Manual transmission and drive unit with such a manual transmission

Abstract

The invention relates to a manual transmission for a vehicle comprising an input shaft, an output shaft, three shifting elements, a first planetary gear set (PS1) with a first sun gear shaft (SO1), a first ring gear shaft (HR1), and a first carrier shaft (ST1), a second planetary gear set (PS2) with a second sun gear shaft (SO2), a second ring gear shaft (HR2), and a second carrier 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 carrier shaft (ST3), wherein the second sun gear shaft (SO2) and the input shaft (An) are connected in a rotationally fixed manner, wherein the first carrier shaft (ST1) and the third sun gear shaft (SO3) are connected in a rotationally fixed manner to a stationary component, wherein the first sun gear shaft (SO1) and the second ring gear shaft (HR2) are connected in a rotationally fixed manner, wherein the output shaft (Ab), the second carrier 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') the first ring gear shaft (HR1) and the third carrier shaft (ST3) are connected in a rotationally fixed manner, wherein in the closed state of the second switching element (C') 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 third switching element (D') the first sun gear shaft (SO1), the second ring gear shaft (HR2) and the third carrier shaft (ST3) 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 with a single electric motor and with 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 having a transmission input shaft and a transmission output shaft. The manual transmission is designed as a three-speed manual transmission with a first shifting element, a second shifting element, a third shifting element, and two interconnected planetary gear sets. The first planetary gear set comprises a first sun gear shaft, a first ring gear shaft, and a first carrier shaft. The second planetary gear set comprises a second sun gear shaft, a second ring gear shaft, and a second carrier shaft. The first carrier shaft is fixedly connected to the second ring gear shaft. The first sun gear shaft forms the transmission input shaft. The second sun gear shaft is fixedly locked to the housing. The second carrier shaft forms the transmission output shaft.The first shifting element can be actuated to shift the first gear, the second shifting element can be actuated to shift the second gear, and the third shifting element can be actuated to shift the third gear.

[0003] The object of the present invention is to provide an alternative manual transmission for a vehicle. In particular, the manual transmission should have two to six gears, a high gear ratio spread, and low actuator complexity. This object is achieved by a manual transmission having the features of independent patent claims 1, 2, 4, 5, and 7. Advantageous embodiments are the subject of the dependent claims, the following description, and the figures.

[0004] A manual transmission according to the invention for a vehicle comprises an input shaft for connecting an electric machine, an output shaft, a first shifting element, a second shifting element, a third shifting element, a first planetary gear set with a first sun gear shaft, a first ring gear shaft and a first carrier shaft, a second planetary gear set with a second sun gear shaft, a second ring gear shaft and a second carrier shaft, and a third planetary gear set with a third sun gear shaft, a third ring gear shaft and a third carrier shaft, wherein the second sun gear shaft and the input shaft are connected in a rotationally fixed manner, wherein the first carrier shaft and the third sun gear shaft are connected in a rotationally fixed manner to a stationary component, wherein the first sun gear shaft and the second ring gear shaft are connected in a rotationally fixed manner, wherein the output shaft, the second carrier shaft and the third ring gear shaft are connected in a rotationally fixed manner,wherein in the closed state of the first shifting element, a first gear is engaged with a first gear ratio, wherein in the first gear, the first ring gear shaft, the third ring gear shaft, the second carrier shaft and the output shaft are connected in a rotationally fixed manner, wherein in the closed state of the second shifting element, a second gear is engaged with a second gear ratio, wherein in the second gear, the first ring gear shaft and the third carrier shaft are connected in a rotationally fixed manner, wherein in the closed state of the third shifting element, a third gear is engaged with a third gear ratio, wherein in the third gear, the first ring gear shaft, the first sun gear shaft and the second ring gear shaft are connected in a rotationally fixed manner. For this purpose, reference is made to the embodiment according to , Fig. 2.

[0005] The manual transmission enables the connection of the electric motor to transmit drive power via the drive shaft, whereby the electric motor can be connected to the drive shaft either with or without an additional gear ratio. The manual transmission is drive-connected either to a differential or to a vehicle wheel via the output shaft. Each of the three planetary sets comprises three shafts, namely the respective sun shaft, the respective ring gear shaft and the respective planetary gear shaft, whereby the respective ring gear shaft carries several planet gears that mesh with the respective sun shaft and the respective ring gear shaft. The first sun shaft and the second ring gear shaft form a first coupling shaft, whereby the second ring gear shaft, the third ring gear shaft and the output shaft connected to it in a rotationally fixed manner form a second coupling shaft.

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

[0007] A “shifting element” is a switchable device which, when closed, connects two shafts or a shaft and a housing in a rotationally fixed manner and, when open, decouples the two shafts or the shaft and the housing from one another. Two shafts can then rotate relative to one another. The shifting elements are designed as gear shifting elements and are therefore configured to shift gears. To shift first gear, the first shifting element can be actuated or closed, with only the first shifting element being closed in first gear. To shift second gear, the second shifting element can be actuated or closed, with only the second shifting element being closed in second gear. To shift third gear, the third shifting element can be actuated or closed, with only the third shifting element being 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, with only the fourth shift element being 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, with only the fifth shift element being 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, with only the sixth shift element being closed in sixth gear.

