Compact and efficient transmission for a vehicle drive train

Abstract

A transmission (1) for a drive train of a vehicle (100) having an input shaft (2), a first output shaft (3), a second output shaft (4), and a differential arranged in the power flow between the input shaft (2) and the two output shafts (3, 4), wherein the differential comprises a first planetary gear set (5) with a plurality of planetary gears (5.4) and a plurality of gear set elements, and a second planetary gear set (6) with a plurality of planetary gears (6.4) and a plurality of gear set elements, wherein a first output torque can be transmitted to the first output shaft (3) by means of the first planetary gear set (5), wherein a support torque of the first planetary gear set (5) can be converted in the second planetary gear set (6) such that a second output torque corresponding to the first output torque can be transmitted to the second output shaft (4), • wherein a first gear set element of the first planetary gear set (5) is connected in a rotationally fixed manner to the input shaft (2), • wherein a second gear set element of the first planetary gear set (5) is connected in a rotationally fixed manner to a first gear set element of the second planetary gear set (6), • wherein a third gear set element of the first planetary gear set (5) is connected in a rotationally fixed manner to the first output shaft (3), • wherein a second gear set element of the second planetary gear set (6) is connected in a rotationally fixed manner to the second output shaft (4), • wherein a third gear set element of the second planetary gear set (6) is connected in a rotationally fixed manner to a stationary component, • wherein the second planetary gear set (6) is arranged axially adjacent to the first planetary gear set (5) and the planetary gears (5.4) of the first planetary gear set (5) have no axial overlap with the planetary gears (6.4) of the second planetary gear set (6), wherein the planetary gears (5.4) of the first planetary gear set (5) have a larger outer diameter than the planetary gears (6.4) of the second planetary gear set (6), • wherein the second planetary gear set (6) with its gear set elements is arranged in the radial direction outside a rotation axis (B) of the respective planetary gear (5.4) of the first planetary gear set 5.

Description

[0001] The invention relates to a transmission for a drive train of a vehicle. Furthermore, the invention relates to a vehicle with a drive train comprising a prime mover and such a transmission.

[0002] DE 10 2021 200 527 A1 discloses a drivetrain for a motor vehicle. The drivetrain comprises an internal combustion engine, a multi-speed transmission, and an integral differential. The differential is configured with two planetary gear sets, each planetary gear set being driveably connected to a respective output shaft. The differential and the respective output shaft are configured to be arranged coaxially with an output axle of the motor vehicle, with the internal combustion engine and the multi-speed transmission being arranged axially parallel to the output axle. By means of the first planetary gear set, a first output torque can be transmitted to the second output shaft, wherein a support torque of the first planetary gear set can be converted in the second planetary gear set such that a second output torque corresponding to the first output torque can be transmitted to the first output shaft.

[0003] An electric drive train is known from US 5 845 732 A.

[0004] DE 10 2014 209 945 A1 relates to a drive device for a vehicle with a transmission arrangement, wherein the introduction of a drive torque and a drive power from a drive motor into the transmission arrangement takes place via a drive shaft with a first sun gear, wherein the transmission arrangement comprises a superposition gear for half-distributing the drive power between a planet carrier and a first ring gear, as well as a reversing gear geared to the superposition gear for half-distributing the drive torque between a first output shaft connected to the superposition gear and a second output shaft connected to the reversing gear. The reversing gear has a planetary gear set that is rotatably mounted on a planet carrier that is fixedly attached to a housing and meshes radially between a second sun gear and a second ring gear, wherein the second ring gear is connected to the second output shaft.

[0005] DE 10 2014 217 397 A1 relates to a drive arrangement with a transmission device, comprising a drive motor which drives a continuously variable transmission via a torque converter, wherein the continuously variable transmission has a continuously variable transmission stage with a variable ratio between a power input shaft and a power output shaft, which cooperates at least indirectly with a differential, wherein the differential is connected to a first and a second output shaft, wherein the differential is designed as a rolling differential with a superposition gear and a reversing gear, wherein the superposition gear has a first planetary gear set and the reversing gear has a second planetary gear set.

