Drive unit for a vehicle

Abstract

A drive unit for a vehicle, comprising a first electric machine (EM1), a second electric machine (EM2) arranged axially parallel thereto, a manual transmission (SG) arranged axially parallel to the two electric machines (EM1, EM2), a differential (DG), a drive shaft (An) for connecting the first electric machine (EM1) to the manual transmission (SG), an output shaft (Ab) for connecting the manual transmission (SG) to the differential (DG), and a first positive-locking switching unit with a first switching element (K), a second switching element (S), and a first sliding sleeve (SM1), which can be moved into one of three switching positions by means of a first actuator (AK1), wherein in a first switching position of the first sliding sleeve (SM1), the first switching element (K) is closed and the second electric machine (EM2) is drivingly connected to the drive shaft (An),wherein in a second switching position of the first sliding sleeve (SM1) both switching elements (K, S) are open and the second electric machine (EM2) is decoupled from the manual transmission (SG), wherein in a third switching position of the first sliding sleeve (SM1) the second switching element (S) is closed and the second electric machine (EM2) is drivingly connected to the output shaft (Ab), wherein the input shaft (An) is designed as a hollow shaft and the output shaft (Ab) is arranged within the input shaft (An).

Description

[0001] The invention relates to a drive unit for a vehicle, wherein the drive unit comprises two electric motors, a multi-speed manual transmission, and a differential. The invention also relates to a vehicle having such a drive unit.

[0002] For example, DE 10 2013 214 238 A1 discloses a drive unit for a vehicle, wherein the drive unit has a plurality of electric machines, at least one planetary gear, and a plurality of positive-locking shifting elements. A first electric machine is permanently coupled, directly or indirectly, to a sun gear of a first planetary gear, wherein a second electric machine is directly or indirectly coupled, depending on the shift position of a first positive-locking shifting element and a second positive-locking shifting element, either to the sun gear of the first planetary gear or to a carrier of the first planetary gear. A ring gear of the first planetary gear is coupled, depending on the shift position of a third positive-locking shifting element and a fourth positive-locking shifting element, either to a housing or to the carrier of the first planetary gear.

[0003] The object of the present invention is to provide an alternative drive unit for a vehicle. In particular, the drive unit should be compact. This object is achieved by a drive unit having the features of independent patent claim 1. Advantageous embodiments are the subject of the dependent claims, the following description, and the figures.

[0004] A drive unit for a vehicle according to the invention comprises a first electric machine, a second electric machine arranged axially parallel thereto, a manual transmission arranged axially parallel to the two electric machines with several gears and at least one first planetary gear set, which has a first sun gear shaft, a first ring gear shaft and a first planetary gear shaft, a differential with a differential input shaft and two differential output shafts, a drive shaft for connecting the first electric machine to the manual transmission, an output shaft for connecting the manual transmission to the differential, a first positive-locking switching unit with a first switching element, a second switching element and a first sliding sleeve, which can be moved into one of three switching positions by means of a first actuator,wherein in a first switching position of the first sliding sleeve, the first switching element is closed and the second electric machine is drivingly connected to a shaft of the first planetary gear set, wherein in a second switching position of the first sliding sleeve, both switching elements are open and the second electric machine is decoupled from the manual transmission, wherein in a third switching position of the first sliding sleeve, the second switching element is closed and the second electric machine is drivingly connected to the drive shaft, wherein the first electric machine is connected to the drive shaft via a first spur gear stage and a second spur gear stage, wherein the second electric machine can be connected to a shaft of the first planetary gear set or to the drive shaft via a third spur gear stage and a fourth spur gear stage,wherein the first switching unit is arranged radially nested with the first spur gear stage and the third spur gear stage.,

[0005] In particular, the first spur gear stage has a first spur gear and a second spur gear, which mesh with one another. Furthermore, the second spur gear stage has a third spur gear and a fourth spur gear, which mesh with one another. The first spur gear is, for example, rotationally fixedly connected to a rotor shaft of the first electric machine, wherein the second and third spur gears are rotationally fixedly connected, wherein the fourth spur gear is rotationally fixedly connected to the drive shaft. In particular, the third spur gear stage has a fifth spur gear and a sixth spur gear, which mesh with one another. Furthermore, the fourth spur gear stage has a seventh spur gear and an eighth spur gear, which mesh with one another.The fifth spur gear, for example, is rotationally fixedly connected to a rotor shaft of the second electric machine, while the sixth and seventh spur gears are rotationally fixedly connected. The eighth spur gear is rotationally fixedly connectable to a shaft of the first planetary gear set or to the drive shaft via the first switching unit. The shafts of the first planetary gear set are the first sun gear shaft, the first ring gear shaft, and the first planetary gear shaft. The first ring gear shaft carries several planetary gears that mesh, i.e., are in tooth engagement, with the first sun gear shaft and the first ring gear shaft.

[0006] For the purposes of the invention, a “shaft” is understood to be a rotatable component of the transmission via which associated components of the transmission are connected to one another in a rotationally fixed manner or via which such a connection can be established upon actuation of one of the shift elements. The respective shaft can connect the components axially or radially, or even both axially and radially. For example, the respective shaft can also be in the form of an intermediate piece via which a respective component is connected radially, for example. The term “shaft” does not exclude the possibility that the components to be connected can be designed as a single piece. In particular, two or more shafts connected to one another in a rotationally fixed manner can be designed as a single piece.

[0007] A “shifting element” is a switchable device which, when closed, connects two shafts or a shaft and a housing in a rotationally fixed manner and, when open, decouples the two shafts or the shaft and the housing. Two shafts can then rotate relative to one another. The first shifting unit has a neutral position between two gear positions, so that with three shift positions there are two gear positions and a neutral position. In a neutral position, two shafts are decoupled from one another via the first shifting unit, with the first sliding sleeve then being in rotational engagement with a single shaft. In particular, the first actuator moves the first sliding sleeve into the respective shift position and thereby couples the second electric machine to the manual transmission and the differential.The first sliding sleeve is designed to be positively engaged and has positive-locking claws that interact positively with a corresponding claw toothing in the respective gear position to establish a rotationally fixed connection between two shafts. Therefore, the respective claw toothing with which the first sliding sleeve interacts positively is to be understood as a shifting element. The first shifting unit preferably comprises unsynchronized claw clutches. Thus, the two shifting elements are designed as positive-locking shifting elements. Positive-locking shifting elements can increase the efficiency of the drive unit due to reduced drag losses. In particular, positive-locking shifting elements are more compact and have an optimized efficiency, offering a cost advantage over friction-locking shifting elements.The use of a single sliding sleeve and a single actuator to switch the first and second switching elements further increases compactness.

[0008] In the closed state of the first switching element, i.e. in the first switching position of the first sliding sleeve, the second electric machine is drive-connected to a shaft of the first planetary gear set, in particular to the first ring gear shaft or the first carrier shaft, whereby a torque summation of the two electric machines is thereby made possible, whereby both electric machines have the gears of the manual transmission.

[0009] In the open state of the first and second switching elements, i.e. in the second switching position or neutral position of the first sliding sleeve, the second electric machine is decoupled from the drive train, whereby, for example in partial load operation, electrical losses and losses due to rotating bearings can be reduced.

[0010] When the second shift element is closed, i.e., when the first sliding sleeve is in the second shift position, the second electric motor is drivingly connected to the drive shaft, allowing drive power from the second electric motor to be transferred to the manual transmission. The second electric motor can thus drive the vehicle independently of the first electric motor or support the tractive force during shifts of the first electric motor. This is commonly known as "output-supported shifting" or "electromotive shifting" (EMS).

[0011] According to the invention, the first shift unit is arranged radially nested with the first spur gear stage and the third spur gear stage. Thus, the first spur gear stage and the third spur gear stage are arranged radially nested on an outer circumference of the first shift unit in order to save axial installation space. As a result, the first shift unit, the first spur gear stage, and the third spur gear stage are at least partially located in the same axial installation space plane.

[0012] According to one embodiment, the manual transmission further comprises a third shifting element and a fourth shifting element, wherein the first sun gear shaft and the input shaft are connected in a rotationally fixed manner, wherein the first carrier shaft and the output shaft are connected in a rotationally fixed manner, wherein the first carrier shaft and the output shaft are connected to the second electric machine in the closed state of the first shifting element, wherein the first ring gear shaft is connected in a rotationally fixed manner to a stationary component in the closed state of the third shifting element, wherein the first ring gear shaft is connected in a rotationally fixed manner to the output shaft and the first carrier shaft in the closed state of the fourth shifting element. A “stationary component” is understood to mean a component that is fixed in a stationary manner, in particular that is connected in a rotationally fixed manner or in one piece to a housing or a part of a housing. Reference is made here to the embodiment according to Fig. 11.

