DE102020211068A1 - Electric drive of a vehicle, drive train and method - Google Patents

Abstract

The invention relates to an electric drive of a vehicle, comprising an electric machine (2) whose rotor (2.1) is connected to an input shaft (11) of a first planetary gear set (5), an output shaft (12) arranged coaxially with the input shaft (11), and two Shifting elements (3, 4), the first planetary gear set (5) being designed as a multi-stage planetary gear whose planetary gears (5.3, 5.4) mounted on a planetary gear carrier (5.6) have two different effective diameters, with a first sun gear (5.1) of the planetary gear set (5) meshes with the larger effective diameter (5.3), with a second sun gear (5.2) of the planetary gear set (5) meshing with the smaller effective diameter (5.4), with the first sun gear (5.1) of the planetary gear set (5) with the input shaft (11) is non-rotatably connected, with the second sun gear (5.2) of the planetary gear set (5) being non-rotatably connected with the output shaft (12), with a first switching element The element (3) is designed to fix the planetary gear carrier (5.5) of the planetary gearset (5) to a non-rotatable component (0), a second shifting element (4) being designed to non-rotatably connect two elements of the first planetary gearset (5) to one another , wherein the first planetary gear set (5) is arranged radially inside the rotor (2.1). The invention also relates to a drive train and a method.

Description

The invention relates to an electric drive, a drive train and a method for shifting the same.

the DE 10 2015 218 252 A1 describes a two-speed transmission for a vehicle, which two-speed transmission is part of a drive train, consisting of a stepped planetary gear set without a ring gear, the motor shaft being permanently connected to the first sun and the output shaft to the second sun. A first coupling can connect the web to the housing in a rotationally fixed manner. This clutch can be designed as a frictional or form-fitting braking device. The input shaft can be connected to the carrier via a second clutch, so that the planetary gear set rotates as a block. Another planetary set and a differential are connected downstream of the transmission. The motor shaft is driven by an electric machine.

The object of the present invention is to provide an alternative electric drive for a vehicle and an alternative drive train. In particular, an electric drive or a drive train is to be provided that is axially short. In addition, a method for switching the electric drive is to be provided. The object is solved by the features of the independent claims. Preferred embodiments emerge from the dependent claims.

According to the first aspect of the invention, an electric drive of a vehicle is provided. The electric drive comprises an electric machine, the rotor of which is connected to an input shaft of a first planetary gear set, an output shaft arranged coaxially to the input shaft, and two shifting elements. The first planetary gear set is designed as a stepped planetary gear, whose planetary gears mounted on a planetary gear carrier have two different effective diameters. A first sun gear of the planetary gear set meshes with the larger effective diameter. A second sun gear of the planetary gear set meshes with the smaller effective diameter. The first sun gear of the planetary gear set is non-rotatably connected to the input shaft. The second sun gear of the planetary gear set is non-rotatably connected to the output shaft. A first switching element is designed to fix the planetary gear carrier of the planetary gear set to a non-rotatable component. A second shifting element is designed to connect two elements of the first planetary gear set to one another in a torque-proof manner. The first planetary gear set is arranged radially inward of the rotor.

A respective non-rotatable connection of the rotatable components of the electric drive is preferably implemented according to the invention via one or more intermediate shafts, which can also be present as short intermediate pieces when the components are spatially close together. In concrete terms, the components that are permanently connected to one another in a rotationally fixed manner can each be present either as individual components that are connected to one another in a rotationally fixed manner or also in one piece. In the second-mentioned case, the respective components and the shaft that may be present are then formed by a common component, this being realized in particular when the respective components in the transmission are spatially close to one another.

In the case of components of the electric drive which are connected to one another in a rotationally fixed manner only by actuation of a respective switching element, a connection is also preferably implemented via one or more intermediate shafts. Fixing takes place in particular by non-rotatable connection with a non-rotatable component of the electric drive, which is preferably a permanently stationary component, preferably a housing of a transmission, a part of such a housing or a non-rotatable component connected thereto. If a planetary gear set is blocked, the translation is always one, regardless of the number of teeth. In other words, the planetary gear set rotates as a block. The “connection” of the rotor of the electric machine to the input shaft is to be understood within the meaning of the invention as such a connection that there is a constant speed dependency between the rotor of the electric machine and the input shaft.

