Transmission, drivetrain and vehicle

Abstract

The invention relates to a transmission (16) for a motor vehicle (10), wherein the transmission (16) comprises an input shaft (18), a first output shaft (22), a second output shaft (24), and a coupling shaft (70). Furthermore, the transmission comprises a first planetary gear set (30), a second planetary gear set (40), a third planetary gear set (50), a fourth planetary gear set (60), a first brake (72), and a second brake (74). The third planetary gear set (50), the fourth planetary gear set (60), the first brake (72), and the second brake (74) form a torque distribution device (17), which is mechanically connected to the input shaft (18) and the coupling shaft (70). The torque distribution device (17) is configured to control the torque distribution to the two output shafts (22, 24). The invention further relates to a drive train and a vehicle (10).

Description

Technical field The present invention relates to a transmission for a vehicle. Furthermore, the invention relates to a drive train and to a vehicle with such a transmission. State of the art Differential gears in motor vehicles allow, for example, the wheels on one side of an axle to rotate at a different speed than those on the other side. This can improve the vehicle's cornering performance. However, differential gears require additional installation space. DE 10 2019 209 460 A1 refers to a transmission with a torque vectoring superposition unit. Description of the invention A first aspect concerns a transmission for a vehicle. A vehicle can be, for example, a passenger car, truck, construction machine, or agricultural machine. The transmission can be a differential transmission, such as a transverse or longitudinal differential. A transmission can be designed to convert an input signal into an output signal. The transmission can be a reduction transmission. A reduction transmission can be understood as a transmission in which the absolute ratio between the input and output signals can be greater than 1. The gearbox has an input shaft, a first output shaft, and a second output shaft. Drive power can be supplied to the input shaft. This drive power can then be distributed to the two output shafts, for example, to drive the edges of an axle or to drive different axles. The gearbox can be configured to provide a differential function, as described above, allowing the output shafts to rotate at different speeds, for example, depending on the torque applied to them. The gearbox can also distribute motor power from one shaft of a drive motor to the two output shafts and thus be configured as a transfer case. The two output shafts can be arranged coaxially. The input shaft can be arranged coaxially with one or both output shafts. A drive motor can be connected to, or connectable to, the input shaft. For example, the drive motor can be an electric machine. The drive motor can be arranged coaxially with the input shaft. The motor shaft can be permanently and rotationally fixed to the input shaft. Alternatively, the motor shaft can be mechanically connected to, or connectable to, the input shaft via a gear stage, for example, a spur gear and / or planetary gear stage. The gear stage can be a reduction stage. The drive motor can be oriented transversely to the input shaft and, for example, mechanically connected to the input shaft via a gear stage in the form of a bevel gear stage.The drive motor can be aligned parallel to the input shaft and offset from it. It can be mechanically connected to the input shaft, for example, via a gear stage in the form of a spur gear, a belt, and / or a chain. Alternatively, the drive motor can be mechanically connected to the input shaft via a gearbox, which is designed to connect the motor shaft and the input shaft via a switchable first gear ratio and at least one different second gear ratio. Freewheels can also be provided between the motor shaft and the input shaft. The drive motor can be, for example, an electric motor, a hydraulic motor, or an internal combustion engine. The transmission comprises a first planetary gear set, a second planetary gear set, a third planetary gear set, a fourth planetary gear set, a first brake, and a second brake. The first and second planetary gear sets can provide the differential function. The third planetary gear set, the fourth planetary gear set, the first brake, and the second brake form a torque distribution device, which is mechanically operatively connected to the first and second planetary gear sets and is designed to control torque distribution to the two output shafts. The torque distribution device is mechanically coupled to the first and second planetary gear sets at the input shaft and the coupling shaft. At least one of the rotating elements of one of these two planetary gear sets can be permanently and rotationally fixed to the input shaft, thus allowing the torque distribution device to be connected there.Each of the rotating elements of these two planetary gear sets can be permanently and rotationally fixed to the coupling shaft, allowing the torque distribution device to be attached here. Such a coupling of the torque distribution device can allow for a simpler arrangement of the planetary gear sets. The coupling can enable different gear ratios for the third and fourth planetary gear sets than other topologies. For example, the rotating elements of the torque distribution device, which can be locked by the first and second brakes, can be easily configured to rotate in different directions at low speeds when driving straight ahead. For instance, selectively applying one of the two brakes can change the torque distribution between the two output shafts. This also allows the relative rotational speed of the two output shafts to be changed. In this way, the transmission can be used for steering or at least to assist steering. The lead from a front axle to a rear axle can also be altered in this way.The torque distribution device is coupled, for example, to the coupling shaft and the first output shaft, for example by a permanently rotationally fixed connection of rotating elements of the third and alternatively or additionally the fourth planetary gear set. The respective axes of rotation of the planetary gear sets can be coaxial with each other. The planetary gear sets can be arranged coaxially with the input shaft and the two output shafts. Each planetary gear set can have at least two rotating elements. One or more of the planetary gear sets can have exactly two rotating elements, in which case another planetary gear set can take over the function of a third rotating element. One or more of the planetary gear sets can have exactly three rotating elements. A planetary gear set can be free of more than two or three rotating elements. For example, none of the planetary gear sets has more than three rotating elements. The transmission can be free of additional planetary gear sets. The planetary gear sets can be designed, for example, as plus planetary gear sets or minus planetary gear sets.The planetary gear sets can also be designed as stepped planetary gear sets, for example, as a positive stepped planetary gear set or a negative stepped planetary gear set. A positive planetary gear set has a positive stationary gear ratio, and a negative planetary gear set has a negative stationary gear ratio. The three rotating elements can be, for example, a sun gear, a planet carrier, and a ring gear. The planetary gear sets can also be designed as gear sets with three rotating elements but only two different types of rotating elements, for example, as a positive stepped planetary gear set with two sun gears or two ring gears, each with a planet carrier. All rotating elements of all planetary gear sets can be arranged coaxially with each other. One or more planet gears can be rotatably mounted on the planet carrier. In a negative planetary gear set, the planet gears mesh with the sun gear and the ring gear, for example. In a positive planetary gear set, two sets of planet gears are provided. The planet gears of the first set mesh with the sun gear and, in pairs, with the planet gears of the second set. The first set can be arranged radially inside and the second set radially outside. The planet gears of the second set mesh with the ring gear and, correspondingly, in pairs with the planet gears of the first set. In a planetary gear set with two identical rotating elements, the two identical rotating elements mesh with the planet gears, for example, with different tooth sections. In a stepped planetary gear set, the planet gears can have tooth sections with different effective diameters.For example, a first gear section can mesh with the sun gear and a second gear section with the ring gear. Due to the stepped planetary gear design, the transmission can be radially more compact for the same gear ratio. The rotating elements of a planetary gear set, for instance, share the same axis of rotation. The first and second planetary gear sets can provide both a gear reduction, such as a reduction, and a differential function in a compact design with few components. Furthermore, the gearbox can thus simply have one