DE102019119949B4 - Drive device for a motor vehicle with a non-rotatable internal gear-sun gear and planet carrier-internal gear connection - Google Patents

Abstract

Drive device (1) for a motor vehicle, comprising an electric drive machine which is operatively connected to a transmission device (3) via a drive shaft (2), the transmission device (3) having at least one first and second planetary gear stage (4, 5) and a differential stage ( 6), wherein the first planetary gear stage (4) has a first planetary gearset with a plurality of planetary gears (7a), the planetary gears (7a) of the first planetary gearset being rotatably arranged on a first planetary gear carrier (8a) and having a first sun gear (9a) and mesh with a first ring gear (10a), the second planetary gear stage (5) having a second planetary gear set with a plurality of planetary gears (7b), the planetary gears (7b) of the second planetary gear set being rotatably arranged on a second planetary gear carrier (8b) and having a second sun gear (9b) and a second ring gear (10b) are in toothed engagement, the first and the second planetary gear set (4, 5) being operatively connected to a double clutch device (11) with a first and a second power-shiftable clutch (12a, 12b). are, wherein the first ring gear (10a) is non-rotatably connected to the second sun gear (9b), the first planetary gear carrier (8a) is non-rotatably connected to the second ring gear (10b) and the first sun gear (9a) is non-rotatably connected to the drive shaft (2), characterized characterized in that the first planetary gear carrier (8a) and the second ring gear (10b) are operatively connected to the differential stage (6), the first ring gear (10a) and the second sun gear (9b) can be fixed in place in a housing (15) and the second planetary gear carrier ( 8b) can be fixed in the housing (15).

Description

The invention relates to a drive device for a motor vehicle, in particular for an electrically driven motor vehicle, with an electric drive machine which is operatively connected to a transmission device via a drive shaft, the transmission device having at least a first and second planetary gear stage and a differential stage, the first planetary gear stage having a first planetary gearset with a plurality of planetary gears, the planetary gears of the first planetary gearset being rotatably arranged on a first planetary gear carrier and meshing with a first sun gear and with a first ring gear, with the second planetary gear set having a second planetary gearset with a plurality of planetary gears, with the planetary gears of the second planetary gearset are rotatably arranged on a second planetary gear carrier and mesh with a second sun gear and with a second ring gear, the first and the second planetary gear set being operatively connected to a double clutch device with a first and a second power-shiftable clutch.

Drive devices for motor vehicles are already known from the prior art. For example shows DE 10 2011 088 668 A1 a drive device with at least one electric drive machine, with at least one first planetary drive with a clutch and with a differential. A rotor shaft of the prime mover is coupled in a torque-proof manner to a first connecting shaft of the planetary drive formed from at least three connecting shafts. A second connection shaft of the first planetary drive can be fixed in a rotationally fixed manner against a component of the drive device by means of a shift sleeve of the shift clutch. A third connection shaft of the first planetary drive is operatively connected to a sum shaft of the differential. The shift sleeve can be shifted into positive engagement either with the second connecting shaft of the first planetary drive or into a torque-transmitting operative connection with the sum shaft of the differential.

The DE 11 2008 003 105 T5 shows a transmission for transferring power from an electric motor to first and second axles of a vehicle having an input shaft arranged to be driven by the electric motor and a first planetary gear set.

The DE 10 2018 112 405 B3 shows a drive device with an electric machine, in particular for an electrically driven motor vehicle.

The DE 10 2012 207 091 A1 shows a multi-speed transmission in planetary design, in particular for a motor vehicle.

The DE 10 2018 008 939 B3 shows an electric drive device, with a planetary gear set, which has a first sun gear, a first planet carrier and a first ring gear, with a planetary gear set, which has a second sun gear that is or can be coupled to the first ring gear in a torque-proof manner, a second planet carrier and a second sun gear that is torque-proof to the first planet carrier coupled or coupleable second ring gear, with an electric machine, which has a rotor, with an input shaft that can be driven by the rotor and is permanently non-rotatably connected to the first sun gear, with an output shaft, with a differential gear, with a first switching element, and with a second Switching element, wherein the planetary gear sets are arranged coaxially to the differential gear, and wherein the differential gear has a ball differential with a differential housing.

