Drive unit for vehicle

Abstract

The invention relates to a drive unit for a vehicle. The drive unit comprises an electric machine and a switching transmission having a first switching element, a second switching element, a third switching element and two planetary sets coupled to each other, the first planetary set having a first sun shaft, a first ring gear shaft and a first carrier shaft, the second planetary set having a second sun shaft, a second ring gear shaft and a second carrier shaft, the second sun shaft can be driven by a motor, the second gear ring shaft is connected to the first carrier shaft in a rotationally fixed manner, the first sun shaft is connected to a stationary component in a rotationally fixed manner, and the first shift element fixes the first planetary group in an actuated state in order to shift the first gear. In the actuated state, a second shift element connects the first ring gear shaft to the second carrier shaft in a rotationally fixed manner in order to shift the second gear, and in the actuated state, a third shift element connects the first ring gear shaft to the second sun shaft in a rotationally fixed manner in order to shift the third gear.

Description

Technical Field

[0001] The invention relates to a drive unit for a vehicle, wherein the drive unit has a single electric motor and a shift transmission device with a plurality of gears. The invention also relates to a vehicle having such a drive unit. Background Art

[0002] For example, DE 10 2019 206 961 A1 discloses a drive unit for an electric vehicle, the drive unit comprising an electric motor and a two-speed switching transmission, the two-speed switching transmission having a first switching element, a second switching element and two planetary sets coupled to each other. The first planetary set comprises a first sun shaft, a first ring gear shaft and a first carrier shaft. The second planetary set comprises a second sun shaft, a second ring gear shaft and a second carrier shaft. The first ring gear shaft is fixedly connected to the second carrier shaft. The first sun shaft can be driven by an electric motor. The second sun shaft is stationary. The first carrier shaft forms a transmission driven shaft of the two-speed switching transmission. The first switching element A can be operated to switch the first gear. The second switching element can be operated to switch the second gear. Summary of the invention

[0003] The object of the invention is to provide an alternative drive unit for a vehicle, in which the number of gears is to be increased. In addition, the drive unit is to be designed in a particularly compact and energy-efficient manner. This object is achieved by a drive unit having the features of the independent patent claims 1, 2, 3 and 4, respectively. Advantageous embodiments are the subject of the dependent claims, the following description and the illustrations.

[0004] The drive unit for a vehicle according to the present invention comprises an electric motor and a switching transmission, wherein the switching transmission has at least a first switching element, a second switching element, a third switching element and two planetary groups coupled to each other, wherein the first planetary group has a first sun shaft, a first ring gear shaft and a first carrier shaft, wherein the second planetary group comprises a second sun shaft, a second ring gear shaft and a second carrier shaft, wherein the second sun shaft can be driven by the electric motor, in particular connected to the drive shaft in a rotationally fixed manner, wherein the second carrier shaft is established as a driven end of the switching transmission, in particular connected to the driven shaft in a rotationally fixed manner. A shaft connection, wherein the second ring gear shaft is non-rotatably connected to the first carrier shaft, wherein the first sun shaft is non-rotatably connected to a stationary component, wherein the first shift element, in an actuated state, connects the first ring gear shaft to the first carrier shaft in a non-rotatable manner to shift the first gear, wherein the second shift element, in an actuated state, connects the first ring gear shaft to the second carrier shaft in a non-rotatable manner to shift the second gear, wherein the third shift element, in an actuated state, connects the first ring gear shaft to the second sun shaft in a non-rotatable manner to shift the third gear. For this purpose, reference is made to Figure 2 implementation method.

[0005] Another drive unit for a vehicle according to the present invention includes an electric motor and a switching transmission, the switching transmission having at least a first switching element, a second switching element, a third switching element and two planetary groups coupled to each other, wherein the first planetary group has a first sun shaft, a first ring gear shaft and a first carrier shaft, wherein the second planetary group includes a second sun shaft, a second ring gear shaft and a second carrier shaft, wherein the second sun shaft can be driven by the electric motor, in particular, connected to the drive shaft in a rotationally fixed manner, wherein the second carrier shaft is established as a driven end of the switching transmission, in particular, connected to the driven shaft in a rotationally fixed manner. The first sun shaft is connected to a driven shaft, wherein the second ring gear shaft is connected to the first carrier shaft in a rotationally fixed manner, wherein the first sun shaft is connected to a stationary component in a rotationally fixed manner, wherein the first shift element, when operated, connects the first ring gear shaft to the stationary component in a rotationally fixed manner to shift the first gear, wherein the second shift element, when operated, connects the first ring gear shaft to the second carrier shaft in a rotationally fixed manner to shift the second gear, wherein the third shift element, when operated, connects the first ring gear shaft to the second sun shaft in a rotationally fixed manner to shift the third gear. For this purpose, reference is made to Figure 3 implementation method.

[0006] Another drive unit for a vehicle according to the present invention includes an electric motor and a switching transmission, the switching transmission having at least a first switching element, a second switching element, a third switching element, a fourth switching element and two planetary groups coupled to each other, wherein the first planetary group has a first sun shaft, a first ring gear shaft and a first carrier shaft, wherein the second planetary group has a second sun shaft, a second ring gear shaft and a second carrier shaft, wherein the second sun shaft can be driven by the electric motor, in particular, connected to the drive shaft in a rotationally fixed manner, wherein the second carrier shaft is established as a driven end of the switching transmission, in particular, connected to the driven shaft in a rotationally fixed manner, wherein the second ring gear shaft is rotationally fixed to the first carrier shaft Relative rotation is connected, wherein the first sun shaft is non-rotatably connected to the stationary component, wherein the first shift element, in an actuated state, connects the first ring gear shaft to the stationary component in a non-rotatable manner so as to shift the first gear, wherein the second shift element, in an actuated state, connects the first ring gear shaft to the second carrier shaft in a non-rotatable manner so as to shift the second gear, wherein the third shift element, in an actuated state, connects the first ring gear shaft to the second sun shaft in a non-rotatable manner so as to shift the third gear, wherein the fourth shift element, in an actuated state, connects the first carrier shaft to the second sun shaft in a non-rotatable manner so as to shift the fourth gear. For this purpose, reference is made to Figure 4 implementation method.