[0008] A further manual transmission according to the invention for a vehicle comprises an input shaft for connecting an electric machine, an output shaft, a first shifting element, a second shifting element, a third shifting element, a first planetary gear set with a first sun gear shaft, a first ring gear shaft and a first carrier shaft, a second planetary gear set with a second sun gear shaft, a second ring gear shaft and a second carrier shaft, and a third planetary gear set with a third sun gear shaft, a third ring gear shaft and a third carrier shaft, wherein the second sun gear shaft and the input shaft are connected in a rotationally fixed manner, wherein the first carrier shaft and the third sun gear shaft are connected in a rotationally fixed manner to a stationary component, wherein the first sun gear shaft and the second ring gear shaft are connected in a rotationally fixed manner, wherein the output shaft, the second carrier shaft and the third ring gear shaft are connected in a rotationally fixed manner,wherein in the closed state of the first shifting element, a first gear is engaged with a first gear ratio, wherein in the first gear, the first ring gear shaft and the third carrier shaft are connected in a rotationally fixed manner, wherein in the closed state of the second shifting element, a second gear is engaged with a second gear ratio, wherein in the second gear, the first ring gear shaft, the first sun gear shaft and the second ring gear shaft are connected in a rotationally fixed manner, wherein in the closed state of the third shifting element, a third gear is engaged with a third gear ratio, wherein in the third gear, the first sun gear shaft, the second ring gear shaft and the third carrier shaft are connected in a rotationally fixed manner. For this purpose, reference is made to the embodiments according to , Fig. 3 and Fig. 6.

[0009] According to one embodiment, the three shifting elements are designed to form a positive-locking shifting unit with five shift positions and a single sliding sleeve, wherein a single actuator is configured to axially shift the sliding sleeve into the respective shift position. In particular, the shifting unit has a neutral position between every two gear positions, so that with five shift positions, three gear positions and two neutral positions are provided. In a neutral position, two shafts are decoupled from one another via the shifting unit, with the sliding sleeve then being in rotational engagement with a single shaft. In particular, the actuator shifts the sliding sleeve into the respective shift position and thereby shifts three gears sequentially, wherein changing between gears always requires passing through a neutral position.The sliding sleeve is designed to be positively engaged and has positive-locking claws that interact positively with a corresponding claw toothing in the respective gear position to establish a rotationally fixed connection between two shafts. Therefore, the respective claw toothing with which the sliding sleeve interacts positively is to be understood as a shifting element. The shifting unit preferably comprises unsynchronized claw clutches. Thus, all shifting elements are designed as positive-locking shifting elements. Positive-locking shifting elements can increase the efficiency of the manual transmission due to reduced drag losses. In particular, positive-locking shifting elements are more compact and have an optimized efficiency, offering a cost advantage over friction-locking shifting elements. Using the sliding sleeve to shift the gears further increases compactness, while only a single actuator is required.

[0010] A further manual transmission according to the invention for a vehicle comprises an input shaft for connecting an electric machine, an output shaft, a first shifting element and a second shifting element, a first planetary gear set with a first sun gear shaft, a first ring gear shaft and a first carrier shaft, a second planetary gear set with a second sun gear shaft, a second ring gear shaft and a second carrier shaft and a third planetary gear set with a third sun gear shaft, a third ring gear shaft and a third carrier shaft, wherein the second sun gear shaft and the input shaft are connected in a rotationally fixed manner, wherein the first carrier shaft and the third sun gear shaft are connected in a rotationally fixed manner to a stationary component, wherein the first sun gear shaft and the second ring gear shaft are connected in a rotationally fixed manner, wherein the output shaft, the second carrier shaft and the third ring gear shaft are connected in a rotationally fixed manner,wherein, in the closed state of the first shifting element, a first gear is engaged with a first ratio, wherein, in the first gear, the first ring gear shaft and the third carrier shaft are connected in a rotationally fixed manner, wherein, in the closed state of the second shifting element, a second gear is engaged with a second ratio, wherein, in the second gear, the first sun gear shaft, the second ring gear shaft and the third carrier shaft are connected in a rotationally fixed manner. For this purpose, reference is made to the embodiment according to , Fig. 5.

[0011] A further manual transmission according to the invention for a vehicle comprises an input shaft for connecting an electric machine, an output shaft, a first shifting element, a second shifting element, a third shifting element and a fourth shifting element, a first planetary gear set with a first sun gear shaft, a first ring gear shaft and a first carrier shaft, a second planetary gear set with a second sun gear shaft, a second ring gear shaft and a second carrier shaft and a third planetary gear set with a third sun gear shaft, a third ring gear shaft and a third carrier shaft, wherein the second sun gear shaft and the input shaft are connected in a rotationally fixed manner, wherein the first carrier shaft and the third sun gear shaft are connected in a rotationally fixed manner to a stationary component, wherein the first sun gear shaft and the second ring gear shaft are connected in a rotationally fixed manner, wherein the output shaft, the second carrier shaft and the third ring gear shaft are connected in a rotationally fixed manner,wherein, in the closed state of the first shifting element, a first gear is engaged with a first gear ratio, wherein in the first gear the first ring gear shaft and the third carrier shaft are connected in a rotationally fixed manner, wherein in the closed state of the second shifting element, a second gear is engaged with a second gear ratio, wherein in the second gear the first sun gear shaft, the second ring gear shaft and the third carrier shaft are connected in a rotationally fixed manner, wherein in the closed state of the third shifting element, a third gear designed as a direct gear is engaged with a third gear ratio, wherein in the third gear, two of the three shafts of the second planetary gear set are connected in a rotationally fixed manner, wherein in the closed state of the fourth shifting element, a fourth gear is engaged with a fourth gear ratio, wherein in the fourth gear the second sun gear shaft, the drive shaft and the third carrier shaft are connected in a rotationally fixed manner. For this purpose, reference is made to the embodiment according to, Fig. 6.