input shaft and two coaxial output shafts. The gearbox can be free of any planetary gear sets other than those mentioned here. The gearbox can be free of any rotating elements other than those mentioned here. For example, the gearbox has exactly four planetary gear sets, with none of the planetary gear sets having more than three rotating elements. The gearbox can be free of any connections between the respective rotating elements and shafts other than those mentioned here. The transmission features a coupling shaft. A first rotating element of the first planetary gear set is mechanically connected to a first rotating element of the second planetary gear set via the coupling shaft. The first rotating element of the first planetary gear set can be, for example, the first sun gear or the first ring gear. The first rotating element of the second planetary gear set can be, for example, the second sun gear or the second ring gear. The torque distribution device is mechanically connected to the coupling shaft. The coupling shaft can be arranged coaxially with the rotating elements, the input shaft, and the output shafts. The coupling shaft connects the first rotating element of the first planetary gear set to the first rotating element of the second planetary gear set, for example, in a permanently rotationally fixed manner.For example, the coupling shaft is formed integrally with the first rotating element of the first planetary gear set and with the first rotating element of the second planetary gear set. The coupling shaft can be a separate component or be formed integrally by the first rotating element of the first planetary gear set and, alternatively or additionally, by the first rotating element of the second planetary gear set. There can also be an additional mechanical connection for coupling, for example, via a spur gear stage or another planetary gear set. A second rotating element of the first planetary gear set is permanently and non-rotatably connected to the first output shaft. At least a portion of the input power can be output here. A third rotating element of the first planetary gear set is permanently and non-rotatably connected to the input shaft. Torque, and generally a driving force, can be applied to the input shaft by the drive motor. The torque distribution device is connected to the input shaft. A second rotating element of the second planetary gear set is fixed to a stationary component. This stationary component can be a gearbox housing or a vehicle frame. A third rotating element of the second planetary gear set is permanently and non-rotatably connected to the second output shaft. The remaining input power, not output at the first output shaft, can be output here.This allows for a simple and compact, even distribution of torque between the two output shafts. The first and second planetary gear sets can be arranged axially side by side or in the same axial gear set plane. The first and second planetary gear sets can be arranged radially stacked. In this case, either the first or the second planetary gear set can be arranged radially outward. In radial stacking, for example, the radially outer planetary gear set can have a sun gear as its first rotating element, and the radially inner planetary gear set can have a ring gear as its first rotating element. These can form a single, integral sun gear. The third and fourth planetary gear sets can be arranged axially side by side, for example, next to or between the first and second planetary gear sets. The planet gears of the first and second planetary gear sets can be, for example, stepless. The first and / or second planetary gear set can be, for example, designed as a negative planetary gear set.The first rotating element of each planetary gear set can then be designed, for example, as a sun gear, the second rotating element as a planet carrier, and the third rotating element as a ring gear. The first and / or second planetary gear set can also be designed, for example, as a plus planetary gear set. In this case, the first rotating element of each planetary gear set can be designed, for example, as a sun gear, the second rotating element as a ring gear, and the third rotating element as a planet carrier. At least one rotating element of the third and, alternatively or additionally, of the fourth planetary gear set is, for example, permanently and rotationally fixed to the coupling shaft. At least one other rotating element of the third and, alternatively or additionally, of the fourth planetary gear set is, for example, permanently and rotationally fixed to the input shaft. For example, a third rotating element of the fourth planetary gear set is permanently and rotationally fixed to the input shaft, a second rotating element of the fourth planetary gear set is permanently and rotationally fixed to the coupling shaft, and at least one rotating element of the third planetary gear set is permanently and rotationally fixed to either the input shaft or the coupling shaft. At least one other rotating element of the third planetary gear set, like its first rotating element, can be locked to the stationary component, for example, by means of the first brake.At least one other rotating element of the fourth planetary gear set, like its first rotating element, can be locked to the stationary component, for example, by means of the second brake. The rotating elements of the third and fourth planetary gear sets with the same numbering, such as the second rotating element of these two planetary gear sets, can be of the same design. For example, the second rotating element of the third planetary gear set is also designed as a planet carrier if the second rotating element of the fourth planetary gear set is designed as a planet carrier. The first and second brakes can each be designed, for example, as friction-based or positive-locking brakes. In one embodiment, the brakes can be designed as multi-disc brakes. Depending on the degree of actuation, the associated rotating elements can be decelerated, for example, rather than being completely locked. The stationary gear ratio of the planetary gear sets can be selected, for example, such that the two rotating elements of the torque distribution device, which can be locked by the two brakes, rotate in opposite directions when driving straight ahead and have a very low rotational speed. If two elements are mechanically connected, a movement of one element causes a reaction in the other. Additional components, such as one or more gear stages, may be present between the elements. A permanently rotationally fixed connection between two elements is understood to be a connection in which the two elements are essentially rigidly coupled to each other in all intended states, so that they rotate at the same speed. This also includes a friction-fit connection, in which slippage may occur. Permanently rotationally fixed elements can, for example, exist as permanently rotationally fixed individual components or as a single unit. A switchable connection can enable torque transmission between two elements in one state and essentially interrupt this torque transmission in another state.For this purpose, a suitable switching element can be provided between the two elements, via which a rotationally fixed connection between the elements can be established. In one embodiment of the transmission, the first rotating element of the first planetary gear set is configured as the first ring gear. The second rotating element of the first planetary gear set can be configured as the first planet carrier. The third rotating element of the first planetary gear set can be configured as the first sun gear. The first rotating element of the second planetary gear set can be configured as the second sun gear. The second rotating element of the second planetary gear set can be configured as the second planet carrier. The third rotating element of the second planetary gear set can be configured as the second ring gear. In this case, the first and second planetary gear sets can, for example, be configured as negative planetary gear sets. In one embodiment of the transmission, the first rotating element of the first planetary gear set is configured as the first sun gear. The second rotating element of the first planetary gear set can be configured as the first ring gear. The third rotating element of the first planetary gear set can be configured as the first planet carrier. The first rotating element of the second planetary gear set can be configured as the second sun gear. The second rotating element of the second planetary gear set can be configured as the second ring gear. The third rotating element of the second planetary gear set can be configured as the second planet carrier. In this case, the first and second planetary gear sets can, for example, also be configured as negative planetary gear sets. In one embodiment of the transmission, the first rotating element of the first planetary gear set is configured as the first sun gear. The second rotating element of the first planetary gear set can be configured as the first planet carrier. The third rotating element of the first planetary gear set can be configured