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 first switching element (A), a second switching element (B), a third switching element (C), • 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 second solar shaft (SO2) and the drive shaft (An) are connected in a rotationally fixed manner, • wherein the first bridge shaft (ST1) and the third sun shaft (SO3) 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 output shaft (Ab), the second web shaft (ST2) and the third ring gear shaft (HR3) 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 ring gear shaft (HR3), the second web shaft (ST2) 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) and the third web shaft (ST3) are connected in a rotationally fixed manner, • wherein in the closed state of the third switching element (C) a third gear with a third gear ratio is engaged, wherein in the third 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] From DE 10 2006 006 642 A1, a multi-stage transmission with seven forward gears and one reverse gear is known. The aim of the document is to optimize the construction effort and also to improve the efficiency in the main driving gears with regard to drag and gear losses. In addition, the multi-stage transmission according to the invention is intended to exert low torques on the shifting elements and planetary gear sets, and to keep the rotational speeds of the shafts, shifting elements, and planetary gear sets as low as possible. Furthermore, the transmission according to the invention is intended to be suitable for any vehicle configuration, in particular for a front-transverse arrangement.The corresponding multi-stage transmission comprises a drive shaft and an output shaft, which are arranged in a housing, three planetary gear sets, at least six rotatable shafts and at least six switching elements, comprising brakes and clutches, the selective engagement of which effect different transmission ratios between the drive shaft and the output shaft, so that at least seven forward gears and one reverse gear are possible.

[0004] The object of the present invention is to provide an alternative transmission for a vehicle. In particular, the transmission should have two to six gears, a wide gear ratio spread, and require minimal actuators. This object is achieved by a transmission with the features of independent claims 1, 2, 4, 5, and 7. 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 first switching element, a second switching element, a third switching element, a first planetary gear set with a first sun shaft, a first ring gear shaft and a first carrier shaft, a second planetary gear set with a second sun shaft, a second ring gear shaft and a second carrier shaft and a third planetary gear set with a third sun shaft, a third ring gear shaft and a third carrier shaft, wherein the second sun shaft and the drive shaft are non-rotatably connected, wherein the first carrier shaft and the third 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, wherein the output shaft, the second carrier shaft and the third ring gear shaft are non-rotatably connected,wherein, in the closed state of the first switching element, a first gear with a first gear ratio is engaged, wherein in the first gear the first ring gear shaft, the third ring gear shaft, the second web 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 gear ratio is engaged, wherein in the second gear the first ring gear shaft and the third web shaft are non-rotatably connected, 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 ring gear shaft, the first sun gear shaft and the second ring gear shaft are non-rotatably connected. For this purpose, reference is made to the embodiment according to , Fig. 2 referred.

[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. Each 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. The first sun gear shaft and the second ring gear shaft form a first coupling shaft, while the second carrier shaft, the third ring gear shaft, and the output shaft (which is rigidly connected to it) form a second coupling shaft.

[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. The switching elements are designed as gear-shifting elements and are thus configured for shifting gears. To shift into first gear, the first switching element can be actuated or closed, whereby only the first switching element is closed in first gear. To shift into second gear, the second switching element can be actuated or closed, whereby only the second switching element is closed in second gear. To shift into third gear, the third switching element can be actuated or closed, whereby only the third switching element is closed in third gear.If a fourth shift element is provided, the fourth shift element can be actuated or closed to engage a fourth gear, whereby only the fourth shift element is closed in fourth gear. If a fifth shift element is provided, the fifth shift element can be actuated or closed to engage a fifth gear, whereby only the fifth shift element is closed in fifth gear. If a sixth shift element is provided, the sixth shift element can be actuated or closed to engage a sixth gear, whereby only the sixth shift element is closed in sixth gear.

[0009] Another transmission according to the invention for a vehicle comprises a drive shaft for connecting an electric machine, an output shaft, a first switching element, a second switching element, a third switching element, a first planetary gear set with a first sun shaft, a first ring gear shaft and a first carrier shaft, a second planetary gear set with a second sun shaft, a second ring gear shaft and a second carrier shaft and a third planetary gear set with a third sun shaft, a third ring gear shaft and a third carrier shaft, wherein the second sun shaft and the drive shaft are non-rotatably connected, wherein the first carrier shaft and the third 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, wherein the output shaft, the second carrier shaft and the third ring gear shaft are non-rotatably connected.wherein, in the closed state of the first switching element, a first gear with a first gear ratio is engaged, wherein in the first gear the first ring gear shaft and the third web shaft are non-rotatably connected, wherein in the closed state of the second switching element a second gear with a second gear 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, 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 gear shaft, the second ring gear shaft and the third web shaft are non-rotatably connected. Reference is made to the embodiments according to , Fig. 3 and Fig. 6 referred.

