Axle drive device for a work machine

Abstract

The present disclosure relates to an axle drive device (1) for a work machine (100), comprising a transfer gearbox (8). The transfer gearbox (8) has a first planetary gear set (22), a second planetary gear set (23), and a third planetary gear set (45). A second element (25) of the first planetary gear set (22) is permanently rotationally rigidly connected to a third element (48) of the third planetary gear set (45). A third element (26) of the first planetary gear set (22) is permanently rotationally rigidly connected to a first element (27) of the second planetary gear set (23). A second element (28) of the second planetary gear set (23) is permanently rotationally rigidly fastened to a stationary component (16). A third element (29) of the second planetary gear set (23) is permanently rotationally rigidly connected to the first element (46) of the third planetary gear set (45). A first output shaft (9) is permanently rotationally rigidly connected to a second element (47) of the third planetary gear set (45). A second output shaft (10) is permanently rotationally rigidly connected to the first element (46) of the third planetary gear set (45).

Description

[0001] ZF Friedrichshafen AG File 303450 Friedrichshafen 2024-08-14

[0002] Axle drive device for a work machine

[0003] Technical field

[0004] The present invention relates to an axle drive device for a working machine. Furthermore, the present invention relates to a working machine with such an axle drive device.

[0005] State of the art

[0006] As part of the electrification of drive trains for construction machinery, axle drives with an electric traction motor have been developed. A disadvantage of the solutions known from the prior art is that these drives cannot simultaneously provide high tractive forces and high travel speeds with a comparatively simple design.

[0007] Description of the invention

[0008] The present disclosure relates to an axle drive device for a working machine. The working machine may be a construction or agricultural machine or a commercial vehicle. For example, the working machine may be a municipal vehicle or a tractor. In addition to the axle drive device, the working machine may have a further axle drive device, which may be identical or of a different design. In one embodiment, the working machine has a further axle which is driven by the axle drive device of the present disclosure. Thus, the axle drive device of the present disclosure may, for example, provide all-wheel drive for the working machine. The axle drive device may be a drive unit that can be integrated into an axle of the working machine.For example, the axle drive unit can be designed to be at least partially coaxial with an axle of the machine. In one embodiment, the axle drive unit is designed such that it is spatially and functionally integrated with an axle of the machine (ZF Friedrichshafen AG File 303450, Friedrichshafen, August 14, 2024), for example, by sharing a common housing. The axle drive unit can have a main direction of extension, which can be parallel, for example, coaxial, with an axle of the machine. In one embodiment, the axle drive unit is designed as a drive unit for a rear axle of the machine.

[0009] The axle drive unit comprises an electric traction motor, which is designed, for example, to provide sufficient power to drive the drive system of the machine, thus accelerating the machine to the required speeds with the necessary tractive forces. Furthermore, the axle drive unit comprises a distribution gearbox with a first output shaft for driving a first wheel of the machine and a second output shaft for driving a second wheel of the machine opposite the first wheel. The first wheel can, for example, be a right wheel and the second wheel a left wheel of the machine. The two opposing wheels of the machine can be driven simultaneously by the axle drive unit of this disclosure.Between the first output shaft and, alternatively or additionally, the second output shaft and the respective wheel, a further gear stage, for example a wheel hub gear, can be provided. This further gear stage can provide an additional reduction and may, for example, be designed as a planetary gear set.

[0010] The electric traction motor can be supplied with the electrical energy required for its operation, for example, from a battery storage system, a fuel cell, or via a diesel-powered generator. A combination of these electrical supply options is also conceivable and preferred; in particular, the electric traction motor can be supplied electrically by a battery storage system and a diesel-powered generator, or by a battery storage system and a fuel cell. ZF Friedrichshafen AG File 303450 Friedrichshafen 2024-08-14

[0011] The transfer case has a first planetary gear set with a first element, a second element, and a third element. Furthermore, the transfer case has a second planetary gear set with a first element, a second element, and a third element. In addition, the transfer case has a third planetary gear set with a first element, a second element, and a third element. The first, second, and third elements can each be a sun gear, a planet carrier, or a ring gear of the respective planetary gear set. Each planetary gear set can be a positive or a negative planetary gear set. Each planetary gear set can have planet gears that can be rotatably mounted on the respective planet carrier of the planetary gear set. The planet gears can mesh with both the sun gear and the ring gear of the respective planetary gear set.