as the first ring gear. The first rotating element of the second planetary gear set can be configured as the second sun gear. The second rotating element of the second planetary gear set can be configured as the second planet carrier. The third rotating element of the second planetary gear set can be configured as the second ring gear. In this case, the first and second planetary gear sets can, for example, also be configured as negative planetary gear sets. In one embodiment of the transmission, the first rotating element of the first planetary gear set is configured as the first sun gear. The second rotating element of the first planetary gear set can be configured as the first ring gear. The third rotating element of the first planetary gear set can be configured as the first planet carrier. The first rotating element of the second planetary gear set can be configured as the second ring gear. The second rotating element of the second planetary gear set can be configured as the second sun gear. The third rotating element of the second planetary gear set can be configured as the second planet carrier. In this case, the first and second planetary gear sets can, for example, also be configured as negative planetary gear sets. In one embodiment of the transmission, a third rotating element of the fourth planetary gear set is permanently and non-rotatably connected to the input shaft. A second rotating element of the fourth planetary gear set can be permanently and non-rotatably connected to the coupling shaft. A first rotating element of the fourth planetary gear set can be locked to the stationary component by means of the second brake. A second rotating element of the third planetary gear set can be permanently and non-rotatably connected to the coupling shaft. A first rotating element of the third planetary gear set can be locked to the stationary component by means of the first brake. The third rotating element of the third planetary gear set can be permanently and non-rotatably connected to the input shaft. Alternatively, the third planetary gear set can also be free of the third rotating element and only have the second and first rotating elements. The numbering of rotating elements can serve to assign them to a planetary gear set. For example, designating a component as the second sun gear can uniquely identify it as belonging to the second planetary gear set. Generally, the numbering, and alternatively or additionally, the designation of components according to their assembly group can facilitate this assignment. A planetary gear set with a second sun gear, for instance, does not necessarily have a first sun gear. Similarly, the numbering of rotating elements can serve for unambiguous assignment. For example, a planetary gear set might not have a first rotating element, even though it has a second and third rotating element. In one embodiment of the transmission, a third rotating element of the fourth planetary gear set is permanently and non-rotatably connected to the coupling shaft. A second rotating element of the fourth planetary gear set can be permanently and non-rotatably connected to the input shaft. A first rotating element of the fourth planetary gear set can be locked to the stationary component by means of the second brake. A second rotating element of the third planetary gear set can be permanently and non-rotatably connected to the input shaft. A first rotating element of the third planetary gear set can be locked to the stationary component by means of the first brake. The third rotating element of the third planetary gear set can be permanently and non-rotatably connected to the coupling shaft. Alternatively, the third planetary gear set can also be free of the third rotating element and only have the second and first rotating elements. In one embodiment of the transmission, the third planetary gear set is free of a third rotating element. The third planetary gear set then has, for example, exactly two rotating elements, which are referred to here as the second and first rotating elements of the third planetary gear set. The respective planet gears of the third planetary gear set can be permanently and rotationally fixed in pairs to the respective planet gears of the fourth planetary gear set. If the third planetary gear set, in its unreduced form with three rotating elements, has two sets of planet gears that mesh with each other and with the ring gear or sun gear in pairs, the set of planet gears that meshes with the rotating element that is omitted can also be omitted. Thus, the planet gears that would otherwise mesh with the third rotating element can also be omitted.The remaining planet gears can be permanently and rotationally fixedly connected to those planet gears of the fourth planet gear set that mesh with the same rotating element as the remaining planet gears of the third planet gear set. For example, the third planet gear set may only have the third planet carrier and the third ring gear, with each third planet gear meshing only with the third ring gear. The fourth planetary gear set, for example, has a radially inner set and a radially outer set of fourth planet gears. The radially inner set of fourth planet gears then meshes, for example, with the fourth sun gear and in pairs with the radially outer set of fourth planet gears. The radially outer set of fourth planet gears then meshes, for example, with the fourth ring gear and in pairs with the radially inner set of fourth planet gears. The third planet gears are then, for example, only permanently and rotationally fixed in pairs to the fourth planet gears of the radially outer set of fourth planet gears. If the fourth planetary gear set is designed as a stepped planetary gear set, its planet gears can, for example, form a third toothed section, which constitutes the third planet gear. This allows the third planetary gear set to provide a gear ratio similar to that of a stepped planetary gear set.The third rotating element of the fourth planetary gear set can, for example, take over the function of the third rotating element omitted in the simplified third planetary gear set. This can result in a simplified design of the third planetary gear set, in which one rotating element can be omitted. The transmission thus has a particularly small number of parts. Alternatively, the third planetary gear set has three rotating elements, and the first rotating element of the third planetary gear set can then be permanently and non-rotatably connected to the input shaft, the coupling shaft, or one of the two output shafts. In this case, the transmission can, for example, be free of a permanent, non-rotatable connection between the third planetary gears and the fourth planetary gears. In one embodiment of the transmission, two of the rotating elements of the fourth planetary gear set are designed as ring gears or sun gears. If the fourth planetary gear set has two ring gears, it can then, for example, be free of a sun gear. In one embodiment of the transmission, the first rotating element of the third planetary gear set is configured as a third ring gear. The second rotating element of the third planetary gear set can be configured as a third planet carrier. The third rotating element of the third planetary gear set, if present, can be configured as a third sun gear or another third ring gear. The first rotating element of the fourth planetary gear set can be configured as a fourth ring gear. The second rotating element of the fourth planetary gear set can be configured as a fourth planet carrier. The third rotating element of the fourth planetary gear set, if present, can be configured as a fourth sun gear or another fourth ring gear. In one embodiment of the transmission, the first rotating element of the third planetary gear set is configured as a third sun gear. The second rotating element of the third planetary gear set can be configured as a third planet carrier. The third rotating element of the third planetary gear set, if present, can be configured as a third ring gear or as another third sun gear. The first rotating element of the fourth planetary gear set can be configured as a fourth sun gear. The second rotating element of the fourth planetary gear set can be configured as a fourth planet carrier. The third rotating element of the fourth planetary gear set, if present, can be configured as a fourth sun gear or another fourth ring gear. In one embodiment of the transmission, the first rotating element of the third planetary gear set is configured as a third sun gear. The second rotating element of the third planetary gear set can be configured as a third ring gear. The third rotating element of the first planetary gear set, if present, can be configured as a third ring gear or as another third sun gear. The first rotating element of the fourth planetary gear set can be configured as a fourth sun gear. The second rotating element of the fourth planetary gear set can be configured as a fourth ring gear. The third rotating element of the fourth planetary gear set, if present, can be configured as a fourth planet carrier or another fourth sun gear. In one embodiment of the transmission, the first