[0010] According to one embodiment, the three switching elements are configured as a positive-locking switching unit with five switching positions and a single sliding sleeve, wherein a single actuator is provided for axially displacing the sliding sleeve into the respective switching position. In particular, 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. Specifically, the actuator displaces the sliding sleeve into the respective switching position and thereby switches three gears sequentially, whereby a change between 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.

[0011] Another transmission according to the invention for a vehicle comprises a drive shaft for connecting an electric machine, an output shaft, a first switching element and a second switching element, a first planetary gear set with a first sun shaft, a first ring gear shaft and a first carrier shaft, a second planetary gear set with a second sun shaft, a second ring gear shaft and a second carrier shaft and a third planetary gear set with a third sun shaft, a third ring gear shaft and a third carrier shaft, wherein the second sun shaft and the drive shaft are non-rotatably connected, wherein the first carrier shaft and the third 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, wherein the output shaft, the second carrier shaft and the third ring gear shaft are non-rotatably connected.wherein, in the closed state of the first switching element, a first gear with a first gear ratio is engaged, wherein in the first gear the first ring gear shaft and the third web shaft are rotationally fixed, wherein, in the closed state of the second switching element, a second gear with a second gear ratio is engaged, wherein in the second gear the first sun gear shaft, the second ring gear shaft and the third web shaft are rotationally fixed. For this purpose, reference is made to the embodiment according to , Fig. 5 referred.

[0012] Another transmission according to the invention for a vehicle comprises a drive shaft for connecting an electric machine, an output shaft, a first switching element, a second switching element, a third switching element and a fourth switching element, a first planetary gear set with a first sun shaft, a first ring gear shaft and a first carrier shaft, a second planetary gear set with a second sun shaft, a second ring gear shaft and a second carrier shaft and a third planetary gear set with a third sun shaft, a third ring gear shaft and a third carrier shaft, wherein the second sun shaft and the drive shaft are non-rotatably connected, wherein the first carrier shaft and the third 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, wherein the output shaft, the second carrier shaft and the third ring gear shaft are non-rotatably connected.wherein, in the closed state of the first switching element, a first gear with a first gear ratio is engaged, wherein in the first gear the first ring gear shaft and the third web shaft are non-rotatably connected, wherein in the closed state of the second switching element a second gear with a second gear ratio is engaged, wherein in the second gear the first sun gear shaft, the second ring gear shaft and the third web shaft are non-rotatably connected, wherein in the closed state of the third switching element a third gear configured as a direct drive with a third gear ratio is engaged, wherein in the third gear two of the three shafts of the second planetary gear set are non-rotatably connected, wherein in the closed state of the fourth switching element a fourth gear with a fourth gear ratio is engaged, wherein in the fourth gear the second sun gear shaft, the drive shaft and the third web shaft are non-rotatably connected. For this purpose, reference is made to the embodiment according to , Fig. 6 referred.

[0013] According to one embodiment, the first and second switching elements are configured as a positive-locking switching unit with three switching positions and a single sliding sleeve, wherein a single actuator is provided for axially displacing the sliding sleeve into the respective switching position. In particular, 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. Specifically, the actuator displaces the sliding sleeve into the respective switching position and thereby switches two gears sequentially.

[0014] Another transmission according to the invention for a vehicle comprises a drive shaft for connecting an electric machine, an output shaft, a first switching element, a second switching element, a third switching element and a fourth switching element, a first planetary gear set with a first sun shaft, a first ring gear shaft and a first carrier shaft, a second planetary gear set with a second sun shaft, a second ring gear shaft and a second carrier shaft and a third planetary gear set with a third sun shaft, a third ring gear shaft and a third carrier shaft, wherein the second sun shaft and the drive shaft are non-rotatably connected, wherein the first carrier shaft and the third 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, wherein the output shaft, the second carrier shaft and the third ring gear shaft are non-rotatably connected.wherein, in the closed state of the first switching element, a first gear with a first gear ratio is engaged, wherein in the first gear the first ring gear shaft, the third ring gear shaft, the second web 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 gear ratio is engaged, wherein in the second gear the first ring gear shaft and the third web shaft are non-rotatably connected, 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 ring gear shaft, the first sun gear shaft and the second ring gear shaft are non-rotatably connected, wherein in the closed state of the fourth switching element a fourth gear with a fourth gear ratio is engaged, wherein in the fourth gear the first sun gear shaft, the second ring gear shaft and the third web shaft are non-rotatably connected. For this purpose, reference is made to the embodiment according to , Fig. 7 referred.

