Drive device for a vehicle

Abstract

The present invention relates to a drive device (1) for a vehicle, comprising a drive (2) for mechanically operative connection to an engine device and an output (3) for mechanically operative connection to a propulsion element (7). Furthermore, the drive device (1) comprises a transmission assembly (4) having a variator (36) and configured coaxially with a central shaft (13) for providing a plurality of driving ranges. The drive device (1) also comprises a reversing assembly (5) having a forward shifting element (KV) for providing the plurality of driving ranges in the forward direction and a reverse shifting element (KR) for providing the plurality of driving ranges in the reverse direction. Torque can be transmitted from the drive (2) to the output (3) via the transmission assembly (4) and the reversing assembly (5).The forward shifting element (KV) and the reverse shifting element (KR) are arranged axially parallel to one another and axially parallel to the central shaft (13) of the transmission assembly (4).

Description

Technical FieldThe present invention relates to a driving device for a vehicle. Moreover, the present invention relates to a vehicle having such a driving device.Prior ArtIn the field of working machines and commercial vehicles, continuously variable power-split transmissions are used. Transmissions of this type can have a plurality of driving ranges which can be shifted by means of a planetary roller having a plurality of shift elements. The transmissions can furthermore have a variator, by means of which the transmission ratio in the respective driving ranges can be varied continuously. In this case, it is known, for example, from DE 10 2006 057 836 to provide a large transmission ratio over a plurality of stages from a transmission input to the variator of the transmission, that is to say to provide a large so-called overdrive. Such transmissions also often include a reversing assembly for providing the travel ranges in both forward and reverse directions. The reversing assembly can have a forward and a reverse switching element, which can be provided separately from one another, as disclosed, for example, in DE 10 2017 200 240. Furthermore, embodiments are known from DE 10 001 915 and DE 19 522 833, in which one of the switching elements of the reversing assembly is arranged coaxially with the planetary roller and the other switching element of the reversing assembly is arranged axially parallel with the planetary roller. The disadvantage of the gear units known from the prior art is their relatively long axial overall length.SUMMARY OF THE INVENTIONIt was therefore an object of the present invention to provide a drive device for a vehicle having a plurality of driving ranges, a variator and a reversing assembly, which drive device has a particularly compact configuration. This object is achieved by the drive device for a vehicle according to claim 1. The drive device has a drive for mechanically operatively connecting to a motor device. The motor device can be one or more combustion and alternatively or additionally electric motors. The drive device further has an output for mechanically operatively connecting to a propulsion element. The propulsion element can be one or more wheels, chains or other propulsion elements of the vehicle. The output of the drive device can be mechanically operatively connected to the propulsion element via one or more differentials, for example via a transverse differential. The drive and the output of the drive device can be provided spaced apart from one another in an axially parallel manner. The vehicle can be a working machine, for example a construction machine or agricultural machine, such as a tractor. Furthermore, the vehicle can be a commercial vehicle, for example a unimog.In addition, the drive device comprises a transmission assembly for providing a plurality of driving ranges. Furthermore, the transmission assembly has a variator for continuously adjusting a transmission ratio. The transmission assembly may provide four driving ranges, for example. In a driving range, a fixed mechanical transmission ratio can be provided between the input and the output of the transmission, wherein the transmission ratio can be varied continuously within the respective driving range by adjusting the variator. The variator can be a hydraulic variator, for example a variator designed as a hydrostatic unit, which can have a plurality of hydraulic machines. Alternatively or additionally, it can be an electrically designed variator, which can have a plurality of electric machines. The transmission assembly is here formed coaxially with a central shaft. The transmission assembly may include one or more planetary gear sets and one or more shift elements, wherein some or all of these components may be coaxial with one another and coaxial with the central shaft. The transmission assembly can thus be designed, for example, as a so-called planetary roller.In addition, the drive device has a reversing assembly with a forward shifting element for providing the plurality of travel ranges of the transmission assembly in the forward direction and a reverse shifting element for providing the plurality of travel ranges of the transmission assembly in the reverse direction. The reversing assembly can have any configuration as long as it can provide the claimed functionality. For example, the reversing