[0007] Another drive unit for a vehicle according to the present invention includes an electric motor and a switching transmission, the switching transmission having at least a first switching element, a second switching element, a third switching element, a fourth switching element and two planetary groups coupled to each other, wherein the first planetary group has a first sun shaft, a first ring gear shaft and a first carrier shaft, wherein the second planetary group has a second sun shaft, a second ring gear shaft and a second carrier shaft, wherein the second sun shaft can be driven by the electric motor, in particular, connected to the drive shaft in a rotationally fixed manner, wherein the second carrier shaft is established as a driven end of the switching transmission, in particular, connected to the driven shaft in a rotationally fixed manner, wherein the second ring gear shaft is connected to the first The carrier shaft is connected in a rotationally fixed manner, wherein the first sun shaft is connected in a rotationally fixed manner to a stationary component, wherein the first shift element, in an actuated state, connects the first ring gear shaft in a rotationally fixed manner to the stationary component, wherein the second shift element, in an actuated state, connects the first ring gear shaft in a rotationally fixed manner to the second carrier shaft in order to shift the second gear, wherein the third shift element, in an actuated state, connects the first ring gear shaft in a rotationally fixed manner to the second sun shaft in order to shift the third gear, wherein the fourth shift element, in an actuated state, connects the second carrier shaft in a rotationally fixed manner to the second sun shaft in order to shift the fourth gear. For this purpose, reference is made to Fig.10 implementation method.

[0008] The switching transmission enables the connection of a single electric motor for the purpose of introducing drive power via a drive shaft. The switching transmission is connected to a differential or a wheel drivingly via a driven shaft. The drive end of the switching transmission is realized via a second sun shaft, wherein the driven end is realized via a second carrier shaft. The second sun shaft is connected to the electric motor drivingly. The second carrier shaft is connected to at least one wheel drivingly. For example, a single drive unit is used in an electric drive axle for an electric vehicle, wherein the driven shaft is then connected to the differential drivingly. Alternatively, two drive units are used in an electric drive axle for an electric vehicle, wherein the respective driven shaft is then connected to the respective wheel drivingly of the drive axle. The switching transmission has three or four gears, which are switched by means of a switching element, thereby providing high energy efficiency for the electric vehicle.

[0009] Actuation of the first shift element can be used to shift the first gear. Actuation of the second shift element can be used to shift the second gear. Actuation of the third shift element can be used to shift the third gear. Actuation of the fourth shift element can be used to shift the fourth gear.

[0010] A "switching element" is understood to be a switchable device which, in the closed state, connects two shafts to one another or to a stationary component in a rotationally fixed manner, and in the open state, decouples the two shafts from one another or to a stationary component. The two shafts can then rotate relative to one another. A "stationary component" is understood to be a component which is stationarily fixed, in particular connected to a part of a housing in a rotationally fixed manner or in one piece. The switching element is designed as a shifting element and is therefore designed to shift gears.

[0011] Within the scope of the present invention, an "axis" is understood to be a rotatable component of a transmission, via which the respective components of the transmission are connected to one another in a rotationally fixed manner, or via which such a connection can be established when one of the switching elements is actuated. The respective axis can connect the components to one another axially or radially or also both axially and radially. Thus, the respective axis can also be present as an intermediate piece, via which the respective components are connected radially, for example. The term "axis" does not exclude that the components to be connected can be embodied in one piece. In particular, two or more axes that are connected to one another in a rotationally fixed manner can be designed in one piece.

[0012] According to a preferred embodiment, all the shifting elements are designed as positive-locking shifting elements. For example, the positive-locking shifting elements are designed as dog clutches. The positive-locking shifting elements can increase the efficiency of the drive unit due to reduced drag losses. In particular, compared with friction-locking shifting elements, positive-locking shifting elements are designed to be more compact and efficiency-optimized and have cost advantages.

[0013] According to a preferred embodiment, the first switching element, the second switching element and the third switching element are combined to form a switching unit with five switching positions, wherein the switching unit has a single sleeve that can be axially displaced. The sleeve can be axially displaced into the respective switching positions by means of a single actuator. Preferably, the sleeve is arranged on the first ring gear shaft in a rotationally fixed manner in all five switching positions. Preferably, the switching device has a neutral position between two gear positions, so that three gear positions and two neutral positions are provided in the case of five switching positions. In the neutral position, the two shafts are decoupled from each other via the switching unit.

[0014] According to a preferred embodiment, the first switching element, the second switching element, the third switching element and the fourth switching element form a switching unit with seven switching positions, wherein the switching unit has a single sleeve that can be axially displaced. The sleeve can be axially displaced into the respective switching position by means of a single actuator. Preferably, the switching device has a neutral position between two gear positions, so that in the case of seven switching positions, four gear positions and three neutral positions are provided.

[0015] In particular, a single actuator moves the sleeve into the respective shift position and thus sequentially shifts up to four gears. Preferably, the sleeve preferably has form-locking claws, which in the respective gear position cooperate in a form-locking manner with the respective corresponding claw tooth engagement in order to establish a rotationally fixed connection between two shafts or between a shaft and a housing. The respective claw tooth engagement that cooperates in a form-locking manner with the sleeve is therefore understood to be a shift element. In particular, the sleeve is arranged axially between two gear positions in the respective neutral position, so that a change between the gears always requires passing through the neutral position. Preferably, the shift unit comprises a non-synchronous dog clutch.

[0016] According to a preferred embodiment, the switching unit is at least partially or completely arranged radially within the motor. In other words, the switching unit is at least partially or completely arranged to overlap the motor axially. For example, the switching unit at least partially or completely extends axially into the motor. As a result, the drive unit is constructed to be more compact, especially in the axial direction.

[0017] According to a preferred embodiment, the drive unit further comprises a differential, wherein the differential comprises a differential input shaft and two differential output shafts, wherein the differential input shaft is at least indirectly connected to the second carrier shaft.