[0012] According to one embodiment, the first and second shifting elements are configured to form a positive-locking shifting unit with three shift positions and a single sliding sleeve, wherein a single actuator is configured for axially displacing the sliding sleeve into the respective shift position. In particular, the shifting unit has a neutral position between two gear positions, so that with three shift positions, two gear positions and one neutral position are provided. In a neutral position, two shafts are decoupled from each other via the shifting unit, with the sliding sleeve then being in rotational engagement with a single shaft.

[0013] In particular, the actuator moves the sliding sleeve into the respective shift position and thereby shifts two gears sequentially.

[0014] A further manual transmission according to the invention for a vehicle comprises an input shaft for connecting an electric machine, an output shaft, a first shifting element, a second shifting element, a third shifting element and a fourth shifting element, a first planetary gear set with a first sun gear shaft, a first ring gear shaft and a first carrier shaft, a second planetary gear set with a second sun gear shaft, a second ring gear shaft and a second carrier shaft and a third planetary gear set with a third sun gear shaft, a third ring gear shaft and a third carrier shaft, wherein the second sun gear shaft and the input shaft are connected in a rotationally fixed manner, wherein the first carrier shaft and the third sun gear shaft are connected in a rotationally fixed manner to a stationary component, wherein the first sun gear shaft and the second ring gear shaft are connected in a rotationally fixed manner, wherein the output shaft, the second carrier shaft and the third ring gear shaft are connected in a rotationally fixed manner,wherein, in the closed state of the first shifting element, a first gear is engaged with a first gear ratio, wherein in the first gear the first ring gear shaft, the third ring gear shaft, the second carrier shaft and the output shaft are connected in a rotationally fixed manner, wherein in the closed state of the second shifting element, a second gear is engaged with a second gear ratio, wherein in the second gear the first ring gear shaft and the third carrier shaft are connected in a rotationally fixed manner, wherein in the closed state of the third shifting element, a third gear is engaged with a third gear ratio, wherein in the third gear the first ring gear shaft, the first sun gear shaft and the second ring gear shaft are connected in a rotationally fixed manner, wherein in the closed state of the fourth shifting element, a fourth gear is engaged with a fourth gear ratio, wherein in the fourth gear the first sun gear shaft, the second ring gear shaft and the third carrier shaft are connected in a rotationally fixed manner. For this purpose, reference is made to the embodiment according to, Fig. 7.

[0015] According to one embodiment, the four shifting elements are configured to form a positive-locking shifting unit with seven shift positions and a single sliding sleeve, wherein a single actuator is configured to axially shift the sliding sleeve into the respective shift position. In particular, the shifting unit has a neutral position between every two gear positions, so that with seven shift positions, four gear positions and three neutral positions are provided. In a neutral position, two shafts are decoupled from one another via the shifting unit, wherein the sliding sleeve is then in rotational engagement with a single shaft. In particular, the actuator shifts the sliding sleeve into the respective shift position and thereby shifts four gears sequentially.

[0016] According to one embodiment, the manual transmission further comprises a fifth shifting element, wherein in the engaged state of the fifth shifting element, a fifth gear designed as a direct gear with a fifth ratio is engaged, wherein in fifth gear, two of the three shafts of the second planetary gear set are connected in a rotationally fixed manner. Thus, the second planetary gear set rotates as a block in fifth gear. The fifth gear is designed as a direct gear and, due to the block rotation of the second planetary gear set, has good efficiency and no gearing losses. For example, in fourth gear, the second planetary gear set is blocked by the second ring gear shaft and the connected first sun shaft being connected in a rotationally fixed manner to the second carrier shaft and the connected output shaft.Alternatively, two other of the three shafts of the second planetary gear set can be connected to each other, 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 gear has a ratio of 1, so that the input shaft and the output shaft rotate at the same speed. Reference is also made to the embodiment according to . Fig. 8.

[0017] According to one embodiment, the five shifting elements are configured to form a positive-locking shifting unit with nine shift positions and a single sliding sleeve, with a single actuator configured to axially shift the sliding sleeve into the respective shift position. In particular, the shifting unit has a neutral position between every two gear positions, so that with nine shift positions, five gear positions and four neutral positions are provided. In a neutral position, two shafts are decoupled from each other via the shifting unit, with the sliding sleeve then being in rotational engagement with a single shaft.

[0018] In particular, the actuator moves the sliding sleeve into the respective shift position and thereby shifts five gears sequentially.

[0019] According to one embodiment, the manual transmission further comprises a sixth shifting element, wherein in the closed state of the sixth shifting 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 carrier shaft are connected in a rotationally fixed manner. For this purpose, reference is made to the embodiment according to Fig. 9.