rotating element of the third planetary gear set is configured as a third ring gear. The second rotating element of the third planetary gear set can be configured as a third sun gear. The third rotating element of the third planetary gear set, if present, can be configured as a third planet carrier or as another third ring gear. The first rotating element of the fourth planetary gear set can be configured as a fourth ring gear. The second rotating element of the fourth planetary gear set can be configured as a fourth sun gear. The third rotating element of the fourth planetary gear set, if present, can be configured as a fourth planet carrier or another fourth sun gear. A second aspect concerns a drive train with a drive motor and a transmission as described in the first aspect. The respective advantages and further characteristics can be found in the description of the first aspect, whereby embodiments of the first aspect also form embodiments of the second aspect and vice versa. The drive train can, for example, have output elements, such as vehicle wheels, which are coupled to the output shafts of the transmission. For example, an output element can be permanently rotationally fixed or mechanically operatively connected to each output shaft, for example via a spur gear or a planetary gear set. A gear stage can be provided between the drive motor and the transmission, which can be designed according to the descriptions in connection with the first aspect. A third aspect concerns a vehicle with a drive train according to the second aspect or a transmission according to the first aspect.The respective advantages and further features can be found in the description of the first and second aspects, whereby elaborations of the first and second aspects also form elaborations of the third aspect and vice versa. Brief description of the characters Fig. 1 schematically illustrates a motor vehicle with a drivetrain comprising a drive motor and a transmission. Fig. 2 schematically illustrates a generic design of the transmission, which includes a torque distribution device. Fig. 3 schematically illustrates a first embodiment of a third planetary gear set and a fourth planetary gear set of the transmission, which form parts of the torque distribution device. Fig. 4 schematically illustrates a variant of the first embodiment of the torque distribution device in which the number of rotating elements is reduced. Fig. 5 schematically illustrates a second embodiment of the torque distribution device. Fig. 6 schematically illustrates a variant of the second embodiment of the torque distribution device in which the number of rotating elements is reduced.Figure 7 schematically illustrates a third embodiment of the torque distribution device. Figure 8 schematically illustrates a variant of the third embodiment of the torque distribution device in which the number of rotating elements is reduced. Figure 9 schematically illustrates a first embodiment of the transmission. Figure 10 schematically illustrates a second embodiment of the transmission. Figure 11 schematically illustrates a third embodiment of the transmission. Figure 12 schematically illustrates a fourth embodiment of the transmission. Figure 13 schematically illustrates a fifth embodiment of the transmission. Figure 14 schematically illustrates a sixth embodiment of the transmission. Figure 15 schematically illustrates a seventh embodiment of the transmission. Figure 16 schematically illustrates an eighth embodiment of the transmission. Figure 17 schematically illustrates a ninth embodiment of the transmission.Figure 18 schematically illustrates a tenth embodiment of the transmission. Figure 19 schematically illustrates an eleventh embodiment of the transmission. Figure 20 schematically illustrates a twelfth embodiment of the transmission. Figure 21 schematically illustrates a thirteenth embodiment of the transmission. Figure 22 schematically illustrates a first coupling method of the drive motor with the transmission. Figure 23 schematically illustrates a second coupling method of the drive motor with the transmission. Figure 24 schematically illustrates a third coupling method of the drive motor with the transmission. Figure 25 schematically illustrates a fourth coupling method of the drive motor with the transmission. Figure 26 schematically illustrates a fifth coupling method of the drive motor with the transmission. Detailed description of embodiments Fig. 1 schematically illustrates a motor vehicle 10 with a drivetrain and four wheels 12. The drivetrain includes a drive motor 14 designed as an electric machine, which is connected to the two rear wheels 12 via a transmission 16 to transmit driving force. The transmission 16 is a differential transmission. Alternatively or additionally, the drivetrain can also drive the front wheels 12, in which case a drive motor 14 and a transmission 16 can be arranged accordingly. Details of the drivetrain and, in particular, the transmission 16 are illustrated in the following figures. The transmission 16 has an input shaft 18, which is connected to a motor shaft 20 of the drive motor 14. Furthermore, the transmission 16 has a first output shaft 22 and a second output shaft 24, which are arranged coaxially with each other and coaxially with the input shaft 18. The transmission 16 forms a torque distribution device 17, which is designed to control the torque distribution to the two output shafts 22, 24. In addition to its differential function, the transmission 16 can thus further support cornering and provide, or at least support, steering for the motor vehicle 10. A generic design of the transmission 16 and the torque distribution device 17 is illustrated in Fig. 2. The transmission 16 has a first planetary gear set 30 and a second planetary gear set 40. The first planetary gear set 30 and the second planetary gear set 40 provide the differential function. A first rotating element of the first planetary gear set 30 is mechanically coupled to a first rotating element of the second planetary gear set 40 via a coupling shaft 70 of the transmission, here in a permanently rotationally fixed manner. A second rotating element of the first planetary gear set 30 is permanently rotationally fixed to the first output shaft 22. A third rotating element of the first planetary gear set 30 is permanently rotationally fixed to the input shaft 18. A second rotating element of the second planetary gear set 40 is fixed to a stationary component, here by a permanently rotationally fixed connection to a transmission housing.A third rotating element of the second planetary gear set 40 is permanently and rotationally fixed to the second output shaft 24. The transmission 16 further comprises a third planetary gear set 50, a fourth planetary gear set 60, a first brake 72, and a second brake 74, which together form the torque distribution device 17. One of the rotating elements of the third planetary gear set 50 and the fourth planetary gear set 60 is permanently and rotationally fixed to the coupling shaft 70. Another rotating element of the third planetary gear set 50 and the fourth planetary gear set 60 is permanently and rotationally fixed to the input shaft 18. Yet another rotating element of the third planetary gear set 50 can be locked to the stationary component by means of the first brake 72 and thus also braked. Yet another rotating element of the fourth planetary gear set 60 can be locked to the stationary component by means of the second brake 74 and thus also braked.In some embodiments with a reduced number of rotating elements, one of the rotating elements that cannot be locked with one of the two brakes 72, 74 is omitted, for example, from the third planetary gear set 50. The torque distribution device 17 is thus coupled to the first planetary gear set 30 and the second planetary gear set 40 on the input shaft 18 and the coupling shaft 70 and is configured to control a torque distribution to the two output shafts 22, 24. Fig. 3 schematically illustrates a first embodiment of the torque distribution device 17. The third planetary gear set 50 has a third sun gear 52, which is permanently and non-rotatably connected to the input shaft 18. The third planetary gear set 50 has a third planet carrier 54, which is permanently and non-rotatably connected to the coupling shaft 70. The third planetary gear set 50 has a third ring gear 56, which can be locked to the stationary component by means of the first brake 72. The fourth planetary gear set 60 has a fourth sun gear 62, which is permanently and non-rotatably connected to the input shaft 18. The fourth planetary gear set 60 has a fourth planet carrier 64, which is permanently and non-rotatably connected to the coupling shaft 70. The fourth planetary gear set 60 has a fourth ring gear 66, which can be locked to the stationary component by means of the second brake 74.On the third planet carrier 54, a set of third planet gears 58 are rotatably mounted, which mesh with the third sun gear 52 and the third ring gear 56. On the fourth planet carrier 64, a set of fourth planet gears 68 are rotatably mounted, which mesh with the fourth sun gear 62 and the fourth ring gear 66. The