[0015] According to one embodiment, the four switching elements are configured as a positive-locking switching unit with seven switching positions and a single sliding sleeve, wherein a single actuator is provided for axially displacing the sliding sleeve into the respective switching position. In particular, 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. Specifically, the actuator displaces the sliding sleeve into the respective switching position, thereby switching four gears sequentially.

[0016] According to one embodiment, the transmission further comprises a fifth shift element, wherein, in the closed state of the fifth shift element, a fifth gear configured as a direct drive with a fifth gear ratio is engaged, wherein in the fifth gear two of the three shafts of the second planetary gear set are rotationally fixed. Thus, in the fifth gear, the second planetary gear set rotates as a single unit. The fifth gear is configured as a direct drive and, due to the unit rotation of the second planetary gear set, has good efficiency and no gear losses. For example, in the fourth gear, the second planetary gear set is locked in place by rotatingly connecting the second ring gear shaft and the associated first sun gear shaft to the second intermediate shaft and the associated output shaft.

[0017] Alternatively, two other shafts of the second planetary gear set can be connected together, for example, the second sun gear shaft and the second bridge shaft, or the second sun gear shaft and the second ring gear shaft. The resulting direct drive has a gear ratio of 1, so that the input shaft and the output shaft rotate at the same speed. Furthermore, reference is made to the embodiment according to Fig. 8 referred.

[0018] According to one embodiment, the five switching elements are configured as a positive-locking switching unit with nine switching positions and a single sliding sleeve, wherein a single actuator is provided for axially displacing the sliding sleeve into the respective switching position. In particular, the switching unit has a neutral position between each pair of gear positions, so that with nine switching positions, five gear positions and four 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. Specifically, the actuator displaces the sliding sleeve into the respective switching position, thereby switching five gears sequentially.

[0019] According to one embodiment, the transmission further comprises a sixth shift element, wherein, in the closed state of the sixth shift element, a sixth gear with a sixth ratio is engaged, wherein in the sixth gear the second sun shaft, the drive shaft and the third web shaft are rotationally fixed together. For this purpose, reference is made to the embodiment according to Fig. 9 referred.

[0020] According to one embodiment, the transmission further comprises a fifth and a sixth shift element, which are formed into a positive-locking shift unit with three shift positions and a single sliding sleeve. In the closed state of the fifth shift element, a fifth gear, designed as a direct drive, with a fifth gear ratio is engaged. In fifth gear, two of the three shafts of the second planetary gear set are rotationally fixed. In the closed state of the sixth shift element, a sixth gear with a sixth gear ratio is engaged. In sixth gear, the second sun shaft, the drive shaft, and the third connecting shaft are rotationally fixed. Thus, in fifth gear, the second planetary gear set rotates as a single unit. The fifth gear is designed as a direct drive and, due to the unit rotation of the second planetary gear set, has good efficiency and no gear losses.For example, in fourth gear, the second planetary gear set is locked by connecting the second ring gear shaft and the associated first sun gear shaft to the second carrier shaft and the associated output shaft in a rotationally fixed manner. Alternatively, any two other shafts of the second planetary gear set can be connected together, for example, the second sun gear shaft and the second carrier shaft, or the second sun gear shaft and the second ring gear shaft. The resulting direct drive has a gear ratio of 1, so that the input shaft and the output shaft rotate at the same speed. Furthermore, reference is made to the embodiment according to... Fig. 10 referred.

[0021] 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.

[0022] 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.

[0023] 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.

[0024] 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.

[0025] 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 drive unit according to the invention with a gearbox according to the second embodiment; Fig. 5 a highly abstracted schematic view of a gearbox according to the invention in a third embodiment; Fig. 6 a highly abstracted schematic view of a transmission according to the invention in a fourth embodiment; Fig. 7 a highly abstracted schematic view of a transmission according to the invention in a fifth embodiment; Fig. 8 a highly abstracted schematic view of a gearbox according to the invention in a sixth embodiment; Fig. 9 a highly abstracted schematic view of a transmission according to the invention in a seventh embodiment and Fig. 10 a highly abstracted schematic view of a transmission according to the invention in an eighth embodiment.

[0026] 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. 4 shown.

[0027] Alternatively, and not shown in detail, the drive unit can be arranged transversely to the longitudinal direction of the vehicle.

[0028] 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.

