Transmission and drive system for a motor vehicle

Abstract

Transmission (1) for a motor vehicle (100), comprising • a first planetary gear set (P1), a second planetary gear set (P2) and a third planetary gear set (P3), wherein each planetary gear set (P1, P2, P3) has a first element (E11, E21, E31), a second element (E12, E22, E32) and a third element (E13, E23, E33), • exactly one drive shaft (WAn) for connecting the transmission (1) to a drive motor (2) of the motor vehicle (100), • a first output shaft (WAb1) and a second output shaft (WAb2) each for connecting the transmission (1) to a wheel (R1, R2) of the motor vehicle (100), • a first coupling shaft (W1) and a second coupling shaft (W2) each for the rotationally fixed connection of two elements of two planetary gear sets (P1, P2, P3), • a switching element (S) for transmitting a torque between one of the two output shafts (WAb1, WAb2) and the second coupling shaft (W2), • wherein one of the elements (E21, E22, E23) of the second planetary gear set (P2) is non-rotatably connected to the drive shaft (WAn), wherein another of the elements (E21, E22, E23) of the second planetary gear set (P2) is non-rotatably connected to the first coupling shaft (W1), wherein another of the elements (E21, E22, E23) of the second planetary gear set (P2) is non-rotatably connected to the second coupling shaft (W2), • wherein one of the elements (E31, E32, E33) of the third planetary gear set (P3) is non-rotatably connected to the first coupling shaft (W1), wherein another of the elements (E31, E32, E33) of the third planetary gear set (P3) is non-rotatably connected to a stationary component, wherein another of the elements (E31, E32, E33) of the third planetary gear set (P3) is non-rotatably connected to the second output shaft (WAb2), • wherein one of the elements (E11, E12, E13) of the first planetary gear set (P1) is non-rotatably connected to the second coupling shaft (W2), wherein another of the elements (E11, E12, E13) of the first planetary gear set (P1) is non-rotatably connected to the first output shaft (WAb1), wherein another of the elements (E11, E12, E13) of the first planetary gear set (P1) is non-rotatably connected to the second output shaft (WAb2).

Description

[0001] The invention relates to a transmission for a motor vehicle. Furthermore, the invention relates to a drive device with such a transmission.

[0002] For example, DE 10 2013 215 877 A1 discloses an epicyclic gear system for splitting the drive power applied to a power input to a first and a second power output, in conjunction with a reduction of the output speed to a speed level below the drive speed at the power input. The epicyclic gear system comprises a first gear stage having a first sun gear, a first planetary gear set, a first planetary carrier, and a first ring gear; a second gear stage having a second sun gear, a second planetary gear set, a second planetary carrier, and a second ring gear; and a third planetary gear stage having a third sun gear, a third planetary gear set, and a third planetary carrier.The first sun gear is configured as the power input, the first planet carrier is rotationally coupled to the second sun gear, the second planet carrier is stationary, the first ring gear is coupled to the third sun gear, the first power output occurs via the third gear stage, and the second power output occurs via the second ring gear of the second gear stage.

[0003] The object of the present invention is to provide an alternative transmission that, in particular, has improved power density and efficiency, as well as a differential locking effect. These objects are achieved by a transmission having the features of patent claim 1 and a transmission having the features of patent claim 10. Advantageous embodiments are the subject of the dependent claims, the following description, and the figures.

[0004] A transmission according to the invention for a motor vehicle comprises a first planetary gear set, a second planetary gear set and a third planetary gear set, each planetary gear set having a first element, a second element and a third element, exactly one drive shaft for connecting the transmission to a drive engine of the motor vehicle, a first output shaft and a second output shaft each for connecting the transmission to a wheel of the motor vehicle, a first coupling shaft and a second coupling shaft each for the rotationally fixed connection of two elements of two planetary gear sets, and a shift element for transmitting a torque between one of the two output shafts and the second coupling shaft, • wherein one of the elements of the second planetary gear set is connected in a rotationally fixed manner to the drive shaft, wherein another of the elements of the second planetary gear set is connected in a rotationally fixed manner to the first coupling shaft, wherein another of the elements of the second planetary gear set is connected in a rotationally fixed manner to the second coupling shaft, • wherein one of the elements of the third planetary gear set is connected in a rotationally fixed manner to the first coupling shaft, wherein another of the elements of the third planetary gear set is connected in a rotationally fixed manner to a stationary component, wherein another of the elements of the third planetary gear set is connected in a rotationally fixed manner to the second output shaft, • wherein one of the elements of the first planetary gear set is connected in a rotationally fixed manner to the second coupling shaft, wherein another of the elements of the first planetary gear set is connected in a rotationally fixed manner to the first output shaft, wherein another of the elements of the first planetary gear set is connected in a rotationally fixed manner to the second output shaft.

[0005] A "connection" of a device or element to the transmission means that the transmission, in particular the corresponding shaft of the transmission, is either directly connected to the device or element, for example in a rotationally fixed manner, or indirectly connected, for example via at least one further component, in particular via at least one further shaft or gear. If two shafts are connected to one another in a rotationally fixed manner, they rotate together in one direction of rotation at one rotational speed. In particular, the connection can also be made via a switching element, which enables a drive-effective coupling and decoupling of the device or element with the corresponding shaft of the transmission.

[0006] A "shaft" is not exclusively understood to mean, for example, a cylindrical, rotatably mounted transmission element for transmitting torque, but rather also general connecting elements that connect individual components or elements together, in particular connecting elements that connect several elements together in a rotationally fixed manner. Two shafts connected in a rotationally fixed manner can be formed as a single piece.

[0007] A "stationary component" is a non-rotating component of the transmission. For example, the stationary component is designed as a housing or housing section of the transmission. Alternatively, the stationary component can be designed as a shaft fixed to the housing.

[0008] The second planetary gear set is therefore connected or connectable to the drive engine at least directly or indirectly via the input shaft, and is connected to the third planetary gear set via the first coupling shaft and to the first planetary gear set via the second coupling shaft. Furthermore, the third planetary gear set is connected to the housing in a rotationally fixed manner and is connected to the first planetary gear set via the second output shaft. The first planetary gear set is additionally connected to the first output shaft. The first planetary gear set is connected or connectable to a first wheel of the motor vehicle at least directly or indirectly via the first output shaft. Furthermore, the first and third planetary gear sets are connected or connectable to a second wheel of the motor vehicle at least directly or indirectly via the second output shaft.