[0012] Torque from the traction motor can be transmitted to the transfer case via the first element of the first planetary gear set. This may require the closing of one or more switching elements. In one embodiment, a rotor shaft of the electric traction motor is mechanically connected to the first element of the first planetary gear set, for example, permanently and rotationally fixed. The second element of the first planetary gear set is permanently and rotationally fixed to the third element of the third planetary gear set. The third element of the first planetary gear set is permanently and rotationally fixed to the first element of the second planetary gear set. Furthermore, the second element of the second planetary gear set is permanently and rotationally fixed to a stationary component, for example, a housing of the axle drive unit.The third element of the second planetary gear set is permanently and rotationally fixed to the first element of the third planetary gear set. Furthermore, the first output shaft is permanently and rotationally fixed to the second element of the third planetary gear set. The second output shaft, however, is permanently and rotationally fixed to the first element of the third planetary gear set.

[0013] By designing the transfer case with three planetary gear sets in the manner described above, high gear ratios can be achieved (ZF Friedrichshafen AG File 303450 Friedrichshafen 2024-08-14)

[0014] Gear ratios can be achieved that are greater than 10 in absolute value; for example, the gear ratio can have a ratio greater than 20 in absolute value. This allows, for instance, very high reduction ratios to be achieved through the transfer case, enabling the use of a high-speed electric traction motor with a compact design. The transfer case can also incorporate a differential lock that can non-rotatably connect two elements of the third planetary gear set, such as the sun gear and the ring gear, or the planet carrier and the ring gear.

[0015] If two elements are mechanically connected, they are coupled directly or indirectly, such that a movement of one element causes a reaction in the other. A mechanical connection can be established, for example, by friction or positive engagement. The mechanical connection can correspond to a gear mesh between the corresponding gears of the two elements. Additional elements, such as one or more spur gear stages, may be present between the elements. A permanent, non-rotatable connection, on the other hand, is a connection in which the two elements are rigidly coupled. The elements can be designed as separate, non-rotatably connected components or as a single piece. A non-rotatable connection between two elements can also be established by a switching element, such as a clutch or a brake. The non-rotatable connection is established when the switching element is actuated.The rotationally fixed connection can be released when the switching element is no longer actuated.

[0016] In one embodiment, the first elements of the three planetary gear sets are each configured as sun gears, the second elements as planet carriers, and the third elements as ring gears. In an alternative embodiment, the first element of the first planetary gear set is configured as a sun gear, the second element as a ring gear, and the third element as a planet carrier. The first element of the second planetary gear set can be configured as a sun gear, the second element as a planet carrier, and the third element as a ring gear. Furthermore, in this ZF Friedrichshafen AG file 303450 Friedrichshafen 2024-08-14

[0017] In this embodiment, the first element of the third planetary gear set is designed as a ring gear, the second element of the third planetary gear set as a planet carrier, and the third element of the third planetary gear set as a sun gear.

[0018] In this type of transfer case configuration, the first and third planetary gear sets can be arranged one behind the other in the axial direction of the axle drive. More precisely, the third planetary gear set can be arranged, for example, in one axial direction, in front of the first planetary gear set, which in turn is positioned in front of the second planetary gear set. This allows for a transfer case that is particularly compact in the radial direction. In an alternative embodiment, the first and third planetary gear sets of the transfer case can be arranged one behind the other in the radial direction at the same axial height. Furthermore, a coupling shaft can be provided that forms a sun gear and a ring gear, forming both the ring gear of the first planetary gear set and the sun gear of the third planetary gear set. This design enables a transfer case that is particularly compact in the axial direction.

[0019] In one embodiment, the axle drive unit has a differential lock for non-rotatably connecting two elements of the third planetary gear set. For example, the differential lock can be used to non-rotatably connect the third element of the second planetary gear set, and therefore, in one embodiment, the first element of the third planetary gear set, to the third element of the third planetary gear set. The differential lock can be arranged radially outside the first planetary gear set, for example, at the same axial height as the first planetary gear set. Alternatively, the differential lock can be used to non-rotatably connect the first element of the third planetary gear set to the second element of the third planetary gear set, with the first and third planetary gear sets being arranged radially one behind the other in this embodiment.The differential lock can now be positioned axially adjacent to the first and third planetary gear sets. ZF Friedrichshafen AG File 303450 Friedrichshafen 2024-08-14.

[0020] In one embodiment, the axle drive unit further comprises a transmission for providing two gears with different gear ratios. The transmission can be arranged in the torque transmission path from the electric traction motor to the first and second output shafts upstream of the transfer case. In addition to the two gears, the transmission can provide further gears. The transmission can be a unit that is spatially and functionally separate from the transfer case. At least one gear of the transmission can be a reduction gear, i.e., a gear with a gear ratio greater than 1. The axle drive unit can be configured to drive the first and second output shafts via the transmission (for example, the first or second gear of the transmission) and the transfer case, using the electric traction motor.In one embodiment, the torque of the electric traction motor can be converted, for example reduced, by both the gearbox and the transfer case.