[0020] According to one embodiment, the manual transmission further comprises a fifth shifting element and a sixth shifting element, which are designed to form a positive shifting unit with three shift positions and a single sliding sleeve, wherein in the closed state of the fifth shifting element, a fifth gear designed as a direct gear is engaged with a fifth ratio, wherein in the fifth gear, two of the three shafts of the second planetary gear set are connected in a rotationally fixed manner, wherein in the closed state of the sixth shifting element, a sixth gear is engaged with a sixth ratio, wherein in the sixth gear, the second sun shaft, the drive shaft, and the third carrier shaft are connected in a rotationally fixed manner. Thus, the second planetary gear set rotates as a block in the fifth gear. The fifth gear is designed as a direct gear and, due to the block rotation of the second planetary gear set, has good efficiency and no gearing losses.For example, in fourth gear, the second planetary gear set is locked by non-rotatably connecting the second ring gear shaft and the connected first sun gear shaft to the second carrier shaft and the connected output shaft. Alternatively, two other of the three shafts of the second planetary gear set can be connected to one another, 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 direct gear thus formed has a gear ratio of 1, so that the input shaft and the output shaft rotate at the same speed. Reference is also made to the embodiment according to . Fig. 10.

[0021] A drive unit for a vehicle according to the invention comprises an electric motor and a manual transmission according to the invention, wherein the electric motor is arranged either coaxially or axially parallel to the manual 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 mounted in a differential carrier so they can rotate about their own axis. The respective output gear is connected in a rotationally fixed manner to the respective differential output shaft. The differential is driven via the differential carrier, which is configured as the differential input shaft. Furthermore, alternative designs of the differential are also conceivable, for example, as a spur gear differential or a planetary differential.The drive power fed into the differential via the differential input shaft is distributed in a conventional manner between the two differential output shafts and transmitted to the drive wheels of the axle. The differential output shafts are designed to be connected to the vehicle's drive wheels in a drivingly effective manner. The respective differential output shaft can be connected to the corresponding vehicle wheel directly or indirectly via a downstream fixed gear, a joint, a propeller shaft, and / or a wheel hub.

[0023] The manual transmission according to the invention is particularly suitable for an electric central drive that has a downstream differential gear, in particular a bevel gear. 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 on the differential is omitted. For example, the electric motor can be connected axially parallel via at least one spur gear transmission. Depending on the required transmission ratio and the installation space, multiple 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 as well as explanations regarding technical effects, advantages, and advantageous embodiments of the manual transmission according to the invention also apply mutatis mutandis to the drive unit according to the invention 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 provided with the same reference numerals. They show: Fig. 1 is a highly abstracted schematic view of a vehicle with a drive axle having a drive unit according to the invention; Fig. 2 a highly abstracted schematic view of a manual transmission according to the invention according to a first embodiment; Fig. 3 a highly abstracted schematic view of a manual transmission according to the invention according to a second embodiment; Fig. 4 a highly abstracted schematic view of a drive unit according to the invention with a manual transmission according to the second embodiment; Fig. 5 a highly abstracted schematic view of a manual transmission according to the invention according to a third embodiment; Fig. 6 a highly abstracted schematic view of a manual transmission according to the invention according to a fourth embodiment; Fig. 7 a highly abstracted schematic view of a manual transmission according to the invention according to a fifth embodiment; Fig. 8 shows a highly abstracted schematic view of a manual transmission according to the invention according to a sixth embodiment; Fig. 9 a highly abstracted schematic view of a manual transmission according to the invention according to a seventh embodiment and Fig. 10 is a highly abstracted schematic view of a manual transmission according to the invention according to an eighth embodiment.

[0026] Fig. 1 shows a vehicle 100 with a first axle 101 with two vehicle wheels R1, R2 and a second axle 102 with two vehicle wheels R3, R4. In the present case, the first axle 101 is designed as the rear drive axle of the vehicle 100 and is equipped with a drive unit according to the invention. The drive unit comprises an electric machine EM, which is designed to generate drive power, a manual transmission SG with several gears and a differential DG. Thus, the vehicle 100 is designed as an electric vehicle, i.e., as an electrically driven vehicle. The drive unit is arranged in the vehicle's longitudinal direction and is drivingly connected to the vehicle wheels R1, R2 of the first axle 101. A detailed design of this drive unit is shown in Fig. 4. Alternatively, and not shown in detail, the drive unit can be arranged transversely to the vehicle's longitudinal direction.

[0027] In the present case, no additional drive unit is arranged on the second axle 102, i.e., the front axle of the vehicle 100, thereby saving costs, weight, and installation space. Alternatively, the drive unit can be arranged on the front axle of the vehicle 100 instead of on the rear axle. To implement an all-wheel drive system, an additional drive unit can be arranged on the second axle 102 and be drivingly connected to the vehicle wheels R3, R4 of this axle 102.

[0028] Fig. 2 shows a manual transmission SG according to a first embodiment. The manual transmission SG comprises an input shaft An, which is designed to connect an electric machine (not shown in detail here), an output shaft Ab, which can be drivingly connected to a differential or a drive wheel of the vehicle, three shifting elements, namely a first shifting element A, a second shifting element B and a third shifting element C, as well as three planetary gear sets PS1, PS2, PS3, each with three shafts. The input 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 one another. The electric machine can be arranged either coaxially or axially parallel to the manual transmission SG and connected to the input shaft An. If the electric machine is arranged axially parallel, at least one spur gear stage can be provided for connection to the input shaft An.This embodiment and the following two embodiments are suitable for installation in the vehicle longitudinally or transversely to the direction of travel of the vehicle.