[0009] For example, the drive machine is designed as an electric machine that can be operated as a drive motor to drive the vehicle and as a generator to recuperate electrical energy. For this purpose, the electric machine is electrically connected to an electrical energy storage device. The electric machine comprises a rotor and a stator, wherein the rotor is connected in a rotationally fixed manner to a rotor shaft. The rotor shaft of the electric machine is connected at least directly or indirectly to the drive shaft. For example, the rotor shaft of the electric machine is connected to the drive shaft via at least one further shaft, via a plurality of gears and / or via a traction means. The electric machine can be arranged on a common axis of rotation with the transmission and thus be designed coaxially to the drive shaft, wherein the rotor shaft is then preferably connected in a rotationally fixed manner to the drive shaft.Alternatively, the electric motor can be designed to be axially parallel to the drive shaft, in which case the rotor shaft is indirectly connected to the drive shaft. Alternatively, the drive motor can be designed as an internal combustion engine with a crankshaft.

[0010] A “switching element” is understood to mean a switchable device which has at least one open and one closed state, wherein in the open state two shafts connected thereto can rotate freely, and wherein in the closed state the two shafts are connected to one another in a rotationally fixed manner.

[0011] According to a preferred embodiment, the shifting element, in a closed state, connects the third element of the first planetary gear set and the first element of the first planetary gear set to one another in a rotationally fixed manner. According to a preferred embodiment, the shifting element, in a closed state, connects the second element of the first planetary gear set and the first element of the first planetary gear set to one another in a rotationally fixed manner.

[0012] The first planetary gear set is therefore blocked via the shifting element. In other words, two elements of the first planetary gear set, for example the sun gear and the ring gear or the sun gear and the planet carrier, are connected in a rotationally fixed manner so that the first planetary gear set rotates as a block and has a gear ratio of 1. Because one of these elements of the first planetary gear set is connected to either the first or the second output shaft, a differential locking effect is also generated by means of the shifting element. The shifting element can be switched by an actuator. A “differential locking effect” is understood to mean a locking effect between the two output shafts. The shifting element can be designed as a frictional or positive locking element. For example, a positive locking element is designed as a dog clutch.A positive-locking shift element can increase the efficiency of the transmission due to reduced drag losses. In particular, positive-locking shift elements are more compact and have an optimized efficiency, offering a cost advantage over frictional shift elements. However, slip operation, i.e., a limited locking effect under differential speed, is not possible with positive-locking shift elements. For example, a frictional shift element comprises several plates or at least one conical friction surface. In the case of a frictional shift element, this can be actuated via an actuator or mechanically, in particular by utilizing axial forces from helical gears. An actuator can be fixed to the housing or arranged so as to rotate with the housing.

[0013] According to a preferred embodiment, the first element of the second planetary gear set is rotationally fixedly connected to the input shaft, wherein the second element of the second planetary gear set is rotationally fixedly connected to the first coupling shaft, wherein the third element of the second planetary gear set is rotationally fixedly connected to the second coupling shaft, wherein the first element of the third planetary gear set is rotationally fixedly connected to the first coupling shaft, wherein the second element of the third planetary gear set is rotationally fixedly connected to a stationary component, wherein the third element of the third planetary gear set is rotationally fixedly connected to the second output shaft, wherein the first element of the first planetary gear set is rotationally fixedly connected to the second coupling shaft, wherein the second element of the first planetary gear set is rotationally fixedly connected to the first output shaft, wherein the third element of the first planetary gear set is rotationally fixedly connected to the second output shaft.For this purpose, reference is made to the embodiments according to the . Fig. 4, Fig. 5 and Fig. 6.

[0014] According to a preferred embodiment, the first element of the second planetary gear set is rotationally fixedly connected to the input shaft, wherein the second element of the second planetary gear set is rotationally fixedly connected to the second coupling shaft, wherein the third element of the second planetary gear set is rotationally fixedly connected to the first coupling shaft, wherein the first element of the third planetary gear set is rotationally fixedly connected to the first coupling shaft, wherein the second element of the third planetary gear set is rotationally fixedly connected to a stationary component, wherein the third element of the third planetary gear set is rotationally fixedly connected to the second output shaft, wherein the first element of the first planetary gear set is rotationally fixedly connected to the second output shaft, wherein the second element of the first planetary gear set is rotationally fixedly connected to the first output shaft, wherein the third element of the first planetary gear set is rotationally fixedly connected to the second coupling shaft.For this purpose, reference is made to the embodiments according to the . Fig. 7 and Fig. 8.

[0015] According to a preferred embodiment, the first element of the second planetary gear set is rotationally fixedly connected to the input shaft, wherein the second element of the second planetary gear set is rotationally fixedly connected to the first coupling shaft, wherein the third element of the second planetary gear set is rotationally fixedly connected to the second coupling shaft, wherein the first element of the third planetary gear set is rotationally fixedly connected to the first coupling shaft, wherein the second element of the third planetary gear set is rotationally fixedly connected to a stationary component, wherein the third element of the third planetary gear set is rotationally fixedly connected to the second output shaft, wherein the first element of the first planetary gear set is rotationally fixedly connected to the second output shaft, wherein the second element of the first planetary gear set is rotationally fixedly connected to the first output shaft, wherein the third element of the first planetary gear set is rotationally fixedly connected to the second coupling shaft.For this purpose, reference is made to the embodiments according to the . Fig. 9 and Fig. 10.

[0016] According to a preferred embodiment, the first element of the second planetary gear set is rotationally fixedly connected to the input shaft, wherein the second element of the second planetary gear set is rotationally fixedly connected to the first coupling shaft, wherein the third element of the second planetary gear set is rotationally fixedly connected to the second coupling shaft, wherein the first element of the third planetary gear set is rotationally fixedly connected to the first coupling shaft, wherein the second element of the third planetary gear set is rotationally fixedly connected to the second output shaft, wherein the third element of the third planetary gear set is rotationally fixedly connected to a stationary component, wherein the first element of the first planetary gear set is rotationally fixedly connected to the second coupling shaft, wherein the second element of the first planetary gear set is rotationally fixedly connected to the second output shaft, wherein the third element of the first planetary gear set is rotationally fixedly connected to the first output shaft.For this purpose, reference is made to the embodiment according to . Fig. 11.

[0017] According to a preferred embodiment, the first element of the second planetary gear set is rotationally fixedly connected to the input shaft, wherein the second element of the second planetary gear set is rotationally fixedly connected to the second coupling shaft, wherein the third element of the second planetary gear set is rotationally fixedly connected to the first coupling shaft, wherein the first element of the third planetary gear set is rotationally fixedly connected to the first coupling shaft, wherein the second element of the third planetary gear set is rotationally fixedly connected to the second output shaft, wherein the third element of the third planetary gear set is rotationally fixedly connected to a stationary component, wherein the first element of the first planetary gear set is rotationally fixedly connected to the second coupling shaft, wherein the second element of the first planetary gear set is rotationally fixedly connected to the second output shaft, wherein the third element of the first planetary gear set is rotationally fixedly connected to the first output shaft.For this purpose, reference is made to the embodiment according to . Fig. 12.

