Drive device for a motor vehicle with a common rigid ring gear and a common rigid planetary gear carrier

Abstract

A drive device (1) for a motor vehicle has an electric drive machine operatively connected to a transmission (3) via a drive shaft (2). The transmission (3) has at least a first planetary gear stage (4) and a second planetary gear stage (5) and a differential stage (6). The first planetary gear stage (4) has a first planetary gear set including a plurality of planetary gears (7a), and the planetary gears (7a) of the first planetary gear set are rotatably arranged on a first planetary gear carrier and mesh with a first sun gear (9a) and a first ring gear. The second planetary gear stage (5) has a second planetary gear set including a plurality of planetary gears (7b), and the planetary gears (7b) of the second planetary gear set are rotatably arranged on a second planetary gear carrier and mesh with a second sun gear (9b) and a second ring gear. The first planetary gear stage (4) and the second planetary gear stage (5) are operatively connected to a dual clutch device (11) having a first power shift clutch (12a) and a second power shift clutch (12b), the first ring gear and the second ring gear are rigidly connected together to form a common ring gear (10), and the first planetary gear carrier and the second planetary gear carrier are rigidly connected together to form a common planetary gear carrier (8).

Description

Technical Field

[0001] The present invention relates to a drive device for a motor vehicle, which has an electric drive machine operatively connected to a transmission device via a drive shaft, wherein the transmission device has at least a first planetary gear stage and a second planetary gear stage and a differential stage, the first planetary gear stage having a first planetary gear set including a plurality of planetary gears, wherein the planetary gears of the first planetary gear set are rotatably arranged on a first planetary gear carrier and mesh with a first sun gear and a first ring gear, and the second planetary gear stage having a second planetary gear set including a plurality of planetary gears, wherein the planetary gears of the second planetary gear set are rotatably arranged on a second planetary gear carrier and mesh with a second sun gear and a second ring gear, and wherein the first planetary gear set and the second planetary gear set are operatively connected to a dual clutch device having a first power shift clutch and a second power shift clutch. Background Art

[0002] Drive devices for motor vehicles are known from the prior art. For example, DE 10 2011 088 668 A1 shows a drive device with at least one electric drive machine, which has at least one first planetary drive including a shifting clutch and a differential. The rotor shaft of the drive machine is connected to a first connecting shaft of a planetary drive formed by at least three connecting shafts in a rotationally fixed manner. The second connecting shaft of the first planetary drive can be fixed against a component of the drive device in a rotationally fixed manner by means of a shifting collar of the shifting clutch. The third connecting shaft of the first planetary drive is operatively connected to the main shaft of the differential. The shifting collar can be converted into an operative connection for transmitting torque in a form-fitting engagement with the second connecting shaft of the first planetary drive or with the main shaft of the differential.

[0003] DE 10 2013 220 835 A1 also discloses a planetary gear, in particular an axle gear mechanism for a motor vehicle, which is used to divide the driving power applied to the power input into a first power output and a second power output in combination with reducing the output speed to a speed below the driving speed at the power input speed level, the planetary gear having a superposition gear stage including a first sun gear, a first planetary gear set, a first planetary gear carrier and a first ring gear, and a reversing gear stage including a second sun gear, a second planetary gear set, a second planetary gear carrier and a second ring gear, wherein the first sun gear serves as the power input, the first ring gear is connected to the second ring gear in a rotationally fixed manner, the first power output is achieved via the first planetary gear carrier of the superposition gear stage, the second power output is achieved via the reversing gear stage, in which the second sun gear represents the second power output, and the second planetary gear set is designed as a double planetary gear set having at least one pair of double planets engaged with each other, wherein one planet of the double planet pair is engaged with the second sun gear and the second ring gear and the other planet of the double planet pair is engaged with the fixed ring gear.

[0004] JP 2017-206 213 A shows a planetary gear, in which two intermeshing planetary gears are arranged on a common planetary gear carrier and one planetary gear intermeshes with a sun gear and the other planetary gear intermeshes with a ring gear, wherein the ring gear can be fixed to the frame via a brake.

