DE102022001308B4 - Electric drive system and method for its operation - Google Patents

Abstract

Electric drive system (1) with
a first electrical machine (10) with a first rotor (110),
a second electric machine (20) with a second rotor (210) and a coupling gear (30),
wherein the coupling gear (30) comprises a four-shaft planetary gear set with a first element (31), a second element (32), a third element (33), a fourth element (34) and a fifth element (35), wherein the second element (32) is connected in a rotationally fixed manner to the fourth element (34),
wherein the coupling gear (30) has a first output shaft (41) and a second output shaft (42) which are designed to derive torques from the coupling gear (30),
wherein the first output shaft (41) is rotationally fixedly connected to the fifth element (35),
marked by
a first switching element (S1) which is designed to couple the second output shaft (42) to the second element (32) in a rotationally fixed manner,
a second switching element (S2) which is designed to couple the second output shaft (42) in a rotationally fixed manner to the third element (33),
a third switching element (S3) which is designed to couple the first rotor (110) to the third element (33) in such a way that torques, originating from the first electric machine (10), can be introduced into the coupling gear (30) at the third element (33),
a fourth switching element (S4) which is designed to couple the first rotor (110) to the second element (32) in such a way that torques, originating from the first electric machine (10), can be introduced into the coupling gear (30) at the second element (32),
a fifth switching element (S5) which is designed to couple the second rotor (210) to the first element (31) in such a way that torques, originating from the second electric machine (20), can be introduced at the first element (31) into the coupling gear (30).

Description

The invention relates to an electric drive system according to the type defined in the preamble of claim 1. Furthermore, the invention relates to various operating methods for such an electric drive system.

An electric drive system with two electric machines, whose power or torque is transmitted via a coupling gear, is basically known from the state of the art, for example from the US 9 494 218 B2 , with particular reference to the 61 ff. and the associated text. The two electrical machines drive two output shafts via the coupling gear, which includes a four-shaft planetary gear set. The rotors of the two electrical machines are connected in a rotationally fixed manner to different elements of the coupling gear, as are the two output shafts.

A rotationally fixed connection in the sense of the present description is to be understood as meaning that two rotatably mounted elements are connected to one another in a rotationally fixed manner when they are arranged coaxially to one another and are connected to one another in such a way that they rotate at the same angular velocity.

The structure according to the mentioned US patent US 9 494 218 B2 This enables a variation of the output power by controlling the two electric machines via their power electronics.

The object of the present invention is to create a very compact electric drive system with two electric machines, which can be operated easily and efficiently both in a torque vectoring mode and in an efficiency mode.

According to the invention, this object is achieved by an electric drive system with the features in claim 1, and here in particular in the characterizing part of claim 1. Advantageous embodiments and further developments emerge from the dependent subclaims. The method claims 12 and 13 define the efficiency operation and the torque vectoring operation of such an electric drive system and together with these also solve the above-mentioned object.

The term torque vectoring in the sense of the present invention is intended to define an operating mode in which both electric machines deliver significant torque for propulsion, whereby the electric machines do not have to be equally strong and do not have to have the same rated power. By selecting the torques of the two electric machines, a torque distribution can then be implemented between the two output shafts and thus, when used in a vehicle, between the two wheels driven directly or indirectly by the output shafts. Such an operating mode is particularly suitable for dynamic driving in curves.

Efficient operation in the sense of the description here means propulsion in which one of the two electric machines is operated alone and the coupling gear acts as a classic differential with an even distribution of the torque in a ratio of 1:1 between both output shafts or wheels. The torque is therefore distributed equally between the two driven wheels, even when cornering, although different speeds will still occur at the wheels. The second electric machine is decoupled in this efficient operation, so it does not have to be dragged along.

The electric drive system according to the invention, by means of which a compact and highly flexible electric drive system is created which allows operation in both a torque vectoring mode and an efficiency mode, comprises at least five different switching elements, of which a first switching element is designed to form the second output shaft in a rotationally fixed manner, in the sense defined above, with a second element of the coupling gear designed as a four-shaft planetary gear set. A second switching element serves to rotationally fixedly couple the second output shaft to the third element, a third switching element can couple the first rotor to the third element in such a way that torques can be introduced into the coupling gear. A fourth switching element is designed to couple the first rotor to the second element in such a way that torques can be introduced into the coupling gear via this path. Finally, a fifth switching element serves to couple the second rotor to the first element in order to introduce torques from the second electric machine into the coupling gear via the first element.