[0018] According to a preferred embodiment, two of the three planetary gear sets are arranged radially nested. In other words, the elements of the two planetary gear sets are arranged axially overlapping such that one of the two planetary gear sets is arranged on the outside and the other of the two planetary gear sets is arranged on the inside. This makes the transmission more compact, particularly in the axial direction. Preferably, the first and third planetary gear sets are arranged radially nested. Alternatively, the first and second planetary gear sets are arranged radially nested.

[0019] According to a preferred embodiment, one of the two coupling shafts or one of the two output shafts is formed integrally with the elements of the respective planetary gear set connected thereto. For example, a coupling shaft or an output shaft can be formed integrally as an intermediate gear with two toothings, wherein an internal toothing of the intermediate gear forms a ring gear for a radially inner planetary gear set, wherein an external toothing of the intermediate gear forms a sun gear for a radially outer planetary gear set. Such an intermediate gear is also called a sun ring gear. Alternatively, a coupling shaft or an output shaft can have toothing that forms a common ring gear for two planetary gear sets. Alternatively, a coupling shaft or an output shaft can have toothing that forms a common sun gear for two planetary gear sets. Alternatively, a coupling shaft or an output shaft can form a common planet carrier.

[0020] According to a preferred embodiment, at least one of the planetary gear sets is designed as a negative planetary gear set, with the first element of the respective planetary gear set being designed as a sun gear, the second element of the respective planetary gear set being designed as a planet carrier, and the third element of the respective planetary gear set being designed as a ring gear. Several planetary gears are rotatably mounted on the planet carrier and mesh with the sun gear and the ring gear.

[0021] The invention further relates to a transmission for a motor vehicle comprising at least a first planetary gear set with a first element, a second element and a third element, wherein the first planetary gear set is designed as a minus planetary gear set with a sun gear, a ring gear and a planet carrier, an input shaft for connecting the transmission to a drive engine of the motor vehicle, a first output shaft and a second output shaft each for connecting the transmission to a wheel of the motor vehicle, a shifting element, wherein one of the elements of the first planetary gear set is connected in a rotationally fixed manner to the first output shaft, wherein another of the elements of the first planetary gear set is connected in a rotationally fixed manner to the second output shaft, and wherein another of the elements of the first planetary gear set is connectable to one of the two output shafts via the shifting element.

[0022] A drive device according to the invention comprises a drive motor and a transmission according to the invention. The drive motor is preferably designed as an electric motor. Alternatively, the drive motor is designed as an internal combustion engine. The drive motor can be arranged coaxially or axially parallel to the drive shaft of the transmission. The drive power of the drive motor is fed into the transmission via the drive shaft and distributed to the two output shafts, with each output shaft being drivingly connected to a respective drive wheel of a drive axle of the vehicle.

[0023] A motor vehicle according to the invention comprises a drive device according to the invention. In particular, the motor vehicle is designed as an electric vehicle and has an electric drive axle with the drive device according to the invention. The above definitions as well as statements regarding technical effects, advantages, and advantageous embodiments of the transmission according to the invention also apply mutatis mutandis to the drive device according to the invention and to the motor vehicle according to the invention.

[0024] Advantageous embodiments of the invention, which are explained below, are illustrated in the drawings, wherein like elements are provided with the same reference numerals. They show: Fig. 1 a highly abstracted schematic view of a motor vehicle with a drive device according to the invention; Fig. 2 a highly abstracted schematic diagram of the drive device according to the invention; Fig. 3 a highly abstracted schematic diagram of the drive device according to the invention according to an alternative embodiment; Fig. 4 a highly abstracted schematic view of the drive device according to the invention according to a first embodiment; Fig. 5 a highly abstracted schematic view of a drive device according to the invention according to a second embodiment; Fig. 6 a highly abstracted schematic view of a drive device according to the invention according to a third embodiment; Fig. 7 a highly abstracted schematic view of a drive device according to the invention according to a fourth embodiment; Fig. 8 shows a highly abstracted schematic view of a drive device according to the invention according to a fifth embodiment; Fig. 9 a highly abstracted schematic view of a drive device according to the invention according to a sixth embodiment; Fig. 10 is a highly abstracted schematic view of a drive device according to the invention according to a seventh embodiment; Fig. 11 is a highly abstracted schematic view of a drive device according to the invention according to an eighth embodiment; and Fig. 12 a highly abstracted schematic view of a drive device according to the invention according to a ninth embodiment.

[0025] Fig. 1 shows a motor vehicle 100 with a first wheel axle 101 with two wheels R1, R2 and a second wheel axle 102 with two wheels R3, R4. In the present case, the first wheel axle 101 is designed as the rear drive axle of the motor vehicle 100 and is equipped with a drive device according to the invention, which has a single drive motor 2 designed as an electric machine and a transmission 1 designed as an epicyclic gear train. Thus, the motor vehicle 100 is designed as an electric vehicle. The drive device is arranged transversely to the vehicle's longitudinal direction and is drivingly connected to the wheels R1, R2 of the first wheel axle 101. In the present case, no further drive device is arranged on the second wheel axle 102, i.e., on the front axle of the vehicle 100, thereby saving costs, weight, and installation space. Alternatively, the drive device can also be arranged on the front axle of the motor vehicle 100 instead of on the rear axle.To implement an all-wheel drive system, a further drive device can be arranged on the second wheel axle 102 and can be drivingly connected to the wheels R3, R4 of this wheel axle 102.

[0026] Fig. 2 and Fig. 3 each show a schematic diagram of the drive device according to Fig. 1. The transmission 1 of the drive device comprises a first planetary gear set P1, a second planetary gear set P2 and a third planetary gear set P3, each graphically represented by a circle. Each planetary gear set P1, P2, P3 has a first element, a second element and a third element, each of which is indicated by three connection options on the respective planetary gear set P1, P2, P3. Furthermore, the transmission 1 comprises five shafts, namely an input shaft WAn for connecting the transmission 1 to the drive engine 2, a first output shaft WAb1 and a second output shaft WAb2, each for connecting the transmission 1 to a wheel of the motor vehicle, as well as a first coupling shaft W1 and a second coupling shaft W2.

[0027] One of the elements of the second planetary gear set P2 is rotationally fixedly connected to the input shaft WAn. The second planetary gear set P2 is drive-effectively connected to the drive motor 2 via the input shaft WAn. In other words, at least one further shaft, gear, shift element, or the like can be arranged in the power flow between the drive motor 2 and the input shaft WAn. Another of the elements of the second planetary gear set P2 is rotationally fixedly connected to the first coupling shaft W1. Another of the elements of the second planetary gear set P2 is rotationally fixedly connected to the second coupling shaft W2.