assembly may include one or more spur gear stages and, alternatively or additionally, one or more planetary gear sets for providing the drive ranges of the transmission assembly in both forward and reverse directions. The forward shifting element and the reverse shifting element can be a frictional or positive shifting element. In one embodiment, the two shift elements are frictional shift elements, for example multiplate clutches. The forward switching element and the reverse switching element may be provided separately and locally separated from each other.The drive device is designed in such a way that a torque can be transmitted from the drive via the transmission assembly and the reversing assembly to the output. For this purpose, it may be necessary for one or more switching elements or switching devices to have to be actuated. The forward shifting element and the reverse shifting element are spaced apart from one another axially parallel within the scope of the present invention and are therefore provided just not coaxially with respect to one another. Furthermore, within the scope of the present invention, both the forward and the reverse shifting elements are arranged axially parallel spaced apart from the central shaft of the transmission assembly. Therefore, neither the forward nor the reverse shifting element is provided coaxially with the transmission assembly, more precisely with the central shaft of the transmission assembly.The drive device of the present invention can be designed with a particularly compact configuration, especially a particularly short axial structural length. This is made possible in that neither the forward nor the reverse shifting element of the reversing assembly is arranged with the transmission assembly one behind the other in the direction of the central shaft. Rather, by the axially parallel arrangement of forward and reverse shifting elements with respect to the central shaft of the transmission assembly, a serial arrangement of the transmission assembly and the shifting elements of the reversing assembly in the radial direction of the transmission assembly can be realized. In this case, by providing forward and reverse shift elements separately, a configuration can also be provided in which they can be arranged in a space-optimized manner in the circumferential direction of the transmission assembly. Thus, as a whole, a drive device can be provided which is particularly compact, both in the axial and in the radial direction, and thus enables simple integration into different vehicles, for example in tractors. At the same time, such a configuration enables a high overdrive functionality, i.e. a high transmission ratio from the motor device to the variator.If two elements are mechanically operatively connected, they are directly or indirectly coupled to one another in such a way that a movement of one element brings about a reaction of the other element. For example, a mechanical operative connection can be provided by a form-fitting or frictional connection. The mechanical operative connection can correspond to meshing of corresponding toothings of the two elements. Further elements, for example one or more spur gear stages, can be provided between the elements. By a permanently rotationally fixed connection of two elements, however, is meant a connection in which the two elements are rigidly coupled to one another for all intended states. The elements can be present here as individual components connected to one another in a rotationally fixed manner or else in one piece. By way of a shifting element, for example a clutch or brake, on the other hand, a rotationally fixed connection between two elements can be selectively established or released.In one embodiment, the drive is arranged at a distance from the central shaft of the transmission assembly in an axially parallel manner. Accordingly, within the scope of this embodiment, the transmission assembly and the drive are not provided coaxial to one another. Instead, the drive and the transmission assembly can be mechanically operatively connected to one another via a transmission stage, for example a spur gear stage, which can be configured in one stage. Thus, the rotational speed in the transmission assembly can be increased, which in turn leads to a reduction of the torques in the transmission assembly. The latter increases the output torques and thus the power density. One of the forward and reverse switching elements may be disposed coaxially with the drive. Alternatively or additionally, the output drive can also be arranged spaced apart axially parallel to the central shaft of the transmission assembly. The transmission assembly can be provided, for example, between the drive and the output. One of the forward and reverse shift elements may be disposed coaxially with the output. For example, within the scope of one embodiment, the reverse shifting element is provided coaxially to the drive and the forward shifting element is provided coaxially to the output. A reverse configuration, in which the forward shifting element is provided coaxially with the drive and the reverse shifting element is provided coaxially with the drive, is also possible in an alternative embodiment. The coaxial arrangement of a shifting element of the reversing assembly and the drive and alternatively or additionally the output allows a drive device with particularly high compactness, especially also in