The individual switching elements can each be present both as a non-positive and as a form-fitting switching element. Force-locking or friction-locking shifting elements are, for example, multi-plate shifting elements, in particular in the form of multi-plate clutches. Positive shifting elements are, for example, claw shifting elements and cone shifting elements in the form of claw or cone clutches.

The electric drive according to the invention does not require ring gears and is also arranged radially inside the rotor, which means that this electric drive is particularly short axially. The output shaft can in particular be arranged inside an input shaft designed as a hollow shape. The electric drive enables an output that is axis-parallel to the input shafts or also coaxial. The electric drive can therefore be used in particular for a front-transverse drive train of a vehicle.

The electric drive enables two gears to be shifted. Thus, in particular, a first gear can be generated by engaging the first shifting element and a second gear can be generated by engaging the second shifting element. In first gear, therefore, the first shifting element is closed while, on the other hand, the second shifting element is open. In second gear, it's the other way around.

In first gear there is preferably a translation of i>1, particularly preferably the translation in first gear is i=2. In second gear, there is preferably a translation of i=1. An increment phi of essentially 2.0 is thus preferably achieved between these two gears. The increment phi is preferably in the range 1.7<phi<2.3, preferably in the range 1.8<phi<2.2, preferably in the range 1.9<phi<2.1. In addition, the increment can be exactly 2.0.

The efficiencies of this preferred connection are very high. In 1st gear, an efficiency of 97.5% can be achieved. In second gear, an efficiency of 100% can be achieved.

If the second shifting element is designed, for example, as a multi-disc clutch, power shifting from first to second gear under traction is possible. Power shifting from second to first gear is also possible. The first shifting element is preferably designed as a claw shifting element in order to enable a transmission that is optimal in terms of cost and efficiency. The stepped planetary gear set is particularly advantageous in this transmission because both ring gears of the planetary stage can be completely omitted.

The second switching element can cause the blocking by non-rotatably connecting the first sun gear and the second sun gear, or by non-rotatably connecting the first sun gear and the planet carrier.

By simultaneously closing the first and second shifting element, the planetary gearset and thus the output are blocked against the housing. This represents the function of a parking lock, which can thus be saved as a separate component/assembly. If a planetary gear set is blocked, the translation is always one, regardless of the number of teeth. In other words, the planetary gear set rotates as a block.

According to a second aspect of the invention, there is provided a powertrain for a vehicle including an electric drive as described above and a differential assembly connected to the output shaft of the first planetary gear set.

• - das Sonnenrad des zweiten Planetenradsatzes mit dem zweiten Sonnenrad des ersten Planetenradsatzes verbunden ist,
• - der Planetenradträger mit einem Eingangselement des Kegelraddifferential verbunden ist,
• - das Hohlrad an dem drehfesten Bauteil festgesetzt ist.

Preferred is a drive train, wherein the differential device comprises a bevel gear differential and a transmission gear in the form of a second planetary gear set, wherein

• - the sun gear of the second planetary gear set is connected to the second sun gear of the first planetary gear set,
• - the planet carrier is connected to an input element of the bevel gear differential,
• - the ring gear is fixed to the non-rotatable component.

• - das erste Stirnrad mit dem zweiten Sonnenrad des Stufenplanetenradsatzes (5) verbunden ist und mit dem zweiten Stirnrad in Zahneingriff steht,
• - das zweite Stirnrad mit einem Eingangselement des Kegelraddifferential verbunden ist.

Alternatively, a drive train is preferred, wherein the differential device comprises a bevel gear differential and a transmission gear in the form of a single-stage spur gear with a first spur gear and a second spur gear, wherein

• - the first spur gear is connected to the second sun gear of the stepped planetary gear set (5) and meshes with the second spur gear,
• - The second spur gear is connected to an input element of the bevel gear differential.