[0005] GB 2 085 099 A shows a transmission for use on a winch, cable drum or other lifting device, which has a plurality of independently actuatable clutches for producing at least three drive transmission ratios via associated planetary gear sets. The planetary gear sets and the clutches run in an oil bath. By means of a control device, two clutches can be actuated simultaneously, so that only one clutch is released and is therefore subjected to the flow resistance of the oil bath. The planetary gear sets and the clutches are used for a variable drive transmission from an input shaft to an output part. Summary of the invention

[0006] The object of the present invention is to develop a drive device for a motor vehicle, the emphasis being on a transmission structure which is as simple as possible, with a large number of identical parts and a suitable distribution or distribution of the gear ratios.

[0007] This object is achieved in the generic arrangement according to the invention in that the first ring gear and the second ring gear are rigidly connected together to form a common ring gear and the first planet carrier and the second planet carrier are rigidly connected together to form a common planet carrier.

[0008] According to the invention, the first clutch can be connected to the second sun gear in a rotationally fixed manner (e.g. permanently) and the second clutch can be connected to the first sun gear in a rotationally fixed manner. Alternatively, the first clutch can also be connected to a common planetary gear carrier in a rotationally fixed manner and the second clutch can be connected to a common ring gear in a rotationally fixed manner, which makes a flexible design of the connection between the drive shaft and the transmission possible.

[0009] In other words, the planetary gears of the first planetary gear set and the second planetary gear set are meshed with the common / shared ring gear and are mounted on the common / shared planetary gear carrier. This has the advantage of reducing the number of parts and simplifying the structure of the transmission device.

[0010] Thus, the term "operatively connected" means that the two transmission elements for torque transmission can be directly connected or there are other transmission elements, such as one or more shafts or gears, between the two transmission elements for torque transmission. Two meshing or intermeshing gears are arranged to transmit torque and speed from one gear to another. Gears refer to, for example, compensating gears, sun gears, ring gears or planetary gears of planetary gear sets.

[0011] A dual clutch device is understood to be a device having two powershift clutches. Furthermore, the term "powershift clutch" is understood to be a device having at least one open state and one closed state and being able to switch between at least two states under load. When open, the clutch does not transmit any torque.

[0012] Advantageous embodiments are claimed in the dependent claims and are described below.

[0013] Preferably, the first ring gear and the second ring gear have the same toothing.

[0014] It may also be advantageous if the common planet carrier is formed from one material and / or is formed integrally in one piece.

[0015] According to the invention, the pitch circle diameter of the first sun gear can be smaller than the pitch circle diameter of the second sun gear, so that different gear ratios can be achieved by the drive device.

[0016] This flexibility in the design of the drive device according to the invention can also be increased by fixing the common ring gear, the common planet carrier, the first sun gear or the second sun gear in a stationary manner in the housing.

[0017] Depending on requirements or manufacturing choice, the drive can also be designed in such a way that a common planetary carrier, a common ring gear, the second sun gear or the first sun gear is operatively connected to the differential stage.

[0018] The first clutch and the second clutch of the dual clutch device can preferably be designed as friction clutches. In addition, the two clutches can preferably be arranged coaxially with each other. In particular, the respective clutch can be actuated by a respective actuator in order to initiate the respective clutch opening or closing. The actuator can be actuated hydraulically, electromechanically, electromagnetically or, for example, even pneumatically.

[0019] It is useful that opening both clutches can achieve power cut at the same time. Closing the first clutch and opening the second clutch can achieve the first gear ratio, while closing the second clutch and opening the first clutch can achieve the second gear ratio. In order to ensure that the shifting process from one clutch to another is essentially free of traction losses, one clutch can be opened and the other clutch closed during the transfer period. Via slip in the clutch designed as a friction clutch, a torque-lossless switching between the two gear stages can occur, which can be seen by the operator of the drive device as a mode switching between the two gear stages without traction losses, which in turn increases the switching comfort of the operator of the drive device. The first gear ratio is preferably different from the second gear. For example, the first gear ratio can be greater than the second gear ratio. Alternatively, the first gear ratio can be less than the second gear ratio.