the radial direction of the gear assembly.In one embodiment, the transmission assembly, the forward shifting element and the reverse shifting element are arranged in the direction of the central shaft of the transmission assembly in such a way that they at least partially overlap. For example, at least one of the shift elements of the reversing assembly is arranged such that it completely overlaps the transmission assembly in the direction of the central shaft of the transmission assembly, i.e. does not protrude beyond the transmission assembly in the direction of the central shaft. Thus, a drive device can be provided which is of particularly compact construction in the axial direction. As explained above, this enables a particularly good integration of the drive device into different vehicles, for example into a tractor. In one embodiment, both the forward and the reverse shifting element of the reversing assembly are arranged such that they completely overlap with the transmission assembly in the direction of the central shaft, i.e. do not protrude beyond the transmission assembly in the direction of the central shaft.In one embodiment, the forward shifting element and the reverse shifting element of the reversing assembly are arranged at the same height in the direction of the central shaft of the transmission assembly. For example, the two shift elements of the reversing assembly are provided at the drive-side end of the transmission assembly, as viewed in the direction of the central shaft of the transmission assembly, as viewed from the drive. The provision of both shift elements of the reversing assembly at the same height in the direction of the central shaft allows a drive device with a low complexity, since by the proximity of the shift elements, for example, a simple common connection of both to the transmission assembly is made possible. At the same time, a drive device can thus be provided which has a relatively regular outer contour and can therefore be easily integrated into different vehicles. In an alternative embodiment, the forward and reverse switching elements of the reversing assembly are arranged at different heights in the direction of the central shaft.In one embodiment, the transmission assembly has at least one planetary gear set, for example a plurality of planetary gear sets, and at least one shift element, for example a plurality of shift elements, for shifting a driving range. In one embodiment, the transmission assembly is configured to provide four different ranges of travel with four planetary gear sets and five shift elements. The planetary gear set and the shift element can be configured coaxially with respect to one another. Viewed from the drive of the drive device, the shift element of the transmission assembly is arranged along the central shaft in front of the planetary gear set of the transmission assembly. In one embodiment, the transmission assembly has a plurality of planetary gear sets, for example three planetary gear sets, and a plurality of shift elements, for example four shift elements, wherein the four shift elements are arranged before the three planetary gear sets as viewed in the direction of the central shaft from the drive.The drive device can furthermore have a housing which, within the scope of an embodiment, can be designed as a load-bearing housing for dissipating forces of the drive device. For this purpose, the housing can have a wall thickness and mechanical strength, which enables it to absorb and dissipate forces of the drive device that occur independently during normal operation. Within the scope of an embodiment, it can thus be made possible for forces of the drive device to be dissipated via the housing. As a result, in this case, no supporting frame for absorbing forces of the drive device has to be provided in the vehicle, in which the drive device is to be integrated. Consequently, within the scope of this embodiment, a drive device can be provided which can be easily integrated into different vehicles in an autonomous manner. The housing can have one or more sections which can be detachably connected to one another.Within the scope of one embodiment, the drive device has a shifting device for mechanically decoupling the reverse shifting element from the output. The switching device can be, for example, a synchronization. By means of the shifting device, it can be ensured that no relative rotations and associated drag losses occur in the reverse shifting element during non-actuation. This can be advantageous above all when the reverse shifting element is a frictional shifting element, for example a multiplate clutch.The transmission assembly may include a first planetary gear set having a first sun gear, a first planet carrier having a planet gear rotatably supported thereon, and a first ring gear. The transmission assembly may further include a second planetary gear set having a second sun gear, a second planet carrier having a planet gear rotatably supported thereon, and a second ring gear. Furthermore, the transmission assembly can have a third planetary gear set with a third sun gear, a third planetary carrier with a planetary gear rotatably mounted thereon and a third ring gear. In addition, the transmission assembly may include a fourth planetary gear set having a fourth sun gear, a fourth planet carrier having a planet gear rotatably supported thereon, and a fourth ring gear. One or more, for example