Manual transmission and drive unit with such a manual transmission

Abstract

manual transmission (SG) for one vehicle (100) • a drive shaft (An) for connecting an electric machine (EM), • an output shaft (Ab), • a positive-locking switching unit with at least one first switching element (A), a second switching element (B) and a single axially displaceable sliding sleeve (SM), • a first planetary set (PS1) with a first sun shaft (SO1), a first ring gear shaft (HR1) and a first bridge shaft (ST1), • a second planetary gear set (PS2) with a second sun gear shaft (SO2), a second ring gear shaft (HR2) and a second bridge shaft (ST2) and • a third planetary gear set (PS3) with a third sun gear shaft (SO3), a third ring gear shaft (HR3) and a third bridge shaft (ST3), • wherein the third solar shaft (SO3) and the drive shaft (An) are connected in a rotationally fixed manner, • wherein the first bridge shaft (ST1) and the second sun shaft (SO2) are rotationally fixed to a stationary component, • wherein the first sun shaft (SO1) and the second ring gear shaft (HR2) are connected in a rotationally fixed manner, • wherein the second web shaft (ST2) and the third ring gear shaft (HR3) are connected in a rotationally fixed manner, • wherein the third web shaft (ST3) and the output shaft (Ab) are connected in a rotationally fixed manner, • wherein in the closed state of the first switching element (A) a first gear with a first gear ratio is engaged, wherein in the first gear the first ring gear shaft (HR1), the third web shaft (ST3) and the output shaft (Ab) are connected in a rotationally fixed manner, • wherein in the closed state of the second switching element (B) a second gear with a second gear ratio is engaged, wherein in the second gear the first ring gear shaft (HR1), the first sun shaft (SO1) and the second ring gear shaft (HR2) are connected in a rotationally fixed manner.

Description

[0001] The invention relates to a manual transmission for a vehicle. Furthermore, the invention relates to a drive unit comprising a single electric motor and such a manual transmission. The invention also relates to a vehicle with such a drive unit.

[0002] For example, DE 10 2019 218 413 A1 discloses a drive unit for an electric vehicle with a manual transmission comprising a transmission input shaft and a transmission output shaft. The manual transmission is designed as a three-speed transmission with a first shift element, a second shift element, a third shift element, and two coupled planetary gear sets. The first planetary gear set comprises a first sun shaft, a first ring gear shaft, and a first carrier shaft. The second planetary gear set comprises a second sun shaft, a second ring gear shaft, and a second carrier shaft. The first carrier shaft is rigidly connected to the second ring gear shaft. The first sun shaft forms the transmission input shaft. The second sun shaft is fixed to the housing. The second carrier shaft forms the transmission output shaft.To engage first gear, the first shift element can be actuated, to engage second gear the second shift element can be actuated, and to engage third gear the third shift element can be actuated.

[0003] Document DE 10 2015 207 497 A1 discloses a transmission comprising three planetary gear sets. The first element of the first planetary gear set is non-rotatably connected to the input shaft, which is detachably connected via a first coupling to a sixth shaft, via a second coupling to an output shaft non-rotatably connected to the second element of the first planetary gear set, and via a third coupling to a fourth shaft non-rotatably connected to the third element of a third planetary gear set. The third shaft is non-rotatably connected to the third element of the first planetary gear set and the second element of the third planetary gear set, and the second element of the second planetary gear set and the first element of the third planetary gear set are coupled to the housing.Where either a fifth shaft is non-rotatably connected to the third element of the second planetary gear set, the fourth shaft is non-rotatably connected to the first element of the second planetary gear set, and a fourth coupling detachably connects the sixth shaft to the fifth shaft, or a fifth shaft is non-rotatably connected to the first element of the second planetary gear set, the sixth shaft is non-rotatably connected to the third element of the second planetary gear set, and a fourth coupling detachably connects the fourth shaft to the fifth shaft.

[0004] The object of the present invention is to provide an alternative transmission for a vehicle. In particular, the transmission should have two to four gears, a wide gear ratio spread, and require minimal actuators. This object is achieved by a transmission with the features of independent claim 1. Advantageous embodiments are the subject of the dependent claims, the following description, and the figures.