The DE 10 2015 104 778 A1 shows an electric axle drive for a motor vehicle, which has a transmission arrangement with two gears, with an electric machine for driving at least one output shaft of the axle of the motor vehicle, with a first spur gear stage that can be driven by means of the electric machine and a second spur gear stage that can be driven via this, and with at least one planetary gear.

The DE 10 2012 017 352 A1 shows a drive device for an in particular electrically driven axle of a motor vehicle, possibly with a driving electric machine, a transmission and a differential, which aborts the driven wheels of the motor vehicle via output shafts.

In the non-patent literature, the content from “KIMMIG, K.-L.; AGNER, I.: Double clutch - wet or dry, that is the question here, LuK SYMPOSIUM 2006, Schaeffler Automotive Buehl GmbH & Co. KG, 2006”.

It is the object of the invention to further develop a drive device for a motor vehicle, the focus being on the simplest possible transmission structure with many identical parts and a suitable transmission ratio distribution or spread.

In the case of a generic device, this object is achieved by three variants according to the invention.

The drive device according to the invention for a motor vehicle comprises an electric drive machine which is operatively connected to a transmission device via a drive shaft.

The transmission device has at least a first and second planetary gear stage and a differential stage, the first planetary gear stage having a first planetary gear set with a plurality of planetary gears, the planetary gears of the first planetary gear set being rotatably arranged on a first planetary gear carrier and having a first sun gear and a first ring gear in the meshing, the second planetary gear stage having a second planetary gear set with a plurality of planetary gears, the planetary gears of the second planetary gear set being rotatably arranged on a second planetary gear carrier and meshing with a second sun gear and with a second ring gear, and with the first and the second planetary gear stage are operatively connected to a dual clutch device having a first and a second power-shiftable clutch, the first ring gear being non-rotatably connected to the second sun gear and the first planetary gear carrier being non-rotatably connected to the second ring gear.

The term “operatively connected” is to be understood as meaning that two transmission elements can be directly connected to one another, or that there are further transmission elements between two transmission elements, for example one or more shafts or gears. Two mutually meshing gears are provided for the transmission of a torque and a speed from one gear to the other gear. A gear is to be understood, for example, as a sun gear, a ring gear and a planet gear of a planetary gear set.

A dual clutch device is to be understood as meaning a device with two power-shiftable clutches. Furthermore, the term “power shiftable clutch” is to be understood as meaning a device which has at least one open and one closed state and can be switched between the at least two states under load. When open, the clutch does not transmit any torque.
In the first solution according to the invention, the first planetary gear carrier and the second ring gear are operatively connected to the differential stage, the first ring gear and the second sun gear can be fixed in a housing, the first sun gear is non-rotatably connected to the drive shaft and the second planetary gear carrier can be fixed in the housing .

In the second solution according to the invention, the first planetary gear carrier and the second ring gear can be fixed in a housing, the first ring gear and the second sun gear are operatively connected to the differential stage, the first sun gear is non-rotatably connected to the drive shaft and the second planetary gear carrier can be fixed in the housing .

In the third solution according to the invention, the first planetary gear carrier and the second ring gear are fixed in a housing, the first ring gear and the second sun gear are operatively connected to the differential stage via the first clutch, the first sun gear is non-rotatably connected to the drive shaft and the second planetary gear carrier is connected to operatively connected to the differential stage via the second clutch.

Advantageous embodiments are claimed in the dependent claims and are explained in more detail below.

An advantageous embodiment can thus also be characterized in that an additional reduction gear is arranged in the torque flow between the electric drive machine and the differential stage. The reduction gear can be arranged on the input side between the electric drive machine and the first planetary gear set or on the output side between the second planetary gear set and the differential stage. The additional reduction gear increases the spread of the gear device and can be designed, for example, as a spur gear stage or as an additional planetary gear stage.

