DE102019119955B4 - Drive device for a motor vehicle with a sun gear-planet gear carrier and/or sun gear-ring 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 characterized in that• the first planet carrier (8a) is non-rotatably connected to the second sun gear (9b), wherein• the first sun gear (9a) is fixed in a housing (15), wherein• the second ring gear (10b) fixed in place in the housing (15), with• the first planet carrier (8a) being non-rotatably connectable to the drive shaft (2) via the first clutch (12a) and• the first ring gear (10a) being non-rotatably connected via the second clutch (12b). can be connected to the drive shaft (2).

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 connecting 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, comprising an input shaft configured to be driven by the electric motor and a first planetary gear set. A second planetary gear set has a first element that is driven by the first planetary gear set, a second element that cannot rotate, and a third element. A differential assembly has a first side gear configured to drive the first axle, a second side gear configured to drive the second axle, and a pair of gears meshing with the first and second side gears. A first clutch, in use, frictionally couples the first member to the differential assembly. A second clutch, in use, frictionally couples the third member to the differential assembly.

The DE 10 2016 220 063 A1 shows a drive device for a motor vehicle, comprising 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 stage and a differential stage, the first planetary stage having a first planetary set with a plurality of planets, the Planets of the first planetary set are rotatably arranged on a first planet carrier and mesh with a first sun and with a first ring gear, the second planetary stage having a second planetary set with a plurality of planets, the planets of the second planetary set being rotatably arranged on a second planetary carrier and meshing with a second sun and with a second ring gear, wherein the first planet carrier is non-rotatably connected to the second sun, wherein the drive shaft is operatively connected to the first sun, further wherein the second ring gear is stationarily fixed to a housing, and wherein the second planetary carrier is operatively connected to the differential stage, with a double clutch device having a first and second power-shiftable clutch being arranged between the first planetary stage and the housing.

The DE 10 2016 220 062 A1 shows a drive device for a motor vehicle, comprising 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 stage and a differential stage, the first planetary stage having a first planetary set with a plurality of planets, the Planets of the first planetary set are rotatably arranged on a first planet carrier and mesh with a first sun and with a first ring gear, the second planetary stage having a second planetary set with a plurality of planets, the planets of the second planetary set being rotatably arranged on a second planetary carrier and meshing with a second sun and with a second ring gear, wherein the first planet carrier is non-rotatably connected to the second sun, wherein the drive shaft is operatively connected to the first sun, further wherein the second ring gear is stationarily fixed to a housing, and wherein the second planet carrier with the differential stage is operatively connected, with a double clutch device having a first and second power-shiftable clutch being arranged between the first and second planetary stages, the first ring gear being connectable to the second sun via the first clutch, and the first ring gear being able to be connected to the housing via the second clutch is.

The DE 10 2016 220 060 B3 shows a drive device for a motor vehicle, comprising 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 stage and a differential stage, the first planetary stage having a first planetary set with a plurality of planets, the Planets of the first planetary set are rotatably arranged on a first planet carrier and mesh with a first sun and with a first ring gear, the second planetary stage having a second planetary set with a plurality of planets, the planets of the second planetary set being rotatably arranged on a second planetary carrier and meshing with a second sun and with a second ring gear, wherein the first planet carrier is non-rotatably connected to the second sun, wherein the drive shaft is operatively connected to the first sun, further wherein the second ring gear is stationarily fixed to a housing, and wherein the second planetary carrier is operatively connected to the differential stage, with a dual clutch device having a first and second power-shiftable clutch being arranged between the first and second planetary stage, the first ring gear being connectable to the second sun via the first clutch, and the first ring gear being connected to the second clutch can be connected to the second planet carrier.

The non-patent literature with KIMMIG, K.-L.; AGNER, I.: Double clutch - wet or dry, that is the question, LuK SYMPOSIUM 2006. Schaeffler Automotive Buehl GmbH & Co. KG, 2006 a drive device for a motor vehicle.