[0005] A transmission according to the invention for a vehicle comprises a drive shaft for connecting an electric machine, an output shaft, a positive-locking switching unit with at least one first switching element, a second switching element and a single axially displaceable sliding sleeve, a first planetary gear set with a first sun shaft, a first ring gear shaft and a first connecting shaft, a second planetary gear set with a second sun shaft, a second ring gear shaft and a second connecting shaft and a third planetary gear set with a third sun shaft, a third ring gear shaft and a third connecting shaft, wherein the third sun shaft and the drive shaft are non-rotatably connected, wherein the first connecting shaft and the second sun shaft are non-rotatably connected to a stationary component, wherein the first sun shaft and the second ring gear shaft are non-rotatably connected and form a first coupling shaft,wherein the second connecting shaft and the third ring gear shaft are non-rotatably connected and form a second coupling shaft, wherein the third connecting shaft and the output shaft are non-rotatably connected, wherein in the closed state of the first switching element a first gear with a first ratio is engaged, wherein in the first gear the first ring gear shaft, the third connecting shaft and the output shaft are non-rotatably connected, wherein in the closed state of the second switching element a second gear with a second ratio is engaged, wherein in the second gear the first ring gear shaft, the first sun gear shaft and the second ring gear shaft are non-rotatably connected.

[0006] The gearbox allows the electric motor to be connected to the drive shaft to transmit power. The electric motor can be connected to the drive shaft either with or without a further reduction gear. The gearbox is connected to either a differential or a vehicle wheel via the output shaft. Each of the three planetary gear sets comprises three shafts: the respective sun gear shaft, the respective ring gear shaft, and the respective carrier shaft. The carrier shaft carries several planet gears that mesh with the respective sun gear shaft and the respective ring gear shaft, i.e., they are in tooth mesh.

[0007] For the purposes of this invention, a "shaft" is understood to be a rotatable component of the transmission by which the respective components of the transmission are connected to one another in a rotationally fixed manner, or by which such a connection can be established when one of the switching elements is actuated. The shaft can connect the components axially or radially, or both axially and radially. The shaft can also serve as an intermediate piece by which a component is connected, for example, radially. The term "shaft" does not preclude the possibility that the components to be connected may be manufactured as a single piece. In particular, two or more shafts connected in a rotationally fixed manner can be manufactured as a single piece. A "stationary component" is understood to be a component that is fixed in a stationary position, in particular that is rotationally fixed or integrally connected to a housing or a part of a housing.

[0008] A "switching element" is a switchable device that, in a closed state, connects two shafts or a shaft and a housing in a rotationally fixed manner, and, in an open state, decouples the two shafts or the shaft and the housing from each other. The two shafts can then rotate relative to each other. These switching elements are designed as gear-shifting elements and are thus configured for shifting gears.

[0009] To engage first gear, the first shift element can be actuated or closed, whereby in first gear only the first shift element is closed. This connects the first ring gear shaft to the output shaft, causing the second coupling shaft to rotate in reverse.

[0010] To engage second gear, the second shift element can be actuated or closed, whereby in second gear only the second shift element is closed. This blocks the second coupling shaft. This occurs indirectly via the first and second planetary gear sets, by means of the second shift element connecting the first ring gear shaft to the first coupling shaft. This completely locks the first and second planetary gear sets. Consequently, the third ring gear is also locked.

[0011] The first and second switching elements form a switching unit with three switching positions, wherein the switching unit has a single axially displaceable sliding sleeve. The sliding sleeve can be moved into the respective switching position by means of a single actuator. Preferably, the switching unit has a neutral position between two gear positions, so that with three switching positions, two gear positions and a neutral position are provided. In a neutral position, two shafts are decoupled from each other via the switching unit, whereby the sliding sleeve is then in rotational engagement with a single shaft. In particular, the actuator moves the sliding sleeve into the respective switching position and thereby switches two gears sequentially, whereby a change between the gears always requires a passage through a neutral position.The sliding sleeve is designed to be positively engaged and features positively engaging claws that, in each gear position, interact positively with corresponding claw teeth to establish a rotationally fixed connection between two shafts. Thus, the respective claw teeth with which the sliding sleeve positively engages can be understood as a shifting element. Preferably, the shifting unit comprises unsynchronized claw clutches. Therefore, all shifting elements are designed as positively engaging shifting elements. Positively engaging shifting elements increase the efficiency of the transmission due to reduced drag losses. In particular, positively engaging shifting elements are more compact, optimized for efficiency, and offer a cost advantage over friction-based shifting elements. Using the sliding sleeve to shift gears further increases compactness, requiring only a single actuator.