The first and second clutch of the double clutch device can preferably be designed as a friction clutch. Furthermore, the two clutches can preferably be arranged coaxially with one another. In particular, the respective clutch can be actuated by a respective actuator in order to initiate opening or closing of the respective clutch. The actuator can be designed to be actuated hydraulically, electromechanically, electromagnetically or, for example, pneumatically.

It is expedient if both clutches can be opened at the same time to switch off the power. Closing the first clutch and opening the second clutch can realize a first gear ratio, whereas closing the second clutch and opening the first clutch can realize a second gear ratio. In order to ensure a shifting process from one clutch to the other clutch that is as free of traction force interruptions as possible, one clutch can be engaged in a transitional period while the other closes, open. The slip in the clutches, designed as friction clutches, can thus switch between two gear stages without torque interruption, which can be perceived by the operator of the drive device as a switch mode between two gear stages without interruption in traction, which in turn increases the shifting comfort for the operator of the drive device. Preferably, the first gear ratio is unequal to the second gear ratio. For example, the first gear ratio may be greater than the second gear ratio. Alternatively, the first gear ratio may be less than the second gear ratio.

Furthermore, the electric drive machine preferably has a stator and a rotor, the rotor being connected to the drive shaft in a torque-proof 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, with a torque transmission device (gear) being arranged between the two shafts.

Furthermore, the differential stage is preferably designed as a spur gear differential, the differential stage being provided for distributing drive power from the drive machine to a first and second output shaft.

The drive machine can be arranged coaxially or axially parallel to the differential stage. The drive shaft is preferably arranged coaxially with the two output shafts. In particular, the drive shaft is designed as a hollow shaft, with at least one of the two output shafts being guided axially through the drive shaft. The two output shafts are preferably arranged on a common drive axle. Alternatively, the drive shaft is arranged axially parallel to the two output shafts, with axially parallel meaning that there is an axial offset between the input shaft and the output shaft.

In other words, the invention relates to a two-speed transmission for electric axles with a favorable spread. In the search for transmissions for two gears with an advantageous transmission ratio distribution in an axis-parallel and coaxial arrangement, the simplest possible transmission structure with many identical parts and suitable transmission ratio distribution or spread should be provided by a combination of two planetary gear stages with a spur gear stage and a shifting element designed as a double clutch or synchro unit, where the basic structure of the transmission has a sun gear-ring gear connection and a planet carrier-ring gear connection. In a first possible coaxial or axially parallel configuration, the fixed shaft can be optionally changed via the switching element, which ensures a high transmission ratio with a high spread. Optionally, an additional spur gear stage, designed as a spur gear differential, for example, can be both upstream and downstream. A second axially parallel configuration with a preceding or following spur gear stage enables a high transmission ratio with a moderate spread. In a third coaxial configuration, the shifting element is arranged on the output side, so that a moderate to high transmission ratio can be achieved with a large spread. In a fourth possible coaxial or axially parallel configuration, a low transmission ratio with a moderate spread can be ensured via the shifting element arranged on the output side. As an option, an additional spur gear stage can be placed both upstream and downstream, which results in a high transmission ratio with a moderate spread.