[0028] One of the elements of the third planetary gear set P3 is rotationally fixed to the first coupling shaft W1. Thus, the third planetary gear set P3 is connected to the second planetary gear set P2 via the first coupling shaft W1. Another of the elements of the third planetary gear set P3 is rotationally fixed to a stationary component of the transmission 1, designed as a housing G, and is thus prevented from rotating. Another of the elements of the third planetary gear set P3 is rotationally fixed to the second output shaft WAb2.

[0029] One of the elements of the first planetary gear set P1 is rotationally fixed to the second coupling shaft W2. Thus, the first planetary gear set P1 is connected to the second planetary gear set P2 via the second coupling shaft W2. Another of the elements of the first planetary gear set P1 is rotationally fixed to the first output shaft WAb1. Another of the elements of the first planetary gear set P1 is rotationally fixed to the second output shaft WAb2. Thus, the first planetary gear set P1 is connected to the third planetary gear set P3 via the second output shaft WAb2.

[0030] According to Fig. 2, the transmission 1 further comprises a shifting element S for transmitting a torque between the second output shaft WAb2 and the second coupling shaft W2. In other words, the second coupling shaft W2 can be connected to the second output shaft WAb2 via the shifting element S.

[0031] According to Fig. 3, the transmission 1 comprises a shifting element S for transmitting a torque between the first output shaft WAb1 and the second coupling shaft W2. In other words, the second coupling shaft W2 can be connected to the first output shaft WAb1 via the shifting element S.

[0032] The shifting element is provided as a differential lock and is preferably designed as a friction clutch. For example, the friction clutch comprises at least two corresponding friction surfaces, i.e. a pair of friction surfaces. For example, the friction clutch is designed as a multi-plate clutch and comprises several pairs of friction surfaces acting in parallel. For example, the friction surfaces are flat. Alternatively, the friction surfaces are conical, which can increase a friction torque. For example, a friction element designed as a friction plate or friction cone or a component axially adjacent to it serves to adjust the axial play. Alternatively, the shifting element S is designed as a dog clutch. Alternatively, the shifting element is designed as a synchronizer. The shifting element S is preferably actuated by means of a hydraulic cylinder that is fixed to the housing or arranged to rotate with the housing.Alternatively, the switching element S is actuated electromechanically, for example, via a spindle, a ramp, or a lever. Alternatively, the switching element S is actuated electromagnetically. The force required to actuate the switching element S results at least partially or entirely from an axial force from at least one helical gear. In particular, the power flow in the first planetary gear set P1 is configured such that forces from the at least one helical gear act on the switching element S during traction and overrun operation of the drive train.

[0033] According to the invention, the shifting element S is provided for transmitting a torque between one of the two output shafts WAb1, WAb2 and the second coupling shaft W2. In particular, one of the two output shafts WAb1, WAb2 is rotationally fixedly connected to an element of the first planetary gear set P1 designed as a planet carrier. The reaction torque of the drive motor 2, in sum with the housing support torque, is inversely equal to the output torques on the two output shafts WAb1, WAb2. Therefore, there is no summation of the output torques analogous to a differential carrier on a rotating component. The sum of the two output torques is not applied to any rotating component of the transmission 1. The sum of the output torques is greater than the input torque, since this is not just a differential, but a transmission with a differential function.

[0034] When the vehicle is traveling straight ahead, the first planetary gear set P1 rotates in a single unit, so that the elements of the first planetary gear set P1 do not roll, thus generating no corresponding losses. The second planetary gear set P2 has no housing support, so that all three elements of the second planetary gear set P2 can rotate. The third planetary gear set P3 has a housing support, which enables torque conversion. The three planetary gear sets P1, P2, and P3 are interconnected in such a way that each planetary gear set P1, P2, and P3 shares exactly one rotationally fixed connection with each planetary gear set P1, P2, and P3.

[0035] Fig. 4 schematically shows the drive device with the transmission 1 according to a first embodiment. The advantage of this first embodiment is the good efficiency and the wide gear ratio range of the transmission 1. The transmission 1 comprises the first planetary gear set P1, the second planetary gear set P2 and the third planetary gear set P3, wherein each of the three planetary gear sets P1, P2, P3 has a first element E11, E21, E31, a second element E12, E22, E32 and a third element E13, E23, E33. In the present case, the first element E11, E21, E31 of the respective planetary gear set P1, P2, P3 is designed as a sun gear, wherein the second element E12, E22, E32 of the respective planetary gear set P1, P2, P3 is designed as a planet carrier, wherein the third element E13, E23, E33 of the respective planetary gear set P1, P2, P3 is designed as a ring gear.Each planet carrier carries at least one planetary gear, which meshes with the sun gear and the ring gear of the respective planetary gear set P1, P2, P3. Thus, each of the three planetary gear sets P1, P2, P3 is designed as a negative planetary gear set.

[0036] The first element E21 of the second planetary gear set P2 is rotationally fixedly connected to the input shaft WAn, wherein the second element E22 of the second planetary gear set P2 is rotationally fixedly connected to the first coupling shaft W1, wherein the third element E23 of the second planetary gear set P2 is rotationally fixedly connected to the second coupling shaft W2. The input shaft WAn is rotationally fixedly connected to the drive motor 2. Alternatively, further elements, in particular shafts, gears, switching elements or other devices, can be arranged in the power flow between the drive motor 2 and the input shaft WAn. For example, the power flow between the drive motor 2 and the input shaft WAn can be interrupted by such a switching element.

[0037] The first element E31 of the third planetary gear set P3 is connected in a rotationally fixed manner to the first coupling shaft W1, wherein the second element E32 of the third planetary gear set P3 is connected in a rotationally fixed manner to a stationary component designed as a housing G, wherein the third element E33 of the third planetary gear set P3 is connected in a rotationally fixed manner to the second output shaft WAb2.

[0038] The first element E11 of the first planetary gear set P1 is connected in a rotationally fixed manner to the second coupling shaft W2, wherein the second element E12 of the first planetary gear set P1 is connected in a rotationally fixed manner to the first output shaft WAb1, wherein the third element E13 of the first planetary gear set P1 is connected in a rotationally fixed manner to the second output shaft WAb2.

[0039] Thus, the third element E13 of the first planetary gear set P1 and the third element E33 of the third planetary gear set P3 are connected to one another in a rotationally fixed manner via the second output shaft WAb2. Furthermore, the first coupling shaft W1 connects the second element E12 of the second planetary gear set P2 in a rotationally fixed manner to the first element E31 of the third planetary gear set P3, while the second coupling shaft W2 connects the third element E23 of the second planetary gear set P2 in a rotationally fixed manner to the first element E11 of the first planetary gear set P1.

