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), • a 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), • wherein one of the elements (E11, E21, E31) of the first planetary gear set (P1) is non-rotatably connected to the drive shaft (WAn), wherein another of the elements (E11, E21, E31) of the first planetary gear set (P1) is non-rotatably connected to the first coupling shaft (W1), wherein another of the elements (E11, E21, E31) of the first planetary gear set (P1) is non-rotatably connected to the second coupling shaft (W2), • wherein one of the elements (E12, E22, E32) of the second planetary gear set (P2) is non-rotatably connected to the first coupling shaft (W1), wherein another of the elements (E12, E22, E32) of the second planetary gear set (P2) is non-rotatably connected to a stationary component, wherein a further element (E12, E22, E32) of the second planetary gear set (P2) is non-rotatably connected to the second output shaft (WAb2), • wherein one of the elements (E13, E23, E33) of the third planetary gear set (P3) is non-rotatably connected to the second coupling shaft (W2), wherein another of the elements (E13, E23, E33) of the third planetary gear set (P3) is non-rotatably connected to the first output shaft (WAb1), wherein another of the elements (E13, E23, E33) of the third planetary gear set (P3) is non-rotatably connected to the second output shaft (WAb2).

Description

[0001] The invention relates to a transmission for a motor vehicle comprising three planetary gear sets and five shafts, wherein one of the five shafts is designed as a drive shaft and is configured to be effectively connected to a drive motor, and wherein two of the five shafts are designed as output shafts and are configured to be effectively connected to a respective wheel of the motor vehicle. The invention further relates to a drive device with such a transmission and to a motor vehicle with such a drive device.

[0002] For example, DE 10 2013 215 877 A1 discloses a planetary gear transmission 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 planetary gear transmission comprises a first gear stage having a first sun gear, a first planet set, a first planet carrier, and a first ring gear; a second gear stage having a second sun gear, a second planet set, a second planet carrier, and a second ring gear; and a third planet stage having a third sun gear, a third planet set, and a third planet carrier.The first sun gear is configured as a power input, the first planet carrier is rotationally fixed 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 is via the third gear stage, and the second power output is via the second ring gear of the second gear stage.

[0003] The object of the present invention is to provide an alternative transmission that exhibits, in particular, improved power density and improved efficiency. The transmission is intended to generate two approximately equal output torques, which are greater than the input torque, from a single input torque. Thus, the transmission is intended to perform both a transmission function, i.e., a torque conversion, and a differential function. These objectives are achieved by a transmission with the features of claim 1.

[0004] Advantageous embodiments are the subject of the dependent claims, the following description and the figures.

[0005] 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, wherein each planetary gear set has a first element, a second element and a third element, five shafts, namely a drive shaft for connecting the transmission to a drive motor 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, • wherein one of the elements of the first planetary gear set is non-rotatably connected to the drive shaft, wherein another of the elements of the first planetary gear set is non-rotatably connected to the first coupling shaft, wherein another of the elements of the first planetary gear set is non-rotatably connected to the second coupling shaft, • wherein one of the elements of the second planetary gear set is non-rotatably connected to the first coupling shaft, wherein another of the elements of the second planetary gear set is non-rotatably connected to a stationary component, wherein another of the elements of the second planetary gear set is non-rotatably connected to the second output shaft, • wherein one of the elements of the third planetary gear set is non-rotatably connected to the second coupling shaft, wherein another of the elements of the third planetary gear set is non-rotatably connected to the first output shaft, wherein another of the elements of the third planetary gear set is non-rotatably connected to the second output shaft.

[0006] The term "connection" of a device or element to the gearbox means that the gearbox, in particular the corresponding shaft of the gearbox, is connected either directly, for example, in a rotationally fixed manner, to the device or element, or indirectly, for example, via at least one further component, in particular via at least one further shaft or gear. If two shafts are rotationally fixed to each other, they rotate together in one direction at one rotational speed. In particular, the connection can also be effected via a switching element, which enables a drive-effective coupling and decoupling of the device or element with the corresponding shaft of the gearbox.

[0007] The term "shaft" does not refer exclusively to, for example, a cylindrical, rotatably mounted gear element for transmitting torque, but rather also encompasses general connecting elements that join individual components or elements together, in particular connecting elements that non-rotatably join several elements. Two non-rotatably joined shafts can be formed in one piece.

[0008] A "stationary component" is a non-rotating part of the gearbox. For example, the stationary component is designed as the gearbox housing or housing section. Alternatively, the stationary component can be designed as a shaft fixed to the housing.

[0009] Therefore, the first planetary gear set is connected or connectable to the drive motor, at least indirectly or directly, via the drive shaft, and to the second planetary gear set via the first coupling shaft, and to the third planetary gear set via the second coupling shaft. Furthermore, the second planetary gear set is rotationally fixed to the housing and connected to the third planetary gear set via the second output shaft. The third planetary gear set is also connected to the first output shaft. The third planetary gear set is connected or connectable, at least indirectly or directly, to a first wheel of the vehicle via the first output shaft. Furthermore, the second and third planetary gear sets are connected or connectable, at least indirectly or directly, to a second wheel of the vehicle via the second output shaft.

[0010] For example, the drive machine is designed as an electric machine that can be operated as a drive motor to propel 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, the rotor being non-rotatably connected to a rotor shaft. The rotor shaft of the electric machine is connected to the drive shaft, at least indirectly or directly. For example, the rotor shaft of the electric machine is connected to the drive shaft via at least one other shaft, via several gears, and / or via a traction element. The electric machine can be arranged on a common axis of rotation with the transmission and thus be coaxial with the drive shaft, in which case the rotor shaft is preferably non-rotatably connected to the drive shaft.Alternatively, the electric machine can be designed parallel to the drive shaft, in which case the rotor shaft is indirectly connected to the drive shaft. Alternatively, the drive machine can be designed as an internal combustion engine with a crankshaft.