• 1 eine erste Ausführungsform einer erfindungsgemäßen Antriebsvorrichtung in koaxialer Bauweise,
• 2 eine erste Modifikation der Antriebsvorrichtung gemäß der ersten Ausführungsform in koaxialer Bauweise,
• 3 eine zweite Modifikation der Antriebsvorrichtung gemäß der ersten Ausführungsform in koaxialer Bauweise,
• 4 eine dritte Modifikation der Antriebsvorrichtung gemäß der ersten Ausführungsform in achsparalleler Bauweise,
• 5 eine zweite Ausführungsform einer erfindungsgemäßen Antriebsvorrichtung in koaxialer Bauweise,
• 6 eine erste Modifikation der Antriebsvorrichtung gemäß der zweiten Ausführungsform in koaxialer Bauweise,
• 7 eine zweite Modifikation der Antriebsvorrichtung gemäß der zweiten Ausführungsform in koaxialer Bauweise,
• 8 eine dritte Modifikation der Antriebsvorrichtung gemäß der zweiten Ausführungsform in achsparalleler Bauweise,
• 9 eine dritte Ausführungsform einer erfindungsgemäßen Antriebsvorrichtung in koaxialer Bauweise,
• 10 eine erste Modifikation der Antriebsvorrichtung gemäß der dritten Ausführungsform in achsparalleler Bauweise,
• 11 eine vierte Ausführungsform einer erfindungsgemäßen Antriebsvorrichtung in koaxialer Bauweise,
• 12 eine Ausführungsform einer nicht erfindungsgemäßen Antriebsvorrichtung in koaxialer Bauweise,
• 13 eine erste Modifikation der Antriebsvorrichtung gemäß der Ausführungsform nach 12 in koaxialer Bauweise, und
• 14 eine zweite Modifikation der Antriebsvorrichtung gemäß der Ausführungsform nach 12 in achsparalleler Bauweise.

Further measures improving the invention are presented in more detail below together with the description of preferred embodiments of the invention with reference to the figures. The figures each show a simplified schematic representation to illustrate the structure of drive devices according to the invention. Show it:

• 1 a first embodiment of a drive device according to the invention in a coaxial design,
• 2 a first modification of the driving device according to the first embodiment in coaxial construction,
• 3 a second modification of the driving device according to the first embodiment in coaxial construction,
• 4 a third modification of the drive device according to the first embodiment in paraxial design,
• 5 a second embodiment of a drive device according to the invention in a coaxial design,
• 6 a first modification of the driving device according to the second embodiment in coaxial construction,
• 7 a second modification of the driving device according to the second embodiment in coaxial construction,
• 8th a third modification of the drive device according to the second embodiment in paraxial design,
• 9 a third embodiment of a drive device according to the invention in a coaxial design,
• 10 a first modification of the drive device according to the third embodiment in paraxial design,
• 11 a fourth embodiment of a drive device according to the invention in a coaxial design,
• 12 an embodiment of a drive device not according to the invention in a coaxial design,
• 13 a first modification of the drive device according to the embodiment 12 in a coaxial design, and
• 14 a second modification of the drive device according to the embodiment 12 in a paraxial design.

The figures are only of a schematic nature and serve exclusively for understanding the invention. The same elements are provided with the same reference numbers. The features of the individual embodiments can be interchanged.

1 shows a first embodiment of a drive device 1 according to the invention in a coaxial design.

The drive device 1 according to the invention for a motor vehicle--not shown here--has an electric drive motor and a transmission device 3--not shown here. The electric drive machine has a stator and a rotor. A drive power (torque) of the electric drive machine is introduced into the gear device 3 via a drive shaft 2, which is arranged between the electric drive machine and the gear device 3 and is designed as a rotor shaft.

The transmission device 3 comprises a first and second planetary gear stage 4, 5 and a differential stage 6. The first planetary gear stage 4 has a first planetary gear set with a plurality of planetary gears 7a, which are arranged rotatably on a first planetary gear carrier 8a and with a first sun gear 9a and with a first Ring gear 10a are in tooth engagement. Consequently, the planet gears 7a of the first planetary gear set mesh radially between the first sun gear 9a and the first ring gear 10a. The second planetary gear stage 5 has a second planetary gear set with a plurality of planetary gears 7b, which are rotatably arranged on a second planetary gear carrier 8b and mesh with a second sun gear 9b and with a second ring gear 10b. Consequently, the planet gears 7b of the second planetary gear set mesh radially between the second sun gear 9b and the second ring gear 10b.

Furthermore, a double clutch device 11 with a first clutch 12a and a second clutch 12b is provided. Closing the first clutch 12a and opening the second clutch 12b realizes a first gear ratio, with closing the second clutch 12b and opening the first clutch 12a realizing a second gear ratio. The first gear ratio is unequal to the second gear ratio. Power is switched off by opening both clutches 12a, 12b.