[0013] According to one embodiment, the manual transmission further comprises a third shifting element and a fourth shifting element, wherein the first sun gear shaft and the input shaft are connected in a rotationally fixed manner, wherein the first carrier shaft and the output shaft are connected in a rotationally fixed manner, wherein the first ring gear shaft is connected to the second electric machine in the closed state of the first shifting element, wherein the first ring gear shaft is connected in a rotationally fixed manner to a stationary component in the closed state of the third shifting element, wherein the first ring gear shaft is connected in a rotationally fixed manner to the output shaft and the first carrier shaft in the closed state of the fourth shifting element. Reference is made here to the embodiment according to Fig. 12.

[0014] According to one embodiment, the manual transmission further comprises a second planetary gear set, a third shifting element, and a fourth shifting element, the second planetary gear set having a second sun gear shaft, a second ring gear shaft, and a second carrier shaft, the first sun gear shaft, the second sun gear shaft, and the input shaft being connected in a rotationally fixed manner, the first carrier shaft and the second ring gear shaft being connected in a rotationally fixed manner, the second carrier shaft and the output shaft being connected in a rotationally fixed manner, the first ring gear shaft being connected to the second electric machine when the first shifting element is in the closed state, the first ring gear shaft being connected in a rotationally fixed manner to a stationary component when the third shifting element is in the closed state, the first ring gear shaft being connected in a rotationally fixed manner to the second ring gear shaft and the first carrier shaft when the fourth shifting element is in the closed state, and the two planetary gear sets are thereby interlocked.To block the two planetary sets, two of the three shafts of the respective planetary set can be connected to one another, or a shaft of the first planetary set can be connected to a shaft of the second planetary set. When a planetary set is blocked, it rotates in the block. The manual transmission thus has two planetary sets, with the two planetary sets arranged axially adjacent to one another to save radial installation space. The second carrier shaft carries a plurality of planet gears that mesh with the second sun shaft and the second ring gear shaft. Reference is made here to the embodiments according to . Fig. 2a and Fig. 4.

[0015] According to one embodiment, the manual transmission further comprises a second planetary gear set, a third shifting element and a fourth shifting element, wherein the second planetary gear set has a second sun shaft, a second ring gear shaft and a second carrier shaft, wherein the first sun shaft, the second sun shaft and the input shaft are connected in a rotationally fixed manner, wherein the first carrier shaft and the second ring gear shaft are connected in a rotationally fixed manner, wherein the first carrier shaft and the second ring gear shaft are connected in a rotationally fixed manner to a stationary component when the third shifting element is in the closed state, wherein the second carrier shaft and the output shaft are connected in a rotationally fixed manner, wherein the first ring gear shaft is connected to the second electric machine when the first shifting element is in the closed state, wherein the first ring gear shaft is connected in a rotationally fixed manner to the stationary component when the fourth shifting element is in the closed state.The manual transmission therefore has two planetary gear sets, with the two planetary gear sets arranged axially adjacent to each other to save radial space. The second carrier shaft carries several planetary gears that mesh with the second sun gear shaft and the second ring gear shaft. Reference is made here to the embodiment shown in . Fig. 3a.

[0016] According to one embodiment, the manual transmission further comprises a second planetary gear set, a third shifting element, and a fourth shifting element, wherein the second planetary gear set has a second sun shaft, a second ring gear shaft, and a second carrier shaft, wherein the first sun shaft and the input shaft are connected in a rotationally fixed manner, wherein the first carrier shaft and the second sun shaft are connected in a rotationally fixed manner, wherein the second carrier shaft and the output shaft are connected in a rotationally fixed manner, wherein the second ring gear shaft is connected in a rotationally fixed manner to a stationary component, wherein the first ring gear shaft is connected to the second electric machine when the first shifting element is in the closed state, wherein the first ring gear shaft is connected in a rotationally fixed manner to the second carrier shaft and the output shaft when the third shifting element is in the closed state,wherein the first ring gear shaft is connected in a rotationally fixed manner to the second sun gear shaft and the first carrier shaft when the fourth shift element is closed. Thus, the transmission has two planetary gear sets, wherein the two planetary gear sets are arranged axially adjacent to one another to save radial installation space. The second carrier shaft carries several planetary gears that mesh with the second sun gear shaft and the second ring gear shaft. Reference is made here to the embodiment according to , Fig. 7.

[0017] According to one embodiment, the manual transmission further comprises a second planetary gear set, a third shifting element, and a fourth shifting element, wherein the second planetary gear set has a second sun shaft, a second ring gear shaft, and a second carrier shaft, wherein the first sun shaft and the input shaft are connected in a rotationally fixed manner, wherein the first carrier shaft and the second sun shaft are connected in a rotationally fixed manner, wherein the first carrier shaft and the second sun shaft are connected to the second electric machine when the first shifting element is in the closed state, wherein the second carrier shaft and the output shaft are connected in a rotationally fixed manner, wherein the second ring gear shaft is connected in a rotationally fixed manner to a stationary component, wherein the first ring gear shaft is connected in a rotationally fixed manner to the second carrier shaft and the output shaft when the third shifting element is in the closed state,wherein the first ring gear shaft is rotationally fixedly connected to the second sun gear shaft and the first carrier shaft in the closed state of the fourth shift element. Thus, the transmission has two planetary gear sets, wherein the two planetary gear sets are arranged axially adjacent to one another in order to save radial installation space. The second carrier shaft carries several planetary gears that mesh with the second sun gear shaft and the second ring gear shaft. Reference is made here to the embodiments according to , Fig. 8 and Fig. 9.

[0018] The third and fourth shifting elements are designed as gear shifting elements and are thus configured for shifting gears. When the third shifting element is closed and the fourth shifting element is open, a first gear with a first gear ratio is engaged. When the fourth shifting element is closed and the third shifting element is open, a second gear with a second gear ratio is engaged.

[0019] According to one embodiment, the third shifting element and the fourth shifting element are combined to form a second positive-locking shifting unit with an axially displaceable second sliding sleeve, wherein the second sliding sleeve can be displaced into one of three shift positions by means of a second actuator. The second shifting unit has a neutral position between two gear positions, so that with three shift positions, two gear positions and a neutral position are provided. In a neutral position, two shafts or a shaft and a stationary component are decoupled from one another via the second shifting unit, wherein the second sliding sleeve is then in rotational engagement with a single shaft or with the stationary component.In particular, the second actuator moves the second sliding sleeve into the respective shift position and thereby shifts two gears, whereby exactly one shift element of the second shift unit is closed to achieve a gear. The second sliding sleeve is designed to be positively engaged and has positive-locking claws which, in the respective gear position, interact positively with a respective corresponding claw toothing in order to establish a rotationally fixed connection between two shafts or a shaft and a stationary component. Thus, the respective claw toothing with which the second sliding sleeve interacts positively is to be understood as a shift element. The second shift unit preferably comprises unsynchronized claw clutches. Thus, all shift elements are designed as positive-locking shift elements. The efficiency of the manual transmission can be increased by means of positive-locking shift elements due to reduced drag losses.In particular, positive-locking shifting elements are more compact and efficient, offering a cost advantage over friction-locking shifting elements. The use of a single sliding sleeve for shifting two gears further increases compactness, while only a single actuator is required. Reference is made to the embodiments shown in [figure omitted]. Fig. 2a, Fig. 3a, Fig. 4, Fig. 7 to Fig. 9, Fig. 11 and Fig. 12.

[0020] According to one embodiment, the manual transmission further comprises a second planetary gear set, a third shifting element, a fourth shifting element, and a fifth shifting element, wherein the second planetary gear set has a second sun gear shaft, a second ring gear shaft, and a second carrier shaft, wherein the first sun gear shaft, the second sun gear shaft, and the input shaft are connected in a rotationally fixed manner, wherein the first carrier shaft and the second ring gear shaft are connected in a rotationally fixed manner to a stationary component when the third shifting element is in the closed state, wherein the second carrier shaft and the output shaft are connected in a rotationally fixed manner, wherein the first ring gear shaft is connected to the second electric machine when the first shifting element is in the closed state, wherein the first ring gear shaft is connected in a rotationally fixed manner to the stationary component when the fourth shifting element is in the closed state.wherein, in the closed state of the fifth shift element, the first ring gear shaft is rotationally fixedly connected to the second ring gear shaft and the first planetary gear shaft, thereby interlocking the two planetary gear sets. Thus, the manual transmission has two planetary gear sets, with the two planetary gear sets arranged axially adjacent to one another to save radial installation space. The second planetary gear shaft carries several planetary gears that mesh with the second sun gear shaft and the second ring gear shaft. Reference is made here to the embodiment according to , Fig. 5.