[0029] The first planetary gear set PS1 comprises three shafts, namely a first sun shaft SO1, a first ring gear shaft HR1, and a first carrier shaft ST1. The first carrier shaft ST1 carries a plurality of planet gears that mesh with the first sun shaft SO1 and the first ring gear shaft HR1. The second planetary gear set PS2 also comprises three shafts, namely a second sun shaft SO2, a second ring gear shaft HR2, and a second carrier shaft ST2. The second carrier shaft ST2 carries a plurality of planet gears that mesh with the second sun shaft SO2 and the second ring gear shaft HR2. The third planetary gear set PS3 also comprises three shafts, namely a third sun shaft SO3, a third ring gear shaft HR3, and a third carrier shaft ST3. The third carrier shaft ST3 carries a plurality of planet gears that mesh with the third sun shaft SO3 and the third ring gear shaft HR3.

[0030] The second sun gear shaft SO2 and the input shaft An are connected for rotational stability. The first carrier shaft ST1 and the third sun gear shaft SO3 are each connected for rotational stability to a stationary component designed as a housing. The first sun gear shaft SO1 and the second ring gear shaft HR2 are connected for rotational stability and form a first coupling shaft. The output shaft Ab, the second carrier shaft ST2, and the third ring gear shaft HR3 are connected for rotational stability and form a second coupling shaft.

[0031] Furthermore, the three planetary gear sets PS1, PS2, PS3 are arranged axially adjacent to each other 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, PS3. The embodiments shown in Fig. 2 to Fig. 10 show only the “upper” half of the respective manual transmission SG, whereby the “lower”, not shown half is designed symmetrically to the “upper” half.

[0032] The first shifting element A, the second shifting element B and the third shifting element C are combined to form a shifting unit with a single sliding sleeve SM and five shift positions, namely three gear positions and two neutral positions. The sliding sleeve SM is arranged radially nested on the outer circumference of the planetary gear sets PS1, PS2, PS3 in order to save axial installation space and thereby increase axial compactness. The respective neutral position is arranged between two gear positions. The five shift positions are achieved by axially shifting the sliding sleeve SM. The sliding sleeve SM has claw shift elements and can be axially shifted into the respective shift position by means of a single actuator AK. Thus, all five shift positions of the shifting unit are arranged linearly. The three gears are shifted one after the other or sequentially by shifting the sliding sleeve SM in an axial direction, beyond the neutral position.This not only saves weight and components, but also costs, installation space and assembly effort.

[0033] When the first shifting element A is closed, a first gear with a first ratio is engaged, whereby in first gear the first ring gear shaft HR1, the third ring gear shaft HR3, the second carrier shaft ST2 and the output shaft Ab are connected in a rotationally fixed manner. When the second shifting element B is closed, a second gear with a second ratio is engaged, whereby in second gear the first ring gear shaft HR1 and the third carrier shaft ST3 are connected in a rotationally fixed manner. When the third shifting element C is closed, a third gear with a third ratio is engaged, whereby in 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.

[0034] First gear is engaged when the sliding sleeve SM is in a first gear position, i.e., a first shift position. When the sliding sleeve SM is in the first shift position, the first shift element A connects the first ring gear shaft HR1, the third ring gear shaft HR3, the second carrier shaft ST2, and the output shaft Ab to engage first gear. First gear is engaged by engaging the sliding sleeve SM and engaging only the first shift element A. The first coupling shaft rotates rapidly in reverse.

[0035] First gear is disengaged by axially shifting the sliding sleeve SM into a neutral position, i.e., into a second shift position. In the second shift 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 shift elements A, B, C are open, whereby an electric machine that can be connected to the drive shaft An can synchronize the target gear. In this case, Fig. 2 shows this second switching position of the sliding sleeve SM.

[0036] Second gear is engaged by axially shifting the sliding sleeve SM into a second gear position, i.e., a third shift position. The second shift element B, in an actuated or closed state—i.e., in the third shift position of the sliding sleeve SM—connects the first ring gear shaft HR1 and the third carrier shaft ST3 to engage second gear. Second gear is engaged by actuating the sliding sleeve SM and closing only the second shift element B. The second coupling shaft rotates in reverse.

[0037] Second gear is engaged by axially shifting the sliding sleeve SM into a second neutral position, i.e., the fourth shift position. In the 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.

[0038] 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.

[0039] Fig. Figure 3 shows a second embodiment of the manual transmission SG according to the invention. The manual transmission SG according to Fig. 3 essentially corresponds to the manual transmission SG according to Fig. 2, whereby one 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 are omitted. The first shifting element B', the second shifting element C' and the third shifting element D' are combined to form a shifting unit with a single sliding sleeve SM and five shift positions, namely three gear positions and two neutral positions. When the first shifting element B' is closed, a first gear with a first ratio is engaged, wherein in first gear the first ring gear shaft HR1 and the third carrier shaft ST3 are connected in a rotationally fixed manner. When the second shifting element C' is closed, a second gear with a second ratio is engaged, wherein in second 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. When the third shifting element D' is closed, a third gear with a third ratio is engaged, wherein in third gear the first sun gear shaft SO1, the second ring gear shaft HR2 and the third carrier shaft ST3 are connected in a rotationally fixed manner.In third gear, the first coupling shaft rotates forward. Otherwise, the design corresponds to that shown in . Fig. 3 the embodiment according to Fig. 2, to which reference is made.