The DE 10 2018 131 492 A1 shows a transmission device for a motor vehicle and a drive device with such a transmission device.

It is therefore 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.

This object is solved by the features of independent claims 1-3.

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 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.

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

Furthermore, an advantageous embodiment can 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 largely uninterrupted shifting process from one clutch to the other clutch, one clutch can open in a transitional period while the other closes. 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 split-power electric axles. 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-planet gear carrier or a sun gear-ring gear connection. In a first possible axially parallel or coaxial configuration, the switching element is arranged on the input side, which ensures a moderate transmission ratio with a moderate spread in the coaxial case and a high transmission ratio with a moderate spread in the axially parallel case. Optionally, an additional spur gear stage, designed as a spur gear differential, for example, can be both upstream and downstream. A second and a third axis-parallel configuration with an input-side shifting element and an optional spur gear stage enable a high transmission ratio with a moderate spread. A fourth coaxial configuration with an input-side switching element ensures a low transmission ratio with a moderate spread, this arrangement also enabling a high transmission ratio with a moderate spread if the alignment is parallel to the axis with a preceding or following spur gear stage.

• 1 eine erste Ausführungsform der erfindungsgemäßen Antriebsvorrichtung in achsparalleler 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 achsparalleler Bauweise,
• 4 eine dritte Modifikation der Antriebsvorrichtung gemäß der ersten Ausführungsform in koaxialer Bauweise,
• 5 eine vierte Modifikation der Antriebsvorrichtung gemäß der ersten Ausführungsform in koaxialer Bauweise,
• 6 eine zweite Ausführungsform der erfindungsgemäßen Antriebsvorrichtung in achsparalleler Bauweise,
• 7 eine erste Modifikation der Antriebsvorrichtung gemäß der zweiten Ausführungsform in koaxialer Bauweise,
• 8 eine zweite Modifikation der Antriebsvorrichtung gemäß der zweiten Ausführungsform in koaxialer Bauweise,
• 9 eine dritte Ausführungsform der erfindungsgemäßen Antriebsvorrichtung in achsparalleler Bauweise,
• 10 eine erste Modifikation der Antriebsvorrichtung gemäß der dritten Ausführungsform in koaxialer Bauweise,
• 11 eine nicht erfindungsgemäße vierte Ausführungsform der Antriebsvorrichtung in koaxialer Bauweise,
• 12 eine erste Modifikation der Antriebsvorrichtung gemäß der vierten Ausführungsform in achsparalleler Bauweise, und
• 13 eine zweite Modifikation der Antriebsvorrichtung gemäß der vierten Ausführungsform in koaxialer 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 on construction of drive devices according to the invention. Show it:

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

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 the 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 double clutch is provided direction 11 arranged on the input side of the transmission device 3. In particular, depending on the circuit of the dual clutch device 11, either the first planetary gear carrier 8a or the first ring gear 10a can be connected in a torque-proof manner to the drive shaft 2 and thus the first or second gear ratio can be implemented.

The first planet carrier 8a is, as described above, on the one hand non-rotatably connected to the first clutch 12a, but in the first embodiment on the other hand also non-rotatably connected to the second sun gear 9b. Furthermore, the first sun gear 9a is arranged in a stationary manner (fixed to the housing) in a housing 15 .

The planetary gears 7b of the second planetary gear set 5 mesh radially between the second sun gear 9b, which is non-rotatably connected to the first planetary gear carrier 8a, and the second ring gear 10b, which is arranged stationary in the housing 15. The second planet carrier 8b is operatively connected to the differential stage 6 and forwards the torque of the electric drive machine to the differential stage 6, which in turn distributes it to the two output shafts 13a, 13b.

2 until 5 show modifications of the drive device 1 according to the invention according to the first embodiment. In the following, only the differences to the in 1 shown drive device 1 received according to the first embodiment.