[0029] 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, three switching elements, namely a first switching element A, a second switching element B, and a third switching element C, as well as 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.

[0030] 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. 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.

[0031] The second sun shaft SO2 and the drive shaft An are connected in a rotationally fixed manner. The first web shaft ST1 and the third sun shaft SO3 are each connected in a rotationally fixed manner to a stationary component designed as a housing. The first sun shaft SO1 and the second ring gear shaft HR2 are connected in a rotationally fixed manner and form a first coupling shaft. The output shaft Ab, the second web shaft ST2, and the third ring gear shaft HR3 are connected in a rotationally fixed manner and form a second coupling shaft.

[0032] 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. Figures 10 show only the “upper” half of the respective manual transmission SG, with the “lower”, not shown half being symmetrical to the “upper” half.

[0033] The first switching element A, the second switching element B, and the third switching element C are combined into a switching unit with a single sliding sleeve SM and five switching positions: three gear positions and two neutral positions. The sliding sleeve SM is radially nested on the outer circumference of the planetary gear sets PS1, PS2, and PS3 to save axial installation space and thus increase axial compactness. The neutral position is located between two gear positions. The five switching positions are achieved by axially sliding the sliding sleeve SM. The sliding sleeve SM has claw switching elements and can be axially moved into the respective switching position by means of a single actuator AK. Therefore, all five switching positions of the switching unit are arranged linearly. 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.

[0034] 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 ring gear shaft HR3, the second connecting shaft ST2, 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 and the third connecting shaft ST3 are non-rotatably connected. When the third shift element C is closed, a third gear with a third 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.

[0035] 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 shift element A connects the first ring gear shaft HR1, the third ring gear shaft HR3, the second connecting shaft ST2, and the output shaft Ab to engage first gear. By actuating the sliding sleeve SM and closing only the first shift element A, first gear is engaged. During this process, the first coupling shaft rotates rapidly in reverse.

[0036] 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, B, and C 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.

[0037] 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 and the third connecting shaft ST3 to engage second gear. By actuating the sliding sleeve SM and closing only the second shift element B, second gear is engaged. The second coupling shaft rotates backward during this process.

[0038] 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 ring gear shaft HR1. In this neutral position, all three shift elements A, B, and C are open, allowing the electric motor EM to synchronize the target gear.

[0039] 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 shift element C connects the first ring gear shaft HR1, the first sun gear shaft SO1, and the second ring gear shaft HR2 to engage third gear. This blocks the first coupling shaft, indirectly by blocking the first planetary gear set PS1.

[0040] 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, wherein a difference between these two embodiments lies in the design of the switching unit. In the present case, the switching unit has three switching elements B', C', D' and five switching positions. The first switching element B' according to Fig. 3 corresponds to the second switching element B according to Fig. 2. The second switching element C' according to Fig. 3 corresponds to the third switching element C according to Fig. 2. The third switching element D' according to Fig. 3 is new compared to Fig. 2. Therefore, the first switching element A is according to Fig. 2. The first switching element B', the second switching element C', and the third switching element D' are combined into a switching unit with a single sliding sleeve SM and five switching positions, namely three gear positions and two neutral positions. In the closed position of the first switching element B', a first gear with a first ratio is engaged, wherein in the first gear the first ring gear shaft HR1 and the third web shaft ST3 are non-rotatably connected. In the closed position of the second switching element C', a second gear with a second ratio is engaged, wherein in the second gear the first ring gear shaft HR1, the first sun gear shaft SO1, and the second ring gear shaft HR2 are non-rotatably connected. In the closed position of the third switching element D', a third gear with a third ratio is engaged, wherein in the third gear the first sun gear shaft SO1, the second ring gear shaft HR2, and the third web shaft ST3 are non-rotatably connected.In third gear, the first coupling shaft rotates forward. Otherwise, the embodiment corresponds to [reference to be added]. Fig. 3 according to the exemplary embodiment Fig. 2, which is referenced.

[0041] Fig. Figure 4 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.

[0042] Otherwise, the embodiment corresponds to Fig. 4 according to the exemplary embodiment Fig. 3, which is referenced.