• - das erste Stirnrad mit dem zweiten Sonnenrad des Stufenplanetenradsatzes drehfest verbunden ist und mit dem dritten Stirnrad in Zahneingriff steht,
• - das dritte Stirnrad drehfest mit dem zweiten Stirnrad verbunden ist, und
• - das zweite Stirnrad mit einem Eingangselement des Kegelraddifferentials verbunden ist.

Alternatively, a drive train is preferred, wherein the differential device comprises a bevel gear differential and a transmission gear in the form of a two-stage spur gear with a first spur gear, a second spur gear and a third spur gear, wherein

• - the first spur gear is non-rotatably connected to the second sun gear of the stepped planetary gear set and meshes with the third spur gear,
• - The third spur gear is non-rotatably connected to the second spur gear, and
• - The second spur gear is connected to an input element of the bevel gear differential.

• - das Sonnenrad des zweiten Planetenradsatzes mit dem zweiten Sonnenrad des ersten Planetenradsatzes verbunden ist,
• - der Planetenradträger mit einem ersten Abtriebswelle verbunden ist,
• - das Hohlrad des zweiten Planetenradsatzes mit dem Sonnenrad des dritten Planetenradsatzes verbunden ist,
• - der Planetenradträger an dem drehfesten Bauteil festgesetzt ist,
• - das Hohlrad mit einem zweiten Abtriebswelle verbunden ist.

Alternatively, a drive train is preferred, wherein the differential device comprises a second planetary gear set and a third planetary gear set, wherein

• - the sun gear of the second planetary gear set is connected to the second sun gear of the first planetary gear set,
• - the planet carrier is connected to a first output shaft,
• - the ring gear of the second planetary gear set is connected to the sun gear of the third planetary gear set,
• - the planetary gear carrier is fixed to the non-rotatable component,
• - the ring gear is connected to a second output shaft.

According to a third aspect of the invention, a method for shifting the electric drive and/or the drive train described above is provided, the first shifting element being closed and the second shifting element being opened in a first gear, and the first shifting element being opened and the second shifting element being opened in a second gear Switching element is closed.

• 1-3 jeweils eine schematische Ansicht eines Antriebsstrangs eines Fahrzeugs bei welchem der erfindungsgemäße Elektroantrieb zur Anwendung kommt;
• 4 eine schematische Ansicht eines Elektroantriebs in einer bevorzugten Ausführungsform;
• 5 eine Schaltmatrix des Getriebes des Elektroantriebs aus 4;
• 6 eine schematische Ansicht eines Antriebsstrangs in einer bevorzugten Ausführungsform;
• 7 eine schematische Ansicht eines Antriebsstrangs in einer bevorzugten Ausführungsform;
• 8 eine schematische Ansicht eines Antriebsstrangs in einer bevorzugten Ausführungsform; und
• 9 eine schematische Ansicht eines Antriebsstrangs in einer bevorzugten Ausführungsform.

Advantageous embodiments of the invention, which are explained below, are shown in the drawings. It shows:

• 1-3 in each case a schematic view of a drive train of a vehicle in which the electric drive according to the invention is used;
• 4 a schematic view of an electric drive in a preferred embodiment;
• 5 a switching matrix of the transmission of the electric drive 4 ;
• 6 a schematic view of a drive train in a preferred embodiment;
• 7 a schematic view of a drive train in a preferred embodiment;
• 8th a schematic view of a drive train in a preferred embodiment; and
• 9 a schematic view of a drive train in a preferred embodiment.

1 until 3 each show a schematic view of a drive train 100 of a vehicle 1000. The vehicle is a passenger car.