[0006] The object of the present invention is to propose a compact and efficient transmission for a vehicle drivetrain. In particular, the transmission should have a differential with a high gear ratio. This object is achieved by a transmission having the features of independent patent claim 1. Advantageous embodiments are the subject of the dependent claims, the following description, and the figures.

[0007] A transmission according to the invention for a drive train of a vehicle comprises an input shaft, a first output shaft, a second output shaft and a differential arranged in the power flow between the input shaft and the two output shafts, wherein the differential comprises a first planetary gear set with a plurality of planetary gears and a plurality of gear set elements and a second planetary gear set with a plurality of planetary gears and a plurality of gear set elements, wherein a first output torque can be transmitted to the first output shaft by means of the first planetary gear set, wherein a support torque of the first planetary gear set in the second planetary gear set can be converted such that a second output torque corresponding to the first output torque can be transmitted to the second output shaft, wherein a first gear set element of the first planetary gear set is connected in a rotationally fixed manner to the input shaft,wherein a second gear set element of the first planetary gear set is rotationally fixedly connected to a first gear set element of the second planetary gear set, wherein a third gear set element of the first planetary gear set is rotationally fixedly connected to the first output shaft, wherein a second gear set element of the second planetary gear set is rotationally fixedly connected to the second output shaft, wherein a third gear set element of the second planetary gear set is rotationally fixedly connected to a stationary component, wherein the second planetary gear set is arranged axially adjacent to the first planetary gear set and the planet gears of the first planetary gear set have no axial overlap with the planet gears of the second planetary gear set, wherein the planet gears of the first planetary gear set have a larger outer diameter than the planet gears of the second planetary gear set,

[0008] In other words, the two planetary gear sets of the differential are not radially stacked, but arranged axially next to one another, so that the planet gears of the two planetary gear sets do not axially overlap. The gear set elements of the first and second planetary gear sets are thus arranged in two axially spaced planes. In particular, no components that do not belong to one of the two planetary gear sets are arranged axially between the two planetary gear sets. The second planetary gear set and its gear set elements are arranged radially outside a rotational axis of the respective planet gear of the first planetary gear set. This creates installation space radially within the second planetary gear set, which can be advantageously used, in particular, for bearings or for oil supply. The two planetary gear sets together form an integral differential.

[0009] For the purposes of this invention, an “integral differential” is understood to mean a differential with a first planetary gear set and a second planetary gear set, wherein the first planetary gear set is drive-connected to the input shaft, to the second planetary gear set, and to the first output shaft. The second planetary gear set is drive-connected to the second output shaft. When the output shafts have identical output speeds, the integral differential has no gearing that rotates in a block or rotates without a rolling movement. Therefore, regardless of the output speeds of the output shafts, there is always a relative movement between the meshing components of the integral differential. With an integral differential, the sums of both wheel torques are not combined into a common axle torque in one component.Rather than being combined, the drive power is divided in the integral differential and passed on to the connected output shafts in accordance with the design of the first and second planetary gear sets. This allows the components of the integral differential to be designed more slenderly due to the comparatively low torque they generate. In addition, the number of components can be reduced and weight saved. Using such an integral differential, the two functions of torque conversion and torque distribution, which are usually performed by two separate assemblies, can be performed by a single integral assembly. The integral differential is therefore a combined transmission and differential gear that performs torque conversion on the one hand and torque distribution to the output shafts on the other.

[0010] A "planetary gear set" is a unit comprising the gear set elements of a sun gear, ring gear, and planet carrier. The planet carrier carries several planet gears arranged on a circular path around the sun gear, which mesh with the ring gear and the sun gear. In particular, the planet gears are rotatably mounted on the planet carrier via planet gear bolts.

[0011] The input shaft is preferably configured to be at least indirectly connected in a rotationally fixed manner to a drive shaft of a drive unit, in particular to a rotor shaft of an electric drive motor. The drive unit generates drive power, which is transmitted to the input shaft via the drive shaft. The drive shaft of the drive unit can be connected in a rotationally fixed manner to the input shaft. Alternatively, the drive shaft and the input shaft are designed as a monolithic component. Depending on the design of the drive train, two or more input shafts can also be provided, in particular if the drive train is a hybridized drive train and therefore two or more drive units are provided.