[0043] Fig. Figure 5 shows a third embodiment of the SG transmission according to the invention. The SG transmission according to Fig. 5 essentially corresponds to the manual transmission SG according to Fig. 2, wherein a difference between these two embodiments lies in the design of the switching unit. In the present case, the switching unit has two switching elements B" and D'' and three switching positions. The first switching element B'' according to Fig. 5 corresponds to the second switching element B according to Fig. 2. The second switching element D'' according to Fig. 5 is new compared to Fig. 2. Therefore, the first switching element A and the third switching element C are according to Fig. 2 is omitted. The first switching element B'' and the second switching element D'' are combined into a switching unit with a single sliding sleeve SM and three switching positions, namely two gear positions and a neutral position. In the closed state of the first switching element B'', a first gear with a first ratio is engaged, wherein in the first gear the first ring gear shaft HR1 and the third connecting shaft ST3 are non-rotatably connected. In the closed state of the second switching element D'', a second gear with a second ratio is engaged, wherein in the second gear the first sun shaft SO1, the second ring gear shaft HR2 and the third connecting shaft ST3 are non-rotatably connected. In the second gear the first coupling shaft rotates forward. Otherwise, the embodiment corresponds to the Fig. 5 according to the exemplary embodiment Fig. 2, which is referenced.

[0044] Fig. Figure 6 shows a fourth embodiment of the SG transmission according to the invention. The SG transmission according to Fig. 6 essentially corresponds to the manual transmission SG according to Fig. 2, wherein a difference between these two embodiments lies in the design of the switching unit. In the present case, the switching unit has two switching elements C''' and D''' and three switching positions. The first switching element C''' according to Fig. 6 corresponds to the third switching element C according to Fig. 2. The second switching element D''' according to Fig. 6 is new compared to Fig. 2. Therefore, the first switching element A and the second switching element B are according to Fig. 2 is omitted. The first switching element C''' and the second switching element D''' are combined into a switching unit with a single sliding sleeve SM and three switching positions, namely two gear positions and a neutral position. In the closed state of the first switching element C''', a first gear with a first ratio is engaged, wherein in the first gear the first ring gear shaft HR1, the first sun gear shaft SO1 and the second ring gear shaft HR2 are rotationally fixed. In the closed state of the second switching element D''', a second gear with a second ratio is engaged, wherein in the second gear the first sun gear shaft SO1, the second ring gear shaft HR2 and the third connecting shaft ST3 are rotationally fixed. In the second gear, the first coupling shaft rotates forward.

[0045] Furthermore, the transmission has a third shift element E'' and a fourth shift element F'', wherein the third and fourth shift elements E'' and F'' are formed into a further positive-locking shift unit with three shift positions and a single sliding sleeve SM', this further shift unit being arranged axially between the second planetary gear set PS2 and the third planetary gear set PS3 and being shifted by means of a separate actuator AK'. In the closed state of the third shift element E'', a third gear configured as a direct drive with a third gear ratio is engaged, wherein in the third gear two of the three shafts of the second planetary gear set PS2 are rotationally fixed together, thereby locking the second planetary gear set PS2.In the third gear, the second connecting shaft ST2, the output shaft Ab (which is non-rotatably connected to it), the third ring gear shaft HR3, the second sun shaft SO2, and the input shaft An (which is non-rotatably connected to it) are non-rotatably connected. As a result, the output shaft Ab rotates at the same speed as the input shaft An. When the fourth shift element F'' is closed, a fourth gear with a fourth gear ratio is engaged, in which the second sun shaft SO2, the input shaft An, and the third connecting shaft ST3 are non-rotatably connected. The first coupling shaft therefore rotates faster. Thus, the transmission exhibits the following characteristics: Fig. 6 Two switching units, each with three switching positions, are provided to implement four gears, wherein only one of the four switching elements is closed in each gear. Otherwise, the embodiment corresponds to the following. Fig. 6 according to the exemplary embodiment Fig. 2, which is referenced.

[0046] Fig. Figure 7 shows a fifth embodiment of the SG transmission according to the invention. The SG transmission according to Fig. 7 essentially corresponds to the manual transmission SG according to Fig. 2, wherein a difference between these two embodiments lies in the design of the switching unit. In the present case, the switching unit has four switching elements A, B, C, D and seven switching positions. The first switching element A according to Fig. 7 corresponds to the first switching element A according to Fig. 2. The second switching element B according to Fig. 7 corresponds to the second switching element B according to Fig. 2. The third switching element C according to Fig. 7 corresponds to the third switching element C according to Fig. 2. The fourth switching element D according to Fig. 7 is new compared to Fig. 2. The first switching element A, the second switching element B, the third switching element C, and the fourth switching element D are combined into a switching unit with a single sliding sleeve SM and seven switching positions, namely four gear positions and three neutral positions. The first five switching positions of the sliding sleeve SM according to this fifth embodiment of the SG transmission correspond exactly to the first five switching positions of the sliding sleeve SM according to the first embodiment of the SG transmission.