[0021] According to one embodiment, the manual transmission further comprises a second planetary gear set, a third shifting element, a fourth shifting element, and a fifth shifting element, wherein the second planetary gear set has a second sun gear shaft, a second ring gear shaft, and a second carrier shaft, wherein the first sun gear shaft and the input shaft are connected in a rotationally fixed manner, wherein the first carrier shaft and the second sun gear shaft are connected in a rotationally fixed manner, wherein the second carrier shaft and the output shaft are connected in a rotationally fixed manner, wherein the second ring gear shaft is connected in a rotationally fixed manner to a stationary component, wherein the first ring gear shaft is connected to the second electric machine in the closed state of the first shifting element, wherein the first ring gear shaft is connected in a rotationally fixed manner to the stationary component in the closed state of the third shifting element,wherein the first ring gear shaft is connected in a rotationally fixed manner to the second carrier shaft and the output shaft in the closed state of the fourth shifting element, wherein the first ring gear shaft is connected in a rotationally fixed manner to the second sun gear shaft and the first carrier shaft in the closed state of the fifth shifting element, thereby locking the two planetary gear sets. Thus, the manual transmission has two planetary gear sets, wherein the two planetary gear sets are arranged axially adjacent to one another in order to save radial installation space. The second carrier shaft carries a plurality of planetary gears that mesh with the second sun gear shaft and the second ring gear shaft. Reference is made here to the embodiment according to , Fig. 6.

[0022] According to one embodiment, the manual transmission further comprises a second planetary gear set, a third shifting element, a fourth shifting element, and a fifth shifting element, wherein the second planetary gear set has a second sun gear shaft, a second ring gear shaft, and a second carrier shaft, wherein the first sun gear shaft and the input shaft are connected in a rotationally fixed manner, wherein the first carrier shaft and the second sun gear shaft are connected in a rotationally fixed manner, wherein the first carrier shaft and the second sun gear shaft are connected to the second electric machine when the first shifting element is in the closed state, wherein the second carrier shaft and the output shaft are connected in a rotationally fixed manner, wherein the second ring gear shaft is connected in a rotationally fixed manner to a stationary component, wherein the first ring gear shaft is connected in a rotationally fixed manner to the stationary component when the third shifting element is in the closed state,wherein the first ring gear shaft is connected in a rotationally fixed manner to the second carrier shaft and the output shaft in the closed state of the fourth shifting element, wherein the first ring gear shaft is connected in a rotationally fixed manner to the second sun gear shaft and the first carrier shaft in the closed state of the fifth shifting element, thereby locking the two planetary gear sets. Thus, the manual transmission has two planetary gear sets, wherein the two planetary gear sets are arranged axially adjacent to one another in order to save radial installation space. The second carrier shaft carries a plurality of planetary gears that mesh with the second sun gear shaft and the second ring gear shaft. Reference is made here to the embodiment according to , Fig. 10.

[0023] The third, fourth, and fifth shift elements are designed as gearshift elements and are thus configured for shifting gears. When the third shift element is closed and the fourth and fifth shift elements are open, a first gear with a first gear ratio is engaged. When the fourth shift element is closed and the third and fifth shift elements are open, a second gear with a second gear ratio is engaged. When the fifth shift element is closed and the third and fourth shift elements are open, a third gear with a third gear ratio is engaged.

[0024] According to one embodiment, the third shifting element, the fourth shifting element, and the fifth shifting element are combined to form a second positive-locking shifting unit with an axially displaceable second sliding sleeve, wherein the second sliding sleeve can be displaced into one of five shift positions by means of a second actuator. The second shifting unit has a neutral position between each two gear positions, so that with five shift positions, three gear positions and two neutral positions are provided. In a respective neutral position, two shafts or a shaft and a stationary component are decoupled from one another via the second shifting unit, wherein the second sliding sleeve is then in rotational engagement with a single shaft or with the stationary component. In particular, the second actuator displaces the second sliding sleeve into the respective shift position and thereby realizes three gears.The second sliding sleeve is designed to be form-fitting and has form-fitting claws which, in the respective gear position, interact in a form-fitting manner with a corresponding claw toothing in order to establish a rotationally fixed connection between two shafts or a shaft and the stationary component. The respective claw toothing with which the second sliding sleeve interacts in a form-fitting manner is therefore to be understood as a shifting element. The second shifting unit preferably comprises unsynchronised claw clutches. The three shifting elements are therefore designed as form-fitting shifting elements. The use of a single sliding sleeve and a single actuator for shifting three gears further increases compactness. Reference is made here to the embodiments according to. Fig. 5, Fig. 6 and Fig. 10.

[0025] According to one embodiment, the differential is arranged coaxially with the manual transmission, and the third differential output shaft is guided axially through the manual transmission, with the differential input shaft being connected to the output shaft in a rotationally fixed manner. This results in a particularly compact drive unit. Reference is made to the embodiments according to Fig. 2a, Fig. 3a and Fig. 5 to Fig. 12.

[0026] According to a preferred embodiment, the differential is designed as a ball or bevel gear differential. A differential designed as a ball or bevel gear differential has two wheel-side output elements, in particular a first output gear and a second output gear. The two output gears each mesh with a compensating element. The compensating elements are mounted in a differential carrier so they can rotate about their own axis. The respective output gear is connected in a rotationally fixed manner to the respective differential output shaft. The differential is driven via the differential carrier, which is configured as the differential input shaft. Furthermore, alternative designs of the differential are also conceivable, for example, as a spur gear differential or a planetary differential.The drive power fed into the differential via the differential input shaft is distributed in a conventional manner between the two differential output shafts and transmitted to the drive wheels of the axle. The differential output shafts are designed to be connected to the vehicle's drive wheels in a drivingly effective manner. The respective differential output shaft can be connected to the corresponding vehicle wheel directly or indirectly via a downstream fixed gear, a joint, a propeller shaft, and / or a wheel hub.

[0027] According to one embodiment, the differential is arranged transversely to the gearbox, with the differential input shaft being connected to the output shaft via a bevel gear stage. Reference is made here to the embodiment according to Fig. 4.

[0028] A vehicle according to the invention comprises a drive unit according to the invention. The above definitions as well as statements regarding technical effects, advantages, and advantageous embodiments of the drive unit according to the invention also apply mutatis mutandis to the vehicle according to the invention.

[0029] Advantageous embodiments of the invention, which are explained below, are illustrated in the drawings, wherein identical or similar elements are provided with the same reference numerals. They show: Fig. 1 is a highly abstracted schematic view of a vehicle with a drive axle having a drive unit according to the invention; Fig. 2a a highly abstracted schematic view of a drive unit according to the invention according to a first embodiment; Fig. 2b a switching matrix for the drive unit according to Fig. 2a; Fig. 3a a highly abstracted schematic view of a drive unit according to the invention according to a second embodiment; Fig. 3b a switching matrix for the drive unit according to Fig. 3a; Fig. 4 a highly abstracted schematic view of a drive unit according to the invention according to a third embodiment; Fig. 5 a highly abstracted schematic view of a drive unit according to the invention according to a fourth embodiment; Fig. 6 a highly abstracted schematic view of a drive unit according to the invention according to a fifth embodiment; Fig. 7 a highly abstracted schematic view of a drive unit according to the invention according to a sixth embodiment; Fig. 8 a highly abstracted schematic view of a drive unit according to the invention according to a seventh embodiment; Fig. 9 a highly abstracted schematic view of a drive unit according to the invention according to an eighth embodiment; Fig. 10 is a highly abstracted schematic view of a drive unit according to the invention according to a ninth embodiment; Fig. 11 a highly abstracted schematic view of a drive unit according to the invention according to a tenth embodiment and Fig. 12 a highly abstracted schematic view of a drive unit according to the invention according to an eleventh embodiment.

[0030] Fig. 1 shows a vehicle 100 with a first axle 101 with two vehicle wheels R1, R2 and a second axle 102 with two vehicle wheels R3, R4. In the present case, the first axle 101 is designed as the rear drive axle of the vehicle 100 and is equipped with a drive unit according to the invention. The drive unit comprises a first and a second electric machine EM1, EM2, each of which is designed to generate drive power, a manual transmission SG with two gears, and a differential DG. Thus, the vehicle 100 is designed as an electric vehicle, i.e., as an electrically driven vehicle. The drive unit is arranged transversely to the vehicle's longitudinal direction and is drivingly connected to the vehicle wheels R1, R2 of the first axle 101. A detailed design of this drive unit is shown in Fig. 2. Alternatively, as well as in Fig. 4, the differential DG can be arranged transversely to the vehicle's longitudinal direction.

[0031] In the present case, no additional drive unit is arranged on the second axle 102, i.e., the front axle of the vehicle 100, thereby saving costs, weight, and installation space. Alternatively, the drive unit can be arranged on the front axle of the vehicle 100 instead of on the rear axle. To implement an all-wheel drive system, an additional drive unit can be arranged on the second axle 102 and be drivingly connected to the vehicle wheels R3, R4 of this axle 102.