all, of the planetary gear sets of the transmission assembly can be designed as a minus planetary gear set. In the minus planetary gear set, the planet gears of the respective planetary gear set can mesh with both the sun gear and the ring gear of the planetary gear set. The different planetary gear sets may have the same outer diameter so as to provide a transmission assembly with particularly high compactness and a regular outer contour.In addition, the transmission assembly may include a first shift element, a second shift element, a third shift element, a fourth shift element, and a fifth shift element. One, several or all shifting elements can be a positively locking or frictional shifting element. In one embodiment, all shift elements are frictional shift elements. The first to fourth shift elements can be, for example, a multiplate clutch. The fifth shifting element can be a multi-disk brake. Other configurations are also conceivable here. Furthermore, within the scope of an embodiment, the transmission assembly comprises an output shaft that is mechanically operatively connected to the reversing assembly. The output shaft can be a hollow shaft which can be arranged coaxially with the central shaft of the transmission assembly. The output shaft may be provided at the driving side end of the transmission assembly.The central shaft can be mechanically operatively connected to the drive and permanently connected to the second planetary carrier and to the first ring gear in a rotationally fixed manner. The first sun wheel can be mechanically operatively connected to the central shaft via the variator, for example via one or more transmission stages, which can be designed as spur gear stages. The variator can be connected to the transmission assembly via a multistage spur gear stage. The first planetary carrier can be permanently connected to the second ring gear and the third planetary carrier in a rotationally fixed manner. Furthermore, the second sun gear can be permanently connected to the third sun gear in a rotationally fixed manner. The third ring gear can be connected to the fourth sun gear in a rotationally fixed manner via the first shifting element. Furthermore, the third sun wheel can be connected to the fourth sun wheel in a rotationally fixed manner via the second shifting element. The third planetary carrier can be connected to the fourth planetary carrier in a rotationally fixed manner via the third shifting element. The fourth planet carrier can be connected to the fourth sun gear in a rotationally fixed manner via the fourth shift element in order to block the fourth planetary gear set. Furthermore, the fourth ring gear can be fixed in a rotationally fixed manner to a transmission housing via the fifth shift element. The transmission housing can be the transmission housing described above. In addition, the fourth planet carrier can be permanently connected to the output shaft in a rotationally fixed manner.By means of a transmission assembly configured in this way, four driving ranges can be provided on the output shaft by actuating the different five shift elements. In addition, the four travel ranges can be provided at the output of the drive device both in the forward and in the rearward direction via the reversing assembly. Viewed from the drive, the fifth shift element can be arranged upstream of the fourth planetary gear set in the direction of the central shaft. The fourth planetary gear set may in turn be arranged upstream of the first, second, third and fourth shift elements, which may be followed by the third, second and first planetary gear set. By such an arrangement, a constant direction of rotation can be realized with only one tooth engagement, for example if the transmission assembly is provided at a distance from the drive parallel to the axis.Moreover, the present invention relates to a vehicle having a drive device according to one of the embodiments described above. The vehicle can be a working machine, for example a agricultural or construction machine. In one embodiment, the work machine is a tractor or a unimog. With regard to the configuration and advantages of the individual features, reference is made to the above explanations in connection with the drive device.Brief Description of the FiguresFIG. 1 shows a driving device for a vehicle according to an embodiment of the present invention. FIG. 2 shows a circuit diagram of the drive device from FIG. 1.Detailed Description of EmbodimentsFIG. 1 shows a drive device 1 for a vehicle according to an embodiment of the present invention. The vehicle in the present embodiment is an agricultural machine in the form of a tractor. The drive device 1 has a drive 2 and an output 3. Furthermore, the drive device 1 has a transmission assembly 4 for providing a plurality of travel ranges and a reversing assembly 5 for providing the travel ranges both in the forward and in the reverse direction. In the present embodiment, the drive 2 is mechanically operatively connected to a motor device, not shown, in the form of an internal combustion engine for driving the drive device 1. The output 3 is mechanically operatively connected via a transverse differential 6 to rear wheels 7 of the vehicle, which rear wheels are designed as propulsion elements. In the present embodiment, in addition to the transverse differential 6, a transmission stage 8 designed as a planetary gear and a brake 9 are also provided