[0011] According to a preferred embodiment, the first element of the first planetary gear set is non-rotatably connected to the input shaft, the second element of the first planetary gear set is non-rotatably connected to the first coupling shaft, the third element of the first planetary gear set is non-rotatably connected to the second coupling shaft, the first element of the second planetary gear set is non-rotatably connected to the first coupling shaft, the second element of the second planetary gear set is non-rotatably connected to a stationary component, the third element of the second planetary gear set is non-rotatably connected to the second output shaft, the first element of the third planetary gear set is non-rotatably connected to the second coupling shaft, the second element of the third planetary gear set is non-rotatably connected to the first output shaft, and the third element of the third planetary gear set is non-rotatably connected to the second output shaft.For this purpose, reference is made to the embodiments according to the . Fig. 3 and Fig. 4 referred.

[0012] According to a preferred embodiment, the first element of the first planetary gear set is non-rotatably connected to the drive shaft, the second element of the first planetary gear set is non-rotatably connected to the second coupling shaft, the third element of the first planetary gear set is non-rotatably connected to the first coupling shaft, the first element of the second planetary gear set is non-rotatably connected to the first coupling shaft, the second element of the second planetary gear set is non-rotatably connected to a stationary component, the third element of the second planetary gear set is non-rotatably connected to the second output shaft, the first element of the third planetary gear set is non-rotatably connected to the second output shaft, the second element of the third planetary gear set is non-rotatably connected to the first output shaft, and the third element of the third planetary gear set is non-rotatably connected to the second coupling shaft.For this purpose, reference is made to the embodiments according to the . Fig. 5 and Fig. 6 referred.

[0013] According to a preferred embodiment, the first element of the first planetary gear set is non-rotatably connected to the drive shaft, the second element of the first planetary gear set is non-rotatably connected to the first coupling shaft, the third element of the first planetary gear set is non-rotatably connected to the second coupling shaft, the first element of the second planetary gear set is non-rotatably connected to the first coupling shaft, the second element of the second planetary gear set is non-rotatably connected to a stationary component, the third element of the second planetary gear set is non-rotatably connected to the second output shaft, the first element of the third planetary gear set is non-rotatably connected to the second output shaft, the second element of the third planetary gear set is non-rotatably connected to the first output shaft, and the third element of the third planetary gear set is non-rotatably connected to the second coupling shaft.For this purpose, reference is made to the embodiments according to the . Fig. 7 and Fig. 8 referred.

[0014] According to a preferred embodiment, the first element of the first planetary gear set is non-rotatably connected to the input shaft, the second element of the first planetary gear set is non-rotatably connected to the first coupling shaft, the third element of the first planetary gear set is non-rotatably connected to the second coupling shaft, the first element of the second planetary gear set is non-rotatably connected to the first coupling shaft, the second element of the second planetary gear set is non-rotatably connected to the second output shaft, the third element of the second planetary gear set is non-rotatably connected to a stationary component, the first element of the third planetary gear set is non-rotatably connected to the second coupling shaft, the second element of the third planetary gear set is non-rotatably connected to the second output shaft, and the third element of the third planetary gear set is non-rotatably connected to the first output shaft.For this purpose, reference is made to the embodiment according to . Fig. 9 referred.

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

[0016] 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 located on the outside and the other 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 second and third planetary gear sets are arranged radially nested.

[0017] According to a preferred embodiment, one of the two coupling shafts or one of the two output shafts is formed integrally with the associated elements of the respective planetary gear set. For example, a coupling shaft or an output shaft can be formed integrally as an intermediate gear with two teeth, wherein an internal tooth of the intermediate gear forms a ring gear for a radially inner planetary gear set, and wherein an external tooth of the intermediate gear forms a sun gear for a radially outer planetary gear set. Such an intermediate gear is also called a sun gear. Alternatively, a coupling shaft or an output shaft can have teeth forming a common ring gear for two planetary gear sets. Alternatively, a coupling shaft or an output shaft can have teeth forming a common sun gear for two planetary gear sets. Alternatively, a coupling shaft or an output shaft can form a common planet carrier.

[0018] According to a preferred embodiment, at least one of the planet gear sets is designed as a negative planet gear set, wherein the first element of the respective planet gear set is designed as a sun gear, the second element of the respective planet gear set is designed as a planet carrier, and the third element of the respective planet gear set is designed as a ring gear. Several planet gears are rotatably mounted on the planet carrier and mesh with the sun gear and the ring gear.

[0019] Alternatively, at least one of the planetary gear sets can be designed as a minus-step planetary gear set, in which case the planet carrier rotatably guides several minus-step planetary gears. Each minus-step planetary gear has two gears connected to each other in a rotationally fixed manner. In other words, each minus-step planetary gear has two toothed sections connected to each other in a rotationally fixed manner, which have different diameters. One of the two toothed sections meshes with the sun gear, and the other meshes with the ring gear. If the first element of the minus-step planetary gear set is a sun gear, then the third element of the minus-step planetary gear set is designed as a ring gear. The second element of the minus-step planetary gear set is designed as the planet carrier in both cases.

[0020] According to a preferred embodiment, at least one of the planet gear sets is designed as a plus planet gear set, wherein the first element of the respective planet gear set is designed as a sun gear, the second element of the respective planet gear set is designed as a ring gear, and the third element of the respective planet gear set is designed as a planet carrier. In a plus planet gear set, the planet carrier carries at least one pair of planet gears, in which one planet gear meshes with the inner sun gear and the other planet gear meshes with the surrounding ring gear, and the planet gears mesh with each other.

[0021] Alternatively, at least one of the planetary gear sets can be designed as a plus-step planetary gear set with two sun gears or as a plus-step planetary gear set with two ring gears. In a plus-step planetary gear set with two sun gears, the first and second elements of the plus-step planetary gear set are each designed as sun gears, with the third element of the plus-step planetary gear set being designed as a planet carrier. In a plus-step planetary gear set with two ring gears, the first and second elements of the plus-step planetary gear set are each designed as ring gears, with the third element of the plus-step planetary gear set being designed as a planet carrier.