In the 2 The first modification shown represents a drive device 1 in a coaxial design. The differential stage 6 is explicitly designed as an additional double planetary gear stage. The torque is transmitted from the second planetary gear carrier 8b to a double planetary gear which is non-rotatably connected thereto, which in turn transfers this to double planetary gears meshing with sun gears formed on the output shafts 13a, 13b and thus drives the output shafts 13a, 13b.

3 shows a second modification of the drive device 1 in paraxial design. An additional reduction gear 14 is interposed between the second planet carrier 8b and the differential stage 6 in the torque flow from the electric drive machine to the output shafts 13a, 13b. According to the second modification, this reduction gear 14 is designed as a spur gear and increases the spread of the gear device 3.

At the in 4 shown, third modification of the first embodiment, 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. In contrast to the in 3 Drive device 1 shown in an axially parallel design here the drive shaft 2 is arranged coaxially to the two output shafts 13a, 13b.

5 again shows a fourth modification of the first embodiment, in which the reduction gear 14, as in FIG 4 shown, third modification, is arranged on the input side between the electric drive machine and the transmission device 3 . In addition, in the fourth modification, the differential stage 6 is designed as a double planetary gear stage, in which the torque is transmitted from the second planetary gear carrier 8b to a double planetary gear non-rotatably connected thereto and finally via the double planetary gears to the output shafts 13a, 13b. The fourth modification can therefore be understood as a combination of the first and third modification.

6 shows a second embodiment of the drive device 1 according to the invention in an axially parallel design. In the following, only the differences to the in 1 drive device 1 shown received.

In the drive device 1 according to the second embodiment, the first clutch 12a of the double clutch device 11 arranged on the input side is connected in a rotationally fixed manner to the first planet carrier 8a and the second clutch 12b is connected in a rotationally fixed manner to the first ring gear 10a, so that by selectively opening or closing the first clutch 12a and the second clutch 12b, the two gear ratios can be realized.

The first ring gear 10a is also non-rotatably connected to the second sun gear 9b. Furthermore, the first sun gear 9a is non-rotatably connected to the second planetary gear carrier 8b and is operatively connected to the differential stage 6 via the reduction gear 14 interposed between the second planetary gear stage 5 and the differential stage 6 . The second ring gear 10b is accommodated in the housing 15 in a stationary manner in the second embodiment.

7 and 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 6 shown drive device 1 received according to the first embodiment.

In the 7 The first modification of the second embodiment shown represents a drive device 1 in a coaxial design Reduction gear 14 interposed on the input side between the electric drive machine and the transmission device 3, in particular the drive shaft 2.

8th 12 shows a second modification of the driving device 1 according to the second embodiment in a coaxial construction. The differential stage 6 is designed explicitly as an additional double planetary gear stage. The torque is transmitted from the second planetary gear carrier 8b or the first sun gear 9a connected thereto in a rotationally fixed manner to a double planetary gear connected in a rotationally fixed manner to it, which in turn transmits the torque to double planetary gears in meshing engagement with the sun gears formed on the output shafts 13a, 13b and thus the Output shafts 13a, 13b drives.

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

In the drive device 1 according to the third embodiment, the first clutch 12a of the double clutch device 11 arranged on the input side is connected in a torque-proof manner to the first planet carrier 8a and the second clutch 12b is connected in a torque-proof manner to the first ring gear 10a, so that by selectively opening or closing the first clutch 12a and the second clutch 12b, the two gear ratios can be realized.

The first ring gear 10a is also non-rotatably connected to the second sun gear 9b. Furthermore, the first sun wheel 9a is connected in a rotationally fixed manner to the second planetary wheel carrier 8b and is fixed in place with it in the housing 15 . The second ring gear 10b is operatively connected to the differential stage 6 via the reduction gear 14 interposed between the second planetary gear stage 5 and the differential stage 6, so that the torque on the output side is transmitted via the second ring gear 10b and the reduction gear 14 to the differential stage 6 and from there to the output shafts 13a, 13b is distributed.