third planet gear set 50 and the fourth planet gear set 60 are designed as negative planet gear sets. In the first embodiment, the third planet gear set 50 and the fourth planet gear set 60 thus have exactly three rotating elements. Fig. 4 schematically illustrates a variant of the first embodiment of the torque distribution device 17 from Fig. 3, in which the number of rotating elements is reduced. The third planetary gear set 50 no longer has a third sun gear 52 and therefore only two rotating elements. Instead, the third planetary gears 58 are permanently and rotationally fixed in pairs to the fourth planetary gears 68, thus forming a stepped planetary gear set. Fig. 5 schematically illustrates a second embodiment of the torque distribution device 17. Compared to the first embodiment shown in Fig. 3, the third planetary gear set 50 and the fourth planetary gear set 60 differ in that they are designed as plus planetary gear sets. A set of radially inner third planetary gears 58 and a set of radially outer third planetary gears 58 are rotatably mounted on the third planet carrier 54, meshing in pairs. The set of radially inner third planetary gears 58 also meshes with the third sun gear 52. The set of radially outer third planetary gears 58 also meshes with the third ring gear 56. A set of radially inner fourth planetary gears 68 and a set of radially outer fourth planetary gears 68 are rotatably mounted on the fourth planet carrier 60, meshing in pairs.The set of radially inner fourth planet gears 58 also meshes with the fourth sun gear 62. The set of radially outer fourth planet gears 68 also meshes with the fourth ring gear 66. As in the embodiment of Fig. 3, the two sun gears 52, 62 are permanently and rotationally fixed to the input shaft 18, the two planet carriers 54, 64 are permanently and rotationally fixed to the coupling shaft 70, and the two ring gears 56, 66 can each be locked to the stationary component by means of a brake 72, 74. Fig. 6 schematically illustrates a variant of the second embodiment of the torque distribution device 17 from Fig. 5, in which the number of rotating elements is reduced. The third planetary gear set 50 no longer has a third sun gear 52 and thus only two rotating elements. Furthermore, the set of radially inner third planetary gears 58, which mesh with the third sun gear 52 in the unreduced design according to Fig. 5, is omitted. Instead, the third planetary gears 58, which correspond to the set of radially outer third planetary gears of the unreduced design, are permanently and rotationally fixed in pairs to the fourth planetary gears 68 of the radially outer set of fourth planetary gears 68 in order to form a stepped planetary gear set. Fig. 7 schematically illustrates a third embodiment of the torque distribution device 17. Compared to the first embodiment of Fig. 3, the third planetary gear set 50 and the fourth planetary gear set 60 differ in that they are designed as negative stepped planetary gear sets. In other variants, the third planetary gear set 50 and the fourth planetary gear set 60 are also designed as positive stepped planetary gear sets. The third planetary gears 58 have a first toothed section and a second toothed section with different effective diameters. The first toothed section of the third planetary gears 58 meshes with the third sun gear 52. The second toothed section of the third planetary gears 58 meshes with the third ring gear 56. The fourth planetary gears 68 also have a first toothed section and a second toothed section with different effective diameters.The first tooth section of the fourth planet gears 68 meshes with the fourth sun gear 62. The second tooth section of the fourth planet gears 68 meshes with the fourth ring gear 66. Furthermore, the connection to the coupling shaft 70 and the input shaft 18 is reversed. Accordingly, the two sun gears 52, 62 are permanently and rotationally fixed to the coupling shaft 70, the two planet carriers 54, 64 are permanently and rotationally fixed to the input shaft 18, and the two ring gears 56, 66 can each be locked to the stationary component by means of a brake 72, 74. Fig. 8 schematically illustrates a variant of the third embodiment of the torque distribution device 17 from Fig. 7, in which the number of rotating elements is reduced. The third planetary gear set 50 no longer has a third sun gear 52 and thus only two rotating elements. Furthermore, the first toothed section of the third planetary gears 58, which meshes with the third sun gear 52 in the unreduced design according to Fig. 7, is omitted. Instead, the third planetary gears 58, which correspond to the second toothed section of the third planetary gears 58 in the unreduced design, are permanently and rotationally fixed in pairs to the fourth planetary gears 68. In one embodiment, the torque distribution device 17 has only one set of planetary gears, each formed in one piece, which has a first, second, and third toothed section. The first toothed section meshes with the fourth sun gear 62.The second gear section meshes with the fourth ring gear 66. The third gear section meshes with the third ring gear 56. At least the effective diameters of the second and third gear sections differ. Fig. 9 illustrates a first embodiment of the transmission 16. The first planetary gear set 30 and the second planetary gear set 40 are stacked radially at the same axial height, with the second planetary gear set 40 arranged radially outside the first planetary gear set 30. In other embodiments, the first planetary gear set 30 and the second planetary gear set 40 are arranged axially side by side. The first and second planetary gear sets 30, 40 are designed as negative planetary gear sets with three rotating elements. A design with the first planetary gear set 30 and, alternatively or additionally, the second planetary gear set 40 as positive planetary gear sets is also possible. A first sun gear 32 forms the input shaft 18. A first planet carrier 34 is permanently and rotationally fixed to the first output shaft 22. A first ring gear 36 is permanently and rotationally fixed to the second sun gear 42. The first ring gear 36 and the second sun gear 42 together form a sun gear. The second planet carrier 44 is fixed to the stationary component. The second ring gear 46 is permanently and rotationally fixed to the second output shaft 24. A set of first planet gears 38 are rotatably mounted on the first planet carrier 34 and mesh with the first sun gear 32 and the first ring gear 36. On the second planet carrier 44 a set of second planet gears 48 are rotatably mounted, which mesh with the second sun gear 42 and the second ring gear 46. In the first embodiment, the third and fourth planetary gear sets 50, 60 are designed as a double plus-step planetary gear set. The third and fourth planetary gear sets 50, 60 are arranged axially adjacent to and next to the first and second planetary gear sets 20, 30. The third planetary gear set 50 has only two rotating elements. A third planet carrier 54 is permanently and rotationally fixed to the input shaft 18. A third ring gear 56 can be locked to the stationary component by means of the first brake 72. The fourth planetary gear set 60 has three rotating elements, two of which are identical, here as ring gears. A fourth ring gear 66 can be locked to the stationary component by means of the second brake 74. A fourth planet carrier 64 is permanently and rotationally fixed to the input shaft 18.A further fourth ring gear 67 is permanently and rotationally fixedly connected to the coupling shaft 70, which is formed here by the sun ring gear described above. Third planet gears 58 are rotatably mounted on the third planet carrier 54 and mesh only with the third ring gear 56. Fourth planet gears 68 are rotatably mounted on the fourth planet carrier 64. The fourth planet gears 68 have two toothed sections, one of which meshes with the fourth ring gear 66 and the other with the fourth ring gear 67. The third planet gears 58 and the fourth planet gears 68 are permanently and rotationally fixed to each other in pairs. The third planet gears 58 and the fourth planet gears 68 can also be configured as planet gears with three toothed sections. Fig. 10 illustrates a second embodiment of the transmission 16, which differs from the first embodiment according to Fig. 9 only in the design of the torque distribution device 17. Only the differences are described here. The fourth planetary gear set 60 has a fourth sun gear 62 and another fourth sun gear 63. The fourth ring gear 66 and the other fourth ring gear 67 are omitted. The fourth sun gear 62 is permanently and rotationally fixed to the coupling shaft 70, and the other fourth sun gear 63 can be locked to the stationary component by means of the second brake 74. In the third planetary gear set 50, the third ring gear 56 is omitted, and instead, the third sun gear 52 is provided, which can be locked to the stationary component by means of the first brake 72. The third and fourth planet gears 58, 68 mesh accordingly with the sun gears 52, 62, 63. Fig. 11 illustrates a third embodiment of the transmission 16. The first planetary gear set 30 and the second