[0032] Fig. 2a shows the drive unit according to a first embodiment. The drive unit comprises an input shaft An for connecting the first electric machine EM1 to the manual transmission SG, an output shaft Ab for connecting the manual transmission SG to the differential DG, and a first positive-locking shifting unit with a first shifting element D, a second shifting element E, and a first sliding sleeve SM1, which can be moved into one of three shift positions by means of a first actuator AK1. The differential DG has a differential input shaft D1 and two differential output shafts D2, D3, wherein the differential DG is arranged coaxially to the manual transmission SG and the third differential output shaft D3 is guided axially through the manual transmission SG, thereby making the drive unit even more compact. In particular, the input shaft An is designed as a hollow shaft. The differential input shaft D1 is connected to the output shaft Ab in a rotationally fixed manner.

[0033] The differential DG is designed as a ball or bevel gear differential. The differential input shaft D1 is designed as a differential carrier. The differential DG, designed as a ball or bevel gear differential, has two wheel-side output elements, in particular a first output gear and a second output gear. The two output gears each mesh with a compensating element. The compensating elements are mounted in the differential carrier so they can rotate about their own axis. The respective output gear is connected in a rotationally fixed manner to the respective differential output shaft D2, D3. The differential DG is therefore driven via the differential carrier, which is connected in a rotationally fixed manner to the output shaft Ab. Arrows on the differential output shafts D2, D3 indicate a connection to a respective vehicle wheel of this vehicle axle.

[0034] The manual transmission SG has a first planetary gear set PS1 and a second planetary gear set PS2. The two planetary gear sets PS1, PS2 are arranged axially adjacent to one another to save installation space and increase compactness. The first planetary gear set PS1 comprises three shafts, namely a first sun gear shaft SO1, a first ring gear shaft HR1 and a first planetary gear shaft ST1. The first planetary gear shaft ST1 carries a plurality of planet gears that mesh with the first sun gear shaft SO1 and the first ring gear shaft HR1. The second planetary gear set PS2 also comprises three shafts, namely a second sun gear shaft SO2, a second ring gear shaft HR2 and a second planetary gear shaft ST2. The second planetary gear shaft ST2 carries a plurality of planet gears that mesh with the second sun gear shaft SO2 and the second ring gear shaft HR2.

[0035] The first electric machine EM1 is connected to the drive shaft An via a first spur gear stage SR1 and a second spur gear stage SR2. In this case, the first spur gear stage SR1 has a first spur gear S1 and a second spur gear S2, which mesh with each other. Furthermore, the second spur gear stage SR2 has a third spur gear S3 and a fourth spur gear S4, which mesh with each other. In this case, the first spur gear S1 is connected in a rotationally fixed manner to a rotor shaft of the first electric machine EM1, wherein the second and third spur gears S2, S3 are connected in a rotationally fixed manner, wherein the fourth spur gear S4 is connected in a rotationally fixed manner to the drive shaft An.

[0036] The second electric machine EM2 can be connected to the first ring gear shaft HR1 or to the drive shaft An via the third spur gear stage SR3 and the fourth spur gear stage SR4. Furthermore, the third spur gear stage SR3 has a fifth spur gear S5 and a sixth spur gear S6, which mesh with each other. The fourth spur gear stage SR4 has a seventh spur gear S7 and an eighth spur gear S8, which mesh with each other. The fifth spur gear S5 is here connected in a rotationally fixed manner to a rotor shaft of the second electric machine EM2, wherein the sixth and seventh spur gears S6, S7 are connected in a rotationally fixed manner, wherein the eighth spur gear S8 can be connected in a rotationally fixed manner to the first ring gear shaft HR1 or to the drive shaft An via the first switching unit. When the first switching element D is closed, the eighth spur gear S8 is connected in a rotationally fixed manner to the first ring gear shaft HR1.When the second shift element E is closed, the eighth spur gear S8 is non-rotatably connected to the input shaft An. The first shift unit is arranged radially nested with the first spur gear stage SR1 and the third spur gear stage SR3 to save axial space.

[0037] The input shaft An, the output shaft Ab, the manual transmission SG and the differential DG are arranged on a common axis of rotation R and are therefore coaxial with one another. The two electric machines EM1, EM2 are arranged axially parallel to the axis of rotation R. According to an axial sequence, the second planetary gear set PS2 is arranged axially adjacent to the differential DG, the first planetary gear set PS1 is arranged axially adjacent to the second planetary gear set PS2, the first switching unit is arranged axially adjacent to the first planetary gear set PS1, the fourth spur gear stage SR4 is arranged axially adjacent to the first switching unit, the second spur gear stage SR2 is arranged axially adjacent to the first spur gear stage SR1.

[0038] In a first switching position of the first sliding sleeve SM1, the first switching element D is closed, whereby the second electric machine EM2 is drivingly connected to the first ring gear shaft HR1. In a second switching position of the first sliding sleeve SM1, both switching elements D, E are opened, whereby the second electric machine EM2 is thereby decoupled from the manual transmission SG. In the present case, Fig. 2a shows this second switching position of the first sliding sleeve SM1. In a third switching position of the first sliding sleeve SM1, the second switching element E is closed and the second electric machine EM2 is drivingly connected to the drive shaft An.

[0039] The manual transmission SG further comprises a third shifting element B and a fourth shifting element C, wherein the third shifting element B and the fourth shifting element C are combined to form a second shifting unit. The two planetary gear sets PS1, PS2 are arranged axially adjacent to one another to save installation space and increase compactness. Furthermore, the second shifting unit is arranged radially stacked on a circumference of the first planetary gear set PS1 and is thus arranged at least partially in a common axial plane with the first planetary gear set PS1, thereby saving axial installation space.

[0040] The first sun gear shaft SO1, the second sun gear shaft SO2, and the input shaft An are connected in a rotationally fixed manner. The first carrier shaft ST1 and the second ring gear shaft HR2 are connected in a rotationally fixed manner. The second carrier shaft ST2 and the output shaft Ab are connected in a rotationally fixed manner. When the third shifting element B is closed, the first ring gear shaft HR1 is connected in a rotationally fixed manner to a stationary component designed as a housing G. When the fourth shifting element C is closed, the two planetary gear sets PS1, PS2 are blocked, with the second ring gear shaft HR2 and the first carrier shaft ST1 being connected in a rotationally fixed manner to the first ring gear shaft HR1.

[0041] The second shifting unit has a second sliding sleeve SM2 and three shift positions, namely two gear positions and a neutral position. The second sliding sleeve SM2 is arranged radially nested on the outer circumference of the first planetary gear set PS1 in order to save axial installation space and thereby increase axial compactness. The neutral position is arranged between the two gear positions. The three shift positions are achieved by axially shifting the second sliding sleeve SM2. The second sliding sleeve SM2 has dog shift elements and can be axially shifted into the respective shift position by means of a second actuator AK2. Thus, all three shift positions of the second shifting unit are arranged linearly. The two gears are shifted one after the other or sequentially by shifting the second sliding sleeve SM2 in an axial direction, beyond the neutral position.This not only saves weight and components, but also costs, installation space and assembly effort.

[0042] In the closed state of the third shifting element B, a first gear with a first ratio is engaged, wherein in the first gear the first ring gear shaft HR1 is connected in a rotationally fixed manner to the stationary component formed as a housing G. In the closed state of the fourth shifting element C, a second gear with a second ratio is engaged, wherein in the second gear the first ring gear shaft HR1 is connected in a rotationally fixed manner to the first carrier shaft ST1 and the second ring gear shaft HR2.

[0043] First gear is engaged when the second sliding sleeve SM2 is in a first gear position, i.e., in a first shift position. The third shift element B, in an actuated or closed state, i.e., in the first shift position of the second sliding sleeve SM2, connects the first ring gear shaft HR1 to the stationary component to shift first gear.

[0044] First gear is disengaged by axially shifting the second sliding sleeve SM2 into a neutral position, i.e., into a second shift position. In the second shift position of the second sliding sleeve SM2, the second sliding sleeve SM2 is only in rotational engagement with the first ring gear shaft HR1. In this neutral position, the shift elements B, C are open. In this case, Fig. 2 shows this second switching position of the second sliding sleeve SM2.

[0045] Second gear is engaged by axially shifting the second sliding sleeve SM2 into a second gear position, i.e., a third shift position. The fourth shift element C, in an actuated or closed state, i.e., in the third shift position of the second sliding sleeve SM2, connects the first ring gear shaft HR1 with the first carrier shaft ST1 and the second ring gear shaft HR2 to engage second gear.

[0046] Fig. 2b shows a switching matrix for the drive unit according to Fig. 2a. In the columns of the switching matrix, a respective state of the drive unit, the respective gear for the first electric machine EM1, the respective gear for the second electric machine EM2 and the four switching elements B, C, D, E of the drive unit are shown according to Fig. 2a. Depending on the switching position of the four switching elements B, C, D, and E, a total of eight states can be realized for the drive unit.