[0012] According to a preferred embodiment, the positive-locking switching unit further comprises a third switching element, wherein, in the closed state of the third switching element, a third gear with a third gear ratio is engaged, wherein in the third gear the first sun shaft, the second ring gear shaft, the third connecting shaft, and the output shaft are rotationally fixedly connected. The third switching element is thus also a gear selector element, whereby only the third switching element can be actuated or closed to engage the third gear. In doing so, the first connecting shaft is connected to the output shaft, and the second connecting shaft then rotates forward.

[0013] According to a preferred embodiment, the first, second, and third switching elements form a switching unit with five switching positions, wherein the switching unit comprises a single axially displaceable sliding sleeve. The sliding sleeve can be axially displaced into the respective switching position by means of a single actuator. Preferably, the switching unit has a neutral position between each pair of gear positions, so that with five switching positions, three gear positions and two neutral positions are provided. In a neutral position, two shafts are decoupled from each other via the switching unit, whereby the sliding sleeve is then in rotational engagement with a single shaft. In particular, the actuator displaces the sliding sleeve into the respective switching position and thereby switches three gears sequentially.

[0014] According to a preferred embodiment, the positive-locking switching unit further comprises a fourth switching element, wherein, in the closed state of the fourth switching element, a fourth gear configured as a direct drive with a fourth gear ratio is engaged, wherein in the fourth gear two of the three shafts of the third planetary gear set are rotationally fixed. This locks the third planetary gear set, causing it to rotate as a single unit. The fourth gear is configured as a direct drive and, due to the block rotation of the third planetary gear set, has good efficiency and no gear losses. For example, in the fourth gear, the third planetary gear set is locked by rotationally fixedly connecting the third ring gear shaft and the associated second carrier shaft to the third carrier shaft and the associated output shaft.Alternatively, two other shafts of the third planetary gear set can be connected together, for example, the third sun gear shaft and the third bridge shaft, or the third sun gear shaft and the third ring gear shaft. The resulting direct drive has a gear ratio of 1, so the input shaft and the output shaft rotate at the same speed.

[0015] According to a preferred embodiment, the first, second, third, and fourth switching elements form a switching unit with seven switching positions, wherein the switching unit comprises a single axially displaceable sliding sleeve. The sliding sleeve can be axially displaced into the respective switching position by means of a single actuator. Preferably, the switching unit has a neutral position between each pair of gear positions, so that with seven switching positions, four gear positions and three neutral positions are provided. In a neutral position, two shafts are decoupled from each other via the switching unit, whereby the sliding sleeve is then in rotational engagement with a single shaft. In particular, the actuator displaces the sliding sleeve into the respective switching position and thereby switches four gears sequentially.

[0016] A drive unit according to the invention for a vehicle comprises an electric machine and a transmission according to the invention, wherein the electric machine is arranged either coaxially or parallel to the transmission. Preferably, the drive unit further comprises a differential with a differential input shaft for connecting the output shaft and two differential output shafts for connecting a respective vehicle wheel.

[0017] 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 rotatably mounted in a differential housing about their own axis. The respective output gear is rotationally fixed to the respective differential output shaft. The differential is driven via the differential housing, which is configured as the differential input shaft. Furthermore, alternative differential designs 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 to the two differential output shafts and transmitted to the drive wheels of the axle in a known manner. The differential output shafts are designed to be effectively connected to the vehicle's drive wheels. Each differential output shaft can be connected directly or indirectly via a downstream fixed gear ratio, a joint, a driveshaft, and / or a wheel hub to its corresponding vehicle wheel.

[0018] The transmission according to the invention is particularly suitable for an electric central drive that has a downstream differential reduction, in particular a bevel gear reduction. The preferred installation position of the drive unit is longitudinal to the direction of travel of the vehicle. Alternatively, the drive unit can be installed transversely to the direction of travel of the vehicle, in which case a downstream bevel gear reduction at the differential is omitted. For example, the electric motor can be connected parallel to the axle via at least one spur gear reduction, whereby, depending on the required gear ratio and the available installation space, several spur gear stages can also be provided.

[0019] A vehicle according to the invention comprises a drive unit according to the invention. The above definitions and descriptions of technical effects, advantages and advantageous embodiments of the transmission according to the invention also apply mutatis mutandis to the drive unit and the vehicle according to the invention.