The elements of the planetary gear set within the meaning of the invention comprise the sun gears, planet carriers and ring gears, i.e. those elements which are formed in a rotationally fixed manner with the respective shafts of the planetary gear set or which form them themselves.

The four-shaft planetary gear set is understood to mean a planetary gear set that has at least 4 such elements, none of which is connected in a rotationally fixed manner to any of the other 3 elements, so that the 4 such elements mentioned can rotate relative to one another (although dependent on one another). The four-shaft planetary gear set is advantageously a planetary gear set with exactly 4 such shafts and is therefore a precisely four-shaft planetary gear set.

The design now enables the corresponding operating modes to be implemented highly efficiently and in a very compact structure, particularly in the axial direction with respect to the two aligned output shafts.

According to the method for operating the electric drive system according to claim 11, for torque vectoring operation, the first switching element is closed, the second switching element is opened, the third switching element is closed, the fourth switching element is opened and the fifth switching element is closed again. This allows torque to be introduced into the coupling gear via both electric machines in order to achieve a desired torque distribution to the two output shafts and thus the driven wheels that are at least indirectly connected to them by selecting the torques of these two electric machines via their electronic or power electronic control.

In the efficiency mode mentioned above, as described in claim 12, the first switching element can then be opened, the second switching element closed, the third switching element opened, the fourth switching element closed and the fifth switching element opened. The coupling gear then acts as a classic differential for propulsion with the first electric machine alone, while the second electric machine is decoupled.

According to a very advantageous development of the invention, the electric drive system according to the invention can provide that the second element is designed as a first planet carrier and the fourth element as a second planet carrier. These two elements, which are connected to one another in a rotationally fixed manner, thus form two planet carriers, which in turn are connected in a rotationally fixed manner, for example with a common shaft.

A first embodiment of the electric drive system in this variant can now provide that first planetary gears are arranged on the second element, i.e. the first planet carrier, which permanently mesh with a toothing of the first element and with a toothing of the third element. They therefore form a first planetary gear within the coupling gear or planetary gear set. The fourth element, i.e. the second planet carrier, then has second planetary gears and third planetary gears. The third planetary gears permanently mesh with a toothing of the fifth element and one of the second planetary gears meshes with one of the third planetary gears and one of the third planetary gears meshes with one of the first planetary gears, in order to enable the transmission of power from the first part of the planetary gear with the first element, the second element or the first planetary gears and the third element to the second part of the planetary gear with the fourth element or its second and third planetary gears and the fifth element.

An alternative embodiment of the variant of the electric drive system according to the invention, in which the second element and the fourth element form two planet carriers, can alternatively provide that the first element no longer meshes with the first planet gears of the first planet carrier and thus of the second element, but that the first planet gears only mesh with a toothing of the third element and instead the second planet gears permanently mesh with a toothing of the first element, whereby here again the third planet gears permanently mesh with a toothing of the fifth element and one of the second planet gears meshes with one of the third planet gears on the one hand and one of the third planet gears with one of the first planet gears on the other hand. In this construction, the first element is ultimately displaced from one half of the planetary gear set to the other half of the planetary gear set in the axial direction.

In both design variants of the electric drive system, it can now be provided that the respective output shaft in the power flow following the respective output shaft and the coupling gear is connected to the driven element, for example the wheels of a vehicle, via a first or second gear stage. A gear stage is therefore arranged between the output shaft and the driven element, for example the wheels. This can be implemented, for example, as a planetary gear, spur gear or the like. It is particularly preferably designed as a planetary gear.

A further very advantageous embodiment of the electric drive system according to the invention can also provide that the third switching element is designed to couple the first rotor to the third element in a rotationally fixed manner. The torques are then no longer introduced indirectly from the first rotor via the third switching element into the coupling gear or its third element - as is also conceivable in principle - but these two elements are directly connected to one another in a rotationally fixed manner via the third switching element in order to implement an even more compact and simpler structure. The same applies to the fifth switching element, which according to a particularly preferred embodiment of the electric drive system according to the invention is designed to couple the second rotor to the first element in a rotationally fixed manner.

Another very favorable embodiment of the electric drive system according to the invention can also provide that, viewed in the axial direction, which is defined by the two output shafts, the first switching element and the second switching element are arranged so as to axially overlap the coupling gear. In the sense of the invention, axially overlapping means that the two switching elements and the coupling gear overlap in at least one plane perpendicular to the axial direction. The switching elements are therefore preferably arranged on the outside or inside of the coupling gear on the circumference, which ensures a very compact structure, especially in the axial extension.