[0040] The second planetary gear set P2 is arranged axially between the third planetary gear set P3 and the first planetary gear set P1, with the third planetary gear set P3 axially adjacent to the drive motor 2. This gives the drive device a compact design. All three planetary gear sets P1, P2, P3 are arranged on a common axis of rotation R. The drive motor 2 is arranged coaxially to the axis of rotation R. The input shaft WAn is designed as a hollow shaft, with the first output shaft WAb1 extending axially through the input shaft WAn and the drive motor 2. The respective output shaft WAb1, WAb2 is, for example, connected in a rotationally fixed manner to a respective wheel of the motor vehicle. Alternatively, the respective output shaft WAb1, WAb2 can be connected indirectly to a respective wheel of the motor vehicle via further transmission elements, in particular spur gear stages, chain drives or cardan shafts.

[0041] The shifting element S is designed to transmit a torque between the second output shaft WAb2 and the second coupling shaft W2, wherein the shifting element S, in a closed state, connects the third element E13 of the first planetary gear set P1 and the first element E11 of the first planetary gear set P1 in a rotationally fixed manner. This blocks the first planetary gear set P1. If the shifting element S is only partially closed, then only a portion of the torque is transmitted between the second coupling shaft W2 and the second output shaft WAb2. By arranging the shifting element S in the power flow between the sun gear and the ring gear of the first planetary gear set P1, the first planetary gear set P1 can be at least partially or completely blocked, wherein the torques occurring in the shifting element S are then lower than when the shifting element S is arranged between the two output shafts WAb1, WAb2.The shifting element S is therefore effectively arranged between the second coupling shaft W2 and the second output shaft WAb2 and acts between the first element E11 of the first planetary gear set P1 and the third element E13 of the first planetary gear set P1. The shifting element S is arranged axially adjacent to the first planetary gear set P1. The shifting element S is arranged axially between the first planetary gear set P1 and the second planetary gear set P2. Alternatively, and not shown here, the shifting element S can be arranged radially on the outside around the second planetary gear set P2. The second planetary gear set P2 can, for example, be designed with a particularly small diameter, which results in space radially between the second planetary gear set P2 and the second output shaft WAb2 in which to arrange the shifting element S. If the shifting element S is arranged radially nested with the second planetary gear set P2, axial length can be saved.

[0042] Fig. 5 shows a second embodiment of the drive device according to the invention. The drive device according to Fig. 5 essentially corresponds to the drive device according to Fig. 4, wherein a difference between these two embodiments lies in the arrangement and connection of the shifting element S. In the present case, the shifting element S is designed to transmit a torque between the first output shaft WAb1 and the second coupling shaft W2, wherein the shifting element S, in a closed state, rotationally fixedly connects the second element E12 of the first planetary gear set P1 and the first element E11 of the first planetary gear set P1. Thus, the shifting element S acts between the first element E11 of the first planetary gear set P1 and the second element E12 of the first planetary gear set P1. The shifting element S is arranged axially adjacent to the first planetary gear set P1.By arranging the shifting element S in the power flow between the sun gear and the planet carrier of the first planetary gear set P1, the first planetary gear set P1 can be at least partially or completely locked, the torques occurring in the shifting element S then being lower than when the shifting element S is arranged between the two output shafts WAb1, WAb2. Although the torques in the shifting element S are higher than when the shifting element S is arranged in the power flow between the sun gear and the ring gear of the first planetary gear set P1, this can result in design advantages, in particular when arranging the shifting element S in the power flow between the sun gear and the ring gear of the first planetary gear set P1 is not structurally possible due to the connectability. Otherwise, the exemplary embodiment corresponds to . Fig. 5 the embodiment according to Fig. 4, to which reference is made.

[0043] Fig. 6 shows a third embodiment of the drive device according to the invention. The drive device according to Fig. 6 essentially corresponds to the drive device according to Fig. 4, wherein one difference between these two embodiments lies in the arrangement of the first and second planetary gear sets P1, P2. An advantage of this third embodiment compared to the first embodiment is a short axial length of the transmission 1. In the present case, the first and second planetary gear sets P1, P2 are arranged radially nested, with the second planetary gear set P2 being arranged radially on the inside and the first planetary gear set P1 being arranged radially on the outside. Thus, the second planetary gear set P2 is arranged closer to the axis of rotation R than the second planetary gear set P2. The elements E11, E12, E13 of the first planetary gear set P1 and the elements E21, E22, E23 of the second planetary gear set P2 overlap in the axial direction. The second coupling shaft W2 is designed as an intermediate gear with internal teeth and external teeth and connects the first planetary gear set P1 and the second planetary gear set P2.In other words, the third element E23 of the second planetary gear set P2, the first element E11 of the first planetary gear set P1, and the second coupling shaft W2 are formed as a single, common component. The internal toothing of the intermediate gear forms a ring gear for the radially inner second planetary gear set P2. The external toothing of the intermediate gear forms a sun gear for the radially outer first planetary gear set P1. The intermediate gear makes the transmission 1 more compact and lighter. Furthermore, the first and third planetary gear sets P1, P3 have a common ring gear. In other words, the third element E13 of the first planetary gear set P1 and the third element E33 of the third planetary gear set P3 are formed as a single component with a single toothing. This reduces assembly effort and increases compactness. In particular, the second output shaft WAb2 is formed as a single piece with the common ring gear.The shifting element S is operatively arranged between the second coupling shaft W2 and the second output shaft WAb2. Thus, the shifting element S acts between the first element E11 of the first planetary gear set P1 and the third element E13 of the first planetary gear set P1. The shifting element S is arranged axially adjacent to the third planetary gear set P3. The shifting element S is arranged axially between the first planetary gear set P1 and the third planetary gear set P3. Otherwise, the embodiment shown in FIG. Fig. 6 the embodiment according to Fig. 4, to which reference is made.