planetary gear set 40 are designed as negative planetary gear sets and are arranged axially side by side. The third planetary gear set 50 and the fourth planetary gear set 60 are designed as positive planetary gear sets and are arranged between the first planetary gear set 30 and the second planetary gear set 40. The first sun gear 32 and the second sun gear 42 are permanently and rotationally fixed to each other via the coupling shaft 70. The first planet carrier 34 is permanently and rotationally fixed to the first output shaft 22. The first ring gear 36 is permanently and rotationally fixed to the input shaft 18. The second planet carrier 44 is fixed to the stationary component. The second ring gear 46 is permanently and rotationally fixed to the second output shaft 24. The third sun gear 52 and the fourth sun gear 62 are permanently and rotationally fixed to the input shaft 18. The third planet carrier 54 and the fourth planet carrier 64 are permanently and rotationally fixed to the coupling shaft 70. The third ring gear 56 can be locked to the stationary component by means of the first brake 72. The fourth ring gear 66 can be locked to the stationary component by means of the second brake 74. The third planet gear set 50 comprises a set of radially inner third planet gears 58, which are rotatably mounted on the third planet carrier 54 and mesh with the third sun gear 52. The third planet gear set 50 comprises a set of radially outer third planet gears 58, which are rotatably mounted on the third planet carrier 54 and mesh with the third ring gear 56. Furthermore, the radially inner third planet gears 58 mesh in pairs with the radially outer third planet gears 58. The fourth planetary gear set 60 comprises a set of radially inner fourth planet gears 68, which are rotatably mounted on the fourth planet carrier 64 and mesh with the fourth sun gear 62. The fourth planetary gear set 60 comprises a set of radially outer fourth planet gears 68, which are rotatably mounted on the fourth planet carrier 64 and mesh with the fourth ring gear 66. Furthermore, the radially inner fourth planet gears 68 mesh in pairs with the radially outer fourth planet gears 68. Fig. 12 illustrates a fourth embodiment of the transmission 16, which is a modification of the first embodiment according to Fig. 11 with a reduced number of rotating elements. Accordingly, the torque distribution device 17 is designed as in the variant of the second embodiment according to Fig. 6. The third sun gear 52 and the radially inner third planet gears 58 are therefore omitted. The third planet gears 58 and the radially outer fourth planet gears 68 are each permanently and rotationally fixed to one another in pairs. In one embodiment, the paired third and radially outer fourth planet gears 58, 68 are formed integrally as a stepped planet gear with two different toothing sections. A first toothing section meshes only with the third ring gear 56, and a second toothing section meshes with the radially inner fourth planet gears 68 and the fourth ring gear 66. Fig. 13 illustrates a fifth embodiment of the transmission 16, which differs from the third embodiment according to Fig. 11 only in the coupling of the torque distribution device 17 to the first planetary gear set 30 and the second planetary gear set 40. Only the differences are described here. In the fifth embodiment, the third planet carrier 54 and the fourth planet carrier 64 are permanently and rotationally fixed to the input shaft 18 and thus to the first ring gear 36 of the first planetary gear set 30. Correspondingly, the third sun gear 52 and the fourth sun gear 62 are now permanently and rotationally fixed to the coupling shaft 70 and thus to the first sun gear 32 and the second sun gear 42 of the first and second planetary gear sets 30, 40. In addition, the axial order of the third planetary gear set 50 and the fourth planetary gear set 60 is reversed in the fifth embodiment compared to the third embodiment. Fig. 14 illustrates a sixth embodiment of the transmission 16, which differs from the fourth embodiment according to Fig. 12 only in the coupling of the torque distribution device 17 to the first planetary gear set 30 and the second planetary gear set 40. This now corresponds to the design of the fifth embodiment according to Fig. 13. The sixth embodiment thus represents a modification of the fifth embodiment according to Fig. 13 with a reduced number of rotating elements. The radially inner third planetary gears 58 and the third sun gear 52 are omitted, and the remaining third planetary gears 58 are permanently and rotationally fixed in pairs to the radially outer fourth planetary gears 68. In one embodiment, the paired third and radially outer fourth planetary gears 58, 68 are formed integrally as a stepped planetary gear with two different toothing areas.A first gear section meshes only with the third ring gear 56 and a second gear section meshes with the radially inner fourth planet gears 68 and the fourth ring gear 66. Fig. 15 illustrates a seventh embodiment of the transmission 16. The first planetary gear set 30 and the fourth planetary gear set 40 are designed as negative planetary gear sets and are arranged axially side by side. The third planetary gear set 50 and the fourth planetary gear set 60 are designed as negative planetary gear sets and are arranged between the first planetary gear set 30 and the second planetary gear set 40. The first sun gear 32 and the second sun gear 42 are permanently and rotationally fixed to each other via the coupling shaft 70. The second planet carrier 34 is permanently and rotationally fixed to the input shaft 18. The first ring gear 36 is permanently and rotationally fixed to the first output shaft 22. The second planet carrier 44 is permanently and rotationally fixed to the second output shaft 24. The second ring gear 46 is fixed to the stationary component. The third sun gear 52 can be locked to the stationary component by means of the first brake 72.The third planet carrier 54 is permanently and rotationally fixed to the input shaft 18. The third ring gear 56 is permanently and rotationally fixed to the coupling shaft 70. The fourth sun gear 62 can be locked to the stationary component by means of the second brake 74. The fourth planet carrier 64 is permanently and rotationally fixed to the input shaft 18. The fourth ring gear 66 is permanently and rotationally fixed to the coupling shaft 70. Fig. 16 illustrates an eighth embodiment of the transmission 16, which is a modification of the seventh embodiment according to Fig. 15 with a reduced number of rotating elements. In the eighth embodiment, the third ring gear 56 is omitted compared to the seventh embodiment. Instead, the third planet gears 58 and the fourth planet gears 68 are now permanently and rotationally fixed to each other in pairs. In one embodiment, the planet gears 58 and 68 connected in pairs are each also formed by a stepped planet gear, which has two different toothed sections. One of the toothed sections meshes with the third sun gear 52, and the other meshes with the fourth sun gear 62 and the fourth ring gear 66. Fig. 17 illustrates a ninth embodiment of the transmission 16, in which, compared to the seventh embodiment according to Fig. 15, only the torque distribution device 17 is modified. Only the differences are explained. The third planetary gear set 50 and the fourth planetary gear set 60 are now designed as plus planetary gear sets. The third planetary gear set 50 each has a set of radially inner and radially outer third planet gears 58, which are rotatably mounted on the third planet carrier 54 and mesh as in the third embodiment according to Fig. 11. The fourth planetary gear set 60 each has a set of radially inner and radially outer fourth planet gears 68, which are rotatably mounted on the fourth planet carrier 64 and mesh as in the third embodiment according to Fig. 11. The third sun gear 52 can be locked to the stationary component by means of the first brake 72.The third planet carrier 54 is permanently and rotationally fixed to the coupling shaft 70. The third ring gear 56 is permanently and rotationally fixed to the input shaft 18. The fourth sun gear 62 can be locked to the stationary component by means of the second brake 74. The fourth planet carrier 64 is permanently and rotationally fixed to the coupling shaft 70. The fourth ring gear 66 is permanently and rotationally fixed to the input shaft 18. Fig. 18 illustrates a tenth embodiment of the transmission 16, which is a modification of the ninth embodiment according to Fig. 17 with a reduced number of rotating elements. The third ring gear 56 and the radially outer third planet gears 58 are omitted. The third planet gears 58 and the radially inner fourth planet gears 68 are each permanently and rotationally fixed to one another in pairs. In one embodiment, the paired third and radially inner fourth planet gears 58, 68 are formed integrally as a stepped planet gear with two different toothing sections. A first toothing section meshes only with the third sun gear 52, and a second toothing section meshes with the radially outer fourth planet gears 68 and the fourth sun gear 