A further advantageous embodiment of the electric drive system according to the invention can also provide that the first element is designed as a sun gear, the third element as a first ring gear and the fifth element as a second ring gear. This allows a very compact and efficient coupling gear, which together with the switching elements ensures a highly flexible electric drive system in a compact design.

Another extremely advantageous development of the electric drive system can now also provide for a sixth switching element. This is designed to couple the first rotor to the second rotor in a rotationally fixed manner. The two electric machines can therefore be connected together via this sixth switching element in order to jointly introduce torque into the coupling gear. In addition to the two modes of torque vectoring and efficiency mode described above, this now also enables boost mode.

According to the method, this particularly favorable embodiment of the electric drive system according to claim 13 can be used in such a way that for boost operation the first switching element is opened, the second switching element is closed, the third switching element is opened, the fourth switching element is closed, the fifth switching element is opened and the sixth switching element is closed accordingly. In this boost operation, propulsion via both electric machines is then possible simultaneously at one input of the coupling gear. The coupling gear acts as a differential gear with an even 1:1 distribution of the torque to the two output shafts and thus at least indirectly to the two driven wheels. When cornering, where the speeds of the two wheels are different depending on whether they are on the inside or outside of the curve, the torques on both wheels still remain the same.

All in all, this makes it possible to implement an electric drive system in a compact design that enables special efficiency and dynamic functionalities.

Further advantageous embodiments of the electric drive system and of the methods for operating the electric drive system also emerge from the exemplary embodiments, which are described in more detail below with reference to the figures.

• 1 eine schematische Darstellung einer ersten möglichen Ausführungsform eines elektrischen Antriebssystems gemäß der Erfindung;
• 2 eine alternative Ausgestaltung des elektrischen Antriebssystems gemäß 1; und
• 3 eine Schalttabelle zur Verdeutlichung der verschiedenen Betriebsmodi;
• 4 eine weitere vorteilhafte Ausgestaltung des elektrischen Antriebssystems gemäß 1.

Showing:

• 1 a schematic representation of a first possible embodiment of an electric drive system according to the invention;
• 2 an alternative design of the electric drive system according to 1 ; and
• 3 a switching table to clarify the different operating modes;
• 4 a further advantageous embodiment of the electric drive system according to 1 .

In the presentation of the 1 the upper half of an electric drive system 1 is shown. This can preferably be used in a vehicle to drive driven wheels. The electric drive system 1 has a first electric machine 10 and a second electric machine 20. Both have a rotor, namely a first rotor 110 of the first electric machine 10 and a second rotor 210 of the second electric machine 20, which serves to deliver torque in motor operation. The electric drive system 1 also has a coupling gear 30, which is designed as a four-shaft planetary gear set. Torque or power is output from the coupling gear 30 via a first output shaft 41 and a second output shaft 42. These two output shafts 41 and 42, which are shown and designed here in alignment with one another, define on the one hand the axis of rotation of the electric drive system 1 and on the other hand the axial direction a, which runs parallel or along the axes of these two output shafts 41 and 42.

The coupling gear 30 comprises in the embodiment of the 1 a first element 31, which is designed as a sun gear and meshes with first planet gears 36 in the area of a toothing not explicitly designated here. These first planet gears 36, which are arranged on a first planet carrier as the second element 32 of the coupling gear 30, mesh on the other hand with a third element 33 of the coupling gear 30, which is designed as a first ring gear. One of several third planet gears 38 of a second planet carrier is now also driven via one of the first planet gears 36 as the fourth element 34 of the coupling gear 30. This also drives at least one second planet gear 37, which is arranged on the same second planet carrier, i.e. the fourth element 34 of the coupling gear 30. In addition, it meshes with a second ring gear as the fifth element 35 of the coupling gear 30. These two parts of the coupling gear 30 with their first ring gear (the third element 33) and the second ring gear (the fifth element 35) are arranged next to each other in the axial direction and are connected on the one hand via the planet carriers (the second element 32 and the fourth element 34) which are connected to one another in a rotationally fixed manner via their shaft and on the other hand via the meshing of one of the first planet gears 36 with one of the third planet gears 38.