[0040] Fig. 4 shows the second embodiment of the manual transmission SG according to the invention in a drive train of a vehicle. In this case, an electric machine EM, a bevel gear stage KG and a differential DG are also arranged in the drive train. The electric machine EM and the manual transmission SG are arranged on a common axis of rotation R and are thus coaxial with one another. The differential DG is connected to the output shaft Ab via the bevel gear stage KG and is arranged transversely thereto. The electric machine EM has a stator EMS fixed to the housing and a rotatable rotor EMR, wherein the input shaft An is connected to the rotor EMR in a rotationally fixed manner. 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, 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, with the other bevel gear of the bevel gear stage KG being non-rotatably connected to the output shaft Ab, and with the two bevel gears meshing. The differential DG, designed as a ball or bevel gear differential, has two wheel-side output elements, in particular a first output gear and a second output gear. The two output gears each mesh with a compensating element. The compensating elements are mounted in the differential carrier so they can rotate about their own axis. The respective output gear is non-rotatably connected to the respective differential output shaft D2, D3. The differential DG is therefore driven via the differential carrier, which is drivingly connected to the output shaft Ab via the bevel gear stage.Arrows on the differential output shafts D2, D3 indicate a connection to a respective vehicle wheel of this vehicle axle. Otherwise, the embodiment corresponds to . Fig. 4 the embodiment according to Fig. 3, to which reference is made.

[0041] Fig. Figure 5 shows a third embodiment of the manual transmission SG according to the invention. The manual transmission SG according to Fig. 5 essentially corresponds to the manual transmission SG according to Fig. 2, whereby 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'' as well as 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 Fig. 2 are omitted. The first shifting element B'' and the second shifting element D'' are combined to form a shifting unit with a single sliding sleeve SM and three shift positions, namely two gear positions and one neutral position. In the closed state of the first shifting element B'', a first gear with a first ratio is engaged, wherein in first gear the first ring gear shaft HR1 and the third carrier shaft ST3 are connected in a rotationally fixed manner. In the closed state of the second shifting element D'', a second gear with a second ratio is engaged, wherein in second gear the first sun gear shaft SO1, the second ring gear shaft HR2 and the third carrier shaft ST3 are connected in a rotationally fixed manner. In second gear the first coupling shaft rotates forward. Otherwise, the embodiment according to Fig. 5 the embodiment according to Fig. 2, to which reference is made.

[0042] Fig. Figure 6 shows a fourth embodiment of the manual transmission SG according to the invention. The manual transmission SG according to Fig. 6 essentially corresponds to the manual transmission SG according to Fig. 2, whereby 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''' as well as 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 Fig. 2 are omitted. The first shifting element C''' and the second shifting element D''' are combined to form a shifting unit with a single sliding sleeve SM and three shift positions, namely two gear positions and one neutral position. When the first shifting element C''' is closed, a first gear with a first ratio is engaged, whereby in 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. When the second shifting element D''' is closed, a second gear with a second ratio is engaged, whereby in second gear the first sun gear shaft SO1, the second ring gear shaft HR2 and the third carrier shaft ST3 are connected in a rotationally fixed manner. In second gear the first coupling shaft rotates forward.

[0043] Furthermore, the manual transmission has a third shifting element E'' and a fourth shifting element F'', wherein the third and fourth shifting elements E'', F'' are designed to form a further positive-locking shifting unit with three shift positions and a single sliding sleeve SM', wherein this further shifting unit is arranged axially between the second planetary gear set PS2 and the third planetary gear set PS3 and is shifted by means of a separate actuator AK'. When the third shifting element E'' is closed, a third gear designed as a direct gear with a third ratio is engaged, wherein in the third gear two of the three shafts of the second planetary gear set PS2 are connected in a rotationally fixed manner and the second planetary gear set PS2 is thereby blocked.In this case, in third gear, the second carrier shaft ST2, the output shaft Ab which is connected to it in a rotationally fixed manner, and the third ring gear shaft HR3 as well as the second sun shaft SO2 and the input shaft An which is connected to it in a rotationally fixed manner are 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 ratio is engaged, whereby in fourth gear the second sun shaft SO2, the input shaft An and the third carrier shaft ST3 are connected in a rotationally fixed manner. The first coupling shaft therefore rotates forwards faster. The manual transmission therefore has the following... Fig. 6 has two switching units, each with three switching positions, for the realization of four gears, whereby only one of the four switching elements is closed in each gear. Otherwise, the embodiment according to Fig. 6 the embodiment according to Fig. 2, to which reference is made.

[0044] Fig. Figure 7 shows a fifth embodiment of the manual transmission SG according to the invention. The manual transmission SG according to Fig. 7 essentially corresponds to the manual transmission SG according to Fig. 2, whereby one 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 shifting element A, the second shifting element B, the third shifting element C, and the fourth shifting element D are combined to form a shifting unit with a single sliding sleeve SM and seven shift positions, namely four gear positions and three neutral positions. The first five shift positions of the sliding sleeve SM according to this fifth embodiment of the manual transmission SG correspond exactly to the first five shift positions of the sliding sleeve SM according to the first embodiment of the manual transmission SG.

[0045] Third gear is disengaged 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, D are open, whereby the electric machine EM can synchronize the target gear. 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 the first sun gear shaft SO1, the second ring gear shaft HR2, and the third carrier shaft ST3 to shift the fourth gear. Otherwise, the embodiment according to Fig. 7 the embodiment according to Fig. 2, to which reference is made.