[0022] According to a preferred embodiment, a constant transmission stage is arranged in the power flow upstream of the drive shaft. This transmission stage is thus designed as a pre-transmission. For example, the transmission stage is designed as a planetary gear set with a sun gear, ring gear, and planet carrier, or as a spur gear stage with at least two gears meshing with each other. If the transmission stage is designed as a planetary gear set, one of the elements of the planetary gear set is fixed to the housing, another element is connected or connectable to a shaft of the drive motor, either directly or indirectly, and another element is rotationally fixed to the drive shaft. If the transmission stage is designed as a spur gear stage, the drive motor is arranged axially parallel to the transmission and thus also to the drive shaft and the two output shafts.Higher gear ratios can be achieved in the gearbox by means of a transmission stage.

[0023] According to a preferred embodiment, a first switching element for engaging a first gear and a second switching element for engaging a second gear are arranged in the power flow upstream of the drive shaft. A "switching element" is understood to be a switchable device that has at least one open and one closed state, wherein, in the open state, two shafts connected to it can rotate freely, and wherein, in the closed state, the two shafts are rotationally fixed to one another. For example, the first and second switching elements, together with a planetary gear set, form a 2-speed assembly that is positioned upstream of the three planetary gear sets of the transmission. The upstream planetary gear set comprises, for example, the elements sun gear, ring gear, and planet carrier. The upstream planetary gear set is locked in place by the first switching element.In other words, two elements of the upstream planetary gear set, for example, the sun gear and the ring gear, are connected in a rotationally fixed manner, so that the upstream planetary gear set rotates as a unit and has a gear ratio of 1. The second switching element connects one of the elements of the upstream planetary gear set, for example, the sun gear, to the housing in a rotationally fixed manner, thus setting a different gear ratio. Therefore, the second switching element is designed as a brake. In this context, a "brake" is understood to be a switchable device that, in a closed state, connects a shaft of the upstream planetary gear set to a housing in a rotationally fixed manner, so that this shaft is then stationary and thus prevented from rotating. In an open state of the switching element, the shaft is decoupled from the housing, allowing it to rotate freely. Each switching element can be switched by a corresponding actuator.

[0024] According to a preferred embodiment, a switching element for generating a locking effect is arranged between the two output shafts. This switching element can be designed as a friction-locking or positive-locking switching element. For example, a positive-locking switching element is designed as a dog clutch. A positive-locking switching element can increase the efficiency of the transmission due to reduced drag losses. In particular, positive-locking switching elements are more compact and efficiency-optimized, and offer a cost advantage over friction-locking switching elements. However, slip operation, i.e., a limited locking effect under differential speed, is not possible with positive-locking switching elements. For example, a friction-locking switching element comprises several plates or at least a conical friction surface.In the case of a friction-fit switching element, it 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 rotate with it.

[0025] A drive device according to the invention comprises a drive motor and a transmission according to the invention. Preferably, the drive motor is designed as an electric motor. Alternatively, the drive motor is designed as an internal combustion engine. The drive motor can be arranged coaxially or 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 effectively connected to a respective drive wheel of a drive axle of the vehicle.

[0026] A vehicle according to the invention comprises a drive device according to the invention. In particular, the vehicle is designed as an electric vehicle and has an electric drive axle with the drive device according to the invention. The above definitions and descriptions of technical effects, advantages, and advantageous embodiments of the transmission according to the invention also apply mutatis mutandis to the drive device and the vehicle according to the invention.

[0027] Advantageous embodiments of the invention, which are explained below, are illustrated in the drawings, wherein identical elements are designated with the same reference numeral. 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 view of the drive device according to the invention in a first embodiment; Fig. 4 a highly abstracted schematic view of a drive device according to a second embodiment of the invention; Fig. 5 a highly abstracted schematic view of a drive device according to a third embodiment according to the invention; Fig. 6 a highly abstracted schematic view of a drive device according to a fourth embodiment according to the invention; Fig. 7 a highly abstracted schematic view of a drive device according to a fifth embodiment according to the invention; Fig. 8 a highly abstracted schematic view of a drive device according to a sixth embodiment according to the invention; Fig. 9 a highly abstracted schematic view of a drive device according to a seventh embodiment according to the invention; Fig. 10 a highly abstracted schematic view of a drive device according to an eighth embodiment according to the invention; Fig. 11 a highly abstracted schematic view of a drive device according to a ninth embodiment according to the invention; Fig. 12 a highly abstracted schematic view of a drive device according to a tenth embodiment according to the invention; Fig. 13 a highly abstracted schematic view of a drive device according to an eleventh embodiment according to the invention; Fig. 14 a highly abstracted schematic view of a drive device according to a twelfth embodiment according to the invention; Fig. 15 a highly abstracted schematic view of a drive device according to the invention in a thirteenth embodiment; Fig. 16 a highly abstracted schematic view of a plus planetary gear set; Fig. 17 a highly abstracted schematic view of a minus-step planetary gear set; Fig. 18 a highly abstracted schematic view of a plus-step planetary gear set with two sun gears; and Fig. 19 a highly abstracted schematic view of a plus stepped planetary gear set with two hollow gears.

[0028] Fig. Figure 1 shows a motor vehicle 100 with a first axle 101 with two wheels R1, R2 and a second axle 102 with two wheels R3, R4. In this case, the first axle 101 is configured as the rear drive axle of the motor vehicle 100 and is equipped with a drive device according to the invention, comprising a single drive motor 2 designed as an electric machine and a transmission 1 designed as a planetary gear transmission. Thus, the motor vehicle 100 is configured as an electric vehicle. The drive device is arranged transversely to the longitudinal direction of the vehicle and is effectively connected to the wheels R1, R2 of the first axle 101. In this case, no further drive device is arranged on the second axle 102, i.e., on the front axle of the vehicle 100, thereby saving costs, weight, and installation space. Alternatively, the drive device can be arranged on the front axle of the motor vehicle 100 instead of the rear axle.To implement an all-wheel drive system, a further drive device can be arranged on the second wheel axle 102 and effectively connected to the wheels R3, R4 of this wheel axle 102.