[0047] 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 first coupling shaft. 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. The fourth gear is engaged by axially shifting the sliding sleeve SM into a fourth gear position, i.e., the seventh shift position. In the seventh shift position of the sliding sleeve SM, the fourth shift element D connects the first sun gear shaft SO1, the second ring gear shaft HR2, and the third connecting shaft ST3 to engage the fourth gear. Otherwise, the embodiment corresponds to the following. Fig. 7 according to the exemplary embodiment Fig. 2, which is referenced.

[0048] Fig. Figure 8 shows a sixth embodiment of the SG transmission according to the invention. The SG transmission according to Fig. 8 essentially corresponds to the manual transmission SG according to Fig. 7, a difference between these two embodiments being the design of the switching unit. In the present case, the switching unit has five switching elements A, B, C, D, E and nine switching positions. The first switching element A according to Fig. 8 corresponds to the first switching element A according to Fig. 7. The second switching element B according to Fig. 8 corresponds to the second switching element B according to Fig. 7. The third switching element C according to Fig. 8 corresponds to the third switching element C according to Fig. 7. The fourth switching element D according to Fig. 8 corresponds to the fourth switching element D according to Fig. 7. The fifth switching element E according to Fig. 8 is new compared to Fig. 7. The first switching element A, the second switching element B, the third switching element C, the fourth switching element D, and the fifth switching element E are combined into a switching unit with a single sliding sleeve SM and nine switching positions, namely five gear positions and four neutral positions. The first seven switching positions of the sliding sleeve SM according to this sixth embodiment of the SG transmission correspond exactly to the first seven switching positions of the sliding sleeve SM according to the fifth embodiment of the SG transmission.

[0049] Fourth gear is engaged by axially shifting the sliding sleeve SM into a fourth neutral position, i.e., the eighth shift position. In the fourth neutral position, the sliding sleeve SM is only in rotational engagement with the first coupling shaft. In this neutral position, all five shift elements A, B, C, D, and E are open, allowing the electric motor EM to synchronize the target gear. Fifth gear is engaged by axially shifting the sliding sleeve SM into a fifth gear position, i.e., the ninth shift position. In the ninth shift position of the sliding sleeve SM, the fifth shift element E connects two of the three shafts of the second planetary gear set PS2 in a rotationally fixed manner to engage fifth gear, which is a direct drive. In fifth gear, the second planetary gear set PS2 is locked.In the present case, in the fifth gear, the second web shaft ST2, the output shaft Ab (which is non-rotatably connected to it), the third ring gear shaft HR3, the second sun shaft SO2, and the input shaft An (which is non-rotatably connected to it) are non-rotatably connected. As a result, the output shaft Ab rotates at the same speed as the input shaft An. Otherwise, the embodiment corresponds to the above. Fig. 8 according to the exemplary embodiment Fig. 7, which is referenced.

[0050] Fig. Figure 9 shows a seventh embodiment of the SG transmission according to the invention. The SG transmission according to Fig. 9 essentially corresponds to the manual transmission SG according to Fig. 8, a difference between these two embodiments being the arrangement of a further switching element. In the present case, the transmission SG has a sixth switching element F, which is designed as a single switching element. In the closed state of the sixth switching element F, a sixth gear with a sixth ratio is engaged, wherein in the sixth gear the second sun shaft SO2, the drive shaft An, and the third link shaft ST3 are rotationally fixedly connected. The first coupling shaft thus rotates forward faster. The sixth switching element F is arranged axially between the second planetary gear set PS2 and the third planetary gear set PS3 and is switched by means of a separate actuator (not shown in detail). Otherwise, the embodiment corresponds to the embodiment according to Fig. 9 according to the exemplary embodiment Fig. 8, to which reference is made.