[0021] The transmission has a transmission input, a transmission output, a first shift element, and a second shift element. The transmission input is mechanically connected to the transmission output via a first gear ratio by means of the first shift element and via a second gear ratio by means of the second shift element. The first and second shift elements can be configured as a dual shift element or as separate shift elements, both spatially and functionally. If the shift elements are configured as a dual shift element, a single actuator can be provided to actuate the shift element. If, on the other hand, the shift elements are configured as single shift elements, a separate actuator can be provided for each shift element.By providing the gear transmission, an axle drive system with a high spread can be provided, enabling both high tractive forces at low driving speeds and high final speeds.

[0022] The switching elements can each be designed as a positive-locking or friction-locking switching element. In one embodiment, one or both switching elements are designed as synchronizers. In a positive-locking configuration (ZF Friedrichshafen AG File 303450 Friedrichshafen 2024-08-14), the switching element can also be designed as a dog clutch, which is compact, cost-effective, and has low drag torque. In a friction-lock configuration, the switching element can be designed as a multi-plate clutch, which enables load shifting. If the switching elements are designed as a double switching element, they can have a neutral position in addition to the gear-shifting positions.

[0023] In one embodiment, the transmission comprises a planetary gear set with a first element, for example a sun gear, a second element, for example a planet carrier, and a third element, for example a ring gear. To provide the first gear, one element of the planetary gear set, for example the sun gear, can be non-rotatably connected to the stationary component, for example the transmission housing described above, by the first switching element. To provide the second gear, on the other hand, two elements of the planetary gear set, for example the sun gear and the ring gear, can be non-rotatably connected to each other by the second switching element to lock them together. Accordingly, the second gear can be a through-drive that can have a gear ratio of 1.The first gear can be a gear with a gear ratio that is greater than 1 in absolute value and therefore provides a reduction.

[0024] In one embodiment, the transmission is designed as a spur gear transmission and comprises a first spur gear stage and a second spur gear stage. One of the spur gear stages can provide a gear ratio greater than 1, thus providing a reduction gear. The other spur gear stage can also be a reduction gear, but it can have a lower gear ratio than the first spur gear stage. The transmission input can be mechanically connected to the transmission output via the first spur gear stage by means of the first shift element, and via the second spur gear stage by means of the second shift element. Each of the spur gear stages can be a single-stage spur gear stage.In this embodiment, the electric traction motor can be arranged parallel to the axis of the transfer case (ZF Friedrichshafen AG File 303450, Friedrichshafen, August 14, 2024) and alternatively or additionally to the first or second output shaft. For example, a rotor shaft of the electric traction motor can be mechanically connected to an input shaft of the transfer case via the transmission, which is designed as a spur gear transmission. In this embodiment, the first and second shift elements of the transmission can be designed as a double shift element, which is arranged coaxially to a rotor shaft of the electric traction motor or alternatively to the transfer case or the first or second output shaft. For example, in this configuration, the double shift element is designed as a double synchronizer.Alternatively, one of the switching elements can be arranged coaxially to the rotor shaft of the electric traction motor and the other switching element coaxially to the transfer case and the first or second output shaft.

[0025] In one embodiment, the electric traction motor has a rotor shaft designed as a hollow shaft, which can be arranged coaxially with and radially within a stator of the electric traction motor. The transfer case and the traction motor, for example, the hollow shaft of the traction motor, can be arranged coaxially with each other. Furthermore, the transfer case and the traction motor can be arranged coaxially with the first and second output shafts. The first output shaft can extend from the transfer case through the hollow shaft of the traction motor. Thus, the first output shaft can extend from the transfer case toward the electric traction motor and be arranged radially within the hollow rotor shaft.Such a configuration allows, for example, the first output shaft to reach a wheel of the driven machine, which can be located on the side of the electric traction motor facing away from the transfer case. The second output shaft can extend away from the transfer case and the electric traction motor. This configuration provides an axle drive arrangement that is particularly compact, especially in the radial direction. In an alternative embodiment, the electric traction motor is spaced parallel to the axle from the transfer case and is arranged alternatively or additionally to the first or second output shaft. In such an embodiment, the rotor shaft can be driven via a spur gear stage and / or a ZF Friedrichshafen AG File 303450 Friedrichshafen 2024-08-14.

[0026] The continuous recirculating element, such as a chain or belt, may be connected to the gearbox and alternatively or additionally to the transfer case.

[0027] In one embodiment, the axle drive unit includes a power take-off (PTO) with a PTO motor for driving an attachment of the machine. The PTO motor can be separate from the electric traction motor. The axis of rotation of the PTO motor can be arranged orthogonally to the first and second output shafts. A hydraulic pump for lubricating and actuating the axle drive unit, for example, the shift elements of the transmission, can be driven by the PTO motor. Furthermore, a coupling device can be selectively mechanically connected to the PTO motor, for example, via a shift element. The attachment can then be mechanically coupled to the coupling device and subsequently driven by the PTO motor.The coupling device and the auxiliary drive motor can be arranged on opposite sides of the first and second output shafts.