[0029] Fig. Figure 2 shows 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 indicated by three connection points on the respective planetary gear set P1, P2, P3. Furthermore, the transmission 1 comprises five shafts: a drive shaft WAn for connecting the transmission 1 to the drive motor 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, and a first coupling shaft W1 and a second coupling shaft W2.

[0030] One of the elements of the first planetary gear set P1 is non-rotatably connected to the drive shaft WAn. The first planetary gear set is effectively connected to the drive motor 2 via the drive shaft WAn. In other words, at least one further shaft, gear, switching element, or the like can be arranged in the power flow between the drive motor 2 and the drive shaft WAn. Another element of the first planetary gear set P1 is non-rotatably connected to the first coupling shaft W1. Another element of the first planetary gear set P1 is non-rotatably connected to the second coupling shaft W2.

[0031] One of the elements of the second planetary gear set P2 is non-rotatably connected to the first coupling shaft W1. Thus, the first planetary gear set P1 is connected to the second planetary gear set P2 via the first coupling shaft W1. Another element of the second planetary gear set P2 is non-rotatably connected to a stationary component of the transmission 1, designed as a housing G. Another element of the second planetary gear set P2 is non-rotatably connected to the second output shaft WAb2.

[0032] One of the elements of the third planetary gear set P3 is non-rotatably connected to the second coupling shaft W2. Therefore, the first planetary gear set P1 is connected to the third planetary gear set P3 via the second coupling shaft W2. Another element of the third planetary gear set P3 is non-rotatably connected to the first output shaft WAb1. Another element of the third planetary gear set P3 is non-rotatably connected to the second output shaft WAb2. Therefore, the second planetary gear set P2 is connected to the third planetary gear set P3 via the second output shaft WAb2.

[0033] Fig. Figure 3 schematically shows the drive device with the gearbox 1 according to a first embodiment. An advantage of this first embodiment is the good efficiency and wide transmission range of the gearbox 1. The gearbox 1 comprises the first planetary gear set P1, the second planetary gear set P2, and the third planetary gear set P3, each of the three planetary gear sets P1, P2, P3 having a first element E11, E21, E31, a second element E12, E22, E32, and a third element E13, E23, E33. In this embodiment, the first element E11, E21, E31 of each planetary gear set P1, P2, P3 is configured as a sun gear, the second element E12, E22, E32 of each planetary gear set P1, P2, P3 is configured as a planet carrier, and the third element E13, E23, E33 of each planetary gear set P1, P2, P3 is configured as a ring gear.Each planet carrier carries at least one planet gear that meshes with the sun gear and the ring gear of the respective planet gear set P1, P2, P3. Thus, each of the three planet gear sets P1, P2, P3 is designed as a conventional minus planet gear set. Alternatively, at least one of the three planet gear sets can be designed as a conventional plus planet gear set, a minus stepped planet gear set, a plus stepped planet gear set with two sun gears, or a plus stepped planet gear set with two ring gears.

[0034] The first element E11 of the first planetary gear set P1 is non-rotatably connected to the drive shaft WAn, the second element E12 of the first planetary gear set P1 is non-rotatably connected to the first coupling shaft W1, and the third element E13 of the first planetary gear set P1 is non-rotatably connected to the second coupling shaft W2. The drive shaft WAn is connected to the drive machine 2. Alternatively, further elements, in particular shafts, gears, switching elements, or other devices, can be arranged in the power flow between the drive machine 2 and the drive shaft WAn. For example, such a switching element can interrupt the power flow between the drive machine 2 and the drive shaft WAn.

[0035] The first element E21 of the second planetary gear set P2 is non-rotatably connected to the first coupling shaft W1, wherein the second element E22 of the second planetary gear set P2 is non-rotatably connected to a stationary component designed as a housing G, and wherein the third element E23 of the second planetary gear set P2 is non-rotatably connected to the second output shaft WAb2.

[0036] The first element E31 of the third planetary gear set P3 is non-rotatably connected to the second coupling shaft W2, the second element E32 of the third planetary gear set P3 is non-rotatably connected to the first output shaft WAb1, and the third element E33 of the third planetary gear set P3 is non-rotatably connected to the second output shaft WAb2. Due to this connection, the third planetary gear set P3 rotates within the block when the vehicle is traveling straight ahead, so that the elements of the third planetary gear set P3 do not roll and therefore no corresponding losses are generated.

[0037] Thus, the third element E23 of the second planetary gear set P2 and the third element E33 of the third planetary gear set P3 are connected to each other in a rotationally fixed manner via the second output shaft WAb2. Furthermore, the first coupling shaft W1 connects the second element E12 of the first planetary gear set P1 in a rotationally fixed manner to the first element E21 of the second planetary gear set P2, while the second coupling shaft W2 connects the third element E13 of the first planetary gear set P1 in a rotationally fixed manner to the first element E31 of the third planetary gear set P3.

[0038] The first planetary gear set P1 is arranged axially between the second planetary gear set P2 and the third planetary gear set P3, with the second planetary gear set P2 being axially adjacent to the drive unit 2. This design results in a compact drive unit. The drive shaft WAn rotates in the opposite direction to the two output shafts WAb1 and WAb2. All three planetary gear sets P1, P2, and P3 are arranged on a common axis of rotation R. The drive unit 2 is arranged coaxially with the axis of rotation R. The drive shaft WAn is designed as a hollow shaft, with the first output shaft WAb1 extending axially through the drive shaft WAn and the drive unit 2. Each output shaft WAb1 and WAb2 is non-rotatably connected to a respective wheel of the vehicle.