[0018] For example, the differential is constructed as a bevel gear differential. The differential constructed as a bevel gear differential has two wheel-side driven elements, in particular a first driven wheel and a second driven wheel. The two driven wheels are respectively engaged with a balancing element. The balancing element is supported in the differential cage in a manner that it can rotate around its own axis. The respective driven wheels are connected to the respective differential output shafts in a rotationally resistant manner. The drive end of the differential is realized via the differential cage, which is established as a differential input shaft. The driving power fed into the differential transmission is distributed to the differential output shaft and transmitted to the drive wheels of the axle. The differential output shaft is established to be connected to the drive wheel of the vehicle in a driving manner. The respective differential output shaft can be directly or directly or indirectly connected to the corresponding wheel via a hinge, an articulated shaft and / or a wheel hub.

[0019] For example, the differential is constructed as an integral differential having a first planetary group and a second planetary group. An "integrated differential" is understood to be a differential having a first planetary group and a second planetary group operatively connected to the first planetary group. The first planetary group of the integral differential is connected to the driven shaft of the switching transmission, especially the second carrier shaft, in a driving manner, and is connected to the second planetary group of the integral differential in a driving manner, and is at least indirectly connected to the first differential output shaft in a driving manner. In addition, the second planetary group of the integral differential is also connected to the second differential output shaft in a driving manner and is supported on a stationary component, especially on a housing component. With the help of this integral differential, the input torque introduced into the integral differential can be transformed and distributed to the two differential output shafts in a defined ratio. In particular, the input torque is transmitted to the two differential output shafts in half.

[0020] According to a preferred embodiment, the drive unit further comprises a third planetary set configured as a constant transmission ratio stage, the third planetary set having a third sun shaft, a third ring gear shaft and a third carrier shaft. For example, the third sun shaft is connected to the second carrier shaft in a rotationally fixed manner, wherein the driven shaft is connected to the third carrier shaft in a rotationally fixed manner, wherein the ring gear shaft is connected to a stationary component in a rotationally fixed manner. A plurality of planetary gears are rotatably supported on the third carrier shaft and are in toothed engagement with the third sun shaft and the third ring gear shaft.

[0021] According to a preferred embodiment, the third planetary group is at least partially or completely arranged radially within the motor. In other words, the third planetary group is at least partially or completely arranged to overlap with the motor axially. For example, the third planetary group at least partially or completely extends axially into the motor. As a result, the drive unit is constructed more compactly, especially in the axial direction.

[0022] According to a preferred embodiment, the first planetary set and the second planetary set are arranged axially adjacent to each other. Preferably, the first planetary set is arranged axially between the second and third planetary sets. Therefore, there are no additional components axially between the respective planetary sets.

[0023] According to a preferred embodiment, the motor is arranged at the first axial end section of the switching transmission, wherein the driven shaft is arranged at the second axial end section of the switching transmission, which is configured opposite thereto. Thus, the motor and the driven shaft are spaced apart from each other to the greatest extent in the axial direction. Alternatively, the motor is arranged at the first axial end section of the switching transmission, wherein the driven shaft axially passes through the motor and is also arranged at the first axial end section of the switching transmission. Thus, for example, the drive shaft connected to the rotor of the motor in a rotationally fixed manner is constructed as a hollow shaft and is set up for axial penetration of the driven shaft.

[0024] The vehicle according to the invention comprises at least one drive unit according to the invention. The above definitions and statements regarding the technical effects, advantages and advantageous embodiments of the drive unit according to the invention apply in the same manner to the vehicle according to the invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] The drawings show advantageous embodiments of the invention explained below, wherein identical or similar elements are provided with the same reference numerals.

[0026] Figure 1 A highly abstract, schematic illustration of a vehicle having a driven axle with a drive unit according to the invention is shown;

[0027] Figure 2 A highly abstract, schematic illustration of a drive unit according to the invention in accordance with a first specific embodiment is shown;

[0028] Figure 3 A highly abstract, schematic illustration of a drive unit according to the invention in accordance with a second specific embodiment is shown;

[0029] Figure 4 A highly abstract, schematic illustration of a drive unit according to the invention in accordance with a third specific embodiment is shown;

[0030] Figure 5 A highly abstract, schematic illustration of a drive unit according to the invention in accordance with a fourth specific embodiment is shown;

[0031] Figure 6 A highly abstract, schematic illustration of a drive unit according to the invention in accordance with a fifth specific embodiment is shown;

[0032] Figure 7 A highly abstract, schematic illustration of a drive unit according to the invention in accordance with a sixth specific embodiment is shown;

[0033] Figure 8 A highly abstract, schematic illustration of a drive unit according to the invention in accordance with a seventh specific embodiment is shown;

[0034] Fig. 9 A highly abstract, schematic illustration of a drive unit according to the invention in accordance with an eighth specific embodiment is shown;

[0035] Fig.10 A highly abstract, schematic illustration of a drive unit according to the invention in accordance with a ninth specific embodiment is shown;

[0036] Fig.11 A highly abstract, schematic illustration of a drive unit according to the invention in accordance with a tenth specific embodiment; and

[0037] Fig.12 A highly abstracted schematic illustration of a drive unit according to the invention in accordance with an eleventh specific embodiment is shown. DETAILED DESCRIPTION

[0038] Figure 1 A vehicle 100 is shown, whose first axle 101 has two wheels R1, R2, and the second axle 102 has two wheels R3, R4. At present, the first axle 101 is configured as the rear drive axle of the vehicle 100 and is equipped with a drive unit according to the present invention. The drive unit includes an electric motor EM set up to generate drive power and a switching transmission device SG with multiple gears. Therefore, the vehicle 100 is configured as an electric vehicle, that is, a vehicle that can be driven electrically. The drive unit is arranged transversely to the longitudinal direction of the vehicle and is connected to the wheels R1, R2 of the first axle 101 in a driving manner. At present, no additional drive unit is arranged on the second axle 102 (i.e., the front axle of the vehicle 100), thereby saving cost, weight and structural space. Alternatively, instead of being arranged on the rear axle, the drive unit can be arranged on the front axle of the vehicle 100. In order to realize an all-wheel drive system, a further drive unit may be arranged on the second axle 102 and connected to the wheels R3 , R4 of the axle 102 in a driving manner.