The powertrain 100 according to FIG 1 shows an electric drive that drives the front axle B of the vehicle 1000 . The drive train includes a transmission 1, which divides the drive torque of the electric machine 2 into two output shafts 9.11 and 9.12. The drive train 100 also includes a differential device, which has a bevel gear differential 9 and a transmission 14 in the form of a spur gear. Transmission 1 and electric machine 2 are arranged coaxially to an axis A. Axis A and axis B are arranged paraxially, so that there is an paraxial output. The forward direction of travel is represented by the arrow 99 . As also in 1 can be seen, the transmission 1 and the electric machine 2 are aligned transversely to the direction of travel 99 of the vehicle 1000 .

The powertrain 100 according to FIG 2 shows an electric drive that drives the front axle B of the vehicle 1000 . The drive train includes a transmission 1, which divides the drive torque of the electric machine 2 into two output shafts 9.11 and 9.12. The drive train 100 also includes a differential device, which includes a planetary gear 8 and a bevel gear differential 9 . Transmission 1 and electric machine 2 are arranged coaxially to an axis A, which coincides with the drive axis B, so that there is a coaxial output. The forward direction of travel is represented by the arrow 99 . As also in 2 can be seen, the transmission 1 and the electric machine 2 are aligned transversely to the direction of travel 99 of the vehicle 1000 .

The powertrain 100 according to FIG 3 shows an electric drive that drives the front axle B of the vehicle 1000 . The drive train includes a transmission 1, which divides the drive torque of the electric machine 2 into two output shafts 13.11 and 8.12. The drive train 100 also includes a differential device which includes two planetary gears 8 , 13 . Transmission 1 and electric machine 2 are arranged coaxially to an axis A, which coincides with the drive axis B, so that there is a coaxial output. The forward direction of travel is represented by the arrow 99 . As also in 3 can be seen, the transmission 1 and the electric machine 2 are aligned transversely to the direction of travel 99 of the vehicle 1000 .

4 shows an electric drive in a first embodiment of the invention for a drive train 100 of a vehicle 1000. The electric drive includes a transmission 1 with a planetary gear set 5, and an electric machine 2. The transmission 1 includes an input shaft 11, which is connected to the rotor 2.1 of the electric machine 2 is, an output shaft 12 arranged coaxially to the input shaft 11, two switching elements 3, 4 for connecting the transmission 1 to the electric machine 2 of the electric drive.

The first planetary gear set 5 is designed as a stepped planetary gear whose planetary gears mounted on a planetary gear carrier 5.5 have two different large effective diameters. A first sun gear 5.1 of the planetary gear set 5 meshes with the larger effective diameter 5.3. A second sun gear 5.2 of the planetary gear set 5 meshes with the smaller effective diameter 5.4. The first sun gear 5.1 of the planetary gear set 5 is connected to the input shaft 11 in a rotationally fixed manner. The second sun gear 5.2 of the Planetary gear set 5 is connected to the output shaft 12 in a torque-proof manner.

A first switching element 3 is designed to fix the planetary gear carrier 5.5 of the planetary gear set 5 to a non-rotatable component 0. A second switching element 4 is designed to non-rotatably connect two elements of the first planetary gear set with one another, ie to block the planetary gear set, with the blocking being effected according to this embodiment by connecting the two sun gears 5.1 and 5.2. In order to construct the electric drive in an axially particularly compact manner, the first planetary gear set 5 is arranged radially inside the rotor 2.1.

By selectively actuating the two shifting elements 3, 4, a total of two forward gears can be provided. If the first switching element 3 is closed, a first gear is engaged, which produces a transmission ratio of i>1, i=2 in the present case. If the second switching element 4 is closed while the first switching element 3 is open, the second gear is engaged with a gear ratio of i=1. Thus, an increment phi of 2.0 is achieved between these two gears, which is within the preferred range of 1.7<phi<2.3.

The first switching element is designed as a claw clutch. The second switching element is designed as a multi-plate clutch. As a result, a power shift from first gear to second gear or vice versa is possible.

5 shows a shift matrix of the transmission 4 . Two forward gears E1 and E2 are indicated in the rows of the matrix. An “X” in the columns of the switching matrix shows which of the switching elements 3 and 4 are closed in which gear. Closing the first shifting element 3 produces a first gear E1 and closing the second shifting element 4 produces a second gear E2. The second shifting element 4 is open during the first gear E1. The first shifting element 3 is open during the second gear E2.