[0039] Fig. Figure 4 shows a second embodiment of the drive device according to the invention. The drive device according to Fig. 4 essentially corresponds to the drive device according to Fig. 3, wherein a difference between these two embodiments lies in the arrangement of the first and third planetary gear sets P1, P3. An advantage of this second embodiment over the first embodiment is a short axial length of the transmission 1. In this embodiment, the first and third planetary gear sets P1, P3 are arranged radially nested, with the first planetary gear set P1 arranged radially inside and the third planetary gear set P3 arranged radially outside. Thus, the first planetary gear set P1 is arranged closer to the axis of rotation R than the third planetary gear set P3. 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. The second coupling shaft W2 is designed as an intermediate gear with internal and external teeth and connects the first planetary gear set P1 and the third planetary gear set P3.In other words, the third element E13 of the first planetary gear set P1, the first element E31 of the third planetary gear set P3, and the second coupling shaft W2 are formed as a single, integrated component. The internal teeth of the intermediate gear form a ring gear for the radially inner first planetary gear set P1. The external teeth of the intermediate gear form a sun gear for the radially outer third planetary gear set P3. The intermediate gear makes the gearbox 1 more compact and lighter. Furthermore, the second and third planetary gear sets P2 and P3 share a common ring gear. In other words, the third element E23 of the second planetary gear set P2 and the third element E33 of the third planetary gear set P3 are formed as a single component with a single tooth profile. This reduces assembly effort and increases compactness. In particular, the second output shaft WAb2 is formed as a single unit with the common ring gear.Otherwise, the embodiment corresponds to the following. Fig. 4 according to the exemplary embodiment Fig. 3, which is referenced.

[0040] Fig. Figure 5 shows a third 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. 3, wherein a difference between these two embodiments lies in the connection of the first and third planetary gear sets P1, P3. The advantages of this third embodiment over the first embodiment are lower gear set torques and consequently also a lower load on the respective components of the transmission 1. The input shaft WAn has the same direction of rotation as the two output shafts WAb1, WAb2. In this embodiment, the first element E11 of the first planetary gear set P1 is non-rotatably connected to the input shaft WAn, the second element E12 of the first planetary gear set P1 is non-rotatably connected to the second coupling shaft W2, and the third element E13 of the first planetary gear set P1 is non-rotatably connected to the first coupling shaft W1.The first element E21 of the second planetary gear set P2 is non-rotatably connected to the first coupling shaft W1, the second element E22 of the second planetary gear set P2 is non-rotatably connected to the stationary component designed as housing G, and the third element E23 of the second planetary gear set P2 is non-rotatably connected to the second output shaft WAb2. Furthermore, the first element E31 of the third planetary gear set P3 is non-rotatably connected to the second output shaft WAb2, the second element E32 of the third planetary gear set P3 is non-rotatably connected to the first output shaft WAb1, and the third element E33 of the third planetary gear set P3 is non-rotatably connected to the second coupling shaft W2. Otherwise, the embodiment corresponds to the following. Fig. 5 according to the exemplary embodiment Fig. 3, which is referenced.

[0041] Fig. Figure 6 shows a fourth 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. 5, wherein a difference between these two embodiments lies in the arrangement of the second and third planetary gear sets P2, P3. An advantage of this fourth embodiment over the third embodiment is a short axial length of the transmission 1. In this embodiment, the second and third planetary gear sets P2, P3 are arranged radially nested, with the second planetary gear set P2 arranged radially inside and the third planetary gear set P3 arranged radially outside. Thus, the second planetary gear set P2 is arranged closer to the axis of rotation R than the third planetary gear set P3. The elements E21, E22, E23 of the second planetary gear set P2 and the elements E31, E32, E33 of the third planetary gear set P3 overlap in the axial direction. An intermediate gear with internal and external teeth is arranged in the power flow between the second planetary gear set P2 and the third planetary gear set P3.The third element E23 of the second planetary gear set P1, the first element E31 of the third planetary gear set P3, and the second output shaft WAb2 are designed as a single component. The internal teeth form a ring gear for the radially inner second planetary gear set P2. The external teeth form a sun gear for the radially outer third planetary gear set P3. The intermediate gear makes the transmission 1 more compact and lighter. Otherwise, the embodiment corresponds to the following. Fig. 6 according to the exemplary embodiment Fig. 5, which is referenced.

[0042] Fig. Figure 7 shows a fifth 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. 3, wherein a difference between these two embodiments lies in the connection of the third planetary gear set P3. An advantage of this fifth embodiment is the good efficiency of the transmission 1. In this embodiment, the first element E11 of the first planetary gear set P1 is non-rotatably connected to the input shaft WAn, the second element E12 of the first planetary gear set P1 is non-rotatably connected to the first coupling shaft W1, and the third element E13 of the first planetary gear set P1 is non-rotatably connected to the second coupling shaft W2. The first element E21 of the second planetary gear set P2 is non-rotatably connected to the first coupling shaft W1, the second element E22 of the second planetary gear set P2 is non-rotatably connected to the stationary component designed as housing G, and the third element E23 of the second planetary gear set P2 is non-rotatably connected to the second output shaft WAb2.The first element E31 of the third planetary gear set P3 is non-rotatably connected to the second output shaft WAb2, the second element E32 of the third planetary gear set P3 is non-rotatably connected to the first output shaft WAb1, and the third element E33 of the third planetary gear set P3 is non-rotatably connected to the second coupling shaft W2. Furthermore, the first and third planetary gear sets P1 and P3 share a common ring gear with a single tooth profile. In other words, the third element E13 of the first planetary gear set P1, the third element E33 of the third planetary gear set P3, and the second coupling shaft W2 are formed as a single component. This reduces assembly effort and increases compactness. In particular, the second coupling shaft W2 is formed integrally with the common ring gear. Otherwise, the embodiment corresponds to [reference to relevant figure]. Fig. 7 according to the exemplary embodiment Fig. 3, which is referenced.