[0051] Fig. Figure 10 shows an eighth embodiment of the SG transmission according to the invention. The SG transmission according to Fig. 10 essentially corresponds to the manual transmission SG according to Fig. 7, a difference between these two embodiments being the arrangement of a further switching unit with two switching elements. In the present case, the SG transmission has a fifth switching element E' and a sixth switching element F', which are formed into a positive-locking switching unit with three switching positions and a single sliding sleeve SM', wherein this further switching unit is arranged axially between the second planetary gear set PS2 and the third planetary gear set PS3 and is switched by means of a separate actuator AK'. In the closed state of the fifth switching element E', a fifth gear configured as a direct drive with a fifth gear ratio is engaged, wherein in the fifth gear two of the three shafts of the second planetary gear set PS2 are rotationally fixed together and the second planetary gear set PS2 is thereby locked.In the present case, in fifth gear, the second connecting shaft ST2, the output shaft Ab (which is non-rotatably connected to it), the third ring gear shaft HR3, the second sun shaft SO2, and the input shaft An (which is non-rotatably connected to it) are non-rotatably connected. As a result, the output shaft Ab rotates at the same speed as the input shaft An. When the sixth shift element F' is closed, a sixth gear with a sixth gear ratio is engaged, in which the second sun shaft SO2, the input shaft An, and the third connecting shaft ST3 are non-rotatably connected. The first coupling shaft therefore rotates faster. Thus, the transmission exhibits the following characteristics: Fig. 10 Two switching units for realizing six gears, wherein in each gear only one of the six switching elements is closed. Otherwise, the embodiment corresponds to according to Fig. 10 according to the exemplary embodiment Fig. 7, 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 AK' actuator SM sliding sleeve 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, B', B'', C''' first switching element B, C', D'', D''' second switching element C, D', E'' third switching element D, F'' fourth switching element E, E' fifth switching element F, F' sixth 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 first switching element (A), a second switching element (B), a third switching element (C), • 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 second solar shaft (SO2) and the drive shaft (An) are connected in a rotationally fixed manner, • wherein the first bridge shaft (ST1) and the third sun shaft (SO3) 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 output shaft (Ab), the second web shaft (ST2) and the third ring gear shaft (HR3) 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 ring gear shaft (HR3), the second web shaft (ST2) 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) and the third web shaft (ST3) are connected in a rotationally fixed manner, • wherein in the closed state of the third switching element (C) a third gear with a third gear ratio is engaged, wherein in the third 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 (SG) for a vehicle (100) comprising • a drive shaft (An) for connecting an electric machine (EM), • an output shaft (Ab), • a first switching element (B'), a second switching element (C'), a third switching element (D'), • 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 second solar shaft (SO2) and the drive shaft (An) are connected in a rotationally fixed manner, • wherein the first bridge shaft (ST1) and the third sun shaft (SO3) 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 output shaft (Ab), the second web shaft (ST2) and the third ring gear shaft (HR3) are connected in a rotationally fixed manner, • wherein in the closed state of the first switching element (B') a first gear with a first gear ratio is engaged, wherein in the first gear the first ring gear shaft (HR1) and the third web shaft (ST3) are connected in a rotationally fixed manner, • wherein in the closed state of the second switching element (C') 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, • wherein in the closed state of the third switching element (D') a third gear with a third gear ratio is engaged, wherein in the third gear the first sun shaft (SO1), the second ring gear shaft (HR2) and the third bridge shaft (ST3) are connected in a rotationally fixed manner. [3] Gearbox (SG) according to claim 1 or 2, wherein the three switching elements (A, B, C / B', C', D') are combined to form a positive-locking switching unit with five switching positions and a single sliding sleeve (SM), wherein a single actuator (AK) is provided for axial displacement of the sliding sleeve (SM) into the respective switching position. [4] Manual transmission (SG) for a vehicle (100) • a drive shaft (An) for connecting an electric machine (EM), • an output shaft (Ab), • a first switching element (B'') and a second switching element (D''), • 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 second solar shaft (SO2) and the drive shaft (An) are connected in a rotationally fixed manner, • wherein the first bridge shaft (ST1) and the third sun shaft (SO3) 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 output shaft (Ab), the second web shaft (ST2) and the third ring gear shaft (HR3) are connected in a rotationally fixed manner, • wherein in the closed state of the first switching element (B'') a first gear with a first gear ratio is engaged, wherein in the first gear the first ring gear shaft (HR1) and the third web shaft (ST3) are connected in a rotationally fixed manner, • wherein in the closed state of the second switching element (D'') a second gear with a second gear ratio is engaged, wherein in the second gear the first sun shaft (SO1), the second ring gear shaft (HR2) and the third bridge shaft (ST3) are connected in a rotationally fixed manner. [5] Manual