[0047] In a first state of the drive unit, the second switching element E and the third switching element B are closed, while the first switching element D and the fourth switching element C are open. As a result, a gear E2 is engaged for the first electric machine EM1 as well as for the second electric machine EM2.

[0048] In a second state of the drive unit, the second switching element E and the fourth switching element C are closed, while the first switching element D and the third switching element B are open. As a result, a gear E3 is engaged for the first electric machine EM1 as well as for the second electric machine EM2.

[0049] In a third state of the drive unit, the first shifting element D and the third shifting element B are closed, while the second shifting element E and the fourth shifting element C are open. As a result, a gear E2 is engaged for the first electric machine EM1, while the second electric machine EM2 is in an intermediate state. In this intermediate state, the second electric machine EM2 is locked.

[0050] In a fourth state of the drive unit, the first switching element D and the fourth switching element C are closed, while the second switching element E and the third switching element B are open. As a result, a gear E3 is engaged for the first electric machine EM1 as well as for the second electric machine EM2.

[0051] In a fifth state of the drive unit, only the first switching element D is closed, while the second switching element E, the third switching element B, and the fourth switching element C are open. This switches the first electric machine EM1 and the second electric machine EM2 to EDS mode. In EDS mode (electrodynamic switching), the two electric machines EM1 and EM2 are in speed-overlapping operation and mutually support their torque, with the torque ratio being fixed and the speed being variable.

[0052] In a sixth state of the drive unit, only the third switching element B is closed, while the first switching element D, the second switching element E, and the fourth switching element C are open. As a result, a gear E2 is engaged for the first electric machine EM1, while the second electric machine EM2 is decoupled from the drive train.

[0053] In a seventh state of the drive unit, only the fourth switching element C is closed, while the first switching element D, the second switching element E, and the third switching element B are open. As a result, a gear E3 is engaged for the first electric machine EM1, while the second electric machine EM2 is decoupled from the drive train.

[0054] In an eighth state of the drive unit, only the second switching element E is closed, while the first switching element D, the third switching element B, and the fourth switching element C are open. This decouples both electric motors EM1, EM2 from the drive train. Likewise, all switching elements B, C, D, and E can be open to decouple both electric motors EM1, EM2 from the drive train.

[0055] The shifting sequence with the load shift from gear E2 of the first electric machine EM1 to gear E3 of the first electric machine EM1 is described as an example. In the initial state, both electric machines EM1, EM2 have gear E2 (state 1 in the shift matrix). The second electric machine EM2 is recoupled via the first switching unit, whereby the second switching element E is opened and the first switching element D is closed. The second electric machine synchronizes the switching elements of the first switching unit. During the recoupling of the second electric machine EM2, the first electric machine EM1 can support the tractive force. The second electric machine EM2 is braked to a speed of zero. The third switching element B is relieved by the appropriate torque ratio of the first electric machine EM1 to the second electric machine EM2 and is then opened, whereby the fifth state according to the shift matrix is ​​reached.In the fifth state, both electric machines EM1, EM2 are in EDS mode, which is used for power shifting from gear E2 to gear E3. The speed of the first electric machine EM1 is synchronized to the level of the target gear E3, after which the fourth shifting element C is closed, whereby the fourth state according to the shift matrix is ​​reached. Both electric machines EM1, EM2 have the same speed because the first planetary gear set PS1 rotates in the block. The second electric machine EM2 can optionally be recoupled from the first shifting element D to the second shifting element E via the first shifting unit, whereby the speed of the second electric machine EM2 does not change. This state is useful, for example, if a traction-interrupted shift follows in gear E2 according to the first state, in which the second shifting element E remains closed.The fourth switching element C is opened, gear E2 is synchronized and the second switching element B is closed.

[0056] Fig. 3a shows a second embodiment of the drive unit according to the invention. The drive unit according to Fig. 3a essentially corresponds to the drive unit according to Fig. 2a, wherein a difference between these two embodiments lies in the design of the manual transmission SG. In the present case, the manual transmission SG has a third shifting element A' and a fourth shifting element B', which are combined in a second shifting unit. In a closed state of the third shifting element A', the second ring gear shaft HR2 and the first carrier shaft ST1 are rotationally fixedly connected to a stationary component designed as a housing G. In a closed state of the fourth shifting element B', the first ring gear shaft HR1 is rotationally fixedly connected to the stationary component designed as a housing G. Thus, the fourth shifting element B' according to Fig. 3a the third switching element B according to Fig. 2a. Otherwise, the embodiment corresponds to Fig. 3 the embodiment according to Fig. 2, to which reference is made.

[0057] Fig. 3b shows a switching matrix for the drive unit according to Fig. 3a. In the columns of the switching matrix, a respective state of the drive unit, the respective gear for the first electric machine EM1, the respective gear for the second electric machine EM2 and the four switching elements A', B', D, E of the drive unit are shown according to Fig. 2a. Depending on the switching position of the four switching elements A', B', D, and E, a total of eight states can be realized for the drive unit.

[0058] In a first state of the drive unit, the second shifting element E and the third shifting element A' are closed, while the first shifting element D and the fourth shifting element B' are open. As a result, a gear E1 is engaged for the first electric machine EM1 as well as for the second electric machine EM2.

[0059] In a second state of the drive unit, the second shifting element E and the fourth shifting element B' are closed, while the first shifting element D and the third shifting element A' are open. As a result, a gear E2 is engaged for the first electric machine EM1 as well as for the second electric machine EM2.

[0060] In a third state of the drive unit, the first shifting element D and the third shifting element A' are closed, while the second shifting element E and the fourth shifting element B' are open. As a result, a gear E1 is engaged for the first electric machine EM1, while the second electric machine EM2 is in an intermediate state. In this intermediate state, the second electric machine EM2 rotates in reverse.

[0061] In a fourth state of the drive unit, the first shifting element D and the fourth shifting element B' are closed, while the second shifting element E and the third shifting element A' are open. As a result, a gear E2 is engaged for the first electric machine EM1, while the second electric machine EM2 is in an intermediate state. In this intermediate state, the second electric machine EM2 is locked.

[0062] In a fifth state of the drive unit, only the first switching element D is closed, while the second switching element E, the third switching element A', and the fourth switching element B' are open. This switches the first electric machine EM1 and the second electric machine EM2 to EDS mode. In EDS mode (electrodynamic switching), the two electric machines EM1 and EM2 are in speed-overlapping operation and mutually support their torque, with the torque ratio being fixed and the speed being variable.

[0063] In a sixth state of the drive unit, only the third shift element A' is closed, while the first shift element D, the second shift element E, and the fourth shift element B' are open. As a result, a gear E1 is engaged for the first electric machine EM1, while the second electric machine EM2 is decoupled from the drive train.

[0064] In a seventh state of the drive unit, only the fourth shift element B' is closed, while the first shift element D, the second shift element E, and the third shift element A' are open. As a result, a gear E2 is engaged for the first electric machine EM1, while the second electric machine EM2 is decoupled from the drive train.

[0065] In an eighth state of the drive unit, only the second switching element E is closed, while the first switching element D, the third switching element A', and the fourth switching element B' are open. This decouples both electric motors EM1, EM2 from the drive train. Likewise, all switching elements A', B', D, and E can be open to decouple both electric motors EM1, EM2 from the drive train.

[0066] The gearshift sequence with the power shift from gear E1 of the first electric machine EM1 to gear E2 of the first electric machine EM1 is described as an example. In the initial state, both electric machines EM1, EM2 have gear E1 (state 1 in the shift matrix). The second electric machine EM2 is recoupled via the first shift unit, with the second shift element E being opened and the first shift element D being closed (state 3 in the shift matrix). The second electric machine EM2 synchronizes the shift elements of the first shift unit. While the second electric machine EM2 is being recoupled, the first electric machine EM1 can support the tractive force. The second electric machine EM2 has a fixed speed ratio to the output. In the third state, a mechanical gear with a lower gear ratio than the two gears E1, E2 acts for the second electric machine EM2.The third state could also serve as a driving state for an extended period of time, for example if there is an efficiency advantage, particularly if the second electric machine EM2 has a lower speed than the first electric machine EM1. The third switching element A' is relieved of load by the appropriate torque ratio of the first electric machine EM1 to the second electric machine EM2 and then opened, whereby the fifth state is reached according to the switching matrix. In the fifth state, both electric machines EM1, EM2 are in an EDS mode, which is used for powershifting from gear E1 to gear E2. In principle, longer driving in EDS mode is also possible. Both electric machines EM1, EM2 can, for example, have the same speed.This state is therefore also suitable for higher driving speeds, as the speed ratio of input to output corresponds to a direct gear when both planetary gear sets PS1, PS2 rotate in unison at the same speed of the electric machines EM1, EM2. The speed of the first electric machine EM1 is synchronized to the level of the target gear E2, after which the fourth shift element B' is closed, reaching the fourth state according to the shift matrix. The second electric machine EM2 is recoupled from the first shift element D to the second shift element E via the first shift unit, reaching the second state, with the second electric machine EM2 synchronizing the shift elements E, D of the first shift unit. While the second electric machine EM2 is being recoupled, the first electric machine EM1 can support the tractive force. The two electric machines EM1, EM2 are then in gear E2.