[0043] Fig. Figure 8 shows a sixth 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 a difference between these two embodiments lies in the arrangement of the second and third planetary gear sets P2, P3. An advantage of this sixth embodiment over the fifth embodiment is a short axial length of the transmission 1. In this embodiment, the second and third planetary gear sets P2, P3 are arranged radially nested, with the second planetary gear set P2 arranged radially inside and the third planetary gear set P3 arranged radially outside. Thus, the second planetary gear set P2 is arranged closer to the axis of rotation R than the third planetary gear set P3. The elements E21, E22, E23 of the second planetary gear set P2 and the elements E31, E32, E33 of the third planetary gear set P3 overlap in the axial direction. An intermediate gear with internal and external teeth is arranged in the power flow between the second planetary gear set P2 and the third planetary gear set P3.In this case, the third element E23 of the second planetary gear set P2 and the first element E31 of the third planetary gear set P3 form a single component. The internal teeth of the intermediate gear form a ring gear for the radially inner second planetary gear set P2. The external teeth of the intermediate gear form a sun gear for the radially outer third planetary gear set P3. The intermediate gear makes the transmission 1 more compact and lighter. Furthermore, the first and third planetary gear sets P1 and P3 share a common ring gear with a single tooth profile. In other words, the third element E13 of the first planetary gear set P1, the third element E33 of the third planetary gear set P3, and the second coupling shaft W2 are designed as a single component. This reduces assembly effort and increases compactness. Otherwise, the embodiment corresponds to the above. Fig. 8 according to the exemplary embodiment Fig. 7, which is referenced.

[0044] Fig. Figure 9 shows a seventh 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. 3, wherein a difference between these two embodiments lies in the connection of the second and third planetary gear sets P2, P3. An advantage of this seventh embodiment of the transmission 1 is its good efficiency and wide transmission range. In this embodiment, the first element E11 of the first planetary gear set P1 is non-rotatably connected to the input shaft WAn, the second element E12 of the first planetary gear set P1 is non-rotatably connected to the first coupling shaft W1, and the third element E13 of the first planetary gear set P1 is non-rotatably connected to the second coupling shaft W2. The first element E21 of the second planetary gear set P2 is non-rotatably connected to the first coupling shaft W1, the second element E22 of the second planetary gear set P2 is non-rotatably connected to the second output shaft WAb2, and the third element E23 of the second planetary gear set P2 is non-rotatably connected to a stationary component.The first element E31 of the third planetary gear set P3 is non-rotatably connected to the second coupling shaft W2, the second element E32 of the third planetary gear set P3 is non-rotatably connected to the second output shaft WAb2, and the third element E33 of the third planetary gear set P3 is non-rotatably connected to the first output shaft WAb1. The drive shaft WAn is designed as a hollow shaft, with the second output shaft WAb2 extending axially through the drive shaft WAn and the drive machine 2. Otherwise, the embodiment corresponds to the above. Fig. 9 according to the exemplary embodiment Fig. 3, which is referenced.

[0045] Fig. Figure 10 shows an eighth 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. 3, wherein a difference between these two embodiments lies in the connection of the three planetary gear sets P1, P2, P3. In the present embodiment, the first element E11 of the first planetary gear set P1 is non-rotatably connected to the drive shaft WAn, the second element E12 of the first planetary gear set P1 is non-rotatably connected to the second coupling shaft W2, the third element E13 of the first planetary gear set P1 is non-rotatably connected to the first coupling shaft W1, the first element E21 of the second planetary gear set P2 is non-rotatably connected to the first coupling shaft W1, the second element E22 of the second planetary gear set P2 is non-rotatably connected to the second output shaft WAb2, and the third element E23 of the second planetary gear set P2 is non-rotatably connected to the stationary component designed as housing G.The first element E31 of the third planetary gear set P3 is non-rotatably connected to the second coupling shaft W2, the second element E32 of the third planetary gear set P3 is non-rotatably connected to the second output shaft WAb2, and the third element E33 of the third planetary gear set P3 is non-rotatably connected to the first output shaft WAb1. The drive shaft WAn is designed as a hollow shaft, with the second output shaft WAb2 extending axially through the drive shaft WAn and the drive machine 2. Otherwise, the embodiment corresponds to the above. Fig. 10 according to the exemplary embodiment Fig. 3, which is referenced.

[0046] Fig. Figure 11 shows a ninth 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 arrangement of a constant reduction stage in the power flow between the drive machine 2 and the drive shaft WAn. In the present case, this reduction stage is designed as a fourth planetary gear set P4 and comprises a first element E41 designed as a sun gear, a second element E42 designed as a planet carrier, and a third element E43 designed as a ring gear. The first element E41 of the fourth planetary gear set P4 is rotationally fixed to the stationary component designed as the housing G. The second element E42 of the fourth planetary gear set P4 is rotationally fixed to the drive shaft WAn. The third element E43 of the fourth planetary gear set P4 is effectively connected to the drive machine 2.Alternatively, the connection of the fourth planetary gear set P4 can also be arranged differently, wherein one of the elements E41, E42, E43 of the fourth planetary gear set P4 is rotationally fixed to the housing G, another of the elements E41, E42, E43 of the fourth planetary gear set P4 is effectively connected to the drive motor 2, i.e., directly or indirectly, or connectable, and wherein another of the elements E41, E42, E43 of the fourth planetary gear set P4 is rotationally fixed to the drive shaft WAn. An advantage of this pre-reduction gear set is that higher gear ratios can be achieved with the transmission 1. Otherwise, the embodiment corresponds to the following. Fig. 11 according to the exemplary embodiment Fig. 4, which is referenced.

[0047] Fig. Figure 12 shows a tenth 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 arrangement of a constant gear reduction stage in the power flow between the drive machine 2 and the drive shaft WAn. In the present embodiment, this reduction is designed as a spur gear stage ST and comprises a first gear Z1, which is effectively connected to the drive machine 2, and a second gear Z2, which is rotationally fixed to the drive shaft WAn. The center distance of the drive machine 2 to the axis of rotation R can be adjusted via the diameters of the two gears Z1, Z2 of the spur gear stage ST. Thus, the drive machine 2 is arranged axially parallel to the drive shaft WAn and to the two output shafts WAb1, WAb2. An advantage of this reduction gear designed as a spur gear stage ST is that higher gear ratios can be achieved with the gearbox 1. Otherwise, the embodiment corresponds to the embodiment shown. Fig. 12 according to the exemplary embodiment Fig. 4, which is referenced.