for each rear wheel 7 in the mechanical operative connection between the output 3 and the rear wheels 7.In addition, the drive device 1 comprises an all-wheel shifting element 10, which is designed as a multiplate clutch in the present case. By means of the all-wheel shifting element 10, front wheels, not shown, can be mechanically operatively connected to the output 3 of the drive device 1 via a longitudinal differential, not shown. The all-wheel switching element 10 is arranged on the drive side of the drive device 1. The drive side is provided opposite to a driven side of the drive device 1. A gear pump 11 for supplying the drive device 1 with lubricating oil is mechanically operatively connected to the drive 2. Furthermore, an auxiliary unit, not shown, can be operatively mechanically connected to the drive 2 via an auxiliary shift element 12, which is designed in the present case as a multiplate clutch. For example, the auxiliary unit can be mechanically coupled to a power take-off shaft, which in turn can be mechanically operatively connected to the drive 2 via the auxiliary shifting element 12. The drive 2 and the output 3 are in the present case each designed as a drive shaft 2 or output shaft 3 and extend substantially from the drive side through the entire drive device 1 to the output side of the drive device 1.The transmission assembly 4 is formed coaxially with a central shaft 13. The central shaft 13 of the transmission assembly 4 is provided parallel to the drive 2 and to the output 3, but spaced apart from both. In the present embodiment, the central shaft 13 of the transmission assembly 4 is arranged between the input 2 and the output 3, as can be seen from FIG. 1. In this case, the central shaft 13 in the present embodiment is mechanically operatively connected to the drive 2 via a single-stage spur gear stage 14, with the result that a torque which is present at the drive 2 can be transmitted via the spur gear stage 14 to the central shaft 13 of the transmission assembly 4. The transmission assembly 4 furthermore has an output shaft 15 which is arranged as a hollow shaft coaxially with the central shaft 13. The output shaft 15 can be operatively connected mechanically to the output 3 via the reversing assembly 5, as will be described below.The transmission assembly 4 further comprises a first planetary gear set 16 with a first sun gear 17, a first planetary carrier 18 with planetary gears 19 rotatably supported thereon and a first ring gear 20. Likewise, the transmission assembly 4 comprises a second planetary gear set 21 with a second sun gear 22, a second planetary carrier 23 with planetary gears 24 rotatably supported thereon and a second ring gear 25. Furthermore, the transmission assembly 4 comprises a third planetary gear set 26 with a third sun gear 27, a third planetary carrier 28 with third planetary gears 29 rotatably supported thereon and a third ring gear 30.Furthermore, the transmission assembly 4 has a first shift element K 1, a second shift element K 2, a third shift element K 3, a fourth shift element K 4 and a fifth shift element BG. The first, second, third and fourth shifting elements K 1, K 2, K 3 and K 4 are each designed as a frictional shifting element, in the present case as a multiplate clutch. The fifth shifting element BG is designed in the present case as a friction brake, in the present case as a multi-disk brake. In the direction of the central shaft 13 of the transmission assembly 4, the first shifting element K 1 and the second shifting element K 2 are arranged at the same overall height. Furthermore, the third shifting element K 3 and the fourth shifting element K 4 are provided in the direction of the central shaft 13 at the same overall height, but at a different overall height than the first shifting element K 1 and the second shifting element K 2. In the present embodiment, the fifth shift element BG is arranged upstream of the fourth planetary gear set 31 as viewed from the drive 2 in the direction of the central shaft 13 of the transmission assembly 4. The fourth planetary gear set 31 is again arranged upstream of the third and fourth shifting elements K 3 and K 4. The third and fourth switching elements K 3 and K 4 are in turn provided before the first and second switching elements K 1 and K 2. The first and second shift elements K 1 and K 2 are now followed, as viewed from the drive 2 in the direction of this central shaft 13, by the third planetary gear set 26 in front of the second planetary gear set 21.The central shaft 13 is permanently connected in a rotationally fixed manner to the second planetary carrier 23 of the second planetary gear set 21 and to the first ring gear 20 of the first planetary gear set 16. Furthermore, the first planetary carrier 18 of the first planetary gear set 16 is permanently connected in a rotationally fixed manner to the second ring gear 25 of the second planetary gear set 21. The first sun gear 17 of the first planetary gear set 16 is mechanically operatively connected to the central shaft 13 via a variator 36. The variator 36 has a constant unit 37, which is operatively connected, in the present case hydraulically operatively connected, to an adjusting unit 38. The constant unit 37 and the adjusting unit 38 of the variator 36 are in the present case each designed as a hydraulic machine and the variator 36 is designed integrally as a hydraulic variator. The constant unit 37 is