62. Fig. 19 illustrates an eleventh embodiment of the transmission 16, in which, compared to the seventh embodiment according to Fig. 15, only the torque distribution device 17 is modified. The third planetary gear set 50 and the fourth planetary gear set 60 form a double negative stepped planetary gear set. The design is similar to that of the double positive stepped planetary gear set in Fig. 9, except that in the fourth planetary gear set 60, all three rotating elements are designed differently. The third and fourth planetary gear sets 50, 60 are arranged axially next to each other and between the first and second planetary gear sets 30, 40. The third planetary gear set 50 has only two rotating elements. A third planet carrier 54 is permanently and rotationally fixed to the input shaft 18. A third ring gear 56 can be locked to the stationary component by means of the first brake 72. The fourth planetary gear set 60 has three rotating elements.A fourth sun gear 62 is permanently and rotationally fixed to the coupling shaft 70. A fourth planet carrier 64 is permanently and rotationally fixed to the input shaft 18. A fourth ring gear 66 can be locked to the stationary component by means of the second brake 74. Third planet gears 58 are rotatably mounted on the third planet carrier 54 and mesh only with the third ring gear 56. Fourth planet gears 68 are rotatably mounted on the fourth planet carrier 64. The fourth planet gears 68 have two toothed sections, one of which meshes with the fourth ring gear 66 and the other with the fourth sun gear 62. The third planet gears 58 and the fourth planet gears 68 are permanently and rotationally fixed to each other in pairs. The third planet gears 58 and the fourth planet gears 68 can also be formed by planet gears with three toothed sections. Fig. 20 illustrates a twelfth embodiment of the transmission 16. The first planetary gear set 30 and the second planetary gear set 40 are arranged in the same axial gear set plane and radially stacked, with the first planetary gear set 30 arranged radially outside the second planetary gear set 40. The third planetary gear set 50 and the fourth planetary gear set 60 are arranged axially next to the first and second planetary gear sets 30, 40. In other embodiments, the first planetary gear set 30 and the second planetary gear set 40 are arranged axially side by side. The first and second planetary gear sets 30, 40 are designed as negative planetary gear sets with three rotating elements. A design with the first planetary gear set 30 and, alternatively or additionally, the second planetary gear set 40 as positive planetary gear sets is also possible. The first ring gear 36 is permanently and rotationally fixed to the first output shaft 22.The first planet carrier 34 is permanently and rotationally fixed to the input shaft 18. The first sun gear 32 is permanently and rotationally fixed to the second ring gear 46, forming the coupling shaft 70. In one embodiment, the first sun gear 32 and the second ring gear 46 form a sun gear that functions as the coupling shaft 70. The second planet carrier 44 is permanently and rotationally fixed to the second output shaft 24. The second sun gear 42 is fixed to the stationary component. The third sun gear 52 can be fixed to the stationary component by means of the first brake 72. The third planet carrier 54 is permanently and rotationally fixed to the input shaft 18. The third ring gear 56 is permanently and rotationally fixed to the coupling shaft 70. The fourth sun gear 62 can be fixed to the stationary component by means of the second brake 74. The fourth planet carrier 64 is permanently and rotationally fixed to the input shaft 18.The fourth ring gear 66 is permanently and rotationally fixed to the coupling shaft 70. Fig. 21 illustrates a thirteenth embodiment of the transmission 16, which is a modification of the twelfth embodiment according to Fig. 20 with a reduced number of rotating elements. In the thirteenth embodiment, the third ring gear 56 is omitted, and the third planet gear set 50 has only two rotating elements. Instead, the third planet gears 58 are permanently and rotationally fixed in pairs to the fourth planet gears 68. In one embodiment, the planet gears connected in pairs are also each formed by a stepped planet gear, which has two different tooth sections. One of the tooth sections meshes with the third sun gear 52, and the other meshes with the fourth sun gear 62 and the fourth ring gear 66. Fig. 22 illustrates a first coupling method of the drive motor 14 with the input shaft 18 of the gearbox 16. The motor shaft 20 of the drive motor 14 is permanently and rotationally fixed to the input shaft 18. The motor shaft 20, and thus also the drive motor 14, are arranged coaxially with the input shaft 18. The input shaft 18 and the motor shaft 20 are positioned radially outside the output shafts 22 and 24. Fig. 23 illustrates a second coupling method for the drive motor 14 with the input shaft 18 of the gearbox 16. The motor shaft 20 of the drive motor 14 is mechanically connected to the input shaft 18 via a fifth planetary gear set 80 and a sixth planetary gear set 90, which are designed as negative planetary gear sets. A fifth sun gear 82 is permanently and rotationally fixed to the motor shaft 20. A fifth planet carrier 84, on which fifth planet gears 88 are rotatably mounted, is permanently and rotationally fixed to a sixth sun gear 92. A fifth ring gear 86 is fixed to the stationary component. A sixth planet carrier 94, on which sixth planet gears 98 are rotatably mounted, is permanently and rotationally fixed to the input shaft 18. A sixth ring gear 96 is fixed to the stationary component. The motor shaft 20 and thus also the drive motor 14 are arranged coaxially with the input shaft 18.The input shaft 18 and the motor shaft 20 are arranged radially outside the output shafts 22, 24. Fig. 24 illustrates a third coupling method for the drive motor 14 with the input shaft 18 of the gearbox 16. The motor shaft 20 of the drive motor 14 is mechanically connected to the input shaft 18 via a spur gear stage 100. In alternative embodiments, a belt or chain is provided as the mechanical connection between the motor shaft 20 and the input shaft 18, either instead of or in addition to the spur gear stage 100. The motor shaft 20, and thus also the drive motor 14, is arranged axially offset from the input shaft 18. The input shaft 18 is positioned radially outside the output shafts 22 and 24. Fig. 25 illustrates a fourth coupling method for the drive motor 14 with the input shaft 18 of the gearbox 16. A gearbox 110 is provided, comprising a first switching element 112, a second switching element 114, and a planetary gear set 120. A sun gear 122 of the planetary gear set 120 can be locked to the stationary component by means of the first switching element 112. The planetary gear set 120 can be locked by means of the second switching element 114, here by a rotationally fixed connection of a ring gear 126 of the planetary gear set 120 to the sun gear 122 of the planetary gear set 120. The ring gear 126 of the planetary gear set 120 is permanently and rotationally fixed to the motor shaft 20. A planet carrier 124 of the planet gear set 120, on which planet gears 128 are rotatably mounted, is permanently and rotationally fixedly connected to the input shaft 18.The motor shaft 20, and thus also the drive motor 14, are arranged coaxially with the input shaft 18 and radially outside the output shafts 22, 24. The gearbox 110 allows for two different gear ratios to be selected for the operative connection between the motor shaft 20 and the input shaft 18. Fig. 26 illustrates a fifth coupling method for the drive motor 14 with the input shaft 18 of the transmission 16. A gearbox 130 is provided, which differs from the gearbox 110 according to the fourth coupling method shown in Fig. 25. Furthermore, the drive motor 14 is not coaxially, but rather spaced parallel to the input shaft 18. The gearbox 130 has a first spur gear stage 132, a second spur gear stage 134, and a shift element 136. The shift element 136 is designed as a double shift element. The gear ratios of the first spur gear stage 132 and the second spur gear stage 134 are different. The shift element 136 allows the motor shaft 20 to be mechanically connected to the input shaft 18 via either the first spur gear stage 132 or the second spur gear stage 134, thus enabling two different gear ratios. The input shaft 18 is again provided coaxially to and radially outside the output shafts 22, 24. Reference sign 10 Motor vehicle 12 Wheels 14 Drive motor 16 Transmission 17 Torque distribution device 18 Input shaft 20 Motor shaft 22 First output shaft 24 Second output shaft 30 First planetary gear set 32 ​​First sun gear 34 First planet carrier 36 First ring gear 38 First planet gears 40 Second planetary gear set 42 Second sun gear 44 Second planet carrier 46 Second ring gear 48 Second planet gears 50 Third planetary gear set 52 Third sun gear 54 Third planet carrier 56 Third ring gear 58 Third planet gears 60 Fourth planetary gear set 62 Fourth sun gear 64 Fourth planet carrier 66 Fourth ring gear 67 Further fourth ring gear 68 Fourth planet gears 70 Coupling shaft 72,74 Brake 80 Fifth planetary gear set 82 Fifth sun gear 84 Fifth planet carrier 86 Fifth ring gear 88 Fifth planet gears 90 Sixth planetary gear set 92 Sixth sun gear 94 Sixth planet carrier 96 Sixth ring gear 98 Sixth planet gears 100 Spur gear stage 110 Shifting gear 112 First shifting element 114 Second shifting element 120 Planetary gear set 122 Sun gear 124 Planet carrier 126 Ring gear 128 Planet gears 130 Shifting gear 132 First spur gear stage 134 Second spur gear stage 136 Shifting element