[0067] Fig. 4 shows a third embodiment of the drive unit according to the invention. The drive unit according to Fig. 4 essentially corresponds to the drive unit according to Fig. 2a, whereby a difference between these two embodiments lies in the arrangement and connection of the differential DG. In this case, the differential DG is connected to the output shaft Ab via a bevel gear stage KG and is thus arranged transversely to the manual transmission SG. The differential DG is, as in the embodiment according to Fig. 2a, it is also designed as a ball or bevel gear differential and has a differential input shaft D1 and two differential output shafts D2, D3. The differential input shaft D1 is designed as a differential cage and is non-rotatably connected to a bevel gear of the bevel gear stage KG, wherein the other bevel gear of the bevel gear stage KG is non-rotatably connected to the output shaft Ab, and wherein the two bevel gears are in meshing engagement. The manual transmission SG is arranged in the longitudinal direction of the vehicle, wherein the differential DG is arranged in the transverse direction of the vehicle. The output shaft Ab does not have to be designed as a hollow shaft and can in particular be designed as a solid shaft, since the second differential output shaft D3 is not passed through it. Otherwise, the embodiment according to Fig. 4 the embodiment according to Fig. 2a, to which reference is made.

[0068] Fig. Figure 5 shows a fourth embodiment of the drive unit according to the invention. The drive unit according to Fig. 5 essentially corresponds to the drive unit according to Fig. 2a, wherein one difference between these two embodiments lies in the design of the manual transmission SG. In the present case, the manual transmission SG has a third shifting element A'', a fourth shifting element B'', and a fifth shifting element C'', which are combined in a second shifting unit.

[0069] In a closed state of the third switching element A'', the second ring gear shaft HR2 and the first carrier shaft ST1 are connected in a rotationally fixed manner to a stationary component designed as a housing G. Thus, the third switching element A'' corresponds to Fig. 5 the third switching element A' according to Fig. 3a. In a closed state of the fourth switching element B'', the first ring gear shaft HR1 is connected in a rotationally fixed manner to the stationary component designed as a housing G. Thus, the fourth switching element B'' corresponds to Fig. 5 the third switching element B according to Fig. 2a. In a closed state of the fifth shifting element C'', the second ring gear shaft HR2 and the first carrier shaft ST1 are connected in a rotationally fixed manner to the first ring gear shaft HR1. Thus, the fifth shifting element C'' corresponds to Fig. 5 the fourth switching element C according to Fig. 2a. The switching matrices according to Fig. 2b and Fig. 3b can be combined (combined set). Three gears, E1, E2, and E3, are available for the two electric motors EM1 and EM2 with EDS powershift function.

[0070] The second shift unit has five shift positions, namely three gear positions and two neutral positions. The respective neutral position is located between two respective gear positions. The five shift positions are achieved by axially displacing the second sliding sleeve SM2. The second sliding sleeve SM2 has claw shift elements and can be axially displaced into the respective shift position by means of the second actuator AK2. Thus, all five shift positions of the second shift unit are arranged linearly. The three gears are shifted one after the other or sequentially by displacing the second sliding sleeve SM2 in an axial direction, via the neutral positions. This not only saves weight and components, but also costs, installation space, and assembly effort.

[0071] When the third shift element A'' is closed, a first gear with a first ratio is engaged. When the fourth shift element B'' is closed, a second gear with a second ratio is engaged. When the fifth shift element C'' is closed, a third gear with a third ratio is engaged.

[0072] The first gear is engaged when the second sliding sleeve SM2 is in a first gear position, i.e., in a first switching position. The third switching element A'' connects, in an actuated or closed state, i.e., in the first switching position of the second sliding sleeve SM2, the first carrier shaft ST1 and the second ring gear shaft HR2 with the stationary component in order to engage the first gear. In the present case, Fig. 5 shows this first switching position of the second sliding sleeve SM2.

[0073] First gear is disengaged by axially shifting the second sliding sleeve SM2 into a first neutral position, i.e., a second shift position. In the second shift position of the second sliding sleeve SM2, the second sliding sleeve SM2 is only in rotational engagement with the stationary component. In this neutral position, the shift elements A'', B'', C'' are open, so that no gear is engaged and a target gear can be synchronized.

[0074] Second gear is engaged by axially shifting the second sliding sleeve SM2 into a second gear position, i.e., a third shift position. The fourth shift element B'' connects the first ring gear shaft HR1 to the stationary component in an actuated or closed state, i.e., in the third shift position of the second sliding sleeve SM2, to engage the second gear.

[0075] Second gear is disengaged by axially shifting the second sliding sleeve SM2 into a second neutral position, i.e., a fourth shift position. In the fourth shift position of the second sliding sleeve SM2, the second sliding sleeve SM2 is only in rotational engagement with the first ring gear shaft HR1. In this neutral position, the shift elements A'', B'', C'' are open, so that no gear is engaged and a target gear can be synchronized.

[0076] Third gear is engaged by axially shifting the second sliding sleeve SM2 into a third gear position, i.e., a fifth shift position. When the second sliding sleeve SM2 is in the fifth shift position, the fifth shift element C'' connects the first ring gear shaft HR1, the second ring gear shaft HR2, and the first carrier shaft ST1 to shift third gear. This interlocks the two planetary gear sets PS1 and PS2. Consequently, the two planetary gear sets PS1 and PS2 rotate as a single unit.

[0077] Therefore, only the second sliding sleeve SM2 and the second actuator AK2 are required to shift the three mechanical gears. Otherwise, the embodiment according to Fig. 5 the embodiment according to Fig. 2a, to which reference is made.

[0078] Fig. Figure 6 shows a fifth embodiment of the drive unit according to the invention. The drive unit according to Fig. 6 essentially corresponds to the drive unit according to Fig. 2a, wherein one difference between these two embodiments lies in the design of the manual transmission SG. The manual transmission SG also has two planetary gear sets PS1, PS2 and a second shifting unit with three shifting elements A''', B''', C'''. The first sun gear shaft SO1 and the input shaft An are connected in a rotationally fixed manner. The first carrier shaft ST1 and the second sun gear shaft SO2 are connected in a rotationally fixed manner. The second carrier shaft ST2 and the output shaft Ab are connected in a rotationally fixed manner. The second ring gear shaft HR2 is connected in a rotationally fixed manner to a stationary component designed as a housing G. The first ring gear shaft HR1 is connected to the second electric machine EM2 when the first shifting element D is closed. The first ring gear shaft HR1 is connected in a rotationally fixed manner to the stationary component when the third shifting element A''' is closed.When the fourth shifting element B''' is closed, the first ring gear shaft HR1 is rotationally fixedly connected to the second carrier shaft ST2 and the output shaft Ab. When the fifth shifting element C''' is closed, the first ring gear shaft HR1 is rotationally fixedly connected to the second sun shaft SO2 and the first carrier shaft ST1. During a load shift, only the first shifting element D is closed. In comparison to the embodiment according to . Fig. 2a, the manual transmission SG provides a higher gear ratio, so that further gear ratios are not necessary. Otherwise, the embodiment according to Fig. 6 the embodiment according to Fig. 2a, to which reference is made.

[0079] Fig. Figure 7 shows a sixth embodiment of the drive unit according to the invention. The drive unit according to Fig. 7 essentially corresponds to the drive unit according to Fig. 6, whereby a difference between these two embodiments lies in the design of the second switching unit. In the present case, the second switching unit has two switching elements B*, C*. In a closed state of the third switching element B*, the output shaft Ab, the second carrier shaft ST2 and the first ring gear shaft HR1 are connected in a rotationally fixed manner. Thus, the third switching element B* corresponds to Fig. 7 the fourth switching element B''' according to Fig. 6. In a closed state of the fourth switching element C*, the first ring gear shaft HR1, the first carrier shaft ST1 and the second sun shaft SO2 are connected in a rotationally fixed manner. Therefore, the fourth switching element C* corresponds to Fig. 7 the fifth switching element C''' according to Fig. 6. Opposite Fig. 7, the switching element A''' has been omitted. This embodiment is particularly suitable for vehicles with a lower vehicle weight. Otherwise, the embodiment according to Fig. 7 the embodiment according to Fig. 6, to which reference is made.