[0048] Fig. Figure 13 shows an eleventh embodiment of the drive device according to the invention. The drive device according to Fig. 13 essentially corresponds to the drive device according to Fig. 4, wherein a difference between these two embodiments lies in the arrangement of a switching element S for generating a locking effect between the two output shafts WAb1, WAb2. In the present embodiment, the switching element S is designed as a friction-locking switching element and, in a partially closed state, generates a torque between the two output shafts WAb1, WAb2. In a fully closed state of the switching element S, the two output shafts WAb1, WAb2 are rotationally fixed to one another via the switching element S. In a fully open state of the switching element S, no torque is transmitted between the two output shafts WAb1, WAb2 via the switching element S. For example, the switching element S can have one or more parallel friction surfaces. Alternatively, the switching element S can have one or more conically shaped friction surfaces.A gearbox 1 with such a locking differential enables particularly sporty driving. Otherwise, the embodiment corresponds to the above. Fig. 13 according to the exemplary embodiment Fig. 4, which is referenced.

[0049] Fig. Figure 14 shows a twelfth embodiment of the drive device according to the invention. The drive device according to Fig. 14 essentially corresponds to the drive device according to Fig. 4, wherein a difference between these two embodiments lies in the arrangement of a switching element S for generating a locking effect between the two output shafts WAb1, WAb2. In the present embodiment, the switching element S is designed as a positive-locking switching element and, in a closed state, generates a locking torque between the two output shafts WAb1, WAb2 by connecting the two output shafts WAb1, WAb2 to each other in a rotationally fixed manner. In an open state of the switching element S, no locking torque is generated between the two output shafts WAb1, WAb2. For example, the switching element S can have several positive-locking claws. A transmission 1 with such a locking differential particularly supports traction when driving off-road. Otherwise, the embodiment corresponds to the embodiment shown in the above. Fig. 14 according to the exemplary embodiment Fig. 4, which is referenced.

[0050] Fig. Figure 15 shows a thirteenth embodiment of the drive device according to the invention. The drive device according to Fig. 15 essentially corresponds to the drive device according to Fig. 11, wherein a difference between these two embodiments lies in the arrangement of a first switching element A for shifting a first gear and a second switching element B for shifting a second gear in the power flow between the drive motor 2 and the drive shaft WAn. In the present case, both switching elements A and B are designed as friction-locking switching elements, for example as multi-plate clutches, and enable load shifting. In a closed state of the first switching element A and an open state of the second switching element B, the first element E41 of the fourth planetary gear set P4 is rotationally fixed to the housing G and a first gear ratio is engaged.In an open state of the first switching element A and a closed state of the second switching element B, the fourth planetary gear set P4 is locked by connecting the first element E41 and the third element E43 of the fourth planetary gear set P4 in a rotationally fixed manner, thereby establishing a second gear ratio. An advantage of such an upstream 2-speed switching device is that it enables high gear ratios at high top speeds. Otherwise, the embodiment corresponds to the embodiment shown in [reference missing]. Fig. 15 according to the exemplary embodiment Fig. 11, to which reference is made.

[0051] The Fig. Figures 16 to 19 show different configurations of planetary gear sets. At least one of the planetary gear sets of the transmission according to the invention can be configured as a conventional plus planetary gear set, a minus stepped planetary gear set, a plus stepped planetary gear set with two sun gears, or a plus stepped planetary gear set with two ring gears, instead of a conventional minus planetary gear set.

[0052] Fig. Figure 16 shows a Plus planetary gear set. The first element E1 of the Plus planetary gear set is configured as a sun gear, the second element E2 as a ring gear, and the third element E3 as a planet carrier. The planet carrier of the Plus planetary gear set carries at least one planet gear pair, consisting of a first planet gear PR1 and a second planet gear PR2. The first planet gear PR1 meshes with the inner sun gear, and the second planet gear PR2 meshes with the surrounding ring gear. Furthermore, the two planet gears PR1 and PR2 of a planet gear pair also mesh with each other.

[0053] Fig. Figure 17 shows a minus-step planetary gear set. The first element E1 of the minus-step planetary gear set is configured as a sun gear and can alternatively be configured as a ring gear. The second element E2 of the minus-step planetary gear set is configured as a planet carrier. The third element E3 of the minus-step planetary gear set is configured as a ring gear and can be configured as a sun gear if the first element E1 of the minus-step planetary gear set is a ring gear. The planet carrier of the minus-step planetary gear set carries at least one minus-step planetary gear, consisting of a first gear ZR1 and a second gear ZR2, wherein the two gears ZR1 and ZR2 are rotationally fixed and integrally connected. In this case, the first gear ZR1 of the minus-step planetary gear has a smaller diameter than the second gear ZR2 of the minus-step planetary gear.The first gear ZR1 of the stepped planetary gear is in mesh with the inner sun gear and the second gear ZR2 of the stepped planetary gear is in mesh with the surrounding ring gear.

[0054] Fig. Figure 18 shows a plus-step planetary gear set with two sun gears. The first element E1 of the plus-step planetary gear set is designed as the first sun gear. The second element E2 of the plus-step planetary gear set is designed as the second sun gear. The third element E3 of the plus-step planetary gear set is designed as the planet carrier. The planet carrier of the plus-step planetary gear set carries at least one step planetary gear, consisting of a first gear ZR1 and a second gear ZR2, wherein the two gears ZR1 and ZR2 are rotationally fixed and integrally connected. In this case, the first gear ZR1 of the step planetary gear has a larger diameter than the second gear ZR2 of the step planetary gear. The first gear ZR1 of the step planetary gear meshes with the first sun gear, and the second gear ZR2 of the step planetary gear meshes with the second sun gear.