[0020] Advantageous embodiments of the invention, which are explained below, are illustrated in the drawings, wherein identical or similar elements are designated with the same reference numeral. They show: Fig. 1 a highly abstracted schematic view of a vehicle with a drive axle which has a drive unit according to the invention; Fig. 2 a highly abstracted schematic view of a transmission according to the invention in a first embodiment; Fig. 3 a highly abstracted schematic view of a gearbox according to the invention in a second embodiment; Fig. 4 a highly abstracted schematic view of a gearbox according to the invention in a third embodiment and Fig. 5 a highly abstracted schematic view of a drive unit according to the invention with a gearbox according to the second embodiment.

[0021] Fig. Figure 1 shows a vehicle 100 with a first axle 101 with two wheels R1, R2 and a second axle 102 with two wheels R3, R4. In this case, 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 invention. The drive unit comprises an electric machine EM, which is configured to generate drive power, a multi-gear transmission SG, 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 longitudinally in the vehicle and is effectively connected to the wheels R1, R2 of the first axle 101. A detailed embodiment of this drive unit is shown in Figure 1. Fig. 5 shown. Alternatively, and not shown in detail, the drive unit can be arranged transversely to the longitudinal direction of the vehicle.

[0022] In this case, no additional drive unit is arranged on the second axle 102, i.e., the front axle of the vehicle 100, thus saving costs, weight, and installation space. Alternatively, the drive unit can be arranged on the front axle of the vehicle 100 instead of the rear axle. To implement an all-wheel drive system, another drive unit can be arranged on the second axle 102 and effectively connected to the vehicle wheels R3 and R4 of this axle 102.

[0023] Fig. Figure 2 shows a transmission SG according to a first embodiment. The transmission SG comprises a drive shaft An, which is configured for connecting an electric motor (not shown in detail here), an output shaft Ab, which can be effectively connected to a differential or a drive wheel of the vehicle, two switching elements, namely a first switching element A and a second switching element B, and three planetary gear sets PS1, PS2, PS3, each with three shafts. The drive shaft An, the planetary gear sets PS1, PS2, PS3, and the output shaft Ab are arranged on a common axis of rotation R and are thus coaxial with each other. The electric motor can be arranged either coaxially or parallel to the transmission SG and connected to the drive shaft An. In the case of an axially parallel arrangement of the electric motor, at least one spur gear stage can be provided for connection to the drive shaft An.This embodiment, as well as the following two embodiments, are suitable for installation in the vehicle longitudinally or transversely to the direction of travel of the vehicle.

[0024] The first planetary gear set PS1 comprises three shafts: a first sun gear shaft SO1, a first ring gear shaft HR1, and a first carrier shaft ST1. The first carrier shaft ST1 carries several planet gears that mesh with the first sun gear shaft SO1 and the first ring gear shaft HR1, i.e., they are in tooth mesh. The second planetary gear set PS2 also comprises three shafts: a second sun gear shaft SO2, a second ring gear shaft HR2, and a second carrier shaft ST2. The second carrier shaft ST2 carries several planet gears that mesh with the second sun gear shaft SO2 and the second ring gear shaft HR2. The third planetary gear set PS3 also comprises three shafts: a third sun gear shaft SO3, a third ring gear shaft HR3, and a third carrier shaft ST3. The third carrier shaft ST3 carries several planet gears that mesh with the third sun gear shaft SO3 and the third ring gear shaft HR3. The third sun gear shaft SO3 and the drive shaft An are non-rotatably connected.The first web shaft ST1 and the second sun shaft SO2 are non-rotatably connected to a stationary component designed as a housing G. The first sun shaft SO1 and the second ring gear shaft HR2 are non-rotatably connected and form a first coupling shaft. The second web shaft ST2 and the third ring gear shaft HR3 are non-rotatably connected and form a second coupling shaft. The third web shaft ST3 and the output shaft Ab are non-rotatably connected.

[0025] Furthermore, the three planetary gear sets PS1, PS2, and PS3 are arranged axially adjacent to one another to save installation space and increase compactness. The second planetary gear set, PS2, is arranged axially between the first and third planetary gear sets, PS1 and PS3. The embodiments described in Fig. 2 to Fig. Figure 5 shows only the “upper” half of the respective manual transmission SG, with the “lower”, not shown half being symmetrical to the “upper” half.