[0044] Fig. Figure 7 shows a fourth embodiment of the drive device according to the invention. The drive device according to Fig. 7 essentially corresponds to the drive device according to Fig. 4, wherein a difference between these two embodiments lies in the connection of the first and second planetary gear sets P1, P2. In the present case, the first element E21 of the second planetary gear set P2 is rotationally fixed to the input shaft WAn, wherein the second element E22 of the second planetary gear set P2 is rotationally fixed to the second coupling shaft W2, wherein the third element E23 of the second planetary gear set P2 is rotationally fixed to the first coupling shaft W1. The first element E31 of the third planetary gear set P3 is rotationally fixed to the first coupling shaft W1, wherein the second element E32 of the third planetary gear set P3 is rotationally fixed to a stationary component designed as a housing G, wherein the third element E33 of the third planetary gear set P3 is rotationally fixed to the second output shaft WAb2.Furthermore, the first element E11 of the first planetary gear set P1 is rotationally fixedly connected to the second output shaft WAb2, wherein the second element E12 of the first planetary gear set P1 is rotationally fixedly connected to the first output shaft WAb1, wherein the third element E13 of the first planetary gear set P1 is rotationally fixedly connected to the second coupling shaft W2. The shifting element S is operatively arranged between the second coupling shaft W2 and the second output shaft WAb2. Thus, the shifting element S acts between the first element E11 of the first planetary gear set P1 and the third element E13 of the first planetary gear set P1. The shifting element S is arranged axially adjacent to the first planetary gear set P1. The shifting element S is arranged axially between the first planetary gear set P1 and the second planetary gear set P2. Alternatively, and not shown here, the shifting element S can be arranged radially outward around the second planetary gear set P2.The second planetary gear set P2 can, for example, be designed with a particularly small diameter, which results in space radially between the second planetary gear set P2 and the second output shaft WAb2 for arranging the shifting element S. If the shifting element S is arranged radially nested with the second planetary gear set P2, axial length can be saved. Otherwise, the embodiment according to . Fig. 7 the embodiment according to Fig. 4, to which reference is made.

[0045] Fig. Figure 8 shows a fifth embodiment of the drive device according to the invention. The drive device according to Fig. 8 essentially corresponds to the drive device according to Fig. 7, wherein one difference between these two embodiments lies in the arrangement of the first and third planetary gear sets P1, P3. An advantage of this fifth embodiment compared to the fourth embodiment is a short axial length of the transmission 1. In the present case, the first and third planetary gear sets P1, P3 are arranged radially nested, with the third planetary gear set P3 being arranged radially on the inside and the first planetary gear set P1 being arranged radially on the outside. The third planetary gear set P3 is therefore arranged closer to the axis of rotation R than the first planetary gear set P1. The elements E11, E12, E13 of the first planetary gear set P1 and the elements E31, E32, E33 of the third planetary gear set P3 overlap in the axial direction. An intermediate gear with an internal toothing and an external toothing is arranged in the power flow between the first planetary gear set P1 and the third planetary gear set P3.The third element E33 of the third planetary gear set P3, the first element E11 of the first planetary gear set P1 and the second output shaft WAb2 are designed as a common component. The internal toothing forms a ring gear for the radially inner third planetary gear set P3. The external toothing forms a sun gear for the radially outer first planetary gear set P1. The intermediate gear makes the transmission 1 more compact and lighter. The shifting element S is effectively arranged between the second coupling shaft W2 and the second output shaft WAb2. The shifting element S therefore acts between the first element E11 of the first planetary gear set P1 and the third element E13 of the first planetary gear set P1. The shifting element S is arranged axially adjacent to the first planetary gear set P1. Otherwise, the exemplary embodiment corresponds to that shown in FIG. Fig. 8 the embodiment according to Fig. 7, to which reference is made.

[0046] Fig. 9 shows a sixth embodiment of the drive device according to the invention. The drive device according to Fig. 9 essentially corresponds to the drive device according to Fig. 4, wherein a difference between these two embodiments lies in the connection of the third planetary gear set P3. In the present case, the first element E21 of the second planetary gear set P2 is rotationally fixedly connected to the input shaft WAn, wherein the second element E22 of the second planetary gear set P2 is rotationally fixedly connected to the first coupling shaft W1, wherein the third element E23 of the second planetary gear set P2 is rotationally fixedly connected to the second coupling shaft W2. The first element E31 of the third planetary gear set P3 is rotationally fixedly connected to the first coupling shaft W1, wherein the second element E32 of the third planetary gear set P3 is rotationally fixedly connected to a stationary component designed as a housing G, wherein the third element E33 of the third planetary gear set P3 is rotationally fixedly connected to the second output shaft WAb2.Furthermore, the first element E11 of the first planetary gear set P1 is rotationally fixedly connected to the second output shaft WAb2, wherein the second element E12 of the first planetary gear set P1 is rotationally fixedly connected to the first output shaft WAb1, wherein the third element E13 of the first planetary gear set P1 is rotationally fixedly connected to the second coupling shaft W2. Furthermore, the first and second planetary gear sets P1, P2 have a common ring gear with a single toothing. In other words, the third element E13 of the first planetary gear set P1, the third element E23 of the second planetary gear set P2 and the second coupling shaft W2 are formed as a common component. This reduces assembly effort and increases compactness. The shifting element S is operatively arranged between the second coupling shaft W2 and the second output shaft WAb2.Thus, the shifting element S acts between the first element E11 of the first planetary gear set P1 and the third element E13 of the first planetary gear set P1. The shifting element S is arranged axially adjacent to the first planetary gear set P1. Otherwise, the embodiment shown in FIG. Fig. 9 the embodiment according to Fig. 4, to which reference is made.

[0047] Fig. 10 shows a seventh embodiment of the drive device according to the invention. The drive device according to Fig. 10 essentially corresponds to the drive device according to Fig. 9, wherein one difference between these two embodiments lies in the arrangement of the first and third planetary gear sets P1, P3. An advantage of this seventh embodiment compared to the sixth embodiment is a short axial length of the transmission 1. In the present case, the first and third planetary gear sets P1, P3 are arranged radially nested, with the third planetary gear set P3 being arranged radially on the inside and the first planetary gear set P1 being arranged radially on the outside. Thus, the third planetary gear set P3 is arranged closer to the axis of rotation R than the first planetary gear set P1. The elements E11, E12, E13 of the first planetary gear set P1 and the elements E31, E32, E33 of the third planetary gear set P3 overlap in the axial direction. An intermediate gear with an internal toothing and an external toothing is arranged in the power flow between the first planetary gear set P1 and the third planetary gear set P3.In this case, the third element E33 of the third planetary gear set P3 and the first element E11 of the first planetary gear set P1 form a common component. The internal toothing of the intermediate gear forms a ring gear for the radially inner third planetary gear set P3. The external toothing of the intermediate gear forms a sun gear for the radially outer first planetary gear set P1. The intermediate gear makes the transmission 1 more compact and lighter. Furthermore, the first and second planetary gear sets P1, P2 have a common ring gear with a single toothing. In other words, the third element E13 of the first planetary gear set P1, the third element E23 of the second planetary gear set P2 and the second coupling shaft W2 are formed as a common component. This reduces assembly effort and increases compactness. The shifting element S is operatively arranged between the second coupling shaft W2 and the second output shaft WAb2.Thus, the shifting element S acts between the first element E11 of the first planetary gear set P1 and the third element E13 of the first planetary gear set P1. The shifting element S is arranged axially adjacent to the second planetary gear set P2. The shifting element S is arranged axially between the first planetary gear set P1 and the second planetary gear set P2. Otherwise, the embodiment according to . Fig. 10 the embodiment according to Fig. 9, to which reference is made.