[0028] Furthermore, the present disclosure relates to a working machine with an axle drive device according to one of the embodiments described above. In addition to the axle drive device, the working machine may have another axle, for example a front axle, which can be driven via the axle drive device. Regarding the designs and advantages of the individual features, reference is made to the above descriptions in connection with the axle drive device for a working machine.

[0029] Brief description of the characters

[0030] Figure 1 shows a wiring concept of a distribution gearbox of an axle drive unit according to one embodiment.

[0031] Figure 2 shows an axle drive unit with a transfer case according to Figure 1, according to one embodiment. ZF Friedrichshafen AG File 303450 Friedrichshafen 2024-08-14

[0032] Figure 3 shows an axle drive device with a distribution gearbox according to Figure 1 in one embodiment.

[0033] Figure 4 shows an axle drive device with a distribution gearbox according to Figure 1 in one embodiment.

[0034] Figure 5 shows an axle drive device with a distribution gearbox according to Figure 1 in one embodiment.

[0035] Figure 6 shows an axle drive device with a distribution gearbox according to Figure 1 in one embodiment.

[0036] Figure 7 shows an axle drive device with a distribution gearbox according to Figure 1 according to one embodiment.

[0037] Figure 8 shows an axle drive device with a distribution gearbox according to Figure 1 in one embodiment.

[0038] Figure 9 shows a working machine with an axle drive device according to one of the embodiments of Figures 2 to 8.

[0039] Detailed description of embodiments

[0040] Figure 2 shows an axle drive unit 1 for a working machine 100 according to one embodiment. In the present embodiment, the working machine 100 is a tractor. In the present embodiment, the axle drive unit 1 is designed as a rear axle drive unit. As described below, the axle drive unit shown in Figure 2 can be used to...

[0041] The axle drive unit 1 also drives a front axle 101 of the working machine 100, which is not shown in this figure. The rear axle drive unit 1 of Figure 2 comprises a right wheel 2 and a left wheel 3, which are driven by means of the

[0042] The axle drive unit 1 can be driven to propel the tractor 100. Furthermore, the axle drive unit 1 has an axis of symmetry which coincides with the axes of rotation of wheels 2 and 3. The axle drive unit 1 is designed coaxially with this axis of symmetry. The axle drive unit 1 comprises an electric traction motor 4 with a stator 5 and a rotor 6 located radially inside it. The rotor 6 of the electric traction motor 4 is permanently and rotationally fixedly connected to a rotor shaft 7 designed as a hollow shaft. The electric traction motor 4, and thus both the stator 5 and the rotor 6, are arranged coaxially with the axis of symmetry described above. The electric traction motor 4 is designed to propel the tractor 100.

[0043] Furthermore, the axle drive unit 1 in Figure 2 comprises a distribution gearbox 8 with a first output shaft 9 and a second output shaft 10. The first output shaft 9 and the second output shaft 10 are each mechanically connected to the wheels 2 and 3, respectively, via a wheel hub gearbox 11. The wheel hub gearboxes 11 are each of planetary design and have a sun gear 12, a planet carrier 13 with planet gears 14 rotatably mounted thereon, and a ring gear 15. The sun gear 12 is permanently and non-rotatably connected to the first 9 and second output shaft 10, respectively. The ring gear 15 is permanently and non-rotatably connected to a stationary component 16, in this case a housing of the axle drive unit 1. The stator 5 of the electric traction motor 4 is also permanently and non-rotatably connected to this housing 16.The planet carrier 13 of the respective wheel hub gear 11 is permanently and rotationally fixed to the respective wheel 2 or 3. The planet carrier 13 can also be selectively and rotationally fixed to the stationary component 16 via a brake 17 in order to brake the associated wheel 2 or 3. Furthermore, the transfer case 8 includes an input shaft 21, via which it is mechanically connected to the electric traction motor 4, for example, permanently and rotationally fixed.

[0044] The axle drive unit 1 further comprises an all-wheel drive output 36, which in the present embodiment is designed in the form of a bevel gear. A front axle 101 of the tractor 100, not shown in Figure 2, can be selectively mechanically coupled to the bevel gear 36. For this purpose, a further bevel gear 37 meshing with the all-wheel drive output 36 is provided, which is connected via a switching element 38 to the ZF Friedrichshafen AG file 303450 Friedrichshafen 2024-08-14

[0045] The front axle 101 can be mechanically connected. A torque can be transmitted from the axle drive unit 1 to the front axle 101 via the switching element 38 through the bevel gear transmission, which consists of the all-wheel drive output 36 and the bevel gear 37. For this purpose, a cardan shaft running transversely to the axis of symmetry of the axle drive unit 1 can be provided, via which the bevel gear transmission 36, 37 can be mechanically coupled to the front axle 101 via the switching element 38. In this case, the all-wheel drive output 36 is mechanically connected to the rotor shaft 7 via a spur gear stage.