The first rotor 110, or a first rotor shaft 11, which is connected in a rotationally fixed manner to the first rotor 110, of the first electric machine 10 can now be connected optionally to the third element 33 or the second element 32 of the coupling gear 30 via a third switching element S3 or a fourth switching element S4. This allows torques from the first electric machine 10 to be introduced into the coupling gear 30. The second output shaft 42 is now connected either to the third element 33 of the coupling gear 3 or to the fourth element 34 via a first switching element S1 or a second switching element S2. The first output shaft 41, on the other hand, is permanently connected in a rotationally fixed manner to the fifth element 35 of the coupling gear 30.

Both output shafts 41, 42 could now directly drive the driven elements, for example the wheels of a vehicle. However, optionally and particularly preferably, with regard to a power flow, there is a first gear stage 51 behind the first output shaft 41 and behind the coupling gear 30 and, accordingly, with regard to the power flow, there is a second gear stage 52 behind the second output shaft 42 and the coupling gear 30. The driven wheels can then be driven indirectly via the two output shafts 41, 42 via these gear stages 51, 52, which are advantageously indicated here as planetary gears.

The term power flow refers to a flow of drive power emanating from the electrical machines and directed to the output shafts 41 and 42.

In order to include the second electric machine 20 in the drive power, a fifth switching element S5 is also provided, via which the second electric machine 20 or its rotor 210 can be coupled to the first element 31 of the coupling gear 30, i.e. the sun gear. In the embodiment of the 1 As already mentioned, this sun gear 31 meshes with the first planet gears 36. In the embodiment of the 1 the fifth switching element S5 is provided to connect a second rotor shaft 21, which is rotationally fixedly connected to the second rotor 210, to the first element 31.

Optionally, a further sixth switching element S6 can be provided. Via this sixth switching element S6, the second rotor 210 of the second electric machine 20 can be coupled in a rotationally fixed manner to the first rotor 110 of the first electric machine 10 in order to deliver torque to the coupling gear 30 equally with both electric machines 10, 20, for example when the fourth switching element S4 is closed.

The design of the electric drive system 1 according to 1 is now constructed in such a way that the two electrical machines 10, 20 are arranged next to one another in the axial direction a, with the fifth switching element S5 and the optional sixth switching element S6 being arranged between the two electrical machines 10, 20 or partially overlapping them in the axial direction a. In the axial direction a, the two electrical machines 10, 20 are then followed in one direction by the coupling gear 30, with the first switching element S1 and the second switching element S2 being arranged axially overlapping. The third switching element S3 and the fourth switching element S4 are arranged between the coupling gear 30 and the first electrical machine 10, if necessary again at least partially overlapping the first electrical machine 10.

In the axial direction a adjacent to the second electric machine 20, the optional first gear ratio 51 and adjacent to The optional second gear ratio 52 can be arranged in the coupling gear 30.

In the presentation of the 2 A further structure of the electric drive system 1 is now shown. This essentially corresponds to the one in 1 already described structure including the arrangement of the individual elements in the axial direction a. The only difference now is that the first element 31 of the coupling gear 30, i.e. the sun gear, which can be coupled to the second rotor 210 of the second electric machine 20 via the fifth switching element S5, no longer meshes with the first planetary gears 36 of the first planet carrier, i.e. the second element 32 of the coupling gear 30, but with the second planetary gears 37 of the second planet carrier, i.e. the fourth element 34 of the coupling gear 30. Otherwise, the structure corresponds to that of the 1 , so there is no need to go into this in detail again.

In the presentation of the 3 A switching table is now shown which shows the position of the individual switching elements S1 to S6 for the various modes that can be implemented with the electric drive system 1. The first mode is a torque vectoring mode, the second mode is an efficiency mode. These two modes do not require the optional sixth switching element S6, but can also be used if this switching element is present. The third mode is a boost mode, which absolutely requires the sixth switching element S6.

Each of the switching elements S1 to S5 or S6, if present, is capable of both coupling and decoupling. In the representation of the 3 The coupled or closed switching element is marked with an x. The decoupled or open position of the respective switching element is marked by a blank field within the switching table.

In the first mode, the torque vectoring mode, the first switching element S1 is closed, the second switching element S2 is open, the third switching element S3 is closed, the fourth switching element S4 is open and the fifth switching element S5 is closed. If the optional sixth switching element is present, this would be open.