[0046] Fig. Figure 8 shows a sixth embodiment of the manual transmission SG according to the invention. The manual transmission SG according to Fig. 8 essentially corresponds to the manual transmission SG according to Fig. 7, whereby one difference between these two embodiments lies in 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 shifting element A, the second shifting element B, the third shifting element C, the fourth shifting element D, and the fifth shifting element E are combined to form a shifting unit with a single sliding sleeve SM and nine shift positions, namely five gear positions and four neutral positions. The first seven shift positions of the sliding sleeve SM according to this sixth embodiment of the manual transmission SG correspond exactly to the first seven shift positions of the sliding sleeve SM according to the fifth embodiment of the manual transmission SG.

[0047] Fourth gear is disengaged by axially moving 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, E are open, allowing the electric machine EM to synchronize the target gear. Fifth gear is engaged by axially moving the sliding sleeve SM into a fifth gear position, i.e. a 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 in order to shift the fifth gear, which is designed as a direct gear. In fifth gear, the second planetary gear set PS2 is blocked.In this case, in fifth gear, the second carrier shaft ST2, the output shaft Ab connected to it for rotational stability, the third ring gear shaft HR3, as well as the second sun gear shaft SO2 and the input shaft An connected to it for rotational stability are connected. As a result, the output shaft Ab rotates at the same speed as the input shaft An. Otherwise, the embodiment corresponds to . Fig. 8 the embodiment according to Fig. 7, to which reference is made.

[0048] Fig. Figure 9 shows a seventh embodiment of the manual transmission SG according to the invention. The manual transmission SG according to Fig. 9 essentially corresponds to the manual transmission SG according to Fig. 8, wherein a difference between these two embodiments lies in the arrangement of a further shifting element. In the present case, the manual transmission SG has a sixth shifting element F, which is designed as a single shifting element. When the sixth shifting element F is engaged, a sixth gear with a sixth ratio is engaged, wherein in the sixth gear, the second sun gear shaft SO2, the input shaft An, and the third carrier shaft ST3 are connected in a rotationally fixed manner. The first coupling shaft therefore rotates forwards more quickly. The sixth shifting element F is arranged axially between the second planetary gear set PS2 and the third planetary gear set PS3 and is shifted by means of a separate actuator (not shown in detail). Otherwise, the embodiment according to Fig. 9 the embodiment according to Fig. 8, to which reference is made.

[0049] Fig. 10 shows an eighth embodiment of the manual transmission SG according to the invention. The manual transmission SG according to Fig. 10 essentially corresponds to the manual transmission SG according to Fig. 7, wherein a difference between these two embodiments lies in the arrangement of a further switching unit with two switching elements. In the present case, the manual transmission SG has a fifth switching element E' and a sixth switching element F', which are designed to form a positive 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'. When the fifth switching element E' is closed, a fifth gear designed as a direct gear with a fifth ratio is engaged, wherein in the fifth gear two of the three shafts of the second planetary gear set PS2 are connected in a rotationally fixed manner and the second planetary gear set PS2 is thereby blocked.In this case, in fifth gear, the second carrier shaft ST2, the output shaft Ab which is connected to it in a rotationally fixed manner, and the third ring gear shaft HR3 as well as the second sun gear shaft SO2 and the input shaft An which is connected to it in a rotationally fixed manner are 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 ratio is engaged, whereby in sixth gear the second sun gear shaft SO2, the input shaft An and the third carrier shaft ST3 are connected in a rotationally fixed manner. The first coupling shaft therefore rotates forwards faster. The manual transmission therefore has the following... Fig. 10 has two switching units for the realization of six gears, whereby in each gear only one of the six switching elements is closed. Otherwise, the embodiment according to Fig. 10 the embodiment according to Fig. 7, to which reference is made. Reference symbol 100 vehicles 101 first axis 102 second axis R1 vehicle wheel R2 vehicle wheel R3 vehicle wheel R4 vehicle wheel On drive shaft From output shaft SG manual transmission EM electric machine EMS stator of the electrical machine EMR rotor of the electric machine PS1 first planetary gear set SO1 first solar wave HO1 first ring gear shaft ST1 first bridge wave PS2 second planetary gear set SO2 second solar wave HO2 second ring gear shaft ST2 second web wave PS3 third planetary set SO3 third solar wave HO3 third ring gear shaft ST3 third web wave AK Actuator AK' Actuator SM sliding sleeve SM' sliding sleeve G Housing R rotation axis KG bevel gear stage DG Differential D1 differential input shaft D2 first differential output shaft D3 second differential output shaft 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 QUOTES CONTAINED IN THE DESCRIPTION

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

[0000] DE 10 2019 218 413 A1

[0002]