[0012] The term "at least indirectly" means that two components are connected to each other via at least one additional component arranged between the two components, or are directly and thus immediately connected to each other. Thus, additional components can be arranged between shafts or gears that are operatively connected to the shaft or gear.

[0013] The input shaft is preferably designed as a hollow shaft. This allows one of the output shafts, preferably the first output shaft, to pass axially through the input shaft. Preferably, one of the output shafts, in particular the first output shaft, passes through the transmission and, if appropriate, through the drive unit of the drive train.

[0014] The output shafts of the transmission are particularly designed to be operatively connected to a respective wheel of the vehicle. The respective output shaft can be connected to the corresponding wheel directly or indirectly, for example, via a joint and / or a wheel hub. The output shafts are preferably arranged coaxially with one another. The coaxial arrangement of the output shafts allows for a radially narrow transmission design.

[0015] Additional intermediate components may be arranged between the input shaft and the drive unit, for example, in the form of planetary gears, spur gears, chain drives, belt drives, angle drives, cardan shafts, torsion dampers, multi-speed transmissions, or the like. Likewise, additional intermediate components may be arranged between the respective output shaft and the wheel operatively connected to it, such as cardan shafts, transmission gears, spring and damping elements, or the like.

[0016] A "shaft" is a rotatable component of the transmission through which the associated components of the transmission are connected to one another in a rotationally fixed manner. The respective shaft can connect the components axially or radially, or even both axially and radially. A shaft is not exclusively understood as a cylindrical, rotatably mounted machine element for transmitting torque, for example, but rather also includes general connecting elements that connect individual components or elements to one another, in particular connecting elements that connect multiple elements to one another in a rotationally fixed manner.

[0017] If two components of the transmission are "rotatably connected," then these components have a permanent coupling within the meaning of the invention, meaning they cannot rotate independently of each other. This is understood to mean a permanent rotary connection. In particular, no shifting element is provided between these components, which can be elements of the differential and / or shafts and / or a non-rotatable component of the transmission. A torsionally flexible connection between two components is also understood to be fixed or non-rotatable.

[0018] A "stationary component" is defined as a component of the transmission that is rotationally and axially fixed, such as a transmission housing or a component connected to it in a rotationally fixed manner. No relative movement can occur between the gear set element, which is rotationally fixed to a stationary component, and the stationary component.

[0019] The first gear set element of the first planetary gear set is preferably connected in a rotationally fixed manner to the first input shaft via a plug-in or driving toothing. This plug-in toothing preferably comprises an internal toothing on the first gear set element of the first planetary gear set and an external toothing on the input shaft. The third gear set element of the first planetary gear set is preferably connected in a rotationally fixed manner to the first output shaft via a plug-in or driving toothing. This plug-in toothing preferably comprises an internal toothing on the third gear set element of the first planetary gear set and an external toothing on the first output shaft.

[0020] According to a preferred embodiment of the invention, the first gear set element of the first planetary gear set is designed as a sun gear, the second gear set element of the first planetary gear set is designed as a ring gear, and the third gear set element of the first planetary gear set is designed as a planet carrier. In particular, planetary gear bolts are arranged on the planet carrier of the first planetary gear set for rotatably supporting the planet gears of the first planetary gear set.

[0021] According to a preferred embodiment of the invention, the first gear set element of the second planetary gear set is designed as a sun gear, the second gear set element of the second planetary gear set is designed as a ring gear, and the third gear set element of the second planetary gear set is designed as a planet carrier. In particular, planetary gear bolts for rotatably supporting the planet gears of the second planetary gear set are arranged on the planet carrier of the second planetary gear set.