[0046] Furthermore, the axle drive unit 1 of the present embodiment comprises a power take-off with its own electric power take-off motor 40, the axis of rotation of which is arranged transversely, for example orthogonally, to the first and second output shafts 9, 10. A hydraulic pump 42 for lubricating and actuating the axle drive unit 1 can be driven by the power take-off motor 40 via a spur gear transmission 41. In addition, a coupling device 44 can be selectively mechanically connected to the power take-off motor 40 via a switching element 43. An implement of the tractor 100 can be mechanically coupled to the coupling device 44, which can then in turn be driven by the power take-off motor 40. In the present embodiment, the coupling device 44 and the power take-off motor 40 are arranged on opposite sides of the first and second output shafts 9, 10.The auxiliary drive motor 40 can be arranged on the side of the output shafts 9, 10 which faces the front axle 101 of the tractor 100.

[0047] Figure 1 shows a general interconnection concept of the transfer case 8 of the embodiments shown in Figures 2 to 8. As can be seen from Figure 1, the transfer case 8 comprises a first planetary gear set 22 with a first element 24, a second element 25, and a third element 26. Furthermore, the transfer case 8 comprises a second planetary gear set 23 with a first element 27, a second element 28, and a third element 29. In addition, the transfer case 8 comprises a third planetary gear set 45 with a first element 46, a second element 47, and a third element 48. ZF Friedrichshafen AG File 303450 Friedrichshafen 2024-08-14

[0048] As can be seen in Figure 1, torque from the electric traction motor 4 can be transmitted to the transfer case 8 via the first element 24 of the first planetary gear set 22. For this purpose, the rotor shaft 7 is mechanically connected to the first element 24 of the first planetary gear set, for example, permanently and non-rotatably. A second element 25 of the first planetary gear set 22 is permanently and non-rotatably connected to a third element 48 of the third planetary gear set 45, in this case via a coupling shaft. A third element 26 of the first planetary gear set 22 is permanently and non-rotatably connected to the first element 27 of the second planetary gear set 23, in this case via a coupling shaft. The second element 28 of the second planetary gear set 23 is permanently and non-rotatably fixed to the stationary component 16, in this case the housing described above.Furthermore, the third element 29 of the second planetary gear set 23 is permanently and rotationally fixedly connected to the first element 46 of the third planetary gear set 45, in this case via a coupling shaft. The first output shaft 9 is mechanically operatively connected to the second element 47 of the third planetary gear set 45, in this case permanently and rotationally fixedly connected. The second output shaft 10 is also mechanically operatively connected to the first element 46 of the third planetary gear set 45 and the third element 29 of the second planetary gear set 23, in this case permanently and rotationally fixedly connected. In addition, the transfer case 8 includes a differential lock 30, by means of which two elements of the third planetary gear set 45 can be rotationally fixedly connected to each other.

[0049] In the embodiment shown in Figure 2, the first elements 24, 27, and 46 of the first 22, second 23, and third planetary gear sets 45 are each configured as sun gears. The second elements 25, 28, and 47 of the first 22, second 23, and third planetary gear sets 45 are each configured as planet carriers. The third elements 26, 29, and 48 of the first 22, second 23, and third planetary gear sets 45 are each configured as ring gears. Viewed from the left wheel 3, in the transfer case 8, the third planetary gear set 45 is arranged in front of the first planetary gear set 22, which in turn is positioned in front of the second planetary gear set 23, in the direction of the axis of symmetry of the axle drive unit 1. In this embodiment, the differential lock 30 is arranged at the same axial height as the first planetary gear set 22, but radially outside of it.The differential lock 30 allows the first element 46 of the third planetary gear set 45 to be selectively connected to the third element 48 of the third planetary gear set 45 in a rotationally fixed manner. ZF Friedrichshafen AG File 303450 Friedrichshafen 2024-08-14

