decoupled from each other.

[0012] Within the scope of the invention, it is proposed that the drive arrangement includes a first torque path for transmitting a first drive torque with a first drive direction of rotation from the input shaft to the output shaft, and a second torque path for transmitting a second drive torque with a second drive direction of rotation from the input shaft to the output shaft.

[0013] The second drive direction of rotation is designed to be opposite to the first drive direction of rotation.

[0014] Furthermore, different gear ratios and / or different gears are implemented in the first and second torque paths. For example, a first gear can be implemented via the first torque path and a second gear via the second torque path. However, it is also possible for the first gear to operate via the second torque path and the second gear via the first torque path. It is intended that the first drive torque is transmitted via the first torque path in the first direction of rotation, and the second drive torque is transmitted via the second torque path in the second direction of rotation.

[0015] It is provided that the first freewheeling device is arranged in the first torque path such that it switches to the transmission state at the first drive torque with the first drive direction of rotation and to the freewheeling state at the second drive torque with the second drive direction of rotation. The second freewheeling device, on the other hand, is arranged in the second torque path such that it is in the transmission state at the second drive torque with the second drive direction of rotation and in the freewheeling state at the first drive torque with the first drive direction of rotation.

[0016] In other words, the selection of torque paths can be chosen depending on the drive direction of the input shaft. If the input shaft rotates in the first drive direction, the drive torque is transmitted via the first torque path; if the input shaft rotates in the second drive direction, the drive torque is transmitted via the second torque path. Since different gear ratios and / or different gears are represented for the two torque paths, the design of the drive arrangement results in the drive arrangement being configured as a two-start gearbox, whereby the gear selection can be chosen, in particular controlled and / or activated, by the drive direction of the input shaft and thus by the drive direction of the electric motor.If the electric motor rotates in the first drive direction, the first torque path is selected; if the electric motor rotates in the opposite direction and / or in the second drive direction, the second torque path is selected.

[0017] This creates a user-friendly drive arrangement that takes advantage of the fact that electric motors can be operated with virtually identical characteristics in both directions of rotation. In this way, the drive arrangement can be implemented completely differently compared to the gearbox of a conventional bicycle.

[0018] In a preferred embodiment of the invention, a direction-of-rotation reversal device is arranged in one of the torque paths, preferably exactly in one of the torque paths. The direction-of-rotation reversal device is preferred because otherwise the vehicle would be driven in one direction during the first torque path and in the opposite direction during the second torque path.

[0019] In a first possible design implementation of the invention, the drive arrangement includes a countershaft, the second torque path of which is routed via the countershaft. The countershaft is arranged, in particular, parallel to and offset from the input shaft and / or the output shaft. Preferably, the input shaft and the output shaft are arranged coaxially with each other. Thus, it is possible for the first torque path to run coaxially with the input shaft and / or output shaft, and for the second torque path to be routed via the countershaft.

[0020] In a first possible embodiment of the invention, the input shaft is connected to the auxiliary shaft via a two-stage spur gear stage. Because the spur gear stage is two-stage, a reversal of the direction of rotation is implemented, so that the two-stage spur gear stage forms the reversing device.

[0021] Alternatively, the input shaft is connected to the auxiliary shaft via a traction element, so that the direction reversal device is formed via the traction element and / or the associated traction element gearbox.

[0022] In another embodiment of the invention, the input shaft is connected to a ring gear and the countershaft to a fixed gear in a rotationally fixed manner. Because the fixed gear meshes with an inner circumference of the ring gear, a reversal of the direction of rotation is also enforced, so that the ring gear-fixed gear combination forms the reversing device.

[0023] According to the invention, the freewheel devices are arranged coaxially and / or concentrically to one another. In particular, they are positioned in a common axial section. The first freewheel device has a first outer freewheel ring and a first inner freewheel ring. The second freewheel device has a second outer freewheel ring and a second inner freewheel ring. In this embodiment, the first outer freewheel ring and the second inner freewheel ring are rotationally fixed to each other and are rotationally fixed to the output shaft.

[0024] The coaxial arrangement of the freewheel devices can be implemented, in particular, in conjunction with the countershaft, with the countershaft driving the second freewheel device via the second outer freewheel ring. The drive of the countershaft can be implemented – as previously described – for example, via the two-stage spur gear, the traction gear, or the ring gear-fixed gear combination. It is particularly preferred that the first inner freewheel ring is rotationally fixed to the input shaft, thus forming the first torque path.