The second output shaft 42 is now driven when the first switching element S1 is closed via a rotationally fixed connection to the fourth element 34, i.e. the second planet carrier. The first output shaft 41 is driven in all modes by its permanent rotationally fixed connection to the second ring gear, the fifth element 35. The closed third switching element S3 ensures that power is input from the first electric machine 10 or its first rotor 110 via the third element 33, i.e. the first ring gear of the coupling gear 30. The fourth switching element S4 is opened accordingly, as is the second switching element S2. The fifth switching element S5 is in turn closed and ensures that power or torque is input from the second electric machine 20 or its second rotor 210 via the first element 31 of the coupling gear 30, i.e. the sun gear, depending on the design variant via the first planetary gears 36 or the second planetary gears 37. In this torque vectoring mode, both electric machines 10, 20 therefore deliver significant torque via the coupling gear 30 for propulsion. The two electric machines 10, 20 can be designed in the same way for this purpose, but they do not have to be. In particular, electric machines 10, 20 of different strengths can be used, i.e., electric machines with different nominal power. By selecting the torques delivered by the respective electric machine 10, 20, which is achieved by controlling them via their electronics or power electronics, a torque distribution can be achieved between the two output shafts 41, 42 and thus between the wheels driven at least indirectly by them. Such a distribution of torque to the different wheels according to a selected specification offers particular advantages when driving dynamically in curves and allows an improvement in driving performance and an increase in driving safety.

Efficiency mode, as its name suggests, serves to operate the electric drive system 1 as efficiently as possible, i.e. with minimal energy input for the drive power generated. For this purpose, propulsion is achieved solely by the first electric machine 10. The second output shaft 42 is connected to the third element 33, i.e. the first ring gear of the coupling gear 30, for which purpose the second switching element S2 is closed and the first switching element S1 is open. When the third switching element S3 is open and the fourth switching element S4 is closed, the first rotor 110 of the first electric machine 10 is connected in a rotationally fixed manner to the second element 32, i.e. the first planet carrier of the coupling gear 30, in order to introduce power or torque into the coupling gear 30 in this way. At the same time, the fifth switching element S5 is open and, if present, the sixth switching element S6 is also open, so the second electric machine 20 is decoupled. In this efficiency mode, the coupling gear 30 serves as a classic differential with a 50:50 torque distribution, even in curves, although the wheels still have different speeds.

The third operating mode is boost mode. This requires the sixth switching element S6. In terms of the position of the switching elements, it essentially corresponds to operation in efficiency mode, i.e. it uses the coupling gear 30 as a classic differential gear with a 50:50 distribution of the torque to both output shafts 41, 42. In addition, the sixth switching element S6 is now closed, so that the first rotor 110 of the first electric machine 10 and the second rotor 210 of the second electric machine 20 are connected to one another in a rotationally fixed manner and the torque generated by the two electric machines 10, 20 is introduced jointly into the coupling gear 30. This allows the maximum power of both electric machines 10, 20 to be made available together in boost mode in order to enable maximum drive power. Unlike torque vectoring, the torques remain the same on both wheels driven by the two output shafts 41, 42, even if the speeds differ from each other when cornering, comparable to efficiency mode.

4 shows in comparison to the design of the 1 in particular an advantageous alternative arrangement of the first gear ratio 51 and the second gear ratio 52. The second gear ratio 52 is arranged with respect to the power flow between the first rotor 110 and the coupling gear 30.

Particularly advantageously, the second gear ratio 52 is arranged with regard to the power flow between the first rotor 110 and the third switching element S3 and between the first rotor 110 and the fourth switching element S4.

The first gear ratio 51 is advantageously arranged between the second rotor 210 and the coupling gear 30 with regard to the power flow.

The first gear ratio 51 is particularly advantageously arranged with regard to the power flow between the fifth shift element S5 and the coupling gear 30.

Alternatively and equally advantageously and not further shown here, the first gear stage 51 can also be arranged between the second rotor 210 and the fifth switching element S5.

Of course, the 4 shown and here in connection with the 4 The arrangement of the gear ratios 51, 52 described above, namely the arrangement with regard to the power flow in front of the coupling gear 30, also applies in the same way to the design of the 2 be transmitted.