[0020] According to the design according to the invention, the electric machine can have a stator and a rotor, wherein the rotor is connected to the drive shaft in a rotationally fixed manner. The drive shaft can be designed as a rotor shaft, or there is an axial offset between the drive shaft and the rotor shaft, wherein the torque transmission (transmission) is arranged between the two shafts.

[0021] Furthermore, the differential stage can preferably be designed as a spur gear differential, wherein the differential stage is provided to distribute the drive power of the drive machine to the first output shaft and the second output shaft.

[0022] The drive machine can be arranged coaxially or axially parallel to the differential stage. In particular, the drive machine and / or the drive shaft can be arranged axially parallel to the two output shafts, wherein axial parallel means that there is an axial offset between the drive shaft and the output shaft. Therefore, the axial installation space of the drive device can be reduced.

[0023] If the drive shaft is arranged coaxially with the two output shafts, the drive shaft can be designed as a hollow shaft, wherein one of the two output shafts is axially guided through the drive shaft. Preferably, the two output shafts are arranged concentrically with the common drive shaft.

[0024] Furthermore, it is preferred that an additional reduction gear is arranged in the torque flow from the electric drive machine to the output shaft between the drive shaft and the transmission, in particular the first planetary gear stage. Alternatively, the reduction gear can also be arranged between the transmission, in particular the second planetary gear stage, and the differential stage. The additional reduction gear provides the possibility of simply increasing the achievable transmission ratio range.

[0025] The operative connection between the drive shaft and / or the output shaft and the sun gear arranged on the shaft can be designed in two ways. On the one hand, the sun gear or the toothing of the sun gear can be placed directly on the shaft, so that the sun gear and the shaft are designed as an integral component. On the other hand, the sun gear can be provided as a component formed separately from the shaft, wherein the sun gear is mounted on the shaft in a torque-proof manner.

[0026] In a preferred embodiment, the ring gear can be fixed in a stationary manner in the housing. The first sun gear can be connected to the second clutch in a rotationally fixed manner and the second sun gear can be connected to the first clutch in a rotationally fixed manner. The planetary gear carrier is operatively connected to the differential stage. Therefore, in the closed state of the second clutch, torque can be transmitted from the drive machine via the first sun gear to the planetary gear carrier and the differential stage. However, in the closed state of the first clutch, torque can be transmitted to the planetary gear carrier and the differential stage via the second sun gear. Therefore, when the second clutch or the first clutch is open, the first planetary gear stage or the second planetary gear stage runs at "idle speed".

[0027] In other words, according to a preferred embodiment, the drive device according to the invention can have a common planetary carrier and a common ring gear, wherein the ring gear is designed as a (stationary) fixed element and the drive can optionally be realized via the sun gear.

[0028] In another preferred embodiment, the planetary gear carrier can be fixed in a stationary manner in the housing. The first sun gear can be connected to the second clutch in a rotationally fixed manner and the second sun gear can be connected to the first clutch in a rotationally fixed manner. The ring gear is operatively connected to the differential stage. Therefore, in the closed state of the second clutch, torque can be transmitted from the drive machine via the first sun gear to the ring gear and the differential stage. However, in the closed state of the first clutch, torque can be transmitted to the ring gear and the differential stage via the second sun gear.

[0029] In other words, according to a further preferred embodiment, the drive device according to the invention can have a common planetary carrier and a common ring gear, wherein the planetary carrier is designed as a (stationary) fixed element and the drive can optionally be realized via a sun gear.