In first gear E1, the translation is i=2. In second gear E2, the translation is i=1. E2 is therefore a so-called direct drive. The increment between these two gears is phi=2.0. For the first gear E1, the efficiency is eta = 98.5%. For the second gear E2, the efficiency is 100.0%.

The following 6 until 10 show a drive train comprising a transmission 1, an electric machine 2 and a differential device which is connected to the output shaft 12 of the first planetary gear set 5.

6 accordingly shows a preferred first drive train comprising the embodiment according to FIG 4 and a differential device, the differential device being formed by a second planetary gear set 8 and a third planetary gear set 13 . Drive axis A and output axis B coincide. Accordingly, there is a coaxial output.

The planetary gear set 8 includes a sun gear 8.1, a planet carrier 8.2 and a ring gear 8.3. The planetary gear set 13 includes a sun gear 13.1, a planet carrier 13.2 and a ring gear 13.3. Planetary gearset 8 and 13 are arranged radially one above the other, with the planetary gearset 8 being arranged radially inward. Ring gear 8.3 is non-rotatably connected to sun gear 13.1. Ring gear 8.3 and sun gear 13.1 are designed in one piece according to this embodiment. The planet carrier 13.2 is fixed. The sun gear 8.1 is connected to the output shaft 12. The ring gear 13.1 is connected to a first output shaft 13.11. The planet carrier 8.2 is connected to a second output shaft 8.12. The shafts 11, 12 are each designed as a hollow shaft. The second output shaft 8.12 is guided through the respective hollow shaft 11, 12 and is connected at one axial end to the planet carrier 8.2.

In other words, a so-called integrated differential is used in this embodiment. The function of generating the overall gear ratio and the differential function are simultaneously represented via this differential gear set.

As a difference to the transmission according to the embodiment gem. 4 the shifting elements 3 and 4 are preferably designed as a double shifting element, to which an actuating element is assigned, with the actuating element being able to actuate the first shifting element on the one hand and the third shifting element on the other hand from a neutral position. The double switching element thus has three switching positions. However, the switching elements can also be designed as individual switching elements. Otherwise, the electric drive or the transmission 1 corresponds to the embodiment according to FIG. 4 , so that reference is made to these statements.

7 shows a preferred second drive train comprising the embodiment according to FIG 4 and a differential device, the differential device comprising a bevel gear differential 9 and a transmission gear, the transmission gear being formed by a planetary gear set 8 . Drive axis A and output axis B coincide. Accordingly, there is a coaxial output.

The bevel gear differential 9 has two wheel-side driven elements, which are designed as a first driven wheel 9.1 and a second driven wheel 9.2. The driven gears 9.1, 9.2 each mesh with a compensating element 9.3 designed as a spur gear. The compensating elements 9.3 are rotatably mounted about their own axis in a differential cage 9.4. The first output gear 9.1 is connected in a torque-proof manner to a first output shaft 9.11 and the second output gear 9.2 to a second output shaft 9.12. The differential gears 9.3, which act between the cage 9.4 and the two driven gears 9.1, 9.2, can transmit a rotational movement from the cage 9.4 to the two driven gears 9.1, 9.2 and provide a compensating rotational movement between the two driven gears 9.1, 9.2.

The negative planetary gear set 8 comprises a ring gear 8.3 fixed to the transmission housing 0, a planetary gear carrier 8.2 and a sun gear 8.1. The planet carrier r8.2 is non-rotatably connected to the cage 9.4. The sun gear 8.1 is connected to the output shaft 12 in a torque-proof manner.

The planetary gear sets 5 and 8 and the bevel gear differential 9 are arranged axially next to one another, with the planetary gear set 8 being arranged axially between the planetary gear set 5 and the bevel gear differential 9 .