[0025] In modified embodiments of the invention, the direction-reversing device can also be arranged between the countershaft and the second freewheel device and can also be implemented, for example, as a two-stage gear stage, traction gear or ring gear-fixed gear combination.

[0026] In another alternative, the freewheel mechanisms are arranged coaxially and / or concentrically to each other, with the second and first outer freewheel rings being non-rotatably connected and forming the output. In contrast, the first inner freewheel ring is non-rotatably connected to the input shaft to form the first torque path. Furthermore, the drive arrangement includes a planetary gear set, in which a ring gear is non-rotatably connected to the input shaft and meshes with at least one planet gear. The planet gear is fixed in the direction of rotation and / or rotatably mounted on a stationary planet carrier. The planet gear meshes with a sun gear, which is non-rotatably connected to the second inner freewheel ring. Very high reduction ratios can be achieved with this planetary gear set.

[0027] Another aspect of the invention relates to a vehicle, wherein the vehicle has the drive arrangement as previously described or according to one of the preceding claims. Furthermore, the vehicle has at least one electric motor as a drive motor. It is preferably provided that the vehicle is a single-track vehicle. Since switching between only two forward gears is possible by reversing the direction of rotation of the input shaft and / or the electric motor, the drive arrangement cannot provide a reverse gear. This is problematic for multi-track vehicles, as these must also be able to reverse. For single-track vehicles, such as bicycles, especially cargo bikes, the rider can manually change direction.

[0028] Further features, advantages, and effects of the invention will become apparent from the following description of preferred embodiments and the accompanying figures. These show: Fig. 1 A schematic representation of a vehicle with a drive arrangement as a first embodiment of the invention. Fig. 2 a schematic representation of a drive arrangement for the vehicle in the Fig. 1 as a second embodiment of the invention; Fig. 3 a schematic representation of a drive arrangement for the vehicle in the Fig. 1 as a third embodiment of the invention; Fig. 4 a schematic representation of a drive arrangement for the vehicle in the Fig. 1, which is not covered by the subject matter of the invention; Fig. 5 a schematic representation of a drive arrangement for the vehicle in the Fig. 1, which is not covered by the subject matter of the invention; Fig. 6 a schematic representation of a drive arrangement for the vehicle in the Fig. 1 as a sixth embodiment of the invention.

[0029] The Fig. Figure 1 shows a highly schematic block diagram of a vehicle 1 with a drive arrangement 2, an embodiment of the invention. The vehicle 1 is, for example, designed as a bicycle, in particular as a single-track bicycle.

[0030] It can, for example, be implemented as a cargo bike. For instance, in vehicle 1, designed as a bicycle, the rear wheel is implemented as a driven wheel.

[0031] The vehicle 1 has an electric motor 3, which provides a drive torque for the vehicle. This drive torque can be configured as a primary drive torque or as an auxiliary drive torque for the vehicle 1. The drive arrangement 2 has an input shaft 4, which is connected to the electric motor 3 via a transmission mechanism. In a simple design, the input shaft 4 can be rotationally fixed to a rotor shaft of the electric motor 3.

[0032] The drive arrangement 2 has an output shaft 5, wherein the output shaft 5 forms an output of the drive arrangement 2. The output shaft 5 is, for example, connected to the driven wheel of the vehicle 1 via a transmission mechanism.

[0033] In the drive arrangement 2, a first torque path 100 and a second torque path 200 are provided. A drive torque can be transmitted from the electric motor 3 via the input shaft 4 to the output shaft 5 via the torque paths 100 and 200. A first freewheel device 6 is arranged in the first torque path 100. A second freewheel device 7 is arranged in the second torque path 200. The freewheel devices 6 and 7 can assume a transmission state in which a drive torque applied to the input of the respective freewheel device 6 or 7 is transmitted to an output of the respective freewheel device 6 or 7. The freewheel devices 6 and 7 can also assume a freewheel state in which a drive torque is not transmitted from the input to the output and / or the input and output are decoupled.While the transmission state exists during a first direction of rotation of the input to the respective freewheeling device 6, 7, the freewheeling state exists during a second direction of rotation of the input, wherein the second direction of rotation is opposite to the first direction of rotation. Optionally, the freewheeling devices 6, 7 can assume an overtaking state, whereby the overtaking state exists when the input rotates in the first direction of rotation, but the output has a higher rotational speed than the input.