[0026] The first switching element A and the second switching element B are combined into a switching unit with a single sliding sleeve SM and three switching positions: two gear positions and a neutral position. The sliding sleeve SM is radially nested on the outer circumference of the first and second planetary gear sets PS1 and PS2 to save axial installation space and thus increase axial compactness. The neutral position is located between the gear positions. The three switching positions are achieved by axially sliding the sliding sleeve SM. The sliding sleeve SM has claw switching elements and can be axially displaced into the respective switching position by means of a single actuator AK. Therefore, all three switching positions of the switching unit are arranged linearly. The two gears are shifted sequentially by moving the sliding sleeve SM in an axial direction, past the neutral position.This not only saves weight and components, but also costs, installation space and assembly effort.

[0027] When the first shift element A is closed, a first gear with a first gear ratio is engaged, in which the first ring gear shaft HR1, the third web shaft ST3, and the output shaft Ab are non-rotatably connected. When the second shift element B is closed, a second gear with a second gear ratio is engaged, in which the first ring gear shaft HR1, the first sun gear shaft SO1, and the second ring gear shaft HR2 are non-rotatably connected.

[0028] First gear is engaged when the sliding sleeve SM is in its first gear position, i.e., in its first shift position. In its actuated or closed state (i.e., in the first shift position of the sliding sleeve SM), the first ring gear shaft HR1, the third web shaft ST3, and the output shaft Ab connect to engage first gear. Actuating the sliding sleeve SM and closing only the first shift element A thus engages first gear.

[0029] The first gear is engaged by axially shifting the sliding sleeve SM into a neutral position, i.e., into a second switching position. In the second switching position of the sliding sleeve SM, the sliding sleeve SM is only in rotational engagement with the first ring gear shaft HR1. In this neutral position, the switching elements A and B are open, whereby an electric machine, which can be connected to the drive shaft An, can synchronize the target gear. In the present case, Fig. 2 shows this second switching position of the sliding sleeve SM.

[0030] Second gear is engaged by axially moving the sliding sleeve SM into a second gear position, i.e., a third shift position. In its actuated or closed state (i.e., in the third shift position of the sliding sleeve SM), the second shift element B connects the first ring gear shaft HR1, the first sun gear shaft SO1, and the second ring gear shaft HR2 to engage second gear. Thus, second gear is engaged by actuating the sliding sleeve SM and closing only the second shift element B.

[0031] Fig. Figure 3 shows a second embodiment of the SG transmission according to the invention. The SG transmission according to Fig. 3 essentially corresponds to the manual transmission SG according to Fig. 2, a difference between these two embodiments lies in the design of the switching unit. In the present case, the SG transmission has exactly three switching elements, namely a first switching element A, a second switching element B, and a third switching element C. The first switching element A, the second switching element B, and the third switching element C are combined to form a switching unit with five switching positions, wherein the switching unit has a single axially displaceable sliding sleeve SM with which the five switching positions are realized. The switching unit is arranged on a circumference of the three planetary gear sets PS1, PS2, PS3, has claw switching elements, and can be axially displaced into the respective switching position by means of a single actuator AK.Therefore, all five shift positions of the shift unit are arranged linearly and consist of three gear positions and two neutral positions, with one neutral position positioned between each pair of gear positions. The three gears are shifted sequentially by moving the sliding sleeve SM in an axial direction, past the neutral position. This not only saves weight and components, but also costs, installation space, and assembly effort. The first three shift positions of the sliding sleeve SM according to this second embodiment of the SG transmission correspond exactly to the first three shift positions of the sliding sleeve SM according to the first embodiment of the SG transmission.

[0032] The second gear is engaged by axially shifting the sliding sleeve SM into a second neutral position, i.e., the fourth shift position. In this second neutral position, the sliding sleeve SM is only in rotational engagement with the first sun gear shaft SO1 and the second ring gear shaft HR2, which form a coupling shaft between the first and second planetary gear sets PS1 and PS2. In this neutral position, all three shift elements A, B, and C are open, allowing the electric motor EM to synchronize the target gear.

[0033] Third gear is engaged by axially shifting the sliding sleeve SM into a third gear position, i.e., a fifth shift position. In the fifth shift position of the sliding sleeve SM, the third shifting element C connects the first sun shaft SO1, the second ring gear shaft HR2, the third web shaft ST3, and the output shaft Ab to engage third gear. Otherwise, the embodiment corresponds to the following. Fig. 4 according to the exemplary embodiment Fig. 2, which is referenced.