The shafts 11, 12 are also each designed as a hollow shaft. The second output shaft 9.12 is guided through the respective hollow shaft 11, 12. Otherwise this drive train corresponds to the embodiment according to FIG. 6 or the electric drive or gear acc. 4 , so that reference is made to these statements.

8th shows a preferred third powertrain. This embodiment differs from the embodiment according to FIG 6 characterized in that the differential device comprises a bevel gear differential 9 and a step-up gear, with the step-up gear being formed by a single-stage spur gear stage 14 . The output axis B is arranged axis-parallel to the input axis A. There is therefore an axis-parallel output.

The single-stage transmission of the spur gear stage causes the overall transmission from axis A of the input to axis B of the output. The spur gear includes two spur gears 14.1 and 14.2. The spur gear 14.1 is non-rotatably connected to the output shaft 12 and meshes with the spur gear 14.2. The spur gear 14.2 is non-rotatably connected to the cage 9.4 and can drive it. In addition, as a variant, the first and second shifting element 3, 4 are designed as claw shifting elements arranged separately from one another. Both switching elements 3, 4 can be inserted at the same time. As a result, the electric machine 2 and thus also the output (output shaft 12) are braked or blocked by the locked wheel set 5 against the housing 0. A parking lock function can be displayed in this way. However, the switching elements could also be designed as lamellar switching elements.

According to this embodiment, push and pull shifts can be shifted under load from gear E1 to gear E2 and vice versa. The drive elements are arranged axially next to the electric machine 2 . This enables an electric machine 2 with a small outer diameter and thus a small center distance between the drive axle A and the driven axle B. For the rest, reference is made to the statements 6 referred.

9 shows a preferred fourth powertrain. This embodiment differs from the embodiment according to FIG 8th characterized in that the transmission gear is formed by a two-stage spur gear 14. The output axis B is arranged axis-parallel to the input axis A. There is therefore an axis-parallel output. The two-stage translation of the spur gear causes the overall translation from axis A of the input to axis B of the output. The spur gear includes four spur gears 14.1, 14.2, 14.3 and 14.4. The spur gear 14.1 is connected to the output shaft 12 in a torque-proof manner. The spur gear 14.2 is non-rotatably connected to the cage 9.4 of the differential 9 and can drive it. Between the spur gears 14.1 and 14.2, two spur gears 14.3 and 14.4 which are non-rotatably connected to one another are arranged as a further stage. The spur gear 14.3 meshes with the spur gear 14.1. Spur gear 14.4 meshes with spur gear 14.2. Otherwise, reference is made to the remarks 8th referred.

Reference List

1

transmission

2

electric machine

2.1

rotor

2.2

stator

3

switching element

4

switching element

5

planetary gear set

5.1

sun gear

5.2

sun gear

5.3

planet wheel

5.4

planet wheel

5.5

ring gear

5.6

planet carrier

6

switching element

7

switching element

8th

planetary gear set

9

bevel gear differential

9.1

output gear

9.2

output gear

9.3

compensating element(s)

9.4

Differential cage, cage

9.11

first output shaft

9.12

second output shaft

10

input shaft

11

input shaft

12

output shaft, output

13

planetary gear set

13.1

sun gear

13.2

planet carrier

13.3

ring gear

14

Spur gear stage, one-stage, two-stage

14.1

spur gear

14.2

spur gear

14.3

spur gear

14.4

spur gear

99

driving direction

100

powertrain

1000

vehicle, car

A

drive axle

B

output axis

E1

first course

E2

second gear

i

translation

phi

increment

etc

efficiency

QUOTES INCLUDED IN DESCRIPTION

This list of the documents cited by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent Literature Cited

• DE 102015218252 A1 [0002]

Claims (11)