[0022] According to a preferred embodiment of the invention, the ring gear of the first planetary gear set has a larger outer diameter than the sun gear of the second planetary gear set, wherein the sun gear of the second planetary gear set is arranged at least indirectly axially on the ring gear of the first planetary gear set. In particular, the inner diameter of the ring gear of the first planetary gear set is substantially the same size as the outer diameter of the sun gear of the second planetary gear set. This means that the difference between the inner diameter of the ring gear of the first planetary gear set and the outer diameter of the sun gear of the second planetary gear set is less than 10%. As a result, the sun gear of the second planetary gear set can be rotationally fixedly connected to the ring gear of the first planetary gear set in a particularly simple and compact manner.Furthermore, the assembly of the sun gear of the second planetary gear set and the ring gear of the first planetary gear set is simplified. For example, the sun gear of the second planetary gear set is arranged indirectly via other components or directly on the ring gear of the first planetary gear set.

[0023] According to a preferred embodiment of the invention, the outer diameter of the planet gears of the first planetary gear set is at least twice the outer diameter of the planet gears of the second planetary gear set. This increases the overall gear ratio of the integral differential compared to an integral differential with equally sized planet gears. Preferably, the outer diameter of the planet gears of the second planetary gear set is two-thirds smaller than the outer diameter of the planet gears of the first planetary gear set. This further increases the overall gear ratio of the integral differential.

[0024] According to a preferred embodiment of the invention, a bearing element for supporting the second output shaft is arranged at least partially radially within the second planetary gear set and at least partially axially overlapping with the second planetary gear set. This allows the support of the second output shaft to be optimized. In particular, the bearing element is arranged radially between the second output shaft and a stationary component, in particular a housing component.

[0025] According to a preferred embodiment of the invention, an oil feed for the second output shaft is arranged at least partially radially within the second planetary gear set and at least partially axially overlapping with the second planetary gear set. This allows the oil feed for the second output shaft to be optimized. The oil feed preferably comprises a ring element arranged radially between the stationary component and the second output shaft.

[0026] According to a preferred embodiment of the invention, the oil feed for the second output shaft and the bearing element for supporting the second output shaft are arranged axially adjacent to one another. In particular, no further components other than the oil feed or the bearing element are arranged between the oil feed for the second output shaft and the bearing element for supporting the second output shaft. This allows for efficient use of the installation space within the second planetary gear set.

[0027] The respective planetary gear set is preferably designed as a negative planetary gear set. A negative planetary gear set corresponds to a planetary gear set with a planet carrier on which first planetary gears are rotatably mounted, a sun gear, and a ring gear. The teeth of at least one of the planetary gears mesh with both the teeth of the sun gear and the toothing of the ring gear, causing the ring gear and the sun gear to rotate in opposite directions when the sun gear rotates with the carrier stationary.

[0028] Alternatively, the respective planetary gear set is designed as a plus planetary gear set. A plus planetary gear set differs from the minus planetary gear set in that the plus planetary gear set has first and second, or inner and outer planet gears, which are rotatably mounted on the planet carrier. The teeth of the first or inner planet gears mesh with the teeth of the sun gear on the one hand and with the teeth of the second or outer planet gears on the other. The teeth of the outer planet gears also mesh with the teeth of the ring gear. This means that when the planet carrier is stationary, the ring gear and the sun gear rotate in the same direction. When one or both planetary gear sets are designed as a plus planetary gear set, the connection between the planet carrier and the ring gear is swapped and the stationary gear ratio is increased by 1.This is also possible in reverse if a negative planetary gear set is to be provided instead of a positive planetary gear set.

[0029] Alternatively, it is also conceivable to design one or more planetary gear sets as stepped planetary gear sets. Each stepped planetary gear of the respective stepped planetary gear set preferably comprises a first gear with a second gear connected thereto in a rotationally fixed manner, wherein the first gear meshes, for example, with the sun gear and the second gear meshes accordingly with the ring gear, or vice versa. These two gears can be connected to one another in a rotationally fixed manner, for example, via an intermediate shaft or a hollow shaft. In the case of a hollow shaft, this can be rotatably mounted on a bolt of the planet carrier. The two gears of the respective stepped planetary gear preferably have different diameters and numbers of teeth in order to set a transmission ratio. Compound planetary gear sets are also conceivable.