mechanically operatively connected to the first sun gear 17 of the first planetary gear set 16 via a spur gear transmission 39. The spur gear transmission 39 is provided along the central shaft 13, viewed from the drive 2, behind the first planetary gear set 16 of the transmission assembly 4. Furthermore, the adjustment unit 38 is mechanically operatively connected to the central shaft 13 of the transmission assembly 4 via a spur gear transmission 40. The spur gear 40 for connecting the adjusting unit 38 is arranged in front of the fifth shifting element BG when viewed in the direction of the central shaft 13 from the drive 2.The second sun gear 22 of the second planetary gear set 21 is permanently connected in a rotationally fixed manner to the third sun gear 27 of the third planetary gear set 26. Furthermore, the second ring gear 25 of the second planetary gear set 21 is permanently connected in a rotationally fixed manner to the third planetary carrier 28 of the third planetary gear set 26. The fourth planet carrier 33 of the fourth planetary gear set 31 is furthermore permanently connected to the output shaft 15 in a rotationally fixed manner. The fourth ring gear 35 of the fourth planetary gear set 31 can be fixed in a rotationally fixed manner on a stationary component 41 by actuating the fifth shift element BG, i.e. the multi-disk brake. The stationary member 41 in the present embodiment is the transmission case described below.By actuating the first shift element K 1, the third ring gear 30 of the third planetary gear set 26 is connectable in a rotationally fixed manner to the fourth sun gear 32 of the fourth planetary gear set 31. By actuating the second shift element K 2, the third sun gear 27 of the third planetary gear set 26 can be connected in a rotationally fixed manner to the fourth sun gear 32 of the fourth planetary gear set 31. By actuating the third shift element K 3, the third planetary carrier 28 of the third planetary gear set 26 can be connected in a rotationally fixed manner to the fourth planetary carrier 33 of the fourth planetary gear set 31. By actuating the fourth shift element K 4, the fourth planet carrier 33 of the fourth planetary gear set 31 can be connected to the fourth sun gear 32 of the fourth planetary gear set 31 in a rotationally fixed manner in order to block the fourth planetary gear set 31.In addition, the drive device 1 comprises the reversing assembly 5, via which the output shaft 15 of the transmission assembly 4 can be operatively connected mechanically to the output 3. The reversing assembly 5 comprises a forward shifting element KV, which is arranged here coaxially to the output 3. In addition, the reversing assembly 5 comprises a reverse switching element KR, which is arranged here coaxially to the drive 2. The forward shifting element KV and the reverse shifting element KR are accordingly provided spaced apart axially parallel to one another. Furthermore, the forward shifting element KV and the reverse shifting element KR are each arranged at an axial distance from the central shaft 13 of the transmission assembly 4. In the direction of the central shaft 13, the forward shifting element KV and the reverse shifting element KR are provided at the same height and radially outside the fifth shifting element BG of the transmission assembly 4, respectively. Both the forward shifting element KV and the reverse shifting element KR are designed as frictional shifting elements, in the present embodiment as multiplate clutches.The forward switching element KV and the reverse switching element KR each have an input plate pack and an output plate pack. In the present embodiment, the input disk set of the forward shifting element KV is mechanically operatively connected to the output shaft 15 of the transmission assembly 4 via a single-stage spur gear stage 42. The output disk pack of the forward shifting element KV is permanently connected in a rotationally fixed manner to the output 3. By actuating the forward shifting element KV, the output shaft 15 can accordingly be mechanically operatively connected to the output 3 via the single-stage spur gear stage 42. The input disk set of the reverse shifting element KR is mechanically operatively connected to the output shaft 15 of the transmission assembly 4 via a spur gear stage 43. The output disk set of the reverse shifting element KR is mechanically operatively connected via a further spur gear stage 44 to a hollow shaft 45 which is arranged coaxially with the output 3. As explained above, the reverse shifting element KR, on the other hand, is arranged coaxially to the drive 2. Viewed in the direction of the central shaft 13 from the drive 2, the hollow shaft 45 is arranged behind the forward shifting element KV. Furthermore, the hollow shaft 45 is arranged in the direction of the central shaft 13 substantially at the same height as the fourth planetary gear set 31 of the transmission assembly 4. By means of a shifting device 46, which is designed as a synchronization in the present case, the hollow shaft 45 can be connected to the output 3 in a rotationally fixed manner. Furthermore, the output drive 3 can be mechanically decoupled from the reverse shifting element KR via the synchronization 46, in order to be able to mechanically decouple the reverse shifting element KR from the output drive 3 in order to reduce drag losses.By actuating the various shift elements K 1, K 2, K 3, K 4 and BG of