Claims

Transmission (16) for a vehicle (10), wherein the transmission (16) comprises an input shaft (18), a first output shaft (22), a second output shaft (24), a coupling shaft (70), a first planetary gear set (30), a second planetary gear set (40), a third planetary gear set (50), a fourth planetary gear set (60), a stationary component, a first brake (72) and a second brake (74), wherein a first rotating element of the first planetary gear set (30) is mechanically connected to a first rotating element of the second planetary gear set (40) via the coupling shaft (70), wherein a second rotating element of the first planetary gear set (30) is permanently and rotationally fixed to the first output shaft (22), wherein a third rotating element of the first planetary gear set (30) is permanently and rotationally fixed to the input shaft (18), and wherein a second rotating element of the second planetary gear set (40) is fixed to the stationary component.wherein a third rotating element of the second planetary gear set (40) is permanently and rotationally fixedly connected to the second output shaft (24), wherein the third planetary gear set (50), the fourth planetary gear set (60), the first brake (72) and the second brake (74) form a torque distribution device (17) which is mechanically operatively connected to the first planetary gear set (30) and the second planetary gear set (40) at the input shaft (18) and the coupling shaft (70) and is configured to control a torque distribution to the two output shafts (22, 24). Gearbox (16) according to claim 1, characterized in that the first rotating element of the first planet gear set (30) is designed as the first ring gear (36), the second rotating element of the first planet gear set (30) is designed as the first planet carrier (34), the third rotating element of the first planet gear set (30) is designed as the first sun gear (32), the first rotating element of the second planet gear set (40) is designed as the second sun gear (42), the second rotating element of the second planet gear set (40) is designed as the second planet carrier (44), and the third rotating element of the second planet gear set (40) is designed as the second ring gear (46). Gearbox (16) according to claim 1, characterized in that the first rotating element of the first planetary gear set (30) is designed as the first sun gear (32), the second rotating element of the first planetary gear set (30) is designed as the first ring gear (36), the third rotating element of the first planetary gear set (30) is designed as the first planet carrier (34), the first rotating element of the second planetary gear set (40) is designed as the second sun gear (42), the second rotating element of the second planetary gear set (40) is designed as the second ring gear (46), and the third rotating element of the second planetary gear set (40) is designed as the second planet carrier (44). Gearbox (16) according to claim 1, characterized in that the first rotating element of the first planet gear set (30) is designed as the first sun gear (32), the second rotating element of the first planet gear set (30) is designed as the first planet carrier (34), the third rotating element of the first planet gear set (30) is designed as the first ring gear (36), the first rotating element of the second planet gear set (40) is designed as the second sun gear (42), the second rotating element of the second planet gear set (40) is designed as the second planet carrier (44), and the third rotating element of the second planet gear set (40) is designed as the second ring gear (46). Gearbox (16) according to claim 1, characterized in that the first rotating element of the first planet gear set (30) is designed as the first sun gear (32), the second rotating element of the first planet gear set (30) is designed as the first ring gear (36), the third rotating element of the first planet gear set (30) is designed as the first planet carrier (34), the first rotating element of the second planet gear set (40) is designed as the second ring gear (46), the second rotating element of the second planet gear set (40) is designed as the second sun gear (42), and the third rotating element of the second planet gear set (40) is designed as the second planet carrier (44). Gearbox (16) according to one of the preceding claims, characterized in that a third rotating element of the fourth planetary gear set (60) is permanently connected to the input shaft (18) in a rotationally fixed manner, a second rotating element of the fourth planetary gear set (60) is permanently connected to the coupling shaft (70) in a rotationally fixed manner, a first rotating element of the fourth planetary gear set (60) can be locked by means of the second brake (72), a second rotating element of the third planetary gear set (50) is permanently connected to the coupling shaft (70) in a rotationally fixed manner, and a first rotating element of the third planetary gear set (50) can be locked by means of the first brake (72). Transmission (16) according to one of claims 1 to 5, characterized in that a third rotating element of the fourth planetary gear set (60) is permanently connected to the coupling shaft (70) in a rotationally fixed manner, a second rotating element of the fourth planetary gear set (60) is permanently connected to the input shaft (18) in a rotationally fixed manner, a first rotating element of the fourth planetary gear set (60) can be locked by means of the second brake (72), a second rotating element of the third planetary gear set (50) is permanently connected to the input shaft (18) in a rotationally fixed manner and a first rotating element of the third planetary gear set (50) can be locked by means of the first brake (72). Gearbox (16) according to claim 6 or 7, characterized in that the third planetary gear set (50) is free of a third rotating element, wherein respective planetary gears (58) of the third planetary gear set (50) are permanently connected in pairs to respective planetary gears (68) of the fourth planetary gear set (60) in a rotationally fixed manner. Gearbox (16) according to claim 8, characterized in that two of the rotating elements of the fourth planetary gear set (60) are designed as ring gears (66) or sun gears (62). Gearbox (16) according to one of claims 6 to 9, characterized in that the first rotating element of the third planet gear set (50) is designed as the first ring gear (56), the second rotating element of the third planet gear set (50) is designed as the third planet carrier (54), the first rotating element of the fourth planet gear set (60) is designed as the fourth ring gear (66), and the second rotating element of the fourth planet gear set (60) is designed as the fourth planet carrier (64). Gearbox (16) according to one of claims 6 to 9, characterized in that the first rotating element of the third planet gear set (50) is designed as the third sun gear (52), the second rotating element of the third planet gear set (50) is designed as the third planet carrier (54), the first rotating element of the fourth planet gear set (60) is designed as the fourth sun gear (62), and the second rotating element of the fourth planet gear set (60) is designed as the fourth planet carrier (64). Gearbox (16) according to one of claims 6 to 9, characterized in that the first rotating element of the third planet gear set (50) is designed as the third sun gear (52), the second rotating element of the third planet gear set (50) is designed as the third ring gear (56), the first rotating element of the fourth planet gear set (60) is designed as the fourth sun gear (62), and the second rotating element of the fourth planet gear set (60) is designed as the fourth ring gear (66). Gearbox (16) according to one of claims 6 to 9, characterized in that the first rotating element of the third planet gear set (50) is designed as a third ring gear (56), the second rotating element of the third planet gear set (50) is designed as a third sun gear (52), the first rotating element of the fourth planet gear set (60) is designed as a fourth ring gear (66), and the second rotating element of the fourth planet gear set (60) is designed as a fourth sun gear (62). Drive train comprising a drive motor (14) and a gearbox (16) according to one of the preceding claims. Drive train according to claim 14, characterized in that a gear stage for providing a transmission ratio is provided in the drive train between the drive motor (14) and the transmission (16). Vehicle (10) with a transmission (16) according to one of claims 1 to 13 or a drive train according to one of claims 14 to 15.

Images