10 12 shows a first modification of the driving device 1 according to the third embodiment in a coaxial construction. In this case, the reduction gear 14 is interposed on the input side between the electric drive machine and the gear device 3 and is designed as a spur gear stage. In contrast to the in 9 Drive device 1 shown in an axially parallel design here the drive shaft 2 is arranged coaxially to the two output shafts 13a, 13b.

In 11 a fourth embodiment of the drive device 1 not according to the invention is shown in a coaxial design. In the following, only the differences to the in 1 drive device 1 shown received.

In the drive device 1 according to the fourth embodiment, the first clutch 12a of the double clutch device 11 arranged on the input side is connected in a rotationally fixed manner to the first planet carrier 8a and the second clutch 12b is connected in a rotationally fixed manner to the first ring gear 10a, so that by selectively opening or closing the first clutch 12a and the second clutch 12b, the two gear ratios can be realized.

The first planetary gear carrier 8a is non-rotatably connected to the second sun gear 9b. Furthermore, the first sun wheel 9a is connected in a rotationally fixed manner to the second planetary wheel carrier 8b and is fixed in place with it in the housing 15 . The second ring gear 10b is operatively connected to the differential stage 6 via the reduction gear 14 interposed between the second planetary gear stage 5 and the differential stage 6, so that the torque on the output side is transmitted via the second ring gear 10b and the reduction gear 14 to the differential stage 6 and from there to the output shafts 13a, 13b is distributed.

12 12 shows a first modification of the drive device 1 according to the fourth embodiment in an axially parallel design. In this case, in the torque flow from the electric drive machine to the output shafts 13a, 13b, the reduction gear 14 designed as a spur gear stage is interposed between the second ring gear 10b and the differential stage 6.

In 13 1 shows a second modification of the driving device 1 according to the fourth embodiment in a coaxial construction. In this case, the reduction gear 14 is interposed on the input side between the electric drive machine and the gear device 3 . Furthermore, the output shafts 13a, 13b are arranged coaxially to the input shaft 2.

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 (5)

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, characterized in that • the first planetary gear carrier (8a) is non-rotatably connected to the second sun gear (9b), wherein • the first sun gear (9a) is fixed in a housing (15), wherein • the second ring gear (10b) fixed in the housing (15), whereby • the first planet carrier (8a) can be connected to the drive shaft (2) in a torque-proof manner via the first clutch (12a) and • the first ring gear (10a) can be connected in a torque-proof manner via the second clutch (12b). can be connected to the drive shaft (2). Drive device (1) according to the preamble of claim 1 , characterized in that • the second planetary gear carrier (8b) is non-rotatably connected to the first sun gear (9a), wherein • the second ring gear (10b) is fixed in a housing (15), wherein • the first planetary gear carrier (8a) via the first clutch (12a) can be connected to the drive shaft (2) in a torque-proof manner, whereby • the first ring gear (10a) can be connected in a torque-proof manner to the drive shaft (2) via the second clutch (12b) and • the first ring gear (10a) can be connected to the drive shaft (2) in a torque-proof manner the second sun gear (9b) is connected. Drive device (1) according to the preamble of claim 1 , characterized in that • the second planetary gear carrier (8b) is non-rotatably connected to the first sun gear (9a), wherein • the first sun gear (9a) is fixed in a housing (15), wherein • the first planetary gear carrier (8a) via the first clutch (12a) can be connected to the drive shaft (2) in a torque-proof manner, whereby • the first ring gear (10a) can be connected in a torque-proof manner to the drive shaft (2) via the second clutch (12b) and • the first ring gear (10a) can be connected to the drive shaft (2) in a torque-proof manner the second sun gear (9b) is connected. 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 3 , characterized in that the drive machine is arranged offset parallel to the axis to the differential stage (6).

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