[0039] according to Figure 2 The drive unit includes an electric motor EM having a stator EMS fixed relative to the housing and a rotatable rotor EMR, and a switching transmission SG having a first switching element A, a second switching element B, a third switching element C and two coupled planetary groups PS1 and PS2. All three switching elements A, B, and C are constructed as form-locking switching elements, thereby saving structural space and improving efficiency. The first planetary group PS1 includes three shafts, namely the first sun shaft SO1, the first ring gear shaft HR1, and the first carrier shaft ST1. The first carrier shaft ST1 carries a plurality of planetary gears, which mesh with the first sun shaft SO1 and the first ring gear shaft HR1, that is, they are in tooth engagement. The second planetary group PS2 also includes three shafts, namely the second sun shaft SO2, the second ring gear shaft HR2, and the second carrier shaft ST2. The second carrier shaft ST2 carries a plurality of planetary gears, which mesh with the second sun shaft SO2 and the second ring gear shaft HR2, that is, they are in tooth engagement. In addition, the two planetary groups PS1 and PS2 are arranged axially adjacent to each other.

[0040] The second sun shaft SO2 is connected to the rotor EMR of the electric motor EM via the drive shaft An in a rotationally fixed manner and can therefore be driven by the electric motor EM. The second carrier shaft ST2 is set up as the driven end of the switching transmission SG and is connected to the driven shaft Ab in a rotationally fixed manner. The drive shaft An is arranged on one side of the drive unit, and the driven shaft Ab is arranged on the opposite side of the drive unit, wherein the drive shaft An and the driven shaft Ab do not overlap each other axially. The driven shaft Ab can be indirectly, for example, via a differential, or directly connected to at least one drive wheel of the vehicle in a driving manner. For example, a drive unit can be provided for each drive wheel of the vehicle.

[0041] The second ring gear shaft HR2 is connected to the first carrier shaft ST1 in a rotationally fixed manner. In particular, the second ring gear shaft HR2 and the first carrier shaft ST1 form a coupling shaft between the two planetary sets PS1, PS2. The first sun shaft SO1 is connected to a stationary component of a housing G configured as a drive device in a rotationally fixed manner. Therefore, the first sun shaft SO1 is stationary and is therefore prohibited from rotating. The drive unit has a rotational axis of symmetry R, ​​which coincides with the drive shaft An and the driven shaft Ab. The motor EM and the switching transmission SG are arranged coaxially with the drive shaft An and the driven shaft Ab, and therefore rotate around the axis of symmetry R. Figures 2 to 10 Only the “upper” half of the drive unit is shown, wherein the “lower” half (not shown) is designed symmetrically to the “upper” half.

[0042] The first shift element A, the second shift element B and the third shift element C are combined to form a shift unit with five shift positions, wherein the shift unit has a single sleeve SM that can be axially displaced, and the five shift positions are realized by means of the sleeve. The sleeve SM is arranged on the first ring gear shaft HR1 in a rotationally fixed manner and can be axially displaced into the respective shift positions by means of a single actuator AK. Therefore, all five shift positions of the shift unit are arranged in a straight line and consist of three gear positions and two neutral positions, wherein the shift unit has exactly one neutral position between the two gear positions. Therefore, by moving the sleeve SM in the axial direction, one to three gears will be switched respectively via the neutral position or in sequence. This not only saves weight and components, but also saves costs, structural space and installation work.

[0043] When the sleeve SM is arranged in the first gear position, i.e., in the first shift position, the first gear is engaged. The first shift element A, in the actuated state, i.e., in the first shift position of the sleeve SM, connects the first ring gear shaft HR1 to the first carrier shaft ST1 in order to shift the first gear. As a result, the first planetary set PS1 is immobilized.

[0044] The first gear is disengaged by axially moving the sleeve SM into a first neutral position, i.e., into a second shift position. In the second shift position of the sleeve SM, the first ring gear shaft HR1 and the first carrier shaft ST1 are not connected to each other in a rotationally fixed manner via the sleeve SM and are therefore decoupled from each other via the sleeve SM. In the first neutral position, the sleeve SM is only in rotational engagement with the first ring gear shaft HR1.

[0045] The second gear is engaged by axially moving the sleeve SM to the second gear position, i.e., to the third shift position. When the second shift element B is actuated, i.e., in the third shift position of the sleeve SM, the first ring gear shaft HR1 is connected to the second carrier shaft ST2 in order to shift the second gear. This slows down the rotation speed of the first ring gear shaft HR1. Figure 2 3 shows the third switching position of the sliding sleeve SM.

[0046] The second gear is engaged by axially moving the sleeve SM into a second neutral position, i.e., into the fourth shift position. In the fourth shift position of the sleeve SM, the first ring gear shaft HR1 and the second carrier shaft ST2 are not connected to each other in a rotationally fixed manner via the sleeve SM and are therefore decoupled from each other via the sleeve SM. In the second neutral position, the sleeve SM is only in rotational engagement with the first ring gear shaft HR1.

[0047] The third gear is engaged by axially moving the sleeve SM into the third gear position, i.e. into the fifth shift position. In the actuated state, i.e. in the fifth shift position of the sleeve SM, the third shift element C connects the first ring gear shaft HR1 to the second sun shaft SO2 in order to shift the third gear. As a result, the first ring gear shaft HR1 rotates at the drive speed introduced by the electric machine EM to the drive shaft An.

[0048] Figure 3 A second embodiment of a drive unit according to the invention is shown. Figure 3 The drive unit is basically the same as that according to Figure 2 The difference between the two embodiments lies in the representation or implementation of the first gear. In the present case, this embodiment represents an interlocking variant for the first planetary set PS1. To shift the first gear, the first shifting element A, in the actuated state, connects the first ring gear shaft HR1 to a stationary component designed as a housing G. The first ring gear shaft HR1 is therefore stationary. Figure 2 Compared to the implementation method, the switch positions two to five and the functions remain unchanged. Figure 3, the first shift position of the sleeve SM is shown in FIG. A further interlocking variant for the first planetary set PS1, not shown in the figure, can be realized in that the first shifting element A connects the first carrier shaft ST1 to the housing G in a rotationally fixed manner. However, this interlocking variant does not allow the use of a sleeve SM which is always connected to the first ring gear shaft HR1. In other respects, according to Figure 3 Embodiments and basis Figure 2 For the corresponding embodiments, please refer to the relevant content.