transmission (SG) for a vehicle (100) comprising • a drive shaft (An) for connecting an electric machine (EM), • an output shaft (Ab), • a first switching element (C'''), a second switching element (D'''), a third switching element (E'') and a fourth switching element (F''), • 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 second solar shaft (SO2) and the drive shaft (An) are connected in a rotationally fixed manner, • wherein the first bridge shaft (ST1) and the third sun shaft (SO3) 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 output shaft (Ab), the second web shaft (ST2) and the third ring gear shaft (HR3) are connected in a rotationally fixed manner, • wherein in the closed state of the first switching element (C''') a first gear with a first gear ratio is engaged, wherein in the first gear the first ring gear shaft (HR1), the first sun gear shaft (SO1) and the second ring gear shaft (HR2) are connected in a rotationally fixed manner, • wherein in the closed state of the second switching element (D''') a second gear with a second gear ratio is engaged, wherein in the second gear the first sun shaft (SO1), the second ring gear shaft (HR2) and the third bridge shaft (ST3) are connected in a rotationally fixed manner, • wherein in the closed state of the third switching element (E'') a third gear designed as a direct drive with a third gear ratio is engaged, wherein in the third gear two of the three shafts of the second planetary set (PS2) are connected in a rotationally fixed manner, • wherein in the closed state of the fourth switching element (F'') a fourth gear with a fourth ratio is engaged, wherein in the fourth gear the second sun shaft (SO2), the drive shaft (An) and the third bridge shaft (ST3) are connected in a rotationally fixed manner. [6] Gearbox (SG) according to claim 4 or 5, wherein the first and second switching elements (B'', D'' / C''', D''') are combined to form a positive-locking switching unit with three switching positions and a single sliding sleeve (SM), wherein a single actuator (AK) is provided for axial displacement of the sliding sleeve (SM) into the respective switching position. [7] Manual transmission (SG) for a vehicle (100) comprising • a drive shaft (An) for connecting an electric machine (EM), • an output shaft (Ab), • a first switching element (A), a second switching element (B), a third switching element (C) and a fourth switching element (D), • 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 second solar shaft (SO2) and the drive shaft (An) are connected in a rotationally fixed manner, • wherein the first bridge shaft (ST1) and the third sun shaft (SO3) 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 output shaft (Ab), the second web shaft (ST2) and the third ring gear shaft (HR3) 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 ring gear shaft (HR3), the second web shaft (ST2) 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) and the third web shaft (ST3) are connected in a rotationally fixed manner, • wherein in the closed state of the third switching element (C) a third gear with a third gear ratio is engaged, wherein in the third gear the first ring gear shaft (HR1), the first sun gear shaft (SO1) and the second ring gear shaft (HR2) are connected in a rotationally fixed manner, • wherein in the closed state of the fourth switching element (D) a fourth gear with a fourth ratio is engaged, wherein in the fourth gear the first sun shaft (SO1), the second ring gear shaft (HR2) and the third bridge shaft (ST3) are connected in a rotationally fixed manner. [8] Gearbox (SG) according to claim 7, wherein the four switching elements (A, B, C, D) are combined to form a positive-locking switching unit with seven switching positions and a single sliding sleeve (SM), wherein a single actuator (AK) is provided for axial displacement of the sliding sleeve (SM) into the respective switching position. [9] Gearbox (SG) according to claim 7 or 8, further comprising a fifth shifting element (E), wherein in the closed state of the fifth shifting element (E) a fifth gear designed as a direct drive with a fifth ratio is engaged, wherein in the fifth gear two of the three shafts of the second planetary set (PS2) are connected in a rotationally fixed manner. [10] Gearbox (SG) according to claim 9, wherein the five switching elements (A, B, C, D, E) are combined to form a positive-locking switching unit with nine switching positions and a single sliding sleeve (SM), wherein a single actuator (AK) is provided for axial displacement of the sliding sleeve (SM) into the respective switching position. [11] Gearbox (SG) according to claim 9 or 10, further comprising a sixth shifting element (F), wherein in the closed state of the sixth shifting element (F) a sixth gear with a sixth ratio is engaged, wherein in the sixth gear the second sun shaft (SO2), the drive shaft (An) and the third web shaft (ST3) are rotationally fixedly connected. [12] Gearbox (SG) according to claim 7 or 8, further comprising a fifth shifting element (E') and a sixth shifting element (F') which are combined to form a positive-locking shifting unit with three shift positions and a single sliding sleeve (SM'), wherein in the closed state of the fifth shifting element (E') a fifth gear designed as a direct drive with a fifth ratio is engaged, wherein in the fifth gear two of the three shafts of the second planetary gear set (PS2) are rotationally fixed, wherein in the closed state of the sixth shifting element (F') a sixth gear with a sixth ratio is engaged, wherein in the sixth gear the second sun shaft (SO2), the drive shaft (An) and the third web shaft (ST3) are rotationally fixed. [13] 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). [14] Drive unit according to claim 13, 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. [15] Vehicle (100) comprising at least one drive unit according to one of claims 13 or 14.

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