the transmission assembly 4, different driving ranges can be provided by the transmission assembly 4. By actuating the forward shifting element KV, the different driving ranges of the transmission assembly 4 can be provided in the forward direction. By actuating the reverse shifting element KR, the different driving ranges can furthermore be provided in the reverse direction when the synchronization 46 is closed. More specifically, the driving ranges shown in FIG. 2 can be switched by the driving device 1. The driving ranges I, II, III and IV are driving ranges for the forward direction. The travel ranges V, VI, VII, and VIII are travel ranges for the rearward direction. The driving range I and the driving range V have the same transmission ratio. Furthermore, the driving range II and the driving range VI have the same transmission ratio. The driving range III and the driving range VII also have the same transmission ratio. The driving range IV and the driving range VIII also have the same transmission ratio.For shifting the driving range I, the first shifting element K 1, the fifth shifting element BG and the forward shifting element KV are actuated. For shifting the driving range II, the second shifting element K2 and the fifth shifting element BG as well as the forward shifting element KV are actuated. For shifting the driving range III, the second shifting element K 2, the third shifting element K 3 and the forward shifting element KV are actuated. For shifting the fourth driving range IV, the second shifting element K 2, the fourth shifting element K 4 and the forward shifting element KV are actuated. For shifting the driving range V, the first shifting element K 1, the fifth shifting element BG and the reverse shifting element KR are actuated. For shifting the sixth driving range VI, the second shifting element K 2, the fifth shifting element BG and the reverse shifting element KR are actuated. For shifting the seventh driving range VII, the second shifting element K 2, the third shifting element K 3 and the reverse shifting element KR are actuated. For shifting the eighth driving range VIII, the second shifting element K 2, the fourth shifting element K 4 and the reverse shifting element KR are actuated. Furthermore, in all reverse ranges V to VIII, the synchronization 46 is closed in order to establish a rotationally fixed connection between the hollow shaft 45 and the output 3. When shifting the forward driving ranges I to IV, on the other hand, the synchronization 46 is opened to release the rotationally fixed connection between the hollow shaft 45 and the output drive 3, whereby drag losses in the reverse shifting element KR can be significantly reduced or even prevented.In addition, the drive device 1 comprises a housing 41, which is shown only in some sections and in which the gear assembly 4, the reversing assembly 5 and the spur gear stages 14, 39, 40, 42, 43 and 44 are accommodated. The drive shaft 2 and the output shaft 3 are also accommodated in the housing, a portion of which projects from the housing for the connection of the above-described components. The variator 36 is mounted on an outer side of the housing. In this case, the housing in the present embodiment is designed as a load-bearing housing and is capable of absorbing and dissipating the forces occurring in the drive device 1. The vehicle, in the present case the tractor, accordingly does not have an additional supporting frame in the present embodiment for receiving the drive device 1. Instead, the drive device 1 can be integrated into the tractor via the housing without the need for mounting on a supporting frame of the tractor.In the drive device 1, the forward KV and the reverse shifting element are thus provided spaced apart axially parallel to the transmission assembly 4, which leads to a particularly compact installation space. At the same time, this embodiment enables a high overdrive functionality, i.e. a particularly high transmission ratio over several stages from the drive 2 to the variator 36. This in turn enables higher output torques and accordingly an increased power density.Reference numerals denote reference numerals1 Drive device 2 Drive 3 Output 4 Transmission assembly 5 Reversing assembly 6 Transverse differential 7 Rear wheels 8 Planetary transmission 9 Brake 10 All-wheel shifting element 11 Transmission pump 12 Auxiliary shifting element 13 Central shaft 14, 39, 40, 42, 43, 44 Spur gear stage 15 Output shaft 16, 21, 26, 31 Planetary gear set 17, 22, 27, 32 Sun gear 18, 23, 28, 33 Planetary carrier 19, 24, 29, 34 Planetary gear 20, 25, 30, 35 Ring gear 36 Variator 37 Constant unit 38 Adjusting unit 41 Housing 45 Hollow shaft 46 Synchronization K 1, K 2, K 3, K 4 Shifting element BG Brake KV Forward shifting element KR Reverse shifting element I, II, III, IV, V, VI, VII, VIII Travel rangeReferences included in the specificationThis list of documents cited by the applicant has been produced in an automated manner and is only included for the better information of the reader. The list is not part of the German patent application or utility model application. The DPMA does not take any adhesion for any faults or omissions.Patent Literature citedDE 10 2006 057 836

[0002] DE 10 2017 200 240

[0002] DE 10 001 915

[0002] DE 19 522 833

[0002]

Claims