[0050] Figure 3 shows an axle drive unit 1 for a working machine 100 according to a further embodiment. The axle drive unit 1 of the embodiment shown in Figure 3 corresponds to the axle drive unit 1 of the embodiment shown in Figure 2, with the exception of the differences described below. In contrast to the axle drive unit 1 from Figure 2, the distribution gear 8 is designed differently in the axle drive unit 1 of the embodiment shown in Figure 3. The first element 24 of the first planetary gear set 22 is designed as a sun gear in the embodiment shown in Figure 3. The second element 25 of the first planetary gear set 22 is designed as a ring gear in the embodiment shown in Figure 3. The third element 26 of the first planetary gear set 22 is designed as a planet carrier in the embodiment shown in Figure 3. The first element 27 of the second planetary gear set 23 is designed as a sun gear in the embodiment shown in Figure 3.In the embodiment shown in Figure 3, the second element 28 of the second planetary gear set 23 is configured as a planet carrier. In the embodiment shown in Figure 3, the third element 29 of the second planetary gear set 23 is configured as a ring gear. Furthermore, in the embodiment shown in Figure 3, the first element 46 of the third planetary gear set 45 is configured as a ring gear. In the embodiment shown in Figure 3, the second element 47 of the third planetary gear set 45 is configured as a planet carrier. Finally, in the embodiment shown in Figure 3, the third element 48 of the third planetary gear set 45 is configured as a sun gear. In the embodiment shown in Figure 3, the differential lock 30 is provided between the first element 46 (the ring gear) of the third planetary gear set 45 and the third element 48 (the sun gear) of the third planetary gear set 45. The differential lock 30 allows these elements to be selectively and rotationally locked together.

[0051] Figure 4 shows an axle drive unit 1 for a machine 100 according to a further embodiment of the present invention. The axle drive unit 1 from Figure 4 is similar to the axle drive unit 1 from Figure 3, except for the differences described below. In contrast to the axle drive unit 1 from Figure 3, in the axle drive unit 1 from Figure 4, the third planetary gear set 45 of the transfer case 8 is arranged at the same axial height as the first planetary gear set 22 of the transfer case 8. In the radial direction of the axle drive unit 1, the first planetary gear set 22 and the third planetary gear set 45 are arranged one behind the other.For this purpose, a sun gear ring is provided, which can be designed in one piece and forms both the second element of the first planet gear set, i.e. the ring gear 25, and the third element of the third planet gear set 45, i.e. the sun gear 48.

[0052] Figure 5 shows an axle drive unit 1 for a working machine 100 according to a further embodiment. The axle drive unit 1 of Figure 5 corresponds to the axle drive unit 1 of Figure 2, except for the differences described below. In contrast to the axle drive unit 1 of Figure 2, in the axle drive unit 1 of Figure 5 the electric traction motor 4 is not coaxial with the first output shaft 9, but spaced parallel to it. Accordingly, the rotor 7 of the electric traction motor 4 is mechanically connected to the input shaft 21 of the distribution gearbox 8 via a spur gear stage 49.

[0053] Figure 6 shows an axle drive unit 1 for a working machine 100 according to a further embodiment. The axle drive unit 1 according to Figure 6 is designed like the axle drive unit 1 from Figure 2, with the exception of the differences described below. In contrast to the embodiment of Figure 2, the embodiment of Figure 6 provides a transmission 50 in the torque transmission path between the electric traction motor 4 and the transfer case 8. The transmission 50 is designed to provide two gears with different gear ratios. It comprises a transmission input 51, a transmission output 52, a first shift element 53, and a second shift element 54. Furthermore, the transmission 50 includes a planetary gear set 55 with a sun gear 56, a planet carrier 57, and a ring gear 58. Planet gears are provided on the planet carrier 57 that mesh with both the sun gear 56 and the ring gear 58.The transmission input 51 is permanently and rotationally fixedly connected to the ring gear 58 of the planetary gear set 55 and the rotor shaft 7 of the electric traction motor 4. The transmission output 52 is permanently and rotationally fixedly connected to the planet carrier 57 and an input shaft 21 of the transfer case 8. ZF Friedrichshafen AG File 303450 Friedrichshafen 2024-08-14. The sun gear 56 can be rotationally fixed to the stationary component 16 by means of the first switching element 53 to provide a first gear with a first reduction ratio. The reduction ratio of the first gear can be greater than 1 and be designed as a reduction gear. By actuating the second switching element 54, the ring gear 58 can be rotationally fixed to the sun gear 56 to lock the planetary gear set 55. Accordingly, in this second gear the transmission input 51 can be connected to the transmission output 52 in a rotationally fixed manner, so that the second gear has a gear ratio of 1.By providing the gear transmission 50, the gear ratio spread of the axle drive unit 1 can be increased. In the present embodiment, the first switching element 53 and the second switching element 54 are designed as friction-fit switching elements, more precisely, multi-plate clutches.

