Transmission comprising a differential

Abstract

The invention relates to a transmission (3) for a drive train (2) of a vehicle (1), comprising a differential (7) which is designed to distribute a drive power to a first output shaft (5) and a second output shaft (6), wherein the differential (7) has a planet carrier (18b) with an at least partly circumferential and segmented spline (9), the spline (9) on the planet carrier (18b) engages into a spline (11) on the housing (21) of the transmission (3) and is connected thereto for conjoint rotation, and at least one bore (23) is formed in the housing (21) between two segments (22) of the spline (9) on the planet carrier (18b) in the circumferential direction, said bores (23) being designed to receive screw elements and fix a housing cover (25) to the housing (21).

Description

[0001] TRANSMISSION INCLUDING A DIFFERENTIAL

[0002] The invention relates to a transmission for a drive train of a vehicle and to a drive train with such a transmission. Furthermore, the invention also relates to a vehicle with such a transmission.

[0003] DE 10 2013 215 877 B4 discloses an epicyclic gear system for splitting the drive power applied to a power input to a first and a second power output, while reducing the output speed to a speed level below the drive speed at the power input. The epicyclic gear system has a first planetary stage comprising a first sun gear, a first planetary set, a first planetary carrier, and a first ring gear. Furthermore, the epicyclic gear system has a second planetary stage comprising a second sun gear, a second planetary set, a second planetary carrier, and a second ring gear. Furthermore, the epicyclic gear system has a third planetary stage comprising a third sun gear, a third planetary set, a third planetary carrier, and a third ring gear.The first sun gear acts as the power input, with the first planet carrier being rotationally fixed to the second sun gear. The second planet carrier is stationary, the first ring gear is rotationally fixed to the third sun gear, and the third ring gear is rotationally fixed to the second planet carrier. A first power output is achieved via the third planetary stage, with a second power output achieved via the second ring gear of the second planetary stage.

[0004] The object of the present invention is to create a compact transmission for a vehicle drivetrain. In particular, the transmission should be more compact in the radial direction and be simple to manufacture and assemble. This object is achieved by a transmission having the features of independent patent claim 1. Advantageous embodiments are the subject of the dependent claims, the following description, and the figures.A transmission according to the invention for a drive train of a vehicle comprises a differential which is designed to distribute a drive power between a first output shaft and a second output shaft, wherein the differential has a planetary carrier with an at least partially circumferential and segmented spline, wherein the spline on the planetary carrier engages in a correspondingly designed spline on a housing of the transmission and is connected to it in a rotationally fixed, in particular form-fitting manner, wherein in the circumferential direction between two segments of the spline on the planetary carrier at least one bore is formed on the housing, wherein these bores on the housing are designed to receive screw elements and to fix a housing cover on the housing.

[0005] The planet carrier is connected to the housing via the intermeshing splines on the planet carrier and the housing, so that the planet carrier is fixed to the housing and thus cannot rotate. The housing can be constructed as a single piece or in multiple pieces, so the term "housing" also refers to a housing part, in particular an element that is connected to the housing in a rotationally fixed manner.

[0006] Segmented spline engagement on the planet carrier means that the planet carrier has a plurality of toothed segments which together form at least partially circumferential spline engagement. In particular, each segment has external teeth, while the housing has internal teeth. Segmenting the spline engagement not only saves material and weight during production of the planet carrier, but also creates circumferential clearance between the segments. According to the invention, these clearances are used to accommodate sections of the housing in which at least one bore is located. This allows the transmission to be made more compact. Screw elements are screwed into these bores on the housing, thereby securing the housing cover to the housing.Alternatively, the bores arranged circumferentially between the segments can also accommodate and / or guide other means, for example, to fix the housing cover to the housing. The differential is designed to be effectively arranged, in the assembled state of the drive train, between an input shaft and a first output shaft and a second output shaft. The differential distributes the drive power applied to the input shaft, which is introduced into the transmission by a drive unit, in particular an electric motor, between the two output shafts. The output shafts thus serve as the output shafts of the transmission.

[0007] A "shaft" is a rotatable component of the transmission through which the associated components of the transmission are connected to one another in a rotationally fixed manner. The respective shaft can connect the components axially or radially, or even both axially and radially. A shaft is not exclusively understood as a cylindrical, rotatably mounted machine element for transmitting torque, for example, but rather also includes general connecting elements that connect individual components or elements to one another, in particular connecting elements that connect multiple elements to one another in a rotationally fixed manner.