[0049] Figure 4 A third embodiment of a drive unit according to the present invention is shown. Figure 4 The drive unit is basically the same as that according to Figure 2 The difference between the two embodiments is that an additional shifting element is arranged to form the fourth gear. At present, the shifting transmission SG has not only the first, second and third shifting elements A, B, C, but also a fourth shifting element D. All four shifting elements A, B, C, D are constructed as shape-locking shifting elements. The first shifting element A, the second shifting element B, the third shifting element C and the fourth shifting element D form a shifting unit with seven shifting positions, wherein the shifting unit has a unique axially movable sleeve SM, by means of which the seven shifting positions are realized. The sleeve SM can be axially moved to the respective shifting positions by means of a unique actuator AK. Therefore, the seven shifting positions of the shifting unit are arranged in a straight line and consist of four gear positions and three neutral positions, wherein the shifting unit has exactly one neutral position between two gear positions. Therefore, by moving the sleeve SM in the axial direction, one to four gears are switched respectively via the neutral position or in sequence. This not only saves weight and components, but also saves costs, structural space and installation effort. Compared with the embodiment according to Figure 2 Compared with the implementation method of the present invention, the positions and functions of switches 1 to 5 remain unchanged. Figure 4 The fifth switching position of the sliding sleeve SM is shown in FIG.

[0050] The third gear is engaged by axially moving the sleeve SM into the third neutral position, i.e. into the sixth shift position. In the sixth shift position of the sleeve SM, the first ring gear shaft HR1 and the second sun shaft SO2 are not connected to each other in a rotationally fixed manner via the sleeve SM and are therefore decoupled from each other via the sleeve SM. In the third neutral position, the sleeve SM is only in rotational engagement with the second sun shaft SO2.

[0051] The fourth gear is engaged by axially moving the sleeve SM into the fourth gear position, i.e. into the seventh shift position. In the actuated state, i.e. in the seventh shift position of the sleeve SM, the fourth shift element D connects the first carrier shaft ST1 to the second sun shaft SO2. This interlocks the second planetary set PS2 and generates a direct gear with a transmission ratio of 1, which is coupled to the transmission ratio series. In other respects, according to Figure 4 Embodiments and basis Figure 2 For the corresponding embodiments, please refer to the relevant content.

[0052] Figure 5 A fourth embodiment of a drive unit according to the invention is shown. Figure 5 The drive unit is basically the same as that according to Figure 2 The difference between the two embodiments is that a differential ID is arranged on the axis of symmetry R. The differential ID is constructed as an integral differential having a first planetary set 30 and a second planetary set 40. The integral differential increases the final drive ratio and can simultaneously realize the differential function. Alternatively, the differential can also be constructed differently, for example, as a ball differential or a bevel gear differential.

[0053] The two planetary groups 30 and 40 of the integral differential can be arranged axially side by side or radially overlapped, i.e., radially stacked, according to the requirements of the integral differential, especially the transmission ratio of the integral differential to be achieved. At present, the two planetary groups 30 and 40 of the integral differential are arranged radially overlapped, thereby saving axial structural space. The sun gear 31 of the first planetary group 30 of the integral differential is constructed as the differential input shaft D1 of the integral differential and is connected to the driven shaft Ab in a rotationally fixed manner.

[0054] The driven end on the integral differential is realized via two differential output shafts D2 and D3, wherein the carrier shaft 33 of the first planetary set 30 of the integral differential is connected to the first differential output shaft D2 in a rotationally fixed manner, wherein the ring gear 42 of the second planetary set 40 of the integral differential is connected to the second differential output shaft D3 in a rotationally fixed manner. The sun gear 41 of the second planetary set 40 of the integral differential is connected to the ring gear 32 of the first planetary set 30 of the integral differential in a rotationally fixed manner, and is currently constructed as an intermediate gear with an internal meshing portion and an external meshing portion. The carrier shaft 43 of the second planetary set 40 of the integral differential carries a plurality of planetary gears meshing with the sun gear 41 and the ring gear 42, and is connected to the housing G in a rotationally fixed manner. In addition, the carrier shaft 33 of the first planetary set 30 of the integral differential carries a plurality of planetary gears meshing with the sun gear 31 and the ring gear 32.

[0055] With the aid of the first planetary set 30 of the integral differential, the first output torque can be transmitted to the first differential output shaft D2. The supporting torque of the first planetary set 30 acting in the opposite direction to the first output torque is transmitted to the second planetary set 40 and can be transformed in the second planetary set 40 so that a second output torque equivalent to the first output torque is transmitted to the second differential output shaft D3. In other words, the driving power fed in via the sun gear 31 of the first planetary set 30 is distributed to the two differential output shafts D2 and D3 with the aid of the integral differential. At present, the first differential output shaft D2 extends through the switching transmission SG and the electric motor EM. The second differential output shaft D3 extends in the opposite direction away from the electric motor EM. In other respects, according to Figure 5 Embodiments and basis Figure 2 For the corresponding embodiments, please refer to the relevant content.

[0056] Figure 6 A fifth embodiment of a drive unit according to the invention is shown. Figure 6 The drive unit is basically the same as that according to Figure 2 Corresponding to the drive unit, the difference between these two embodiments is that a constant transmission ratio stage is arranged. At present, the constant transmission ratio stage is constructed as a third planetary set PS3 and includes a third sun shaft SO3, a third ring gear shaft HR3 and a third carrier shaft ST3. The third carrier shaft ST3 carries a plurality of planetary gears, which mesh with the third sun shaft SO3 and the third ring gear shaft HR3. The third ring gear shaft HR3 is connected to a stationary component constructed as a housing G in a rotationally fixed manner and is therefore prohibited from rotating. The third sun shaft SO3 is connected to the second carrier shaft ST2 in a rotationally fixed manner, wherein the third carrier shaft ST3 is connected to the driven shaft Ab in a rotationally fixed manner. Therefore, the third planetary set PS3 is constructed as a rear-mounted wheel set and is arranged in the power flow between the second carrier shaft ST2 and the driven shaft Ab in order to increase the final transmission ratio of the switching transmission SG. In other respects, according to Figure 6 Embodiments and basis Figure 2 For the corresponding embodiments, please refer to the relevant content.