In other words, by shifting the dual clutch device 11, the torque transmitted from the electric drive motor via the transmission device 3 to the differential stage 6 can be optionally varied between the first and the second gear ratio. The torque thus transmitted is finally passed on from the differential stage 6 to output shafts 13a, 13b, which are connected, for example, to drive wheels of the motor vehicle. The transmission device 3 thus essentially enables two-gear operation of the motor vehicle.

In the drive device 1 according to the first embodiment, the first sun wheel 9a is connected in a torque-proof manner to the drive shaft 2 and thus introduces the torque of the electric drive machine into the transmission device 3 . The first planetary gear carrier 8a is connected in a torque-proof manner to the second ring gear 10b and is also operatively connected to the differential stage 6, so that the torque of the electric drive machine in the first embodiment is transmitted to the differential stage 6 via the torsionally rigid combination of the first planetary gear carrier 8a and the second ring gear 10b , which finally distributes it to the output shafts 13a, 13b.

The first ring gear 10a is connected in a rotationally fixed manner to the second sun gear 9b and can be fixed/received/arranged in a housing 15 in a stationary/rotatable/housing-fixed manner via the first clutch 12a. By contrast, the second planetary gear carrier 8b can be fixed in place in the housing 15 via the second clutch 12b of the double clutch device 11 interposed in the first embodiment in the axial direction between the first planetary gear stage 4 and the second planetary gear stage 5 . In the first embodiment, the dual clutch device 11 thus permits an optional housing-fixed arrangement of the non-rotatable combination of the first ring gear 10a and the second sun gear 9b or the second planetary gear carrier 8b.

2 until 4 show modifications of the drive device 1 according to the invention according to FIG the first embodiment. In the following, only the differences to the in 1 shown drive device 1 received according to the first embodiment.

At the in 2 illustrated first modification of the drive device 1 according to the first embodiment, the differential stage 6 is interposed in the axial direction of the input shaft 2 and the output shafts 13a, 13b between the first planetary gear set 4 and the double clutch device 11. In addition, the differential stage 6 is designed as an additional double planetary gear stage, with a double planetary gear carrier on which two planetary gear sets are mounted being inserted between the first planetary gear carrier 8a and the second ring gear 10b and connected to them in a torque-proof manner. The two planetary gear sets each mesh with corresponding sun gears formed on the output shafts 13a, 13b and thus distribute the torque to the output shafts 13a, 13b.

3 12 shows a second modification of the drive device 1 according to the first embodiment. A reduction gear 14 designed as a spur gear stage is arranged on the input side between the electric drive machine and the gear device 3, as a result of which the spread of the drive device 1 can be increased.

In 4 in turn, a third modification of the drive device 1 according to the first embodiment is shown in an axially parallel design. The reduction gear 14 is arranged on the output side between the second planetary gear stage 5 and the differential stage 6 .

5 shows a second embodiment of the drive device 1 according to the invention in a coaxial design. In the following, only the differences to the in 1 drive device 1 shown received.

How out 5 As can be seen, in the drive device 1 according to the second embodiment, the double clutch device 11 is arranged on the output side in the transmission device 3 and is not interposed between the first planetary gear set 4 and the second planetary gear set 5 .

6 until 8th show modifications of the drive device 1 according to the invention according to the second embodiment. In the following, only the differences to the in 5 illustrated drive device 1 received according to the second embodiment.

At the in 6 illustrated first modification of the drive device 1 according to the second embodiment is similar to that in FIG 2 illustrated, first modification of the first embodiment, the differential stage 6 interposed in the axial direction of the input shaft 2 and the output shafts 13a, 13b between the first planetary gear set 4 and the dual clutch device 11. In addition, the differential stage 6 is designed as an additional double planetary gear stage, the double planetary gear carrier on which the two planetary gear sets are mounted being non-rotatably attached to the first planetary gear carrier 8a. The two planetary gear sets each mesh with corresponding sun gears formed on the output shafts 13a, 13b and thus distribute the torque to the output shafts 13a, 13b.