[0030] According to an advantageous development, the ring gear can be connected to the second clutch in a rotationally fixed manner and the planetary gear carrier can be connected to the first clutch in a rotationally fixed manner. If the first sun gear is now arranged in a rotationally fixed manner in the housing, the second sun gear can be operatively connected to the differential stage, so that the introduced torque is transmitted to the differential stage via the second sun gear. Alternatively, the first sun gear can also be operatively connected to the differential stage. In this case, the second sun gear is arranged in a rotationally fixed manner in the housing and the torque is transmitted to the differential stage via the first sun gear.

[0031] In other words, the invention relates to an axially parallel two-speed transmission with a common ring gear and planetary carrier for an electric axle. The combination of two planetary gear stages with a spur gear stage and a shifting element designed as a double clutch or synchronizer unit ensures a transmission structure that is as simple as possible with many identical parts and a suitable gear ratio distribution or distribution. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] The present invention will be described below with the aid of the accompanying drawings. In the accompanying drawings:

[0033] Figure 1 A first embodiment of a drive device according to the invention in an axially parallel design is shown,

[0034] Figure 2 A modification of the first embodiment of the drive device according to the invention in a coaxial design is shown,

[0035] Figure 3 A second embodiment of the drive device according to the invention in an axially parallel design is shown,

[0036] Figure 4 A modification of the second embodiment of the drive device according to the invention in a coaxial design is shown,

[0037] Figure 5 A third embodiment of the drive device according to the invention is shown in an axially parallel design, and

[0038] Figure 6 A modification of the third embodiment of the drive device according to the invention is shown in a coaxial design.

[0039] The drawings are merely schematic in nature and are only useful for understanding the invention. Identical elements have identical reference numerals. Features of the various embodiments are interchangeable. DETAILED DESCRIPTION

[0040] Figure 1 A first embodiment of a drive device 1 according to the invention is shown in an axially parallel design.

[0041] The drive device 1 for a motor vehicle (not shown here) according to the invention has an electric drive machine (not shown here) and a transmission 3. The electric drive machine has a stator and a rotor. The drive power of the electric drive machine is transmitted to the transmission 3 via a drive shaft 2, which is arranged between the electric drive machine and the transmission 3 and is designed as a rotor shaft.

[0042] The transmission 3 comprises a first planetary gear stage 4 and a second planetary gear stage 5 and a differential stage 6. The first planetary gear stage 4 has a first planetary set having a plurality of planetary gears 7a rotatably arranged on a first planetary gear carrier 8a and meshing with a first sun gear 9a and a first ring gear. Thus, the planetary gears 7a of the first planetary gear set radially mesh with each other between the first sun gear 9a and the first ring gear. The drive shaft 2 is connected to the first sun gear 9a in a rotationally fixed manner. The second planetary gear stage 5 has a second planetary set having a plurality of planetary gears 7b rotatably arranged on a second planetary gear carrier 8b and meshing with a second sun gear 9b and a second ring gear. Thus, the planetary gears 7b of the second planetary gear set radially mesh with each other between the second sun gear 9b and the second ring gear. The drive shaft 2 is also connected to the first sun gear 9a in a rotationally fixed manner.

[0043] The first ring gear and the second ring gear form a common ring gear 10. In particular, the common ring gear 10 is integrally assembled from the first ring gear and the second ring gear so that the first ring gear and the second ring gear and thus also the common ring gear 10 have the same toothing.

[0044] In addition, the first planetary gear carrier 8a and the second planetary gear carrier 8b form a common planetary gear carrier 8. The common planetary gear carrier 8 basically takes the form of a double planetary gear in which the first planetary gear carrier 8a and the second planetary gear carrier 8b are permanently (non-detachably) assembled into one piece. For example, the first planetary gear carrier 8a and the second planetary gear carrier 8b can be welded to each other.

[0045] On the input side of the drive device 1 there is a dual clutch device 11 having a first power shift clutch 12 a and a second power shift clutch 12 b which are each operatively connected to the first planetary gear set 4 and the second planetary gear set 5 , respectively.