[0030] A vehicle according to the invention comprises a drive train with a drive unit and a transmission according to the invention. The transmission is drivingly connected to the drive unit. The drive unit is preferably an electric machine, wherein the input shaft of the transmission is a rotor of the electric machine or is connected or coupled in a rotationally fixed manner to the rotor or a rotor shaft. The rotor is rotatably mounted relative to a housing-fixed stator of the electric machine. The electric machine is preferably connected to an accumulator that supplies the electric machine with electrical energy. Furthermore, the electric machine is preferably controllable or regulatable by power electronics. Alternatively, the drive unit can also be an internal combustion engine, wherein the input shaft in this case is, for example, a crankshaft or is connected or coupled in a rotationally fixed manner to the crankshaft.

[0031] Preferably, the drive unit is arranged coaxially with the integral differential. This eliminates the need for an additional transmission from the input shaft to the rotor shaft, rotor, or crankshaft of the drive unit. In this case, one of the output shafts passes axially through the drive unit.

[0032] The drive train according to the type described above can be used in a vehicle. The vehicle is preferably a motor vehicle, in particular an automobile (e.g., a passenger car weighing less than 3.5 t), a bus, or a truck (e.g., a bus and truck weighing more than 3.5 t). In particular, the vehicle is an electric vehicle or a hybrid vehicle. The vehicle comprises at least two axles, one of the axles forming an axle drivable by means of the drive train. The drive train according to the invention is operatively arranged on this drivable axle, the drive train transmitting drive power from the drive unit to the wheels of this axle via the transmission according to the invention. It is also conceivable to provide such a drive train for each axle.The drivetrain is preferably installed in a front-transverse design, so that the input shaft and the output shafts are aligned essentially transversely to the vehicle's longitudinal direction. Alternatively, the drivetrain can be arranged diagonally to the vehicle's longitudinal and transverse axes, with the output shafts connected via corresponding joints to the wheels of the respective axle, which are arranged transversely to the vehicle's longitudinal axis.

[0033] The above definitions as well as explanations of technical effects, advantages and advantageous embodiments of the transmission according to the invention also apply mutatis mutandis to the drive train according to the invention, and vice versa.

[0034] In the following, an embodiment of the invention is explained in more detail with reference to the schematic drawings, wherein identical or similar components are provided with the same reference numerals. Fig. 1 is a highly schematic view of a vehicle with a drive train having a transmission according to the invention; Fig. 2 a highly schematic view of a section of the transmission according to the invention; and Fig. 3 a detailed schematic sectional view of a section of the transmission according to the invention.

[0035] Fig. 1 shows a vehicle 100 with a first axle 101 with two vehicle wheels R1, R2 and a second axle 102 with two vehicle wheels R3, R4. In the present case, the first axle 101 is designed as the rear drive axle of the vehicle 100 and comprises a drive train with a drive unit 10 designed as an electric machine and a transmission 1 according to the invention. The drive unit 10 is configured to generate drive power and is drivingly connected to the transmission 1. The vehicle 100 is therefore designed as an electric vehicle, i.e. as an electrically drivable vehicle. The drive unit 10 is arranged coaxially to the transmission 1 and transversely to the vehicle longitudinal direction and is drivingly connected to the vehicle wheels R1, R2 of the first axle 101 via an integral differential in the transmission 1.In the present case, no additional drive train is arranged on the second axle 102, i.e., the front axle of the vehicle 100, thereby saving costs, weight, and installation space. Alternatively, the drive train can be arranged on the front axle of the vehicle 100 instead of on the rear axle. To implement an all-wheel drive system, an additional drive unit can be arranged on the second axle 102 and connected to the vehicle wheels R3, R4 of this axle 102.

[0036] Fig. 2 and Fig. 3 show a section of the transmission 1 according to the invention, with the focus here being on the integral differential. The transmission 1 comprises an input shaft 2, a first output shaft 3, a second output shaft 4, as well as a first planetary gear set 5 and a second planetary gear set 6. The two planetary gear sets 5, 6 form the integral differential and are arranged in the power flow between the input shaft 2 and the two output shafts 3, 4. By means of the first planetary gear set 5, a first output torque can be transmitted to the first output shaft 3, wherein a support torque of the first planetary gear set 5 can be converted in the second planetary gear set 6 such that a second output torque corresponding to the first output torque can be transmitted to the second output shaft 4.