[0080] Fig. Figure 8 shows a seventh embodiment of the drive unit according to the invention. The drive unit according to Fig. 8 essentially corresponds to the drive unit according to Fig. 7, wherein one difference between these two embodiments lies in the design of the manual transmission SG. The manual transmission SG also has two planetary gear sets PS1, PS2 and a second switching unit with two switching elements B**, C**. The first sun gear shaft SO1 and the input shaft An are connected in a rotationally fixed manner. The first carrier shaft ST1 and the second sun gear shaft SO2 are connected in a rotationally fixed manner, wherein the first carrier shaft ST1 and the second sun gear shaft SO2 are connected to the second electric machine EM2 when the first switching element D is closed. The second carrier shaft ST2 and the output shaft Ab are connected in a rotationally fixed manner. The second ring gear shaft HR2 is connected in a rotationally fixed manner to a stationary component designed as a housing G. The first ring gear shaft HR1 is connected in a rotationally fixed manner to the second carrier shaft ST2 and the output shaft Ab when the third switching element B** is closed.When the fourth shifting element C** is closed, the first ring gear shaft HR1 is connected in a rotationally fixed manner to the second sun shaft SO2 and the first carrier shaft ST1. When the first shifting element D is closed, the second electric machine EM2 is connected to the output independently of the second shifting unit and can thus support the tractive force (electromotive shift), while the shifting elements of the second shifting unit can be switched over without load, with the first electric machine EM1 synchronizing the second shifting unit. The third shifting element B** and the fourth shifting element C** are arranged together on one side of the first planetary gear set PS1. Otherwise, the exemplary embodiment corresponds to that shown in FIG. Fig. 8 the embodiment according to Fig. 7, to which reference is made.

[0081] Fig. Figure 9 shows an eighth embodiment of the drive unit according to the invention. The drive unit according to Fig. 9 essentially corresponds to the drive unit according to Fig. 8, whereby one difference between these two embodiments is the arrangement of the second switching unit. The third switching element B** is arranged on one side of the first planetary gear set PS1, and the fourth switching element C** is arranged on the opposite side of the first planetary gear set PS1. This can result in design advantages. Otherwise, the embodiment according to Fig. 9 the embodiment according to Fig. 8, to which reference is made.

[0082] Fig. Figure 10 shows a ninth embodiment of the drive unit according to the invention. The drive unit according to Fig. 10 essentially corresponds to the drive unit according to Fig. 6, whereby a difference between these two embodiments lies in the connection of the manual transmission SG. In the present case, the first switching element D, when closed, connects the eighth spur gear S8 to the first carrier shaft ST1 and the second sun shaft SO2. When the first switching element D is closed, the second electric machine EM2 is connected to the output independently of the switching elements A''', B''', C''' of the second switching unit and can thus support the tractive force, while the switching elements A''', B''', C''' of the second switching unit can be switched load-free, with the first electric machine EM1 synchronizing them. Otherwise, the embodiment according to Fig. 10 the embodiment according to Fig. 6, to which reference is made.

[0083] Fig. 11 shows a tenth embodiment of the drive unit according to the invention. The drive unit according to Fig. 11 essentially corresponds to the drive unit according to Fig. 2a, wherein one difference between these two embodiments lies in the design of the manual transmission SG. In the present case, the manual transmission SG only has a first planetary gear set PS1, a third shifting element A1 and a fourth shifting element C1. The third shifting element A1 and the fourth shifting element C1 are combined in a second shifting unit. When the third shifting element A1 is closed, the first ring gear shaft HR1 is rotationally fixedly connected to a stationary component designed as a housing G. When the fourth shifting element C1 is closed, the first ring gear shaft HR1 is rotationally fixedly connected to the first carrier shaft ST1 and the output shaft Ab. Furthermore, the first shifting element D, in the closed state, connects the eighth spur gear S8 to the first carrier shaft ST1 and the output shaft Ab.When the first switching element D is closed, the second electric machine EM2 is connected to the output independently of the second switching unit. Otherwise, the embodiment corresponds to FIG. Fig. 11 the embodiment according to Fig. 2a, to which reference is made.

[0084] Fig. 12 shows an eleventh embodiment of the drive unit according to the invention. The drive unit according to Fig. 12 essentially corresponds to the drive unit according to Fig. 2a, wherein a difference between these two embodiments lies in the design of the manual transmission SG. In the present case, the manual transmission SG has only a first planetary gear set PS1, a third shifting element A2, and a fourth shifting element C2. The third shifting element A2 and the fourth shifting element C2 are combined in a second shifting unit. In a closed state of the third shifting element A2, the first ring gear shaft HR1 is rotationally fixedly connected to a stationary component designed as a housing G. In a closed state of the fourth shifting element C2, the first ring gear shaft HR1 is rotationally fixedly connected to the first carrier shaft ST1 and the output shaft Ab. Furthermore, the first shifting element D, in the closed state, connects the eighth spur gear S8 to the first ring gear shaft HR1. Otherwise, the embodiment according to Fig. 12 the embodiment according to Fig. 2a, to which reference is made. Reference symbol 100 vehicles 101 first axis 102 second axis R1 vehicle wheel R2 vehicle wheel R3 vehicle wheel R4 vehicle wheel On drive shaft From output shaft SG manual transmission EM1 first electric machine EM2 second electric machine ST1 first spur gear stage ST2 second spur gear stage ST3 third spur gear stage ST4 fourth spur gear stage S1 first spur gear S2 second spur gear S3 third spur gear S4 fourth spur gear S5 fifth spur gear S6 sixth spur gear S7 seventh spur gear S8 eighth spur gear PS1 first planetary gear set SO1 first solar wave HO1 first ring gear shaft ST1 first bridge wave PS2 second planetary gear set SO2 second solar wave HO2 second ring gear shaft ST2 second web wave AK1 first actuator AK2 second actuator SM1 first sliding sleeve SM2 second sliding sleeve G Housing R rotation axis KG bevel gear stage DG Differential D1 differential input shaft D2 first differential output shaft D3 second differential output shaft D first switching element E second switching element A1, A2, B, A', B*, B**, A'', A''' third switching element C1, C2, C, B', C*, C**, B'', B''' fourth switching element C'', C''' fifth switching element QUOTES CONTAINED IN THE DESCRIPTION

[0000] This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions. Cited patent literature

[0000] DE 10 2013 214 238 A1

[0002]