[0046] Furthermore, according to the first embodiment, the planetary gear carrier 8 is operatively connected to the differential stage 6. The differential stage 6 can be designed as a spur gear differential. The differential stage 6 is arranged to distribute the drive power to the first output shaft 13a and the second output shaft 13b via the drive shaft 2 and the transmission 3. In the first embodiment, the drive shaft 2 is arranged axially parallel to the two output shafts 13a, 13b. Furthermore, the drive machine can be arranged axially parallel to the differential stage 6.

[0047] In the first embodiment, a further reduction gear 14 designed as a spur gear is arranged between the planet carrier 8 and the differential stage 6 .

[0048] In the first embodiment, the ring gear 10 is arranged in a stationary manner in the housing 15. In addition, in the first embodiment, the first sun gear 9a and the second sun gear 9b are each connected to the second clutch 12b and the first clutch 12a in a rotationally fixed manner, respectively, so that the first sun gear 9a or the second sun gear 9b can be switched to transmit torque or rotate freely.

[0049] Closing the second clutch 12b and opening the first clutch 12a achieves a first gear ratio, wherein closing the first clutch 12a and opening the second clutch 12b achieves a second gear ratio. The first gear ratio is different from the second gear ratio. Opening both clutches 12a, 12b achieves a power cut, wherein the drive machine is disconnected from the two output shafts 13a, 13b.

[0050] The first gear ratio (closing the second clutch 12b) converts the first planetary gear set 4 into a fixed transmission (dual-shaft transmission) with a fixed gear ratio, wherein the input torque is introduced into the first planetary gear set 4 via the first sun gear 9a. Via the ring gear 10 fixed to the housing, the planet gears 7a roll on the ring gear 10 and rotate the planet carrier 8 in the same direction as the sun gear 9a. The output torque is transmitted to the differential stage 6 via the planet carrier 8 and is further distributed to the output shafts 13a and 13b.

[0051] The second gear ratio (which closes the first clutch 12a) renders the first planetary gear set 4 substantially inactive, since the input torque is now transmitted from the drive shaft to the second sun gear 9b and introduced into the second planetary gear set 5. Via the ring gear 10 fixed to the housing, the planetary gears 7b roll on the ring gear 10 and rotate the planetary gear carrier 8 in the same direction as the sun gear 9b. Via the planetary gear carrier 8, the torque developed from the planetary gear stage 5 is introduced into the differential stage 6 and further distributed to the output shafts 13a and 13b.

[0052] In the first embodiment, the dual clutch device 11 is arranged on the drive side, that is, at the input where the torque is input into the drive shaft 2. In the first embodiment, the reduction gear 14 is then arranged on the output side between the second planetary gear stage 5 and the differential stage 6. The drive shaft 2, the first planetary gear stage 4, the second planetary gear stage 5, the reduction gear 14 and the differential stage 6 are arranged in this order in the direction of the torque flow.

[0053] Figure 2 A modification of the first embodiment of the drive device 1 according to the invention in a coaxial design is shown. In the following, only the modification of the first embodiment of the drive device 1 in a coaxial design will be discussed. Figure 1 The differences from the first embodiment are shown.

[0054] The reduction gear 14 is not arranged on the output side between the second planetary gear stage 5 , in particular the planetary gear carrier 8 , and the differential stage 6 , but rather on the input side between the electric drive machine or drive shaft 2 and the dual clutch device 11 .

[0055] In other words, in the drive device 1 according to the modification of the first embodiment, the electric drive machine, the reduction gear 14, the drive shaft 2, the first planetary gear set 4, the second planetary gear set 5, and the differential set 6 are arranged in this order.

[0056] Figure 3 A second embodiment of a drive device 1 according to the invention in an axially parallel design is shown. In the following, only the differences with respect to the first embodiment described above will be discussed.