Claims (14)

Electric drive system (1) with a first electric machine (10) with a first rotor (110), a second electric machine (20) with a second rotor (210) and a coupling gear (30), wherein the coupling gear (30) has a four-shaft planetary gear set with a first element (31), a second element (32), a third element (33), a fourth element (34) and a fifth element (35), wherein the second element (32) is connected in a rotationally fixed manner to the fourth element (34), wherein the coupling gear (30) has a first output shaft (41) and a second output shaft (42), which are designed to output torques from the coupling gear (30), wherein the first output shaft (41) is connected in a rotationally fixed manner to the fifth element (35), characterized by a first switching element (S1) which is designed to couple the second output shaft (42) in a rotationally fixed manner to the second element (32), a second Switching element (S2) which is designed to couple the second output shaft (42) to the third element (33) in a rotationally fixed manner, a third switching element (S3) which is designed to couple the first rotor (110) to the third element (33) in such a way that torques, originating from the first electrical machine (10), can be introduced at the third element (33) into the coupling gear (30), a fourth switching element (S4) which is designed to couple the first rotor (110) to the second element (32) in such a way that torques, originating from the first electrical machine (10), can be introduced at the second element (32) into the coupling gear (30), a fifth switching element (S5) which is designed to couple the second rotor (210) to the first element (31) in such a way that torques, originating from the second electrical machine (20), can be introduced at the first element (31) into the coupling gear (30) may be initiated. Electric drive system (1) according to Claim 1 , characterized in that the second element (32) is designed as a first planet carrier, and the fourth element (34) is designed as a second planet carrier. Electric drive system (1) according to Claim 2 , characterized in that first planetary gears (36) are arranged on the second element (32), the first planetary gears (36) permanently meshing with a toothing of the first element (31) and with a toothing of the third element (33), and second planetary gears (37) and third planetary gears (38) are arranged on the fourth element (34), the third planetary gears (38) permanently meshing with a toothing of the fifth element (35), and one of the second planetary gears (37) meshing with one of the third planetary gears (38), and one of the third planetary gears (38) meshing with one of the first planetary gears (36). Electric drive system (2) according to Claim 2 , characterized in that first planetary gears (36) are arranged on the second element (32), the first planetary gears (36) permanently meshing with a toothing of the third element (33), and in that second planetary gears (37) and third planetary gears (38) are arranged on the fourth element (34), the second planetary gears (37) permanently meshing with a toothing of the first element (31), the third planetary gears (38) permanently meshing with a toothing of the fifth element (35), one of the second planetary gears (37) meshing with one of the third planetary gears (38), and one of the third planetary gears (38) meshing with one of the first planetary gears (36). Electric drive system (1) according to one of the preceding claims, characterized by a first transmission stage (51) which is arranged behind the first output shaft (41) and behind the coupling gear (30) with regard to a power flow, and by a second transmission stage (52) which is arranged behind the second output shaft (42) and behind the coupling gear (30) with regard to the power flow. Electric drive system (1) according to one of the Claims 1 until 4 , characterized by a first transmission stage (51) which is arranged with respect to a power flow between the second rotor (210) and the coupling gear (30), and by a second transmission stage (52) which is arranged with respect to the power flow between the first rotor (110) and the coupling gear (30). Electric drive system (1) according to one of the Claims 1 until 5 , characterized in that the third switching element (S3) is designed to couple the first rotor (110) in a rotationally fixed manner to the third element (33). Electric drive system (1) according to one of the Claims 1 until 5 , characterized in that the fifth switching element (S5) is designed to couple the second rotor (210) in a rotationally fixed manner to the first element (31). Electric drive system (1) according to one of the preceding claims, characterized in that, viewed in an axial direction (a), the first switching element (S1) and the second switching element (S2) are arranged axially overlapping the coupling gear (30). Electric drive system (1) according to one of the preceding claims, characterized in that the first element (31) is designed as a sun gear, the third element (33) as a first ring gear and the fifth element (35) as a second ring gear. Electric drive system (1) according to one of the preceding claims, characterized by a sixth switching element (S6) which is designed to couple the first rotor (110) in a rotationally fixed manner to the second rotor (210). Method for operating the electric drive system (1) according to one of the Claims 1 until 11 , characterized in that for a torque vectoring operation the first switching element (S1) is closed, the second switching element (S2) is opened, the third switching element (S3) is closed, the fourth switching element (S4) is opened and the fifth switching element (S5) is closed. Method for operating the electric drive system (1) according to one of the Claims 1 until 11 , characterized in that for an efficiency operation the first switching element (S1) is opened, the second switching element (S2) is closed, the third switching element (S3) is opened, the fourth switching element (S4) is closed and the fifth switching element (S5) is opened. Method for operating the electric drive system (1) according to Claim 11 , characterized in that for a boost operation the first switching element (S1) is opened, the second switching element (S2) is closed, the third switching element (S3) is opened, the fourth switching element (S4) is closed, the fifth switching element (S5) is opened and the sixth switching element (S6) is closed.

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