Claims

[1] Manual transmission (SG) for a vehicle (100) comprising • a drive shaft (An) for connecting an electrical machine (EM), • an output shaft (Ab), • a first switching element (A), a second switching element (B), a third switching element (C), • a first planetary gear set (PS1) with a first sun shaft (SO1), a first ring gear shaft (HR1) and a first carrier shaft (ST1), • a second planetary gear set (PS2) with a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2) and • a third planetary gear set (PS3) with a third sun shaft (SO3), a third ring gear shaft (HR3) and a third carrier shaft (ST3), • 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 connected in a rotationally fixed manner to a stationary component, • wherein the first sun shaft (SO1) and the second ring gear shaft (HR2) are connected in a rotationally fixed manner, • whereby the output shaft (Ab), the second carrier 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 carrier 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 transmission ratio is engaged, wherein in the second gear the first ring gear shaft (HR1) and the third carrier 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 electrical machine (EM), • an output shaft (Ab), • a first switching element (B'), a second switching element (C'), a third switching element (D'), • a first planetary gear set (PS1) with a first sun shaft (SO1), a first ring gear shaft (HR1) and a first carrier shaft (ST1), • a second planetary gear set (PS2) with a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2) and • a third planetary gear set (PS3) with a third sun shaft (SO3), a third ring gear shaft (HR3) and a third carrier shaft (ST3), • 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 connected in a rotationally fixed manner to a stationary component, • wherein the first sun shaft (SO1) and the second ring gear shaft (HR2) are connected in a rotationally fixed manner, • whereby the output shaft (Ab), the second carrier 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 ratio is engaged, wherein in the first gear the first ring gear shaft (HR1) and the third carrier 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 gear 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 transmission ratio is engaged, wherein in the third gear the first sun shaft (SO1), the second ring gear shaft (HR2) and the third carrier shaft (ST3) are connected in a rotationally fixed manner. [3] Manual transmission (SG) according to claim 1 or 2, wherein the three switching elements (A, B, C / B', C', D') are combined to form a positive switching unit with five switching positions and a single sliding sleeve (SM), wherein a single actuator (AK) is arranged for the axial displacement of the sliding sleeve (SM) into the respective switching position. [4] Manual transmission (SG) for a vehicle (100) comprising • a drive shaft (An) for connecting an electrical machine (EM), • an output shaft (Ab), • a first switching element (B'') and a second switching element (D''), • a first planetary gear set (PS1) with a first sun shaft (SO1), a first ring gear shaft (HR1) and a first carrier shaft (ST1), • a second planetary gear set (PS2) with a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2) and • a third planetary gear set (PS3) with a third sun shaft (SO3), a third ring gear shaft (HR3) and a third carrier shaft (ST3), • 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 connected in a rotationally fixed manner to a stationary component, • wherein the first sun shaft (SO1) and the second ring gear shaft (HR2) are connected in a rotationally fixed manner, • whereby the output shaft (Ab), the second carrier 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 ratio is engaged, wherein in the first gear the first ring gear shaft (HR1) and the third carrier 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 transmission ratio is engaged, wherein in the second gear the first sun shaft (SO1), the second ring gear shaft (HR2) and the third carrier 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 electrical 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 gear set (PS1) with a first sun shaft (SO1), a first ring gear shaft (HR1) and a first carrier shaft (ST1), • a second planetary gear set (PS2) with a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2) and • a third planetary gear set (PS3) with a third sun shaft (SO3), a third ring gear shaft (HR3) and a third carrier shaft (ST3), • 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 connected in a rotationally fixed manner to a stationary component, • wherein the first sun shaft (SO1) and the second ring gear shaft (HR2) are connected in a rotationally fixed manner, • whereby the output shaft (Ab), the second carrier 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 transmission ratio is engaged, wherein in the second gear the first sun shaft (SO1), the second ring gear shaft (HR2) and the third carrier 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 gear with a third ratio is engaged, wherein in the third gear two of the three shafts of the second planetary gear 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 web shaft (ST3) are connected in a rotationally fixed manner. [6] Manual transmission (SG) according to claim 4 or 5, wherein the first and the second switching element (B'', D'' / C''', D''') are combined to form a positive switching unit with three switching positions and a single sliding sleeve (SM), wherein a single actuator (AK) is arranged for the 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 electrical 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 gear set (PS1) with a first sun shaft (SO1), a first ring gear shaft (HR1) and a first carrier shaft (ST1), • a second planetary gear set (PS2) with a second sun shaft (SO2), a second ring gear shaft (HR2) and a second carrier shaft (ST2) and • a third planetary gear set (PS3) with a third sun shaft (SO3), a third ring gear shaft (HR3) and a third carrier shaft (ST3), • 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 connected in a rotationally fixed manner to a stationary component, • wherein the first sun shaft (SO1) and the second ring gear shaft (HR2) are connected in a rotationally fixed manner, • whereby the output shaft (Ab), the second carrier 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 carrier 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 transmission ratio is engaged, wherein in the second gear the first ring gear shaft (HR1) and the third carrier 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 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 carrier shaft (ST3) are connected in a rotationally fixed manner. [8] Manual transmission (SG) according to claim 7, wherein the four switching elements (A, B, C, D) are combined to form a positive switching unit with seven switching positions and a single sliding sleeve (SM), wherein a single actuator (AK) is arranged for the axial displacement of the sliding sleeve (SM) into the respective switching position. [9] Manual transmission (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 gear 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 connected in a rotationally fixed manner. [10] Manual transmission (SG) according to claim 9, wherein the five switching elements (A, B, C, D, E) are combined to form a positive switching unit with nine switching positions and a single sliding sleeve (SM), wherein a single actuator (AK) is arranged for the axial displacement of the sliding sleeve (SM) into the respective switching position. [11] Manual transmission (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 gear ratio is engaged, wherein in the sixth gear the second sun shaft (SO2), the drive shaft (An) and the third carrier shaft (ST3) are connected in a rotationally fixed manner. [12] Manual transmission (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 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 gear is engaged with a fifth gear ratio, wherein in the fifth gear two of the three shafts of the second planetary gear set (PS2) are connected in a rotationally fixed manner, wherein in the closed state of the sixth shifting element (F') a sixth gear is engaged with a sixth gear ratio, wherein in the sixth gear the second sun shaft (SO2), the drive shaft (An) and the third carrier shaft (ST3) are connected in a rotationally fixed manner. [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 axially parallel or coaxial with 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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