[0008] According to one embodiment, the root diameter of the spline on the housing has a radial overlap with the bores for receiving screw elements and securing the housing cover to the housing. Due to the radial overlap of the root diameter of the spline on the housing and the bores for receiving screw elements on the housing, the gearbox is designed to be more compact, particularly in the radial direction. This is because the bores for receiving the screw elements on the housing are thereby shifted further radially inward. The outer diameter of the housing is reduced without affecting the axial dimensions of the housing.

[0009] For example, the root diameter of the spline on the housing and the holes for accommodating screw elements and securing the housing cover to the housing are essentially arranged on a common circular path. In other words, the center of the holes for accommodating screw elements on the housing is essentially located on the root diameter of the spline on the housing, i.e. with at most minor deviations of a few millimeters. This represents a good compromise between a compact design and simple manufacture and assembly of the gearbox. In particular, all holes designed to accommodate screw elements and secure the housing cover to the housing are arranged on this common circular path, which essentially corresponds to the root diameter of the spline on the housing. This further improves the manufacture and assembly of the gearbox.

[0010] According to one embodiment, exactly two bores are formed in the circumferential direction between two segments of the spline on the planet carrier for accommodating screw elements and securing the housing cover to the housing. Thus, in the circumferential direction, after each segment of the spline on the planet carrier, there are always two bores on the housing designed to accommodate screw elements. This is followed in the circumferential direction by another segment of the spline on the planet carrier.

[0011] According to one embodiment, the spline on the planet carrier has at least three, preferably six, segments evenly distributed in the circumferential direction. For example, the planet carrier further has at least six, preferably twelve, bores evenly distributed in the circumferential direction for receiving screw elements and securing the housing cover to the housing.

[0012] According to one embodiment, bores for receiving planetary gear pins are arranged on the planetary carrier, with exactly one bore for a pin being arranged in the circumferential direction between two segments of the spline on the planetary carrier. In particular, the bores for receiving pins for planetary gears and the segments of the spline on the planetary carrier are arranged in such a way that the seats for the planetary gears on the planetary carrier remain machinable. This, in particular, improves the production of the transmission.According to a preferred embodiment, the differential has a first planetary gear set and at least one second planetary gear set operatively connected thereto, wherein a first output torque can be transmitted at least indirectly to the first output shaft by means of the first planetary gear set of the differential, wherein a support torque of the first planetary gear set in the second planetary gear set can be converted such that a second output torque corresponding to the first output torque can be transmitted to the second output shaft.

[0013] The differential can be designed in any desired manner. Preferably, the differential is an integral differential comprising a first planetary gear set and at least one second planetary gear set operatively connected thereto. A first output torque can be transmitted at least indirectly to the first output shaft by means of the first planetary gear set of the differential. A support torque of the first planetary gear set can be converted in the second planetary gear set of the differential such that a second output torque corresponding to the first output torque can be transmitted to the second output shaft.

[0014] For the purposes of this invention, an integral differential is understood to mean a differential with a first planetary gear set and at least one second planetary gear set operatively connected to the first planetary gear set, wherein the first planetary gear set is drive-connected to the input shaft, to the second planetary gear set, and at least indirectly to the first output shaft. The second planetary gear set is also drive-connected to the second output shaft. By means of such an integral differential, the input torque at the input shaft can be converted and divided or transmitted to the two output shafts in a defined ratio. Preferably, the input torque is transmitted 50% each, i.e. half, to the output shafts. Thus, the differential has no component to which the sum of the two output torques is applied. In other words, the generation of a cumulative torque is prevented.Furthermore, at identical output shaft speeds, the differential has no gears rotating within the block or rotating without rolling motion. Therefore, regardless of the output shaft speeds, there is always a relative movement between the meshing components of the differential.

[0015] A “planetary gear set” is a unit comprising a sun gear, a ring gear and several planetary gears guided by a planet carrier on a circular path around the sun gear, the planetary gears meshing with the ring gear and the sun gear.