[0057] In the drive device 1 according to the second embodiment, the planetary gear carrier 8 is arranged in a stationary manner in the housing 15 compared to the first embodiment. The first gear ratio (closing the first clutch 12a) converts the first planetary gear set 4 into a fixed transmission (dual-shaft transmission) with a fixed gear ratio, wherein the input torque is introduced into the first planetary gear set 4 via the first sun gear 9a. Via the planetary gear carrier 8 fixed to the housing, the planetary gear 7a rolls on the ring gear 10 and thus rotates the ring gear in the same direction as the sun gear 9a. The output torque is transmitted to the differential stage 6 via the ring gear 10 and is further distributed to the output shafts 13a and 13b.

[0058] The second gear ratio (which closes the second clutch 12b) renders the first planetary gear set 4 substantially inactive, since the input torque is now transmitted from the drive shaft to the second sun gear 9b and introduced into the second planetary gear set 5. Via the planetary gear carrier 8 fixed to the housing, the planetary gears 7b roll on the ring gear 10 and thus rotate the ring gear in the same direction as the sun gear 9b. Via the ring gear 10, the torque formed from the planetary gear stage 5 is introduced into the differential stage 6 and further distributed to the output shafts 13a and 13b.

[0059] Figure 4 A modification of the second embodiment of the drive device 1 according to the invention in a coaxial design is shown. In the following, only the embodiment related to Figure 3 The differences from the first embodiment are shown.

[0060] The reduction gear 14 is not arranged on the output side between the second planetary gear stage 5 , in particular the ring gear 10 , and the differential stage 6 , but rather on the input side between the electric drive machine or drive shaft 2 and the dual clutch device 11 .

[0061] In other words, in the drive device 1 according to the modification of the second embodiment, the electric drive machine, the reduction gear 14, the drive shaft 2, the first planetary gear set 4, the second planetary gear set 5, and the differential set 6 are arranged in this order.

[0062] Figure 5 A third embodiment of a drive device 1 according to the invention in an axially parallel design is shown. In the following, only the differences with respect to the first embodiment described above will be discussed.

[0063] In the drive device 1 according to the third embodiment, in contrast to the first embodiment, the first clutch 12a is connected in a rotationally fixed manner to the planetary carrier 8. The second clutch 12b is in turn connected in a rotationally fixed manner to the ring gear 10. Furthermore, the first sun gear 9a is arranged in a stationary manner in the housing 15 and the second sun gear 9b is operatively connected to the differential stage 6 via a rotationally fixed connection to the reduction gear 14.

[0064] The first gear ratio (closing the first clutch 12a) converts the first planetary gear set 4 into a fixed transmission (dual-shaft transmission) with a fixed gear ratio, wherein the input torque is introduced into the first planetary gear set 4 via the planetary carrier 8. The planetary gears 7a roll on the first sun gear 9a fixed to the housing and in the process rotate the second sun gear 9b in the same direction as the planetary carrier 8. The output torque is transmitted to the differential stage 6 via the second sun gear 9b and is further distributed to the output shafts 13a and 13b.

[0065] The second gear ratio (closing the second clutch 12b) renders the first planetary gear stage 4 substantially inactive, since the input torque is now transmitted from the drive shaft to the ring gear 10. The planetary gears 7a roll on the first sun gear 9a fixed to the housing and rotate the second sun gear 9b in the same direction as the ring gear 10. Via the second sun gear 9b, the torque developed from the planetary gear stage 5 is introduced into the differential stage 6 and further distributed to the output shafts 13a and 13b.

[0066] Figure 6A modification of the third embodiment of the drive device 1 according to the invention in a coaxial design is shown. In the following, only the modification of the third embodiment of the drive device 1 in coaxial design will be discussed. Figure 5 The differences from the first embodiment are shown.

[0067] The reduction gear 14 is not arranged on the output side between the second planetary gear stage 5 , in particular the second sun gear 9 b , and the differential stage 6 , but rather on the input side between the electric drive machine or drive shaft 2 and the dual clutch device 11 .

[0068] In other words, in the drive device 1 according to the modification of the third embodiment, the electric drive machine, the drive shaft 2, the reduction gear 14, the first planetary gear set 4, the second planetary gear set 5, and the differential set 6 are arranged in this order.