7 12 shows a second modification of the drive device 1 according to the second embodiment. The reduction gear 14 designed as a spur gear stage is arranged on the input side between the electric drive machine and the gear device 3, as a result of which the spread of the drive device 1 can be increased.

In 8th in turn, a third modification of the drive device 1 according to the second embodiment is shown in an axially parallel design. The reduction gear 14 is arranged on the output side between the second planetary gear stage 5 and the differential stage 6 .

9 shows a third embodiment of the drive device 1 according to the invention in a coaxial design. In the following, the differences to the in 1 drive device 1 shown received.

In the drive device 1 according to the third embodiment, the reduction gear 14 is interposed on the input side between the electric drive machine and the gear device 3 . The drive shaft 2 is non-rotatably connected to the first sun gear 9a, so that the torque is transmitted from the electric drive motor via the reduction gear 14 to the drive shaft 2 and is passed via the first sun gear 9a into the transmission device 3, in particular the first planetary gear stage 4.

The first planetary gear carrier 8a is connected in a torque-proof manner to the second ring gear 10b and, in the third specific embodiment, can be fixed in place in the housing 15 via the second clutch 12b of the double clutch device 11 arranged on the output side. The second planet carrier 8b can in turn be fixed in place in the housing 15 via the first clutch 12a. The dual clutch device 11 thus allows in the third embodiment, an optional housing-fixed Arrangement of the non-rotatable combination of the first planet carrier 8a and the second ring gear 10b or the second planet carrier 8b. During operation, the torque is diverted to the differential stage 6 via the first ring gear 10a and the second sun gear 9b, which is connected to it in a torque-proof manner.

In 10 a first modification of the drive device 1 according to the third embodiment is shown in an axially parallel design. The reduction gear 14 is arranged on the output side between the second planetary gear stage 5 and the differential stage 6 .

11 shows a fourth embodiment of the drive device 1 according to the invention in a coaxial design. In the following, the differences to the in 1 drive device 1 shown received.

In the drive device 1 according to the fourth specific embodiment, the first sun gear 9a is connected in a torque-proof manner to the drive shaft 2 and thus introduces the torque of the electric drive machine into the transmission device 3 . The first planetary gear carrier 8a is arranged in a stationary manner in the housing 15 . Furthermore, the second ring gear 10b is also arranged in a stationary manner in the housing 15 . In other words, in the fourth embodiment, the first planetary gear carrier 8a and the second ring gear 10b are non-rotatably connected to each other via the housing 15 .

The first ring gear 10a in turn is non-rotatably connected to the second sun gear 9b. In addition, the non-rotatable combination of the first ring gear 10a and the second sun gear 9b can be operatively connected to the differential stage 6 via the first clutch 12a of the double clutch device 11 arranged on the output side. The second planet carrier 8b can be operatively connected to the differential stage 6 via the second clutch 12b.

In other words, the first or second gear ratio can be realized in the drive device 1 according to the fourth embodiment by selectively operatively connecting the non-rotatable combination of the first ring gear 10a and the second sun gear 9b or the second planetary gear carrier 8b to the differential stage 6.

12 shows an embodiment of a drive device 1 not according to the invention in a coaxial design. In the following, the differences to the in 1 drive device 1 shown received.

In the drive device 1 according to the embodiment 12 the first sun wheel 9a is connected in a rotationally fixed manner to the drive shaft 2 and thus introduces the torque of the electric drive machine into the transmission device 3 . The first planetary gear carrier 8a is connected in a torque-proof manner to the second ring gear 10b and can be operatively connected to the differential stage 6 via the first clutch 12a of the double clutch device 11 arranged on the output side. The second planet carrier 8b can be operatively connected to the differential stage 6 via the second clutch 12b.

In other words, in the drive device 1 according to the embodiment 12 the first or second gear ratio can be realized by selectively operatively connecting the non-rotatable combination of the first planetary gear carrier 8a and the second ring gear 10b or the second planetary gear carrier 8b to the differential stage 6 .