[0057] Figure 7 A sixth embodiment of a drive unit according to the invention is shown. Figure 7 The drive unit is basically the same as that according to Figure 2 The difference between the two embodiments lies in the arrangement or orientation of the output shaft Ab. In the present case, the output shaft Ab is axially guided through the drive shaft An and the electric motor EM, which are designed as hollow shafts. In other words, the drive end and the output end of the switching transmission SG are located on the same side, rather than on opposite sides. In other respects, according to Figure 7 Embodiments and basis Figure 2For the corresponding embodiments, please refer to the relevant content.

[0058] Figure 8 A seventh embodiment of a drive unit according to the present invention is shown. Figure 8 The drive unit is basically the same as that according to Figure 7 The present invention corresponds to a drive unit of the present invention, wherein the difference between the two embodiments is that a constant transmission ratio stage is arranged. In the present invention, the constant transmission ratio stage is constructed as a third planetary set PS3 and includes a third sun shaft SO3, a third ring gear shaft HR3 and a third carrier shaft ST3. The third carrier shaft ST3 carries a plurality of planetary gears, which mesh with the third sun shaft SO3 and the third ring gear shaft HR3. The third ring gear shaft HR3 is connected to a stationary component constructed as a housing G in a rotationally fixed manner and is therefore prohibited from rotating. The third sun shaft SO3 is connected to the second carrier shaft ST2 in a rotationally fixed manner, wherein the third carrier shaft ST3 is connected to the driven shaft Ab in a rotationally fixed manner. Therefore, the third planetary set PS3 is constructed as a rear-mounted gear set and is arranged in the power flow between the second carrier shaft ST2 and the driven shaft Ab in order to increase the final transmission ratio of the switching transmission SG. In addition, the third planetary set PS3 is completely radially arranged within the motor EM. In other words, the motor EM and the third planetary set PS3 are radially nested, thereby making the drive unit axially more compact. In other respects, according to Figure 8 Embodiments and basis Figure 7 For the corresponding embodiments, please refer to the relevant content.

[0059] Fig. 9 An eighth embodiment of a drive unit according to the invention is shown. Fig. 9 The drive unit is basically the same as that according to Figure 2 The difference between the two embodiments is that the diameter of the switching element is reduced. In the present case, the diameter of the switching elements A, B, C of the switching unit is arranged to be smaller than that according to Figure 2 The embodiment is smaller. As a result, the switching unit is partially, in particular half, arranged radially inside the electric motor EM. As a result, the drive unit is constructed more compactly in the axial direction. In other respects, according to Fig. 9 Embodiments and basis Figure 2 For the corresponding embodiments, please refer to the relevant content.

[0060] Fig.10 A ninth embodiment of a drive unit according to the present invention is shown. Fig.10 The drive unit is basically the same as that according to Figure 3The difference between the two embodiments is that an additional shifting element is arranged to form the fourth gear. At present, the switching transmission SG has not only the first, second and third shifting elements A, B, C, but also a fourth shifting element D. All the shifting elements A, B, C, D are constructed as shape-locking shifting elements. The first shifting element A, the second shifting element B, the third shifting element C and the fourth shifting element D form a shifting unit with seven shifting positions, wherein the shifting unit has a unique axially movable sleeve SM, by means of which the seven shifting positions are realized. The sleeve SM can be axially moved to the respective shifting positions by means of a unique actuator AK. Therefore, the seven shifting positions of the shifting unit are arranged in a straight line and consist of four gear positions and three neutral positions, wherein the shifting unit has exactly one neutral position between the two gear positions. Therefore, by moving the sleeve SM in the axial direction, one to four gears are switched respectively via the neutral position or in sequence. This not only saves weight and components, but also saves costs, structural space and installation effort. Compared with the embodiment according to Figure 3 Compared with the implementation method of the present invention, the positions and functions of switches 1 to 5 remain unchanged. Fig.10 : shows a first switching position of the sliding sleeve SM.

[0061] The third gear is engaged by axially moving the sleeve SM into the third neutral position, i.e. into the sixth gear position. In the sixth shift position of the sleeve SM, the first ring gear shaft HR1 and the second sun shaft SO2 are no longer connected in a rotationally fixed manner to one another via the sleeve SM and are therefore decoupled from one another via the sleeve SM. In the third neutral position, the sleeve SM is in rotational engagement with the second sun shaft SO2.

[0062] The fourth gear is engaged by axially moving the sleeve SM into the fourth gear position, i.e. into the seventh shift position. When the fourth shift element D is actuated, i.e. in the seventh shift position of the sleeve SM, the second carrier shaft ST2 is connected to the second sun shaft SO2. This interlocks the second planetary set PS2 and generates a direct gear with a transmission ratio of 1, which is coupled to the transmission ratio series. In other respects, according to Fig.10 Embodiments and basis Figure 3 For the corresponding embodiments, please refer to the relevant content.

[0063] Fig.11 FIG. 10 shows a tenth embodiment of a drive unit according to the present invention. Fig.11 The drive unit is basically the same as that according to Fig.10The difference between the two embodiments lies in the arrangement of the electric motor EM, the two spur gear stages SR1, SR2 for forming the pre-gear ratio, and the differential ID. In the present case, the electric motor EM is arranged parallel to the axis of the shifting gear SG and is connected to the shifting gear SG in a driving manner via the two spur gear stages SR1, SR2. Therefore, the electric motor EM is arranged on the axis R', which is parallel to the axis of symmetry R on which the shifting gear SG is arranged. The rotor shaft RW is connected to the rotor (not shown) of the electric motor EM in a rotationally fixed manner. The first spur gear stage SR1 has a first gear Z11 and a second gear Z12 that are in tooth engagement with each other. The first gear Z11 of the first spur gear stage SR1 is connected to the rotor shaft RW in a rotationally fixed manner. The second gear Z12 of the first spur gear stage SR1 is arranged parallel to the axis of symmetry R and the axis R'. The second spur gear stage SR2 has a first gear Z21 and a second gear Z22 that are in tooth engagement with each other. The first gear Z21 of the second spur gear stage SR2 is connected to the second gear Z12 of the first spur gear stage SR1 in a rotationally fixed manner. The second gear Z22 of the second spur gear stage SR2 is connected to the drive shaft An in a rotationally fixed manner. The two spur gear stages SR1 and SR2 not only generate an additional transmission ratio for the electric motor EM, but also adjust the center distance between the switching transmission SG and the electric motor EM, that is, between the axis of symmetry R and the axis R', as required. The two spur gear stages SR1 and SR2 can also be supplemented according to Figures 2 to 9 In the embodiment of the invention, the motor EM is thus constructed parallel to the axis of the switching transmission SG.