[0054] Figure 7 shows an axle drive unit 1 for a working machine 100 according to a further embodiment. The drive unit 1 according to Figure 7 is designed like the axle drive unit 1 according to Figure 6, with the exception of the differences described below. In contrast to the axle drive unit 1 from Figure 6, the transmission 50 in the axle drive unit 1 from Figure 7 is designed as a spur gear transmission. The electric traction motor 4 is also arranged parallel to the axis and spaced apart from the first output shaft 9, as in the embodiment of Figure 5. The first switching element 53 and the second switching element 54 are provided coaxially to the rotor shaft 7, which forms the transmission input 51. In the present embodiment, these are designed as a double switching element with a single actuation. The double switching element is designed as a double synchronizer in the present embodiment.Furthermore, the spur gear transmission 50 comprises a first spur gear stage 60 for providing a first gear and a second spur gear stage 61 for providing a second gear. By actuating the first switching element 53, the transmission input 51 can be mechanically connected to the transmission output 52 via the first spur gear stage 60. By actuating the second switching element 54, the transmission input 51 can be mechanically connected to the transmission output 52 via the second spur gear stage 61. In the present embodiment, the transmission output 52 is permanently rotationally fixed to the input shaft 21 of the ZF Friedrichshafen AG File 303450 Friedrichshafen 2024-08-14.

[0055] The transfer case 8 is connected. As in the embodiment according to Figure 6, the first gear ratio in the present embodiment has a gear ratio greater than 1 in absolute terms and is therefore designed as a reduction gear. The second gear ratio in the present embodiment is also designed as a reduction gear, but has a gear ratio smaller in absolute terms than the first gear ratio.

[0056] Figure 8 shows an axle drive unit 1 for a working machine 100 according to a further embodiment. The axle drive unit 1 according to Figure 8 is designed like the axle drive unit 1 according to Figure 7, with the exception of the differences described below. In contrast to the axle drive unit 1 from Figure 7, in the axle drive unit 1 from Figure 8 the double switching element, which has both the first switching element 53 and the second switching element 54, is provided coaxially to the first output shaft 9. The rotor shaft 7 of the electric traction motor 4 and thus the gearbox input

[0057] The 51, however, remain arranged parallel to the axis of the first output shaft 9. Accordingly, as in the embodiment of Figure 7, in the axle drive unit 1 from Figure 8, the transmission input 51 is connected to the transmission output via the first spur gear stage 60 or the second spur gear stage 61 by actuating the first switching element 53 or the second switching element 54.

[0058] 52 selectively mechanically bondable.

[0059] Figure 9 shows a working machine 100 according to one embodiment. In the present embodiment, the working machine 100 is designed as a tractor. It comprises an axle drive unit 1 according to one of the previously described embodiments, which is designed as a rear axle drive unit. Furthermore, the working machine 100 comprises a front axle 101, which can be driven via the rear axle drive unit 1 by closing the switching element 38 described above. ZF Friedrichshafen AG File 303450 Friedrichshafen 2024-08-14

[0060] Reference mark

[0061] 1 axle drive unit

[0062] 2, 3 wheel

[0063] 4.40 electric motor

[0064] 5 Stator

[0065] 6, 7 Rotor, rotor shaft

[0066] 8 Transfer case

[0067] 9, 10 Output wave

[0068] 11 Wheel hub gears

[0069] 12, 56 sun wheel

[0070] 13, 57 Planetary carriers

[0071] 14 planetary gear

[0072] 15, 58 ring gear

[0073] 16 stationary component

[0074] 17 Brake

[0075] 21 Input wave

[0076] 22, 23, 45, 55 Planetary gear set

[0077] 30 Differential lock

[0078] 24, 27, 46 first element

[0079] 25, 28, 47 second element

[0080] 26, 29, 48 third element

[0081] 38, 43, 53, 54 Switching element

[0082] 36 All-wheel drive

[0083] 37 Bevel gear

[0084] 41, 49, 60, 61 Spur gear stage

[0085] 42 Hydraulic pump

[0086] 44 Coupling device

[0087] 50-speed transmission

[0088] 51 Gearbox input

[0089] 52 Gearbox output

[0090] 100 working machines

[0091] 101 Front axle

Claims

ZF Friedrichshafen AG File 303450 Friedrichshafen 2024-08-14 Patent claims 1. Axle drive device (1) for a working machine (100) comprising an electric traction motor (4) and a distribution gearbox (8) with a first output shaft (9) for driving a first wheel (2) of the working machine (100) and a second output shaft (10) for driving a second wheel (3) of the working machine (100) opposite the first wheel (2), wherein the axle drive device (1) is configured to drive the first (9) and the second output shaft (10) via the distribution gearbox (8) with the electric traction motor (4), wherein the distribution gearbox (8) comprises a first planetary gear set (22) with a first element (24), a second element (25) and a third element (26), a second planetary gear set (23) with a first element (27), a second element (28) and a third element (29), and a third planetary gear set (45) with a first element (46), a second element (47) and a third element (48) haswherein a torque of the traction motor (4) can be introduced into the transfer case (8) via the first element (24) of the first planetary gear set (22), the second element (25) of the first planetary gear set (22) is permanently and rotationally fixedly connected to the third element (48) of the third planetary gear set (45), the third element (26) of the first planetary gear set (22) is connected to the first element (27) of the second, planetary gear set (23) is permanently connected in a rotationally fixed manner, the second element (28) of the second planetary gear set (23) is permanently fixed to a stationary component (16), the third element (29) of the second planetary gear set (23) is permanently connected in a rotationally fixed manner to the first element (46) of the third planetary gear set (45), the first output shaft (9) is permanently connected in a rotationally fixed manner to the second element (47) of the third planetary gear set (45), and wherein the second output shaft (10) is permanently connected in a rotationally fixed manner to the first element (46) of the third planetary gear set (45).