[0037] A first gear set element of the first planetary gear set 5 is designed as a sun gear 5.1 and is rotationally fixedly connected to the input shaft 2. A second gear set element of the first planetary gear set 5 is designed as a ring gear 5.2 and is rotationally fixedly connected to a first gear set element of the second planetary gear set 6, designed as a sun gear 6.1. A third gear set element of the first planetary gear set 5 is designed as a planet carrier 5.3 and is rotationally fixedly connected to the first output shaft 3. Several planet gears 5.4 are rotatably mounted on the planet carrier 5.3 of the first planetary gear set 5, with each planet gear 5.4 meshing with the sun gear 5.1 and the ring gear 5.2 of the first planetary gear set 5. A second gear set element of the second planetary gear set 6 is designed as a ring gear 6.2 and is rotationally fixedly connected to the second output shaft 4. A third gear set element of the second planetary gear set 6 is the planet carrier 6.3 and is connected in a rotationally fixed manner to a stationary component which is designed as a housing G.

[0038] The second planetary gear set 6 is arranged axially adjacent to the first planetary gear set 5, and the planet gears 5.4 of the first planetary gear set 5 have no axial overlap with the planet gears 6.4 of the second planetary gear set 6. The two planetary gear sets 5, 6 rotate about a common axis of rotation A of the transmission 1. The two output shafts 3, 4 are arranged on the common axis of rotation A of the transmission 1 and are each connected to a wheel of the vehicle; this is illustrated in a simplified manner by an arrow on the respective output shaft 3, 4.

[0039] The planet gears 5.4 of the first planetary gear set 5 have a larger outer diameter than the planet gears 6.4 of the second planetary gear set 6. The second planetary gear set 6 is arranged with its gear set elements in the radial direction outside a rotational axis B of the respective planet gear 5.4 of the first planetary gear set 5. Thus, the planet gears 6.4 of the second planetary gear set 6 are radially further away from the common rotational axis A than the planet gears 5.4 of the first planetary gear set 5. This creates installation space radially within the second planetary gear set 5, which installation space can be used advantageously, in particular for bearings and an oil feed.

[0040] Fig. 3 shows the gearbox section according to Fig.2 in more detail. The ring gear 5.2 of the first planetary gear set 5 has a larger outer diameter than the sun gear 6.1 of the second planetary gear set 6. The sun gear 6.1 of the second planetary gear set 6 is arranged axially on the ring gear 5.2 of the first planetary gear set 5 and is connected thereto in a rotationally fixed manner.

[0041] A bearing element 7 for supporting the second output shaft 4 is arranged radially within the second planetary gear set 6 and axially overlapping the second planetary gear set 6. Furthermore, an oil feed 8 for the second output shaft 4 is arranged radially within the second planetary gear set 6 and axially overlapping the second planetary gear set 6. The oil feed 8 for the second output shaft 4 and the bearing element 7 for supporting the second output shaft 4 are arranged axially adjacent to one another.

[0042] The oil feed 8 comprises a ring element 9, which is arranged radially between a stationary component designed as a housing G and the second output shaft 4. The bearing element 7 is designed as a deep groove ball bearing and is supported on the stationary component designed as a housing G.

[0043] Because the respective outer diameter of the planetary gears 5.4 of the first planetary gear set 5 is more than twice as large as the respective outer diameter of the planetary gears 6.4 of the second planetary gear set 6, the overall gear ratio of the integral differential is significantly increased. Due to the advantageous arrangement of the bearing element 7 and the oil feed 8 within the second planetary gear set 6, this increase in the overall gear ratio is space-neutral and thus creates a particularly compact transmission 1. Reference symbol 1 gearbox 2 input shaft 3 First output shaft 4 Second output shaft 5 First planetary gear set 5.1 Sun gear of the first planetary gear set 5.2 Ring gear of the first planetary gear set 5.3 Planet carrier of the first planetary gear set 5.4 Planetary gear of the first planetary gear set 6 Second planetary gear set 6.1 Sun gear of the second planetary gear set 6.2 Ring gear of the second planetary gear set 6.3 Planet carrier of the second planetary gear set 6.4 Planetary gear of the second planetary gear set 7 Bearing element 8 Oil feed 9 Ring element 10 drive machine G Housing A rotation axis 100 vehicles 101 first axis 102 second axis R1 vehicle wheel R2 vehicle wheel R3 vehicle wheel R4 vehicle wheel