[0034] Furthermore, a direction-of-rotation reversing device 8 is arranged in the second torque path 200, wherein the direction-of-rotation reversing device 8 causes a reversal of the direction of rotation in the second torque path 200. In the illustrated embodiment, the direction-of-rotation reversing device 8 is arranged upstream of the second freewheeling device 7 and in the second torque path 200 in the direction of the torque flow. However, it is also possible for the direction-of-rotation reversing device 8 to be arranged in series downstream of the second freewheeling device 7. Alternatively, it is possible for the direction-of-rotation reversing device 8 to be arranged in the first torque path 100, either in series upstream or downstream of the first freewheeling device 6.

[0035] The function of drive arrangement 2 is as follows: If the drive motor 3 rotates in a first drive direction, or the input shaft 4 rotates in a first drive direction, the first drive torque travels over the first torque path 100. The first freewheel device 6 is designed to assume the transmission state during the first drive direction, so that the first drive torque is transmitted to the output shaft 5 in the first drive direction. If, however, the second torque path 200 is followed, the direction of rotation is first reversed by the direction-of-rotation reversing device 8 and then engages the second freewheel device 7. The second freewheel device 7 is designed to assume the freewheel state during the reversed first drive direction, so that the first drive torque is not transmitted to the output shaft 5.

[0036] If, on the other hand, the drive motor 3 and / or the input shaft 4 rotate in the second drive direction, which is opposite to the first drive direction, the first freewheel device 6 will switch to the freewheel state, so that the second drive torque cannot be transmitted to the output shaft 5 via the first torque path 100. However, the second drive direction is reversed on the second torque path 200 by the direction-reversing device 8 and then engages the second freewheel device 7. This device is designed to assume the transmission state when the second drive direction is reversed, so that the second drive torque is transmitted to the output shaft 5.

[0037] It should be emphasized that the first drive torque via the first torque path 100 leads to the same direction of rotation of the output shaft 5 as when the second drive torque is transmitted via the second torque path 200 to the output shaft 5.

[0038] Furthermore, it is planned that different gear ratios and / or different gears are implemented in the first torque path 100 and in the second torque path 200, so that the first drive torque is translated via the first torque path 100 with a different gear ratio than the second drive torque via the second torque path 200.

[0039] The drive arrangement thus forms a two-speed gearbox, which can be switched between the two gears by reversing the direction of rotation of the input shaft 4 and / or the electric motor 3. In an intermediate state (sailing mode), no drive torque is transmitted to the output shaft 5.

[0040] The following embodiments constructively implement the drive arrangement 2 in exemplary embodiments of the invention: The Fig. Figure 2 shows a schematic representation of an embodiment of the drive arrangement 2 with the electric motor 3. The first torque path 100 extends via the input shaft 4, which is arranged coaxially to a rotor shaft of the electric motor 3 and / or is rotationally fixed to it. The input shaft 4 is rotationally fixed to an input of the first freewheel device 6. More precisely, the first freewheel device 6 has a first inner freewheel ring 9 and a first outer freewheel ring 10, wherein the input shaft 4 is rotationally fixed to the first inner freewheel ring 9.

[0041] The drive arrangement 3 has a countershaft 11, the countershaft 11 being arranged parallel to, but radially offset from, the input shaft 4 and / or the output shaft 5. The input shaft 4 is connected to the countershaft 11 via a two-stage spur gear stage 12, the two-stage spur gear stage 12 forming the reversing device 8.

[0042] The two-stage spur gear stage 12 comprises a fixed gear 13, which is non-rotatably connected to the input shaft 4. The two-stage spur gear stage 12 also comprises an intermediate gear 14, which meshes with the first fixed gear 13. Furthermore, the two-stage spur gear stage 12 includes a second fixed gear 15, which is non-rotatably mounted on the countershaft 11 and meshes with the intermediate gear 14. For example, the gears 13, 14, and 15 are designed as spur gears. A fixed output gear 16 is non-rotatably mounted on the countershaft 11 and meshes with an input of the second freewheel assembly 7. More precisely, the second freewheel device 7 has a second inner freewheel ring 17 and a second outer freewheel ring 18, with the output fixed gear 16 meshing with the second outer freewheel ring 18. For example, the second outer freewheel ring 18 has a circumferential toothing.