[0069] In addition, in a modification of the third embodiment, the first sun gear 9a is connected to the differential stage 6 in a rotationally fixed manner and the second sun gear 9b is accommodated in a stationary manner in the housing 15. Therefore, in the case of the first gear ratio, the torque introduced via the planetary gear carrier 8 is transferred to the differential stage 6 via the first sun gear 9a. In the second gear ratio, the torque introduced via the ring gear 10 is transferred to the differential stage 6 via the first sun gear 9a and is finally distributed to the output shafts 13a, 13b.

[0070] Description of Reference Numerals

[0071] 1 drive device 2 drive shaft 3 transmission device 4 first planetary gear stage 5 second planetary gear stage 6 differential stage 7a first planetary gear 7b second planetary gear 8 common planetary gear carrier 9a first sun gear 9b second sun gear 10 common ring gear 11 double clutch device 12a first clutch 12b second clutch 13a, 13b output shaft 14 reduction gear 15 housing

Claims

1. A drive device (1) for a motor vehicle, comprising an electric drive machine, the electric drive machine being operatively connected to a transmission (3) via a drive shaft (2), the transmission (3) having at least a first planetary gear stage (4) and a second planetary gear stage (5) and a differential stage (6), the first planetary gear stage (4) having a first planetary gear set comprising a plurality of planetary gears (7a), the planetary gears (7a) of the first planetary gear set being rotatably arranged on a first planetary gear carrier and meshing with a first sun gear (9a) and a first ring gear, the second planetary gear stage (5) having a second planetary gear set comprising a plurality of planetary gears (7b) and a differential stage (6). The invention relates to a gear set, wherein the planetary gears (7b) of the second planetary gear set are rotatably arranged on a second planetary gear carrier and mesh with a second sun gear (9b) and a second ring gear, and the first planetary gear stage (4) and the second planetary gear stage (5) are operatively connected to a dual clutch device (11) comprising a first power shift clutch (12a) and a second power shift clutch (12b), the first ring gear and the second ring gear are rigidly connected together to form a common ring gear (10), and the first planetary gear carrier and the second planetary gear carrier are rigidly connected together to form a common planetary gear carrier (8), characterized in that: The common ring gear (10), the common planetary gear carrier (8), the first sun gear (9a) or the second sun gear (9b) are fixed in a stationary manner in the housing (15); the first power shift clutch (12a) is connected to the second sun gear (9b) in a rotationally fixed manner and the second power shift clutch (12b) is connected to the first sun gear (9a) in a rotationally fixed manner, or the first power shift clutch (12a) is connected to the common planetary gear carrier (8) in a rotationally fixed manner and the second power shift clutch (12b) is connected to the common ring gear (10) in a rotationally fixed manner.

2. The drive device (1) according to claim 1, characterized in that The first ring gear and the second ring gear have the same teeth.

3. The drive device (1) according to claim 1 or 2, characterized in that: The common planetary gear carrier (8), the common ring gear (10), the second sun gear (9b) or the first sun gear (9a) is operatively connected to the differential stage (6).

4. A drive device (1) according to claim 1 or 2, It is characterized in that Opening the two power shift clutches (12a, 12b) achieves power cutoff.

5. A drive device (1) according to claim 1 or 2, It is characterized in that Closing the first power shift clutch (12a) and opening the second power shift clutch (12b) achieves a first gear ratio, and closing the second power shift clutch (12b) and opening the first power shift clutch (12a) achieves a second gear ratio.

6. The drive device (1) according to claim 5, It is characterized in that The first gear ratio is different from the second gear ratio.

7. A drive device (1) according to claim 1 or 2, It is characterized in that The electric drive machine has a stator and a rotor, wherein the rotor is connected to the drive shaft (2) in a rotationally fixed manner.

8. A drive device (1) according to claim 1 or 2, It is characterized in that The drive machine is offset or arranged coaxially with the differential stage (6) in an axially parallel manner.

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