[0048] Fig. 11 shows an eighth embodiment of the drive device according to the invention. The drive device according to Fig. 11 essentially corresponds to the drive device according to Fig. 4, wherein a difference between these two embodiments lies in the connection of the planetary gear sets P1, P2, P3. In the present case, the first element E21 of the second planetary gear set P2 is rotationally fixedly connected to the input shaft WAn, wherein the second element E22 of the second planetary gear set P2 is rotationally fixedly connected to the first coupling shaft W1, wherein the third element E23 of the second planetary gear set P2 is rotationally fixedly connected to the second coupling shaft W2. The first element E31 of the third planetary gear set P3 is rotationally fixedly connected to the first coupling shaft W1, wherein the second element E32 of the third planetary gear set P3 is rotationally fixedly connected to the second output shaft WAb2, wherein the third element E33 of the third planetary gear set P3 is rotationally fixedly connected to a stationary component designed as a housing G.Furthermore, the first element E11 of the first planetary gear set P1 is rotationally fixedly connected to the second coupling shaft W2, wherein the second element E12 of the first planetary gear set P1 is rotationally fixedly connected to the second output shaft WAb2, wherein the third element E13 of the first planetary gear set P1 is rotationally fixedly connected to the first output shaft WAb1. The input shaft WAn is designed as a hollow shaft, wherein the second output shaft WAb2 extends axially through the input shaft WAn and the drive machine 2. The shifting element S is operatively arranged between the second coupling shaft W2 and the second output shaft WAb2. Thus, the shifting element S acts between the first element E11 of the first planetary gear set P1 and the second element E12 of the first planetary gear set P1. The shifting element S is arranged axially adjacent to the first planetary gear set P1. The shifting element S is arranged axially between the first planetary gear set P1 and the second planetary gear set P2.Alternatively, and not shown here, the shifting element S can be arranged radially on the outside around the second planetary gear set P2. The second planetary gear set P2 can, for example, be designed to be particularly small in diameter, which means that there is space radially between the second planetary gear set P2 and the second output shaft WAb2 in order to arrange the shifting element S there. If the shifting element S is arranged radially nested with the second planetary gear set P2, axial length can be saved. Otherwise, the exemplary embodiment corresponds to . Fig. 11 the embodiment according to Fig. 4, to which reference is made.

[0049] Fig. 12 shows a ninth embodiment of the drive device according to the invention. The drive device according to Fig. 12 essentially corresponds to the drive device according to Fig. 4, wherein a difference between these two embodiments lies in the connection of the planetary gear sets P1, P2, P3. In the present case, the first element E21 of the second planetary gear set P2 is rotationally fixedly connected to the input shaft WAn, wherein the second element E22 of the second planetary gear set P2 is rotationally fixedly connected to the second coupling shaft W2, wherein the third element E23 of the second planetary gear set P2 is rotationally fixedly connected to the first coupling shaft W1. The first element E31 of the third planetary gear set P3 is rotationally fixedly connected to the first coupling shaft W1, wherein the second element E32 of the third planetary gear set P3 is rotationally fixedly connected to the second output shaft WAb2, wherein the third element E33 of the third planetary gear set P3 is rotationally fixedly connected to a stationary component designed as a housing G.Furthermore, the first element E11 of the first planetary gear set P1 is rotationally fixedly connected to the second coupling shaft W2, wherein the second element E12 of the first planetary gear set P1 is rotationally fixedly connected to the second output shaft WAb2, wherein the third element E13 of the first planetary gear set P1 is rotationally fixedly connected to the first output shaft WAb1. The input shaft WAn is designed as a hollow shaft, wherein the second output shaft WAb2 extends axially through the input shaft WAn and the drive machine 2. The shifting element S is operatively arranged between the second coupling shaft W2 and the second output shaft WAb2. Thus, the shifting element S acts between the first element E11 of the first planetary gear set P1 and the second element E12 of the first planetary gear set P1. The shifting element S is arranged axially adjacent to the first planetary gear set P1. The shifting element S is arranged axially between the first planetary gear set P1 and the second planetary gear set P2.Alternatively, and not shown here, the shifting element S can be arranged radially on the outside around the second planetary gear set P2. The second planetary gear set P2 can, for example, be designed to be particularly small in diameter, which means that there is space radially between the second planetary gear set P2 and the second output shaft WAb2 in order to arrange the shifting element S there. If the shifting element S is arranged radially nested with the second planetary gear set P2, axial length can be saved. Otherwise, the exemplary embodiment corresponds to . Fig. 12 the embodiment according to Fig. 4, to which reference is made.

[0050] According to all nine exemplary embodiments, the transmission 1 comprises the first planetary gear set P1, which is designed as a minus planetary gear set with a sun gear, a ring gear and a planet carrier, the input shaft WAn, which is designed to connect the transmission 1 to the drive engine 2, the first output shaft WAb1 and the second output shaft WAb2, each of which is designed to connect the transmission 1 to a wheel of the motor vehicle, and the shifting element S. One of the elements E11, E12, E13 of the first planetary gear set P1 is always connected in a rotationally fixed manner to the first output shaft WAb1, wherein another of the elements E11, E12, E13 of the first planetary gear set P1 is always connected in a rotationally fixed manner to the second output shaft WAb2, and wherein another of the elements E11, E12, E13 of the first planetary gear set P1 is always connectable via the shifting element S to one of the two output shafts WAb1, WAb2. is. Reference symbol 1 gearbox 2 drive machine W1 first coupling shaft W2 second coupling shaft WAn drive shaft WAb1 first output shaft WAb2 second output shaft G Housing S switching element R rotation axis P1 first planetary gear set E11 first element of the first planetary gear set E12 second element of the first planetary gear set E13 third element of the first planetary gear set P2 second planetary gear set E21 first element of the second planetary gear set E22 second element of the second planetary gear set E23 third element of the second planetary gear set P3 third planetary gear set E31 first element of the third planetary gear set E32 second element of the third planetary gear set E33 third element of the third planetary gear set 100 motor vehicles 101 first wheel axle 102 second wheel axle R1 wheel R2 wheel R3 bike R4 wheel