[0016] Preferably, a first sun gear of the first planetary gear set is configured to be non-rotatably connected to the input shaft when the drive train is assembled. A first planet carrier of the first planetary gear set is further preferably configured to be at least indirectly non-rotatably connected to the first output shaft. A first ring gear of the first planetary gear set is further preferably at least indirectly non-rotatably connected to a second sun gear of the second planetary gear set. A second ring gear of the second planetary gear set is also preferably configured to be at least indirectly non-rotatably connected to the second output shaft. The planet carrier of the second planetary gear set, also referred to below as the second planet carrier, is non-rotatably connected to the housing or a part of the housing. The planet carrier described above belongs to the second planetary gear set and is thus the second planet carrier in this example.

[0017] According to one embodiment, the first planetary carrier is connected to the first output shaft in a rotationally fixed manner via a spline. The spline is provided for supporting and transmitting a torque and a rotational speed. The spline provides a detachable connection between the first planetary carrier and the first output shaft, whereby the spline can effectively transmit and support a torque and a rotational speed during operation.

[0018] A housing part is defined as a rotationally and axially fixed component of the transmission, for example, the transmission housing itself, a part of it, or a cover of the transmission housing. Components that rest on the housing part are therefore fixed to the housing. The term "fixed to the housing" means that no relative movement occurs or can occur between the respective component and the transmission housing part.

[0019] The fact that two components of the transmission are "connected" or "coupled" or "connected to one another" in a rotationally fixed manner means, in the context of the invention, a permanent coupling of these components so that they cannot rotate independently of one another. This is therefore understood to mean a permanent rotary connection. In particular, no switching element is provided between these components, which can be elements of the differential and / or shafts and / or a rotationally fixed component of the transmission; instead, the corresponding components are firmly coupled to one another. A torsionally flexible connection between two components is also understood to be fixed or rotationally fixed.

[0020] The invention includes the technical teaching that the transmission further comprises a carrier element that is connected in a rotationally fixed manner to the second output shaft and operatively connects the second planetary gear set to the second output shaft. If the second ring gear of the second planetary gear set is at least indirectly connected in a rotationally fixed manner to the second output shaft, the carrier element is to be understood as a coupling shaft, in particular as a ring gear carrier of the second ring gear. The second ring gear of the second planetary gear set is accordingly connected in a rotationally fixed manner to the second output shaft via the ring gear carrier. It is conceivable that the carrier element and the second output shaft are formed as a single piece. In this case, the carrier element is part of the second output shaft. The carrier element is designed, for example, as a sheet-metal, annular disk-shaped component that is connected in a rotationally fixed manner to the second ring gear, for example via a crown gear or the like.The carrier element can also be integrally connected, for example, by a material bond, to the second ring gear of the second planetary gear set or to the second output shaft. The carrier element can compensate for a radial offset between the second ring gear and the second output shaft. A drive train according to the invention for a vehicle comprises a transmission according to the invention, an input shaft, a first output shaft, and a second output shaft. The differential of the transmission is operatively arranged between the input shaft and the two output shafts and distributes the drive power applied to the input shaft between the two output shafts.

[0021] When the drive train is in the assembled state, the transmission is operatively connected to the drive unit via the input shaft. The drive unit is preferably an electric machine, wherein the input shaft of the drive unit is a rotor of the electric machine or is connected or coupled in a rotationally fixed manner to the rotor or a rotor shaft of the electric machine. The rotor is rotatably mounted relative to a stator of the electric machine that is fixed to the housing. The electric machine is preferably connected to an energy storage device that supplies the electric machine with electrical energy. Furthermore, the electric machine can preferably be controlled or regulated by power electronics. Alternatively, the drive unit can also be an internal combustion engine, wherein the input shaft in this case is, for example, a crankshaft or is connected or coupled in a rotationally fixed manner to the crankshaft.

[0022] The input shaft is preferably designed as a hollow shaft. This allows one of the output shafts, in particular the first output shaft, to be guided axially through the input shaft. One of the output shafts, in particular the first output shaft, is preferably guided through the transmission and, if applicable, through the drive unit of the drive train. The respective output shaft is thus guided "inline" through the transmission in order to transmit drive power to the vehicle wheel operatively connected to it. In this case, the output shafts are arranged coaxially to one another, which has a positive effect on the required radial installation space. The coaxial arrangement of the output shafts therefore enables a radially compact design of the transmission. A parallel, offset arrangement of the output shafts is also conceivable and can be implemented using appropriate gear ratios.The output shafts of the drive train are designed, in particular, to be operatively connected to a wheel of the vehicle. The respective output shaft can be connected to the corresponding wheel directly or indirectly, i.e., via a joint and / or a wheel hub, for example.