[0055] Fig.Figure 19 shows a plus-step planetary gear set with two ring gears. The first element E1 of the plus-step planetary gear set is designed as the first ring gear. The second element E2 of the plus-step planetary gear set is designed as the second ring gear. The third element E3 of the plus-step planetary gear set is designed as the planet carrier. The planet carrier of the plus-step planetary gear set carries at least one step planetary gear, consisting of a first gear ZR1 and a second gear ZR2, wherein the two gears ZR1 and ZR2 are rotationally fixed and integrally connected. In this case, the first gear ZR1 of the step planetary gear has a larger diameter than the second gear ZR2 of the step planetary gear.

[0056] The first gear ZR1 of the stepped planetary gear is in tooth mesh with the first ring gear and the second gear ZR2 of the stepped planetary gear is in tooth mesh with the second ring gear. Reference sign 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 A first switching element B second switching element S switching element R axis of rotation 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 P4 fourth planetary gear set E41 first element of the fourth planetary gear set E42 second element of the fourth planetary gear set E43 third element of the fourth planetary gear set E1 first element E2 second element E3 third element PR1 first planetary gear PR2 second planetary gear ZR1 first gear of the stepped planetary gear ZR2 second gear of the stepped planetary gear ST Spur Gear Stage Z1 first gear of the spur gear stage Z2 second gear of the spur gear stage 100 motor vehicles 101 first wheel axle 102 second wheel axle R1 wheel R2 wheel R3 wheel 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), • 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 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), • wherein one of the elements (E11, E21, E31) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the drive shaft (WAn), wherein another of the elements (E11, E21, E31) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the first coupling shaft (W1), wherein another of the elements (E11, E21, E31) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the second coupling shaft (W2), • wherein one of the elements (E12, E22, E32) 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 (E12, E22, E32) of the second planetary gear set (P2) is connected in a rotationally fixed manner to a stationary component, wherein another of the elements (E12, E22, E32) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the second output shaft (WAb2), • wherein one of the elements (E13, E23, E33) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the second coupling shaft (W2), wherein another of the elements (E13, E23, E33) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the first output shaft (WAb1), wherein another of the elements (E13, E23, E33) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the second output shaft (WAb2). [2] Transmission according to claim 1, • wherein the first element (E11) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the drive shaft (WAn), wherein the second element (E12) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the first coupling shaft (W1), 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), • wherein the first element (E21) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the first coupling shaft (W1), wherein the second element (E22) of the second planetary gear set (P2) is connected in a rotationally fixed manner to a stationary component, wherein the third element (E23) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the second output shaft (WAb2), • wherein the first element (E31) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the second coupling shaft (W2), wherein the second element (E32) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the first output shaft (WAb1), 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). [3] Transmission (1) according to claim 1, • wherein the first element (E11) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the drive shaft (WAn), wherein the second element (E12) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the second coupling shaft (W2), wherein the third element (E13) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the first coupling shaft (W1), • wherein the first element (E21) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the first coupling shaft (W1), wherein the second element (E22) of the second planetary gear set (P2) is connected in a rotationally fixed manner to a stationary component, wherein the third element (E23) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the second output shaft (WAb2), • wherein the first element (E31) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the second output shaft (WAb2), wherein the second element (E32) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the first output shaft (WAb1), wherein the third element (E33) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the second coupling shaft (W2). [4] Transmission (1) according to claim 1, • wherein the first element (E11) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the drive shaft (WAn), wherein the second element (E12) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the first coupling shaft (W1), 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), • wherein the first element (E21) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the first coupling shaft (W1), wherein the second element (E22) of the second planetary gear set (P2) is connected in a rotationally fixed manner to a stationary component, wherein the third element (E23) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the second output shaft (WAb2), • wherein the first element (E31) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the second output shaft (WAb2), wherein the second element (E32) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the first output shaft (WAb1), wherein the third element (E33) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the second coupling shaft (W2). [5] Transmission (1) according to claim 1, • wherein the first element (E11) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the drive shaft (WAn), wherein the second element (E12) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the first coupling shaft (W1), 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), • wherein the first element (E21) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the first coupling shaft (W1), wherein the second element (E22) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the second output shaft (WAb2), wherein the third element (E23) of the second planetary gear set (P2) is connected in a rotationally fixed manner to a stationary component, • wherein the first element (E31) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the second coupling shaft (W2), 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 the first output shaft (WAb1). [6] Transmission (1) according to claim 1, • wherein the first element (E11) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the drive shaft (WAn), wherein the second element (E12) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the second coupling shaft (W2), wherein the third element (E13) of the first planetary gear set (P1) is connected in a rotationally fixed manner to the first coupling shaft (W1), • wherein the first element (E21) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the first coupling shaft (W1), wherein the second element (E22) of the second planetary gear set (P2) is connected in a rotationally fixed manner to the second output shaft (WAb2), wherein the third element (E23) of the second planetary gear set (P2) is connected in a rotationally fixed manner to a stationary component, • wherein the first element (E31) of the third planetary gear set (P3) is connected in a rotationally fixed manner to the second coupling shaft (W2), 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 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) according to one of the preceding claims, wherein at least one of the planetary gear sets (P1, P2, P3) is designed as a plus 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 ring gear, wherein the third element (E13, E23, E33) of the respective planetary gear set (P1, P2, P3) is designed as a planet carrier. [11] Transmission (1) according to one of the preceding claims, wherein a constant gear ratio stage is arranged in the power flow in front of the drive shaft (WAn). [12] Transmission (1) according to one of the preceding claims, wherein a first shifting element (A) for shifting a first gear and a second shifting element (B) for shifting a second gear are arranged in the power flow in front of the drive shaft (WAn). [13] Transmission (1) according to one of the preceding claims, wherein a switching element (S) for generating a locking effect is arranged between the two output shafts (WAb1, WAb2). [14] Drive device with a drive machine (2) and a transmission (1) according to one of claims 1 to 13. [15] Motor vehicle (100) with a drive device according to claim 14.

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