Drive device (1) for a vehicle, having a drive (2) for mechanically operatively connecting to a motor device, a drive output (3) for mechanically operatively connecting to a propulsion element (7), a transmission assembly (4) which has a variator (36) and is formed coaxially with respect to a central shaft (13) and is intended for providing a plurality of driving ranges, and a reversing assembly (5) having a forward shifting element (KV) for providing the plurality of driving ranges in the forward direction, and a reverse shifting element (KR) for providing the plurality of driving ranges in the reverse direction, it being possible for a torque to be transmitted from the drive (2) via the transmission assembly (4) and the reversing assembly (5) to the drive output (3), and wherein the forward shifting element (KV) and the reverse shifting element (KR) are arranged axially parallel spaced apart from one another and in each case axially parallel spaced apart from the central shaft (13) of the transmission assembly (4).Drive device (1) according to Claim 1, characterized in that the drive (2) is arranged at an axially parallel spacing from the central shaft (13) of the transmission assembly (4) and one of the forward and the reverse shifting element (KV; KR) is arranged coaxially with respect to the drive (2).Drive device (1) according to Claim 1 or 2, characterized in that the output drive (3) is arranged at an axially parallel spacing from the central shaft (13) of the transmission assembly (4) and one of the forward and the reverse shift element (KV; KR) is arranged coaxially with respect to the output drive (3).Drive device (1) according to one of the preceding claims, characterized in that the transmission assembly (4), the forward shifting element (KV) and the reverse shifting element (KR) at least partially overlap in the direction of the central shaft (13) of the transmission assembly (4).Drive device (1) according to one of the preceding claims, characterized in that the forward shifting element (KV) and the reverse shifting element (KR) are arranged at the same height in the direction of the central shaft (13) of the transmission assembly (4).Drive device (1) according to one of the preceding claims, characterized in that the transmission assembly (4) has at least one planetary gear set (16; 21; 26; 31) and at least one shift element (K1; K2; K3; K4; BG) for shifting a driving range, wherein, as viewed from the drive (2), the shift element (K1; K2; K3; K4; BG) of the transmission assembly (4) is arranged along the central shaft (13) in front of the planetary gear set (16; 21; 26; 31) of the transmission assembly (4).Drive device (1) according to one of the preceding claims, characterized in that the drive device (1) has a load-bearing housing (41) for diverting forces from the drive device (1).Drive device (1) according to one of the preceding claims, characterized in that the drive device (1) has a switching device (46) for mechanically decoupling the reverse switching element (KR) from the output drive (3) in order to reduce drag losses.Drive device (1) according to one of the preceding claims, characterized in that the transmission assembly (4) comprises a first planetary gear set (16) having a first sun wheel (17), a first planetary carrier (18) having a planetary wheel (19) mounted rotatably thereon and a first ring gear (20), a second planetary gear set (21) having a second sun wheel (22), a second planetary carrier (23) having a planetary wheel (24) mounted rotatably thereon and a second ring gear (25), a third planetary gear set (26) having a third sun wheel (27), a third planetary carrier (28) having a planetary wheel (29) mounted rotatably thereon and a third ring gear (30), a fourth planetary gear set (31) having a fourth sun wheel (32), a fourth planetary carrier (33) having a planetary wheel (34) mounted rotatably thereon and a fourth ring gear (35), a first shift element (K1), a second shift element (K2), a third shift element (K3), a fourth shifting element (K4), a fifth shifting element (BG) and an output shaft (15) mechanically operatively connected to the reversing assembly (5), wherein the central shaft (13) is mechanically operatively connected to the drive (2) and permanently rotationally fixed to the second planetary carrier (23) and to the first ring gear (20), the first sun gear (17) is mechanically operatively connected to the central shaft (13) via the variator (36), the first planetary carrier (18) is permanently rotationally fixed to the second ring gear (25) and to the third planetary carrier (28), the second sun gear (22) is permanently rotationally fixed to the third sun gear (27), the third ring gear (30) is rotationally fixed to the fourth sun gear (32) via the first shifting element (K1), the third sun gear (27) is rotationally fixed to the fourth sun gear (32) via the second shifting element (K2), the third planet carrier (28) can be connected in a rotationally fixed manner to the fourth planet carrier (33) via the third shifting element (K3), the fourth planet carrier (33) can be connected in a rotationally fixed manner to the fourth sun wheel (32) via the fourth shifting element (K4), the fourth ring gear (35) can be fixed in a rotationally fixed manner to a transmission housing (41) via the fifth shifting element (BG), and the fourth planet carrier (33) is permanently connected in a rotationally fixed manner to the output shaft (15).Vehicle having a drive device (1) according to one of the preceding claims.

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