[0034] Fig. Figure 4 shows a third embodiment of the SG transmission according to the invention. The SG transmission according to Fig. 4 essentially corresponds to the manual transmission SG according to Fig. 3, a difference between these two embodiments lies in the design of the switching unit. In the present case, the transmission SG has exactly four switching elements, namely a first switching element A, a second switching element B, a third switching element C, and a fourth switching element D. The first switching element A, the second switching element B, the third switching element C, and the fourth switching element D are combined to form a switching unit with seven switching positions, wherein the switching unit has a single axially displaceable sliding sleeve SM with which the seven switching positions are realized. The switching unit is arranged on a circumference of the three planetary gear sets PS1, PS2, PS3, has claw switching elements, and can be axially displaced into the respective switching position by means of a single actuator AK.Thus, all seven shift positions of the shift unit are arranged linearly and consist of four gear positions and three neutral positions, with a neutral position positioned between each pair of gear positions. The four gears are shifted sequentially by moving the sliding sleeve SM in an axial direction, past the neutral position. This not only saves weight and components, but also costs, installation space, and assembly effort. The first three shift positions of the sliding sleeve SM according to this third embodiment of the SG transmission correspond exactly to the first three shift positions of the sliding sleeve SM according to the first embodiment of the SG transmission. The fourth and fifth shift positions of the sliding sleeve SM according to this third embodiment of the SG transmission correspond exactly to the fourth and fifth shift positions of the sliding sleeve SM according to the second embodiment of the SG transmission.

[0035] The third gear is engaged by axially shifting the sliding sleeve SM into a third neutral position, i.e., the sixth shift position. In the third neutral position, the sliding sleeve SM is only in rotational engagement with the third web shaft ST3 and the output shaft Ab. In this neutral position, all four shift elements A, B, C, and D are open, allowing the electric motor EM to synchronize the target gear.

[0036] The fourth gear is engaged by axially shifting the sliding sleeve SM into a fourth gear position, i.e., a seventh shift position. In the seventh shift position of the sliding sleeve SM, the fourth shift element D connects three shafts of the third planetary gear set PS3 in a rotationally fixed manner to lock the third planetary gear set PS3 and establish a direct drive. In the closed state of the fourth shift element D, the second carrier shaft ST2, the third ring gear shaft HR3, the third carrier shaft ST3, and the output shaft Ab are rotationally fixedly connected. Otherwise, the embodiment corresponds to the following. Fig. 4 according to the exemplary embodiment Fig. 3, which is referenced.

[0037] Fig. Figure 5 shows the second embodiment of the SG transmission according to the invention in a vehicle drivetrain. In this embodiment, an electric machine EM, a bevel gear stage KG, and a differential DG are also arranged in the drivetrain. The electric machine EM and the SG transmission are arranged on a common axis of rotation R and are thus coaxial with each other. The differential DG is connected to the output shaft Ab via the bevel gear stage KG and is arranged transversely to it. The electric machine EM has a housing-fixed stator EMS and a rotatable rotor EMR, with the drive shaft An being rotationally fixed to the rotor EMR. The differential DG is designed as a ball or bevel gear differential and has a differential input shaft D1 and two differential output shafts D2 and D3.The differential input shaft D1 is designed as a differential carrier and is non-rotatably connected to a bevel gear of the bevel gear stage KG, the other bevel gear of the bevel gear stage KG being non-rotatably connected to the output shaft Ab, and the two bevel gears being in mesh. 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 rotatably mounted in the differential carrier about their own axis. The respective output gear is non-rotatably connected to the respective differential output shafts D2 and D3. Thus, the differential DG is driven via the differential carrier, which is effectively connected to the output shaft Ab via the bevel gear stage.Arrows on the differential output shafts D2 and D3 indicate a connection to a respective vehicle wheel on this vehicle axle.