Claims

[1] Transmission (1) for a drive train of a vehicle (100) comprising an input shaft (2), a first output shaft (3), a second output shaft (4) and a differential arranged in the power flow between the input shaft (2) and the two output shafts (3, 4), wherein the differential comprises a first planetary gear set (5) with several planet gears (5.4) and several gear set elements and a second planetary gear set (6) with several planet gears (6.4) and several gear set elements, wherein a first output torque can be transmitted to the first output shaft (3) by means of the first planetary gear set (5), wherein a support torque of the first planetary gear set (5) in the second planetary gear set (6) can be converted such that a second output torque corresponding to the first output torque can be transmitted to the second output shaft (4), • wherein a first gear set element of the first planetary gear set (5) is non-rotatably connected to the input shaft (2), • wherein a second gear set element of the first planetary gear set (5) is non-rotatably connected to a first gear set element of the second planetary gear set (6), • wherein a third gear set element of the first planetary gear set (5) is non-rotatably connected to the first output shaft (3), • wherein a second gear set element of the second planetary gear set (6) is non-rotatably connected to the second output shaft (4), • wherein a third gear set element of the second planetary gear set (6) is connected to a stationary component in a rotationally fixed manner, • wherein the second planetary gear set (6) is arranged axially adjacent to the first planetary gear set (5) and the planet gears (5.4) of the first planetary gear set (5) do not have any axial overlap with the planet gears (6.4) of the second planetary gear set (6), wherein the planet gears (5.4) of the first planetary gear set (5) have a larger outer diameter than the planet gears (6.4) of the second planetary gear set (6), • wherein the second planet gear set (6) with its gear set elements is arranged in a radial direction outside a rotation axis (B) of the respective planet gear (5.4) of the first planet gear set 5. [2] Gearbox (1) according to claim 1, wherein the first gear set element of the first planet gear set (5) is designed as a sun gear (5.1), wherein the second gear set element of the first planet gear set (5) is designed as a ring gear (5.2), wherein the third gear set element of the first planet gear set (5) is designed as a planet carrier (5.3). [3] Gearbox (1) according to claim 1 or 2, wherein the first gear set element of the second planet gear set (6) is designed as a sun gear (6.1), wherein the second gear set element of the second planet gear set (6) is designed as a ring gear (6.2), wherein the third gear set element of the second planet gear set (6) is designed as a planet carrier (6.3). [4] Gearbox (1) according to claim 2 in combination with claim 3, wherein the ring gear (5.2) of the first planet gear set (5) has a larger outer diameter than the sun gear (6.1) of the second planet gear set (6), wherein the sun gear (6.1) of the second planet gear set (6) is arranged at least indirectly axially on the ring gear (5.2) of the first planet gear set (5). [5] Gearbox (1) according to one of the preceding claims, wherein a bearing element (7) for supporting the second output shaft (4) is arranged at least partially radially within the second planetary gear set (6). [6] Transmission (1) according to one of the preceding claims, wherein an oil supply (8) for the second output shaft (4) is arranged at least partially radially within the second planetary gear set (6). [7] Gearbox (1) according to claim 5 in combination with claim 6, wherein the oil supply (8) for the second output shaft (4) and the bearing element (7) for supporting the second output shaft (4) are arranged axially adjacent to each other. [8] Gearbox (1) according to claim 6 or 7, wherein the oil supply (8) comprises a ring element (9) arranged radially between a stationary component and the second output shaft (4). [9] Gearbox (1) according to one of the preceding claims, wherein the outer diameter of the planet gears (5.4) of the first planet gear set (5) is at least twice as large as the outer diameter of the planet gears (6.4) of the second planet gear set (6). [10] Vehicle (100) with a drive train comprising a drive unit (10) and a transmission (1) according to any of the preceding claims.

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