Furthermore, in the embodiment according to 12 the first ring gear 10a is arranged stationary in the housing 15. Furthermore, the second sun wheel 9b is also arranged in a stationary manner in the housing 15 . In other words, in this embodiment the first ring gear 10a and the second sun gear 9b are connected to one another in a torque-proof manner via the housing 15 .

In the 13 illustrated first modification of the embodiment 12 represents a drive device 1 in a coaxial design. In this case, the reduction gear 14 is interposed on the input side between the electric drive machine and the transmission device 3 , in particular the drive shaft 2 .

14 FIG. 12 shows a second modification of the drive device 1 according to the embodiment 12 in a paraxial design. The reduction gear 14 is interposed on the output side between the dual clutch device 11 and the differential stage 6 .

Reference List

1

drive device

2

drive shaft

3

gear device

4

first planetary gear stage

5

second planetary gear stage

6

differential stage

7a

first planet gear(s).

7b

second planet gear(s).

8a

first planet carrier

8b

second planet carrier

9a

first sun gear

9b

second sun wheel

10a

first ring gear

10b

second ring gear

11

dual clutch device

12a

first clutch

12b

second clutch

13a, 13b

output shaft

14

reduction gear

15

Housing

Claims (8)

Drive device (1) for a motor vehicle, comprising an electric drive machine which is operatively connected to a transmission device (3) via a drive shaft (2), the transmission device (3) having at least one first and second planetary gear stage (4, 5) and a differential stage ( 6), wherein the first planetary gear stage (4) has a first planetary gearset with a plurality of planetary gears (7a), the planetary gears (7a) of the first planetary gearset being rotatably arranged on a first planetary gear carrier (8a) and having a first sun gear (9a) and mesh with a first ring gear (10a), the second planetary gear stage (5) having a second planetary gear set with a plurality of planetary gears (7b), the planetary gears (7b) of the second planetary gear set being rotatably arranged on a second planetary gear carrier (8b) and having a second sun gear (9b) and a second ring gear (10b) are in toothed engagement, the first and the second planetary gear set (4, 5) being operatively connected to a double clutch device (11) with a first and a second power-shiftable clutch (12a, 12b). are, wherein the first ring gear (10a) is non-rotatably connected to the second sun gear (9b), the first planetary gear carrier (8a) is non-rotatably connected to the second ring gear (10b) and the first sun gear (9a) is non-rotatably connected to the drive shaft (2), characterized characterized in that the first planetary gear carrier (8a) and the second ring gear (10b) are operatively connected to the differential stage (6), the first ring gear (10a) and the second sun gear (9b) can be fixed in a housing (15) and the second Planet carrier (8b) can be fixed in the housing (15). Drive device (1) according to the preamble of claim 1 , characterized in that the first planetary gear carrier (8a) and the second ring gear (10b) can be fixed in place in a housing, the first ring gear (10a) and the second sun gear (9b) are operatively connected to the differential stage (6) and the second planetary gear carrier (8b) can be fixed in the housing (15). Drive device (1) according to the preamble of claim 1 , characterized in that the first planetary gear carrier (8a) and the second ring gear (10b) are fixed in a housing, the first ring gear (10a) and the second sun gear (9b) with the differential stage (6) via the first clutch (12a ) are operatively connected and the second planet carrier (8b) is operatively connected to the differential stage (6) via the second clutch (12b). Drive device (1) according to one of Claims 1 until 3 , characterized in that an additional reduction gear (14) is arranged in the torque flow between the electric drive machine and the differential stage (6). Drive device (1) after claim 4 , characterized in that the reduction gear (14) is arranged between the electric drive motor and the first planetary gear stage (4). Drive device (1) after claim 4 , characterized in that the reduction gear (14) is arranged between the second planetary gear stage (5) and the differential stage (6). Drive device (1) according to one of the preceding claims, characterized in that the drive machine is arranged coaxially to the differential stage (6). Drive device (1) according to one of Claims 1 until 6 , characterized in that the drive machine is arranged offset parallel to the axis to the differential stage (6).

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