[0043] The first outer freewheel ring 10 and the second inner freewheel ring 17 are rotationally fixed to each other and together form the output shaft 5, which drives a driven wheel 19. When the input shaft 4 rotates in the first drive direction, the first drive torque is introduced via the first torque path 100 into the first freewheel device 6, which is in the transmission state and transmits the first drive torque to the output shaft 5. When the input shaft 4 rotates in the second drive direction, the second drive torque is introduced via the two-stage spur gear stage 12, which acts as a direction-reversing device 8, via the auxiliary shaft 11 into the second freewheel device 7, which is in the transmission state and transmits the second drive torque to the output shaft 5. In particular, the first torque path 100 provides a first gear and the second torque path 201 provides a second gear.

[0044] Fig. Figure 3 shows a similar representation to the Fig. 2 An alternative embodiment of the invention, wherein a traction gear 20 is used instead of the two-stage spur gear stage 12. The traction gear 20 has the first fixed gear 13, which is rotationally fixed to the input shaft 4, and the second fixed gear 15, which is rotationally fixed to the auxiliary shaft 11, wherein the two fixed gears 13, 15 are connected via a traction element 21, such as an endless belt, a chain, or the like. In this embodiment, the traction gear 20 acts in the Fig. 2 as a direction-of-rotation reversing device 8, so that with regard to the functions of the drive arrangement 2, the previous description of the Fig. 2 is referred to.

[0045] It should be emphasized that in both embodiments, in the Fig. 2 and Fig. 3 the freewheeling device 6, 7 are arranged coaxially and / or concentrically to each other and / or to the input shaft 4 / or to the input shaft 5.

[0046] The Fig. Figure 4 shows that the electric motor 3 drives the input shaft 4, which is connected to the first inner freewheel ring 9 of the first freewheel device 6 to represent the first torque path 100. The first outer freewheel ring 10 is rotationally fixed to the output shaft 5.

[0047] However, the second torque path 200 is designed differently: The drive arrangement 2 has a ring gear-fixed gear combination 22, wherein a ring gear 23 is rotationally fixed to the input shaft 4 and meshes with a fixed gear 24 on the countershaft 11. Thus, the ring gear-fixed gear combination 22 forms the direction-reversing device 8.

[0048] The second freewheel assembly 7 is arranged coaxially to the auxiliary shaft 2, with the auxiliary shaft 11 forming an input to the second freewheel assembly 7. The output of the second freewheel assembly 7 is operatively connected to the first freewheel assembly 6. More precisely, the second freewheel inner ring 17 is rotationally fixed to the auxiliary shaft 11 and forms the input. The second freewheel outer ring 18 has a circumferential face toothing which meshes with a circumferential face toothing of the first freewheel outer ring 10 to close the second torque path 200 in the direction of the output shaft 5. Regarding the function, reference is made to the preceding description, wherein the freewheel assemblies 6, 7 assume the freewheeling states or transmission states as described. This arrangement is not encompassed by the subject matter of the invention.

[0049] The Fig. Figure 5 shows an arrangement, also not covered by the subject matter of the invention, in modification to Fig. 4, wherein the two-stage spur gear stage 12 is used as the direction-reversing device 8 instead of the ring gear-fixed gear combination 22. For its function, reference is made to the preceding description. Instead of the ring gear-fixed gear combination 22, the two-stage spur gear stage 12 can be used in the exemplary embodiments of the Fig. 2, Fig. 3, Fig. 4 to Fig. 5 the traction gear 20 is also used.

[0050] The Fig.Figure 6 shows a further embodiment of the invention, wherein the freewheel devices 6, 7 are again arranged coaxially to each other. The first torque path 100 is again formed starting from the electric motor 3 via the input shaft 4 to the first freewheel device 6, more precisely to the first freewheel inner ring 9, and via the first freewheel device 6 in the transmission state to the output shaft 5 as in the preceding figures.