[0038] Otherwise, the embodiment corresponds to Fig. 5 according to the exemplary embodiment Fig. 3, which is referenced. Reference sign 100 vehicles 101 first axis 102 second axis R1 vehicle wheel R2 vehicle wheel R3 vehicle wheel R4 vehicle wheel On drive shaft From the output shaft SG manual transmission EM electric machine EMS stator of the electric machine EMR Rotor of the electric machine PS1 first planetary set SO1 first solar wave HO1 first hollow gear shaft ST1 first bridge wave PS2 second planetary set SO2 second solar wave HO2 second hollow gear shaft ST2 second bridge shaft PS3 third planetary set SO3 third solar wave HO3 third hollow gear shaft ST3 third bridge wave AK actuator SM sliding sleeve G Housing R axis of rotation KG bevel gear stage DG Differential D1 Differential input shaft D2 first differential output shaft D3 second differential output shaft A first switching element B second switching element C third switching element The fourth switching element

Claims

[1] Manual transmission (SG) for a vehicle (100) comprising • a drive shaft (An) for connecting an electric machine (EM), • an output shaft (Ab), • a positive-locking switching unit with at least one first switching element (A), a second switching element (B) and a single axially displaceable sliding sleeve (SM), • a first planetary set (PS1) with a first sun shaft (SO1), a first ring gear shaft (HR1) and a first bridge shaft (ST1), • a second planetary gear set (PS2) with a second sun gear shaft (SO2), a second ring gear shaft (HR2) and a second bridge shaft (ST2) and • a third planetary gear set (PS3) with a third sun gear shaft (SO3), a third ring gear shaft (HR3) and a third bridge shaft (ST3), • wherein the third solar shaft (SO3) and the drive shaft (An) are connected in a rotationally fixed manner, • wherein the first bridge shaft (ST1) and the second sun shaft (SO2) are rotationally fixed to a stationary component, • wherein the first sun shaft (SO1) and the second ring gear shaft (HR2) are connected in a rotationally fixed manner, • wherein the second web shaft (ST2) and the third ring gear shaft (HR3) are connected in a rotationally fixed manner, • wherein the third web shaft (ST3) and the output shaft (Ab) are connected in a rotationally fixed manner, • wherein in the closed state of the first switching element (A) a first gear with a first gear ratio is engaged, wherein in the first gear the first ring gear shaft (HR1), the third web shaft (ST3) and the output shaft (Ab) are connected in a rotationally fixed manner, • wherein in the closed state of the second switching element (B) a second gear with a second gear ratio is engaged, wherein in the second gear the first ring gear shaft (HR1), the first sun shaft (SO1) and the second ring gear shaft (HR2) are connected in a rotationally fixed manner. [2] Manual transmission (MT) according to claim 1, wherein the positive-locking shifting unit has two gear positions and a neutral position, wherein the neutral position is arranged between the two gear positions. [3] Gearbox (SG) according to claim 1, wherein the positive-locking switching unit further comprises a third switching element (C), wherein in the closed state of the third switching element (C) a third gear with a third ratio is engaged, wherein in the third gear the first sun shaft (SO1), the second ring gear shaft (HR2), the third web shaft (ST3) and the output shaft (Ab) are connected in a rotationally fixed manner. [4] Gearbox (SG) according to claim 3, wherein the positive-locking shifting unit has three gear positions and two neutral positions, wherein a neutral position is arranged between each pair of gear positions. [5] Gearbox (SG) according to claim 3, wherein the positive-locking switching unit further comprises a fourth switching element (D), wherein in the closed state of the fourth switching element (D) a fourth gear designed as a direct drive with a fourth ratio is engaged, wherein in the fourth gear two of the three shafts of the third planetary gear set (PS3) are rotationally fixed together. [6] Gearbox (SG) according to claim 5, wherein the positive-locking shifting unit has four gear positions and three neutral positions, wherein a neutral position is arranged between each pair of gear positions. [7] Gearbox (SG) according to claim 5 or 6, wherein in the closed state of the fourth shifting element (D) the second web shaft (ST2), the third ring gear shaft (HR3), the third web shaft (ST3) and the output shaft (Ab) are connected in a rotationally fixed manner. [8] Drive unit for a vehicle (100) comprising an electric machine (EM) and a manual transmission (SG) according to one of the preceding claims, wherein the electric machine (EM) is arranged parallel to the axis or coaxially to the manual transmission (SG). [9] Drive unit according to claim 8, further comprising a differential (DG) with a differential input shaft (D1) for connecting the output shaft (Ab) and two differential output shafts (D2, D3) for connecting a respective vehicle wheel. [10] Vehicle (100) comprising at least one drive unit according to one of claims 8 or 9.

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