Electric drive of a vehicle, comprising - an electric machine (2), the rotor (2.1) of which is connected to an input shaft (11) of a first planetary gear set (5), an output shaft (12) arranged coaxially with the input shaft (11), and two shifting elements (3, 4), - wherein the first planetary gear set (5), ◯ is designed as a multi-stage planetary gear, whose planetary gears (5.3, 5.4) mounted on a planetary gear carrier (5.6) have two different large effective diameters, ◯ with a first sun gear (5.1) of the planetary gear set (5) with the larger effective diameter (5.3) being in tooth mesh, ◯ with a second sun gear (5.2) of the planetary gear set (5) with the smaller effective diameter (5.4) being in tooth mesh, - the first sun gear (5.1) of the planetary gear set (5) being non-rotatably connected to the input shaft (11), - the second sun gear (5.2) of the planetary gear set (5) being non-rotatably connected to the output shaft (12), - wherein a first switching element (3) is designed to fix the planet carrier (5.5) of the planetary gear set (5) on a non-rotatable component (0), - wherein a second switching element (4) is designed to connect two elements of the first planetary gear set (5) to one another in a rotationally fixed manner, - Wherein the first planetary gear set (5) is arranged radially inside the rotor (2.1). electric drive after claim 1 , wherein the second switching element (4) causes the blocking by - non-rotatably connecting the first sun gear (5.1) and the second sun gear (5.2), or by - non-rotatably connecting the first sun gear (5.1) and the planet carrier (5.5). electric drive after claim 1 or 2 , wherein the output shaft (12) is arranged inside the input shaft (11), which is designed as a hollow shape. Electric drive according to one of the preceding claims, wherein at least one of the two shifting elements (3, 4) is designed as a positive shifting element, in particular as a claw clutch. Electric drive according to one of the preceding claims, wherein at least one of the two shifting elements (3, 4) is designed as a frictional shifting element, in particular as a multi-plate clutch or a cone clutch. Drive train (100) for a vehicle with an electric drive according to one of the preceding claims and a differential device which is connected to the output shaft (12) of the first planetary gear set (5). drive train after claim 6 , wherein the differential device comprises a bevel gear differential (9) and a transmission gear in the form of a second planetary gear set (8), wherein - the sun gear (8.1) of the second planetary gear set (8) is connected to the second sun gear (5.2) of the first planetary gear set (5). - the planetary gear carrier (8.2) is connected to an input element of the bevel gear differential (9), - the ring gear (8.3) is fixed to the non-rotating component (0). drive train after claim 6 , wherein the differential device comprises a bevel gear differential (9) and a transmission gear in the form of a single-stage spur gear (14) with a first spur gear (14.1) and a second spur gear (14.2), wherein - the first spur gear (14.1) with the second sun gear (5.2 ) of the stepped planetary gear set (5) and meshing with the second spur gear (14.2), - the second spur gear (14.2) is connected to an input element (9.1) of the bevel gear differential (9). drive train after claim 6 , wherein the differential device comprises a bevel gear differential (9) and a transmission gear in the form of a two-stage spur gear stage (14) with a first spur gear (14.1), a second spur gear (14.2) and a third spur gear (14.3), wherein - the first spur gear (14.1 ) is non-rotatably connected to the second sun gear (5.2) of the stepped planetary gear set (5) and meshes with the third spur gear (14.2), - the third spur gear (14.3) is non-rotatably connected to the second spur gear (14.2), and - the second Spur gear (14.2) is connected to an input element (9.3) of the bevel gear differential (9). drive train after claim 6 , wherein the differential device comprises a second planetary gear set (8) and a third planetary gear set (13), wherein - the sun gear (8.1) of the second planetary gear set (8) is connected to the second sun gear (5.2) of the first planetary gear set (5), - the planetary gear carrier (8.2) is connected to a first output shaft (8.4), - the ring gear (8.3) of the second planetary gear set (8) is connected to the sun gear (13.1) of the third planetary gear set (13), - the planetary gear carrier (13.2) to the non-rotatable component (0) is fixed, - the ring gear (13.3) is connected to a second output shaft (13.4). Method for shifting the electric drive and/or the drive train according to one of the preceding claims, wherein in a first gear (E1) the first shifting element (3) is closed and the second shifting element (4) is opened and wherein in a second gear (E2) the first switching element (3) is opened and the second switching element (4) is closed.

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