[0064] The differential ID is constructed as a bevel gear differential and is arranged in the power flow after the switching transmission SG. The bevel gear differential has a first driven wheel and a second driven wheel. The two driven wheels are respectively engaged with a balancing element. The balancing element is supported in the differential cage in a manner that can rotate around its own axis. The respective driven wheels are connected to the respective differential output shafts D2 and D3 in a rotationally fixed manner. The drive end of the differential is realized via the differential cage, which is established as a differential input shaft D1. The differential input shaft D1 is connected to the driven shaft Ab in a rotationally fixed manner. The driving power fed into the differential ID is distributed to the differential output shafts D2 and D3 and transmitted to the drive wheels of the axle. The differential output shafts D2 and D3 are established to be connected to the drive wheels of the vehicle in a driving manner, wherein this aspect is indicated by respective arrows. The respective differential output shafts D2, D3 can be connected to the corresponding wheels directly or directly, or indirectly or indirectly via a joint, an articulated shaft and / or a wheel hub. The differential ID is arranged coaxially with the switching transmission SG, wherein the first differential output shaft D2 extends axially through the entire switching transmission SG. In other aspects, according to Fig.11 Embodiments and basis Figure 3For the corresponding embodiments, please refer to the relevant content.

[0065] Fig.12 An eleventh embodiment of a drive unit according to the present invention is shown. Fig.12 The drive unit is basically the same as that according to Fig.10 The drive unit of the embodiment of the present invention corresponds to the embodiment of the present invention, wherein the difference between the two embodiments lies in the arrangement of the motor EM, the spur gear stage SR for forming the pre-gear ratio, the third planetary group PS3 for forming the constant gear ratio and the differential ID. In the present embodiment, the motor EM is arranged parallel to the axis of the switching transmission SG and is connected to the switching transmission SG in a driving manner via the spur gear stage SR. Therefore, the motor EM is arranged on the axis R', which is parallel to the axis of symmetry R where the switching transmission SG is arranged. The rotor shaft RW is connected to the rotor (not shown) of the motor EM in a rotationally fixed manner. The spur gear stage SR has a first gear Z1, a second gear Z2 and a third gear Z3, wherein the second gear Z2 is constructed as an intermediate gear and is in tooth engagement with both the first gear Z1 and the third gear Z3. The first gear Z1 of the spur gear stage SR is connected to the rotor shaft RW in a rotationally fixed manner. The second gear Z2 of the spur gear stage SR is arranged parallel to the axis of symmetry R and the axis R'. The third gear Z3 of the spur gear stage SR is connected to the drive shaft An in a rotationally fixed manner. The spur gear stage SR not only generates an additional transmission ratio for the electric motor EM, but also adjusts the center distance between the switching transmission SG and the electric motor EM, that is, between the axis of symmetry R and the axis R', as required. Figures 2 to 9 In the installation example, a spur gear stage SR can also be added so that the electric machine EM is designed to be axis-parallel to the shifting gear SG.

[0066] The third planetary set PS3 is constructed as a constant transmission ratio stage and includes a third sun shaft SO3, a third ring gear shaft HR3 and a third carrier shaft ST3. The third carrier shaft ST3 carries a plurality of planetary gears, which mesh with the third sun shaft SO3 and the third ring gear shaft HR3. The third ring gear shaft HR3 is connected to a stationary component constructed as a housing G in a rotationally fixed manner and is therefore prohibited from rotating. The third sun shaft SO3 is connected to the second carrier shaft ST2 in a rotationally fixed manner, wherein the third carrier shaft ST3 is connected to the driven shaft Ab in a rotationally fixed manner. Therefore, the third planetary set PS3 is constructed as a rear-mounted gear set and is arranged in the power flow between the second carrier shaft ST2 and the driven shaft Ab in order to increase the final transmission ratio of the switching transmission SG. The overall transmission ratio is increased by the third planetary set PS3, without the switching transmission SG being loaded with an increased torque load.

[0067] The differential ID is constructed as a bevel gear differential and is arranged in the power flow after the third planetary group PS3. The bevel gear differential has a first driven wheel and a second driven wheel. The two driven wheels are respectively engaged with a balancing element. The balancing element is supported in the differential cage in a manner that it can rotate around its own axis. The respective driven wheels are connected to the respective differential output shafts D2 and D3 in a rotationally fixed manner. The drive end of the differential is realized via the differential cage, which is set up as a differential input shaft D1. The differential input shaft D1 is connected to the driven shaft Ab in a rotationally fixed manner. The driving power fed into the differential ID is distributed to the differential output shafts D2 and D3 and transmitted to the drive wheels of the axle. The differential output shafts D2 and D3 are set up to be connected to the drive wheels of the vehicle in a driving manner, wherein this aspect is indicated by respective arrows. The respective differential output shafts D2, D3 can be connected to the corresponding wheels directly or directly or indirectly via a joint, an articulated shaft and / or a wheel hub. The differential ID is arranged coaxially with the switching transmission SG, wherein the first differential output shaft D2 extends axially through the entire switching transmission SG. In other aspects, according to Fig.10 Embodiments and basis Figure 3 For the corresponding embodiments, please refer to the relevant content.