Claims

[1] Drive unit for a vehicle (100), comprising • a first electrical machine (EM1), • a second electrical machine (EM2) arranged parallel to the axis, • a manual transmission (SG) arranged axially parallel to the two electric machines (EM1, EM2) with several gears and at least one first planetary gear set (PS1), which has a first sun shaft (SO1), a first ring gear shaft (HR1) and a first carrier shaft (ST1), • a differential (DG) with one differential input shaft (D1) and two differential output shafts (D2, D3), • a drive shaft (An) for connecting the first electric machine (EM1) to the manual transmission (SG), • an output shaft (Ab) for connecting the manual transmission (SG) to the differential (DG), • a first positive-locking switching unit with a first switching element (D), a second switching element (E) and a first sliding sleeve (SM1), which can be moved into one of three switching positions by means of a first actuator (AK1), • wherein in a first switching position of the first sliding sleeve (SM1) the first switching element (D) is closed and the second electric machine (EM2) is drivingly connected to a shaft of the first planetary gear set (PS1), • wherein in a second switching position of the first sliding sleeve (SM1) both switching elements (D, E) are open and the second electric machine (EM2) is decoupled from the manual transmission (SG), • wherein in a third switching position of the first sliding sleeve (SM1) the second switching element (E) is closed and the second electric machine (EM2) is drivingly connected to the drive shaft (An), • wherein the first electric machine (EM1) is connected to the drive shaft (An) via a first spur gear stage (SR1) and a second spur gear stage (SR2), • wherein the second electric machine (EM2) can be connected to a shaft of the first planetary gear set (PS1) or to the drive shaft (An) via a third spur gear stage (SR3) and a fourth spur gear stage (SR4), • wherein the first switching unit is arranged radially nested with the first spur gear stage (SR1) and the third spur gear stage (SR3). [2] Drive unit according to claim 1, wherein the manual transmission (SG) further comprises a third switching element (A1) and a fourth switching element (C1), • the first sun shaft (SO1) and the drive shaft (An) are connected in a rotationally fixed manner, • wherein the first web shaft (ST1) and the output shaft (Ab) are connected in a rotationally fixed manner and are connected to the second electrical machine (EM2) when the first switching element (D) is closed, • wherein the first ring gear shaft (HR1) is connected in a rotationally fixed manner to a stationary component in the closed state of the third switching element (A1) and is connected in a rotationally fixed manner to the output shaft (Ab) and the first web shaft (ST1) in the closed state of the fourth switching element (C1). [3] Drive unit according to claim 1, wherein the manual transmission (SG) further comprises a third switching element (A2) and a fourth switching element (C2), • the first sun shaft (SO1) and the drive shaft (An) are connected in a rotationally fixed manner, • the first carrier shaft (ST1) and the output shaft (Ab) are connected in a rotationally fixed manner, • wherein the first ring gear shaft (HR1) is connected to the second electrical machine (EM2) in the closed state of the first switching element (D), is connected in a rotationally fixed manner to a stationary component in the closed state of the third switching element (A2) and is connected in a rotationally fixed manner to the output shaft (Ab) and the first web shaft (ST1) in the closed state of the fourth switching element (C2). [4] Drive unit according to claim 1, wherein the manual transmission (SG) further comprises a second planetary gear set (PS2), a third shifting element (B) and a fourth shifting element (C), • wherein the second planetary gear set (PS2) comprises a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2), • wherein the first sun shaft (SO1), the second sun shaft (SO2) and the drive shaft (An) are connected in a rotationally fixed manner, • wherein the first carrier shaft (ST1) and the second ring gear shaft (HR2) are connected in a rotationally fixed manner, • the second carrier shaft (ST2) and the output shaft (Ab) are connected in a rotationally fixed manner, • wherein the first ring gear shaft (HR1) is connected to the second electrical machine (EM2) in the closed state of the first switching element (D), is connected in a rotationally fixed manner to a stationary component in the closed state of the third switching element (B), and is connected in a rotationally fixed manner to the second ring gear shaft (HR2) and the first web shaft (ST1) in the closed state of the fourth switching element (C). [5] Drive unit according to claim 1, wherein the manual transmission (SG) further comprises a second planetary gear set (PS2), a third shift element (A') and a fourth shift element (B'), • wherein the second planetary gear set (PS2) comprises a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2), • wherein the first sun shaft (SO1), the second sun shaft (SO2) and the drive shaft (An) are connected in a rotationally fixed manner, • wherein the first carrier shaft (ST1) and the second ring gear shaft (HR2) are connected in a rotationally fixed manner and are connected in a rotationally fixed manner to a stationary component in the closed state of the third switching element (A'), • the second carrier shaft (ST2) and the output shaft (Ab) are connected in a rotationally fixed manner, • wherein the first ring gear shaft (HR1) is connected to the second electrical machine (EM2) in the closed state of the first switching element (D) and is connected in a rotationally fixed manner to the stationary component in the closed state of the fourth switching element (B'). [6] Drive unit according to claim 1, wherein the manual transmission (SG) further comprises a second planetary gear set (PS2), a third shift element (B*) and a fourth shift element (C*), • wherein the second planetary gear set (PS2) comprises a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2), • the first sun shaft (SO1) and the drive shaft (An) are connected in a rotationally fixed manner, • the first web shaft (ST1) and the second sun shaft (SO2) are connected in a rotationally fixed manner, • the second carrier shaft (ST2) and the output shaft (Ab) are connected in a rotationally fixed manner, • wherein the second ring gear shaft (HR2) is connected to a stationary component in a rotationally fixed manner, • wherein the first ring gear shaft (HR1) is connected to the second electrical machine (EM2) in the closed state of the first switching element (D), is connected in a rotationally fixed manner to the second carrier shaft (ST2) and the output shaft (Ab) in the closed state of the third switching element (B*), and is connected in a rotationally fixed manner to the second sun shaft (SO2) and the first carrier shaft (ST1) in the closed state of the fourth switching element (C*). [7] Drive unit according to claim 1, wherein the manual transmission (SG) further comprises a second planetary gear set (PS2), a third shifting element (B**) and a fourth shifting element (C**), • wherein the second planetary gear set (PS2) comprises a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2), • the first sun shaft (SO1) and the drive shaft (An) are connected in a rotationally fixed manner, • wherein the first web shaft (ST1) and the second sun shaft (SO2) are connected in a rotationally fixed manner and are connected to the second electrical machine (EM2) in the closed state of the first switching element (D), • the second carrier shaft (ST2) and the output shaft (Ab) are connected in a rotationally fixed manner, • wherein the second ring gear shaft (HR2) is connected to a stationary component in a rotationally fixed manner, • wherein the first ring gear shaft (HR1) is connected in a rotationally fixed manner to the second carrier shaft (ST2) and the output shaft (Ab) in the closed state of the third switching element (B**) and is connected in a rotationally fixed manner to the second sun shaft (SO2) and the first carrier shaft (ST1) in the closed state of the fourth switching element (C**). [8] Drive unit according to one of claims 2 to 7, wherein the third switching element (A1, A2, B, A', B*, B**) and the fourth switching element (C1, C2, C, B', C*, C**) are combined to form a second positive switching unit with an axially displaceable second sliding sleeve (SM2), wherein the second sliding sleeve (SM2) is displaceable into a respective one of three switching positions by means of a second actuator (AK2). [9] Drive unit according to claim 1, wherein the manual transmission (SG) further comprises a second planetary gear set (PS2), a third shifting element (A''), a fourth shifting element (B'') and a fifth shifting element (C''), • wherein the second planetary gear set (PS2) comprises a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2), • wherein the first sun shaft (SO1), the second sun shaft (SO2) and the drive shaft (An) are connected in a rotationally fixed manner, • wherein the first carrier shaft (ST1) and the second ring gear shaft (HR2) are connected in a rotationally fixed manner and are connected in a rotationally fixed manner to a stationary component in the closed state of the third switching element (A''), • the second carrier shaft (ST2) and the output shaft (Ab) are connected in a rotationally fixed manner, • wherein the first ring gear shaft (HR1) is connected to the second electrical machine (EM2) in the closed state of the first switching element (D), is connected in a rotationally fixed manner to the stationary component in the closed state of the fourth switching element (B''), and is connected in a rotationally fixed manner to the second ring gear shaft (HR2) and the first web shaft (ST1) in the closed state of the fifth switching element (C''). [10] Drive unit according to claim 1, wherein the manual transmission (SG) further comprises a second planetary gear set (PS2), a third shifting element (A'''), a fourth shifting element (B''') and a fifth shifting element (C'''), • wherein the second planetary gear set (PS2) comprises a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2), • the first sun shaft (SO1) and the drive shaft (An) are connected in a rotationally fixed manner, • the first web shaft (ST1) and the second sun shaft (SO2) are connected in a rotationally fixed manner, • the second carrier shaft (ST2) and the output shaft (Ab) are connected in a rotationally fixed manner, • wherein the second ring gear shaft (HR2) is connected to a stationary component in a rotationally fixed manner, • wherein the first ring gear shaft (HR1) is connected to the second electrical machine (EM2) in the closed state of the first switching element (D), is connected in a rotationally fixed manner to the stationary component in the closed state of the third switching element (A'''), is connected in a rotationally fixed manner to the second carrier shaft (ST2) and the output shaft (Ab) in the closed state of the fourth switching element (B'''), and is connected in a rotationally fixed manner to the second sun shaft (SO2) and the first carrier shaft (ST1) in the closed state of the fifth switching element (C'''). [11] Drive unit according to claim 1, wherein the manual transmission (SG) further comprises a second planetary gear set (PS2), a third shifting element (A'''), a fourth shifting element (B''') and a fifth shifting element (C'''), • wherein the second planetary gear set (PS2) comprises a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2), • the first sun shaft (SO1) and the drive shaft (An) are connected in a rotationally fixed manner, • wherein the first web shaft (ST1) and the second sun shaft (SO2) are connected in a rotationally fixed manner and are connected to the second electrical machine (EM2) in the closed state of the first switching element (D), • the second carrier shaft (ST2) and the output shaft (Ab) are connected in a rotationally fixed manner, • wherein the second ring gear shaft (HR2) is connected to a stationary component in a rotationally fixed manner, • wherein the first ring gear shaft (HR1) is connected in a rotationally fixed manner to the stationary component in the closed state of the third switching element (A'''), is connected in a rotationally fixed manner to the second carrier shaft (ST2) and the output shaft (Ab) in the closed state of the fourth switching element (B'''), and is connected in a rotationally fixed manner to the second sun shaft (SO2) and the first carrier shaft (ST1) in the closed state of the fifth switching element (C'''). [12] Drive unit according to one of claims 9 to 11, wherein the third switching element (A'', A'''), the fourth switching element (B'', B''') and the fifth switching element (C'', C''') are combined to form a second positive switching unit with an axially displaceable second sliding sleeve (SM2), wherein the second sliding sleeve (SM2) is displaceable into a respective one of five switching positions by means of a second actuator (AK2). [13] Drive unit according to one of the preceding claims, wherein the differential (DG) is arranged coaxially to the manual transmission (SG) and the third differential output shaft (D3) is guided axially through the manual transmission (SG), wherein the differential input shaft (D1) is connected to the output shaft (Ab) in a rotationally fixed manner. [14] Drive unit according to one of claims 1 to 12, wherein the differential (DG) is arranged transversely to the manual transmission (SG) and the differential input shaft (D1) is connected to the output shaft (Ab) via a bevel gear stage (KG). [15] Vehicle (100) comprising at least one drive unit according to one of the preceding claims.

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