2. Axle drive device (1 ) according to claim 1 , characterized in that the first elements (24, 27, 46) of the three planet gear sets (22, 23, 45) are each designed as sun gears, the second elements (25, 28, 47) of the three planet gear sets (22, 23, 45) are each designed as planet carriers and the third elements (26, 29, 48) of the three planet gear sets (22, 23, 45) are each designed as ring gears. ZF Friedrichshafen AG File 303450 Friedrichshafen 2024-08-14 3. Axle drive device (1) according to claim 1, characterized in that the first element (24) of the first planet gear set (22) is configured as a sun gear, the second element (25) of the first planet gear set (22) as a ring gear, the third element (48) of the third planet gear set (45) as a sun gear, the third element (26) of the first planet gear set (22) as a planet carrier, the first element (27) of the second planet gear set (23) as a sun gear, the second element (28) of the second planet gear set (23) as a planet carrier, the third element (29) of the second planet gear set (23) as a ring gear, the first element (46) of the third planet gear set (45) as a ring gear, and wherein the second element (47) of the third planet gear set (45) is configured as a planet carrier.

4. Axle drive device (1 ) according to claim 3, characterized in that the first and the third planetary gear set (22, 45) are arranged one behind the other in an axial direction of the axle drive device (1 ).

5. Axle drive device (1 ) according to one of the preceding claims, characterized in that the axle drive device (1 ) has a differential lock (30) for rotationally fixedly connecting the third element (29) of the second planet gear set (23) with the third element (48) of the third planet gear set (45), wherein the differential lock (30) is arranged radially outside the first planet gear set (22).

6. Axle drive device (1) according to claim 3, characterized in that the first and the third planetary gear set (22, 45) are arranged one behind the other in an axial direction of the axle drive device (1) at the same axial height and in a radial direction of the axle drive device (1).

7. Axle drive device (1) according to one of the preceding claims, characterized in that the axle drive device (1 ) has a gear transmission (50) for providing two gears with different gear ratios, wherein the gear transmission (50) has a gear input (51 ), a gear output (52 ), a first switching element (53 ) and a second switching element ZF Friedrichshafen AG File 303450 Friedrichshafen 2024-08-14 (54) wherein the transmission input (51) can be mechanically connected to the transmission output (52) by means of the first switching element (53) via a first transmission and by means of the second switching element (54) via a second transmission.

8. Axle drive device (1 ) according to claim 7, characterized in that the gear transmission (50) has a planetary gear set (55) with a first element (56), a second element (57) and a third element (58), wherein, for the provision of the first gear, an element (56) of the planetary gear set (55) can be connected to the stationary component (16) in a rotationally fixed manner by the first switching element (53), and wherein, for the provision of the second gear, two elements (56, 58) of the planetary gear set (55) can be connected to each other in a rotationally fixed manner by the second switching element (54) to lock the same.

9. Axle drive device (1 ) according to claim 7 or 8, characterized in that the gear transmission (50) has a first spur gear stage (60) and a second spur gear stage (61 ), wherein the transmission input (51 ) is mechanically commutatively connected to the transmission output (52) for providing the first gear by means of the first switching element (53) via the first spur gear stage (60) and for providing the second gear by means of the second switching element (54) via the second spur gear stage (61 ).

10. Axle drive device (1 ) according to one of the preceding claims, characterized in that the electric traction motor (4) has a rotor shaft (7) designed as a hollow shaft, the distribution gearbox (8) and the traction motor (4) are arranged coaxially to each other, and the first output shaft (9) of the distribution gearbox (8) extends through the hollow shaft (7) of the traction motor (4).

11. Axle drive device (1 ) according to one of the preceding claims, characterized in that the axle drive device (1 ) has an auxiliary drive with an auxiliary drive motor (40) for driving an attachment of the working machine. ZF Friedrichshafen AG File 303450 Friedrichshafen 2024-08-14 12. Working machine (100) with an axle drive device (1 ) according to one of the preceding claims.

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