[0051] The second torque path 200 is realized via a planetary gear stage 25, wherein a ring gear 26 is non-rotatably connected to the input shaft 4 and engages with a planet gear 27. The planet gear 27 is rotatably mounted on a stationary planet carrier 28. The planetary gear stage 25 forms the direction-reversing device 8.

[0052] The second freewheel assembly 7 is connected to the planet gear 27 via a sun gear 29, with the sun gear 29 meshing with the planet gear 27. The sun gear 29 is non-rotatably connected to the second freewheel inner ring 17. In contrast, the second freewheel outer ring 18 and the first freewheel outer ring 10 are non-rotatably connected to each other and to the output shaft 5. The function of the drive arrangement 2 is as described above, such that the torque path 100 is closed in the first drive direction and the torque path 200 is closed in the second drive direction. Reference symbol list 1 vehicle 2 Drive arrangement 3 Electric motor 4 Input shaft 5 Output shaft 6 first free-running device 7 second free-running device 8 Reversing device 9 first freewheel inner ring 10 first freewheel outer ring 11 Secondary shaft 12 two-stage spur gear stage 13 first fixed wheel 14 Intermediate wheel 15 second fixed wheel 16 Output fixed gear 17 second freewheel inner ring 18 second freewheel outer ring 19 driven wheel 20 traction gearboxes 21 traction elements 22 Ring gear-fixed gear combination 23 Ring gear 24" fixed wheel 25 planetary gear stage 26 Ring gear 27 planetary gear 28 planetary carriers 29 Sun wheel 100 first moment path 200 second moment path

Claims

[1] Drive arrangement (2) for a vehicle (1) with an input shaft (4), wherein the input shaft (4) can be coupled to an electric motor (3), with an output shaft (5), wherein the output shaft (5) forms an output of the drive arrangement (2), wherein the drive arrangement (2) comprises a first and a second freewheel device (6,7), furthermore comprehensive a first torque path (100) for transmitting a first drive torque with a first drive direction of rotation from the input shaft (4) to the output shaft (5), and by a second torque path (200) for transmitting a second drive torque with a second drive direction of rotation from the input shaft (4) to the output shaft (5), wherein the second drive direction of rotation is opposite to the first drive direction of rotation, wherein the first and the second torque paths (100, 200) implement different gear ratios and / or different gears, wherein the first freewheel device (6) is arranged in the first torque path (100) such that it is in a transmission state during the first drive torque with the first drive direction of rotation and in a freewheel state during the second drive torque with the second drive direction of rotation and wherein the second freewheel device (7) is arranged in the second torque path (200) such that it is in a transmission state during the second drive torque with the second drive direction of rotation and in a freewheel state during the first drive torque with the first drive direction of rotation, characterized by, that the freewheel devices (6,7) are arranged coaxially and / or concentrically to each other and that the first freewheel device (6) has a first freewheel outer ring (10) and a first freewheel inner ring (9) and that the second freewheel device (7) has a second freewheel outer ring (18) and a second freewheel inner ring (17), wherein the first freewheel outer ring (10) and the second freewheel outer ring (18) are coupled in a rotationally fixed manner and are connected in a rotationally fixed manner to the output shaft (5). [2] Drive arrangement (2) according to claim 1, characterized by , that in one of the torque paths (100, 200) a rotation direction reversal device is arranged, so that the output shaft (5) has the same direction of rotation in both torque paths (100, 200). [3] Drive arrangement (2) according to one of the preceding claims, characterized by , that this has a secondary shaft (11), wherein the second torque path (200) runs via the secondary shaft (11). [4] Drive arrangement (2) according to claim 3, characterized by , that the input shaft (4) is connected to the auxiliary shaft (11) via a two-stage spur gear stage (12) to form the reversing device (8). [5] Drive arrangement (2) according to claim 3, characterized by , that the input shaft (4) is connected to the auxiliary shaft (11) via a traction gear (20) to form the reversing device (8). [6] Drive arrangement (2) according to claim 3, characterized by , that the input shaft (4) is connected to a ring gear (23) and the countershaft (11) is connected to a fixed gear (24) in a rotationally fixed manner, the ring gear (23) meshing with the fixed gear (24) to form the reversing device (8). [7] Vehicle (1), characterized by a drive arrangement (2) according to one of the preceding claims, characterized by , that the vehicle (1) is designed as a single-track vehicle.

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