Claims

[1] Transmission (1) for a motor vehicle (100), comprising • a first planetary gear set (P1), a second planetary gear set (P2) and a third planetary gear set (P3), each planetary gear set (P1, P2, P3) having a first element (E11, E21, E31), a second element (E12, E22, E32) and a third element (E13, E23, E33), • exactly one drive shaft (WAn) for connecting the transmission (1) to a drive engine (2) of the motor vehicle (100), • a first output shaft (WAb1) and a second output shaft (WAb2) each for connecting the transmission (1) to a wheel (R1, R2) of the motor vehicle (100), • a first coupling shaft (W1) and a second coupling shaft (W2) each for the rotationally fixed connection of two elements of two planetary gear sets (P1, P2, P3), • a switching element (S) for transmitting a torque between one of the two output shafts (WAb1, WAb2) and the second coupling shaft (W2), • wherein one of the elements (E21, E22, E23) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the drive shaft (WAn), wherein another of the elements (E21, E22, E23) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the first coupling shaft (W1), wherein another of the elements (E21, E22, E23) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the second coupling shaft (W2), • wherein one of the elements (E31, E32, E33) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the first coupling shaft (W1), wherein another of the elements (E31, E32, E33) of the third planetary gear set (P3) is connected in a rotationally fixed manner to a stationary component, wherein another of the elements (E31, E32, E33) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the second output shaft (WAb2), • wherein one of the elements (E11, E12, E13) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the second coupling shaft (W2), wherein another of the elements (E11, E12, E13) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the first output shaft (WAb1), wherein another of the elements (E11, E12, E13) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the second output shaft (WAb2). [2] Transmission according to claim 1, • wherein the first element (E21) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the drive shaft (WAn), wherein the second element (E22) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the first coupling shaft (W1), wherein the third element (E23) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the second coupling shaft (W2), • wherein the first element (E31) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the first coupling shaft (W1), wherein the second element (E32) of the third planetary gear set (P3) is connected in a rotationally fixed manner to a stationary component, wherein the third element (E33) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the second output shaft (WAb2), • wherein the first element (E11) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the second coupling shaft (W2), wherein the second element (E12) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the first output shaft (WAb1), wherein the third element (E13) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the second output shaft (WAb2). [3] Transmission (1) according to claim 1, • wherein the first element (E21) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the drive shaft (WAn), wherein the second element (E22) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the second coupling shaft (W2), wherein the third element (E23) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the first coupling shaft (W1), • wherein the first element (E31) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the first coupling shaft (W1), wherein the second element (E32) of the third planetary gear set (P3) is connected in a rotationally fixed manner to a stationary component, wherein the third element (E33) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the second output shaft (WAb2), • wherein the first element (E11) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the second output shaft (WAb2), wherein the second element (E12) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the first output shaft (WAb1), wherein the third element (E13) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the second coupling shaft (W2). [4] Transmission (1) according to claim 1, • wherein the first element (E21) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the drive shaft (WAn), wherein the second element (E22) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the first coupling shaft (W1), wherein the third element (E23) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the second coupling shaft (W2), • wherein the first element (E31) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the first coupling shaft (W1), wherein the second element (E32) of the third planetary gear set (P3) is connected in a rotationally fixed manner to a stationary component, wherein the third element (E33) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the second output shaft (WAb2), • wherein the first element (E11) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the second output shaft (WAb2), wherein the second element (E12) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the first output shaft (WAb1), wherein the third element (E13) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the second coupling shaft (W2). [5] Transmission (1) according to claim 1, • wherein the first element (E21) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the drive shaft (WAn), wherein the second element (E22) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the first coupling shaft (W1), wherein the third element (E23) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the second coupling shaft (W2), • wherein the first element (E31) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the first coupling shaft (W1), wherein the second element (E32) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the second output shaft (WAb2), wherein the third element (E33) of the third planetary gear set (P3) is connected in a rotationally fixed manner to a stationary component, • wherein the first element (E11) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the second coupling shaft (W2), wherein the second element (E12) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the second output shaft (WAb2), wherein the third element (E13) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the first output shaft (WAb1). [6] Transmission (1) according to claim 1, • wherein the first element (E21) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the drive shaft (WAn), wherein the second element (E22) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the second coupling shaft (W2), wherein the third element (E23) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the first coupling shaft (W1), • wherein the first element (E31) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the first coupling shaft (W1), wherein the second element (E32) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the second output shaft (WAb2), wherein the third element (E33) of the third planetary gear set (P3) is connected in a rotationally fixed manner to a stationary component, • wherein the first element (E11) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the second coupling shaft (W2), wherein the second element (E12) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the second output shaft (WAb2), wherein the third element (E13) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the first output shaft (WAb1). [7] Transmission (1) according to one of the preceding claims, wherein two of the three planetary gear sets (P1, P2, P3) are arranged radially nested. [8] Transmission (1) according to one of the preceding claims, wherein one of the two coupling shafts (W1, W2) or one of the two output shafts (WAb1, WAb2) is formed in one piece with the elements of the respective planetary gear set (P1, P2, P3) connected thereto. [9] Transmission (1) according to one of the preceding claims, wherein at least one of the planetary gear sets (P1, P2, P3) is designed as a minus planetary gear set, wherein the first element (E11, E21, E31) of the respective planetary gear set (P1, P2, P3) is designed as a sun gear, wherein the second element (E12, E22, E32) of the respective planetary gear set (P1, P2, P3) is designed as a planet carrier, wherein the third element (E13, E23, E33) of the respective planetary gear set (P1, P2, P3) is designed as a ring gear. [10] Transmission (1) for a motor vehicle (100), comprising • at least one first planetary gear set (P1) with a first element (E11), a second element (E12) and a third element (E13), wherein the first planetary gear set (P1) is designed as a minus planetary gear set with a sun gear, a ring gear and a planet carrier, • a drive shaft (WAn) for connecting the transmission (1) to a drive engine (2) of the motor vehicle (100), • a first output shaft (WAb1) and a second output shaft (WAb2) each for connecting the transmission (1) to a wheel (R1, R2) of the motor vehicle (100), • a switching element (S), • wherein one of the elements (E11, E12, E13) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the first output shaft (WAb1), wherein another of the elements (E11, E12, E13) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the second output shaft (WAb2), and wherein another of the elements (E11, E12, E13) of the first planetary gear set (P1) is connectable to one of the two output shafts (WAb1, WAb2) via the switching element (S). [11] Transmission (1) according to one of the preceding claims, wherein the switching element (S) is designed as a friction clutch or claw clutch. [12] Transmission (1) according to one of the preceding claims, wherein actuation of the switching element (S) takes place at least partially by means of an axial force resulting from a helical toothing. [13] Transmission (1) according to one of the preceding claims, wherein the switching element (S) in a closed state connects the third element (E13) of the first planetary gear set (P1) and the first element (E11) of the first planetary gear set (P1) in a rotationally fixed manner. [14] Transmission (1) according to one of claims 1 to 12, wherein the switching element (S) in a closed state connects the second element (E12) of the first planetary gear set (P1) and the first element (E11) of the first planetary gear set (P1) in a rotationally fixed manner. [15] Drive device with a drive machine (2) and a transmission (1) according to one of claims 1 to 14.

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