[0068] Reference numerals list

[0069] An drive shaft

[0070] Ab driven shaft

[0071] SG switching transmission

[0072] 100 vehicles

[0073] 101 First Axle

[0074] 102 Second Axle

[0075] R1 Wheels

[0076] R2 Wheels

[0077] R3 Wheels

[0078] R4 Wheels

[0079] EM Motor

[0080] EMS stator

[0081] EMR Rotors

[0082] PS1 First Planet Group

[0083] SO1 First Sun Axis

[0084] HO1 first ring gear shaft

[0085] ST1 first frame axis

[0086] PS2 Second Planet Set

[0087] SO2 Second Solar Axis

[0088] HO2 second ring gear shaft

[0089] ST2 Second Frame Axle

[0090] PS3 Third Planet Set

[0091] SO3 Third Sun Axis

[0092] HO3 third gear ring shaft

[0093] ST3 third frame axle

[0094] SM Sliding Bushing

[0095] A first switching element

[0096] B Second switching element

[0097] C The third switching element

[0098] D Fourth switching element

[0099] AK Actuator

[0100] G housing

[0101] R symmetry axis

[0102] R' axis

[0103] ID Differential

[0104] D1 differential input shaft

[0105] D2 first differential output shaft

[0106] D3 Second differential output shaft

[0107] 30 First Planet Group

[0108] 31 Sun gear of the first planetary group

[0109] 32 Ring gear of the first planetary set

[0110] 33 Carrier axis of the first planetary group

[0111] 40 Second Planet Group

[0112] 41 Sun gear of the second planetary group

[0113] 42 Ring gear of the second planetary group

[0114] 43 Carrier axis of the second planetary group

[0115] SR1 first spur gear stage

[0116] Z11 First Gear

[0117] Z12 Second Gear

[0118] SR2 second spur gear stage

[0119] Z21 first gear

[0120] Z22 Second Gear

[0121] SR Spur Gear Stage

[0122] Z1 first gear

[0123] Z2 second gear

[0124] Z3 third gear

[0125] RW rotor shaft

Claims

1. A drive unit for a vehicle (100), comprising an electric machine (EM) and a shifting transmission (SG), the shifting transmission having at least a first shifting element (A), a second shifting element (B), a third shifting element (C) and two planetary sets (PS1, PS2) coupled to each other, wherein: The first planetary set (PS1) comprises a first sun shaft (SO1), a first ring gear shaft (HR1) and a first carrier shaft (ST1), wherein the second planetary set (PS2) comprises a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2), wherein the second sun shaft (SO2) can be driven by the electric motor (EM), wherein the second ring gear shaft (HR2) is connected to the first carrier shaft (ST1) in a rotationally fixed manner, wherein the first sun shaft (SO1) is connected to a stationary component in a rotationally fixed manner, • wherein the first shifting element (A) in the actuated state immobilizes the first planetary set (PS1) in order to shift the first gear, • wherein the second shifting element (B) connects the first ring gear shaft (HR1) and the second carrier shaft (ST2) in a rotationally fixed manner in order to shift the second gear, when the second shifting element (B) is actuated. • In this case, the third shift element (C) connects the first ring gear shaft (HR1) and the second sun gear shaft (SO2) in a rotationally fixed manner in order to shift the third gear when the third shift element (C) is actuated.

2. The drive unit for a vehicle (100) according to claim 1, characterized in that: The second carrier shaft (ST2) is configured as a driven end of the switching transmission (SG).

3. The drive unit for a vehicle (100) according to claim 1 or 2, characterized in that: • When the first shift element (A) is actuated, it connects the first ring gear shaft (HR1) to the first carrier shaft (ST1) in a rotationally fixed manner in order to shift a first gear.

4. The drive unit for a vehicle (100) according to claim 1 or 2, characterized in that: • When the first shift element (A) is actuated, it connects the first ring gear shaft (HR1) to a stationary component in a rotationally fixed manner in order to shift a first gear.

5. A drive unit for a vehicle (100) according to any one of the preceding claims, characterized in that The shifting transmission (SG) has a fourth shifting element (D).

6. The drive unit for a vehicle (100) according to claim 5, characterized in that: • the first shifting element (A) connects the first ring gear shaft (HR1) and the first carrier shaft (ST1) in a rotationally fixed manner in order to shift the first gear, when the first shifting element (A) is actuated. • In this case, the fourth shift element (D) connects the first carrier shaft (ST1) and the second sun shaft (SO2) in a rotationally fixed manner in order to shift the fourth gear when the fourth shift element (D) is actuated.

7. The drive unit for a vehicle (100) according to claim 5, characterized in that: • the first shifting element (A) in the actuated state connects the first ring gear shaft (HR1) to a stationary component in a rotationally fixed manner in order to shift the first gear, • In this case, the fourth shift element (D) connects the second carrier shaft (ST2) and the second sun shaft (SO2) in a rotationally fixed manner in order to shift the fourth gear when the fourth shift element (D) is actuated.

8. A drive unit according to any one of the preceding claims, wherein: The first shift element (A), the second shift element (B) and the third shift element (C) are combined to form a shift unit having five shift positions, wherein the shift unit has a single axially displaceable sliding sleeve (SM).

9. The drive unit according to any one of claims 1, 2, 3 or 4 in combination with claim 5, wherein: The sliding sleeve (SM) is arranged on the first ring gear shaft (HR1) in a rotationally fixed manner.

10. A drive unit according to any one of claims 5, 6 or 7, wherein: The first shift element (A), the second shift element (B), the third shift element (C) and the fourth shift element (D) form a shift unit having seven shift positions, wherein the shift unit has a single axially displaceable sliding sleeve (SM).

11. The drive unit according to any one of claims 8 to 10, wherein: The shift unit has a neutral position between two gear positions.

12. The drive unit according to any one of claims 8 to 11, wherein: The switching unit is arranged at least partially radially within the electric machine (EM).

13. A drive unit according to any one of the preceding claims, wherein: All shift elements (A, B, C, D) are designed as form-locking shift elements.

14. Drive unit according to any of the preceding claims, further comprising a differential (ID) having a differential input shaft (D1) at least indirectly connected to the second carrier shaft (ST2) and two differential output shafts (D2, D3).

15. The drive unit according to claim 14, wherein: The differential (ID) is constructed as an integral differential having a first planetary set (30) and a second planetary set (40).

16. The drive unit according to claim 1, further comprising a third planetary gear set (PS3) configured as a constant transmission ratio stage, the third planetary gear set comprising a third sun shaft (SO3), a third ring gear shaft (HR3) and a third carrier shaft (ST3).

17. The drive unit according to claim 16, wherein: The third planetary set (PS3) is at least partially arranged radially within the electric machine (EM).

18. Vehicle (100) comprising at least one drive unit according to any of the preceding claims.

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