[0023] The transmission according to the invention, in particular a drive train with such a transmission, can be used in a vehicle. Thus, a vehicle according to the invention has at least one such drive train. The vehicle is preferably a motor vehicle, in particular an automobile (e.g., a passenger car weighing less than 3.5 t), a bus, or a truck (e.g., a bus and a truck weighing more than 3.5 t). In particular, the vehicle is an electric vehicle or a hybrid vehicle. The vehicle comprises at least two axles, one of which forms an axle that can be driven by the drive train. The drive train according to the invention is operatively arranged on this drivable axle, the drive train transmitting drive power from the drive unit to the wheels of this axle via the transmission according to the invention. It is also conceivable to provide such a drive train for each axle.The drivetrain is preferably installed in a front-transverse design, so that the input shaft and the output shafts are aligned essentially transversely to the vehicle's longitudinal direction. Alternatively, the drivetrain can be arranged diagonally to the vehicle's longitudinal and transverse axes, with the output shafts connected via corresponding joints to the wheels of the respective axle, which are arranged transversely to the vehicle's longitudinal axis.

[0024] The above definitions as well as statements on technical effects, advantages and advantageous embodiments of the transmission according to the first aspect of the invention also apply mutatis mutandis to the drive train according to the invention according to the second aspect of the invention and to the vehicle according to the invention according to the third aspect of the invention.

[0025] In the following, exemplary embodiments of the invention are explained in more detail with reference to the schematic drawings, wherein identical or similar components are provided with the same reference numerals. Fig. 1 shows a highly schematic plan view of an exemplary vehicle with a drive train according to the invention, which includes a transmission according to the invention.

[0026] Fig. 2 is a highly simplified representation of the transmission according to the invention,

[0027] Fig. 3 is a schematic perspective view of a planet carrier of the transmission according to the invention,

[0028] Fig. 4 is a schematic sectional view of a section of the transmission according to the invention,

[0029] Fig. 5 is a further schematic sectional view of a section of the transmission according to the invention, and

[0030] Fig. 6 is a highly simplified sectional view of a housing of the transmission according to the invention.

[0031] According to Fig. 1, a vehicle 1 with two axles 10a, 10b is shown, with a drive train 2 according to the invention being arranged on the first axle 10a in a drive-effective manner. The vehicle 1 is an electric vehicle, with the drive of the vehicle 1 being purely electric. The first axle 10a can be either the front axle or the rear axle of the vehicle 1 and forms a driven axle of the vehicle 1. Here, the drive train 2 is arranged, for example, on a non-steerable rear axle of the vehicle 1.

[0032] The drive train 2 comprises a drive unit 12 designed as an electric machine and a transmission 3 operatively connected thereto, the structure and arrangement of the transmission 3 being explained in more detail in the following figures. The detailed structure of the drive unit 12 is not shown here. The drive unit 12 or electric machine in any case has an accumulator that supplies it with electrical energy and power electronics for controlling and regulating the drive unit 12. By energizing a stator (not shown here), a rotor (likewise not shown here) that is rotatably arranged relative to the stator and is connected in a rotationally fixed manner to an input shaft 4 indicated by an arrow in Fig. 2 is set in a rotational movement relative to the stator.The input shaft 4 is to be understood as a drive shaft which transmits a drive power of the drive unit 12 into the transmission 3, wherein the drive power is converted by a differential 7 designed as an integral differential and distributed between a first output shaft 5 and a second output shaft 6.

[0033] The drive unit 12 is arranged coaxially with the integral differential 7. Likewise, the output shafts 5, 6 are arranged coaxially with each other and with the drive unit 12 and, in the assembled state of the drive train 2, extend from the transmission 3 in opposite directions to wheels 13 of the first axle 10a. Joints 14 are arranged between the respective wheel 13 and the output shafts 5, 6 as shown in Fig. 2 to compensate for any misalignment of the output shafts 5, 6 relative to the wheel hubs of the first axle 10a (not shown here).

[0034] The transmission 3 shown in Fig. 2 and partially in Fig. 4 and Fig. 5 is designed as a differential 7 and comprises two planetary gear sets 15, 16, each with a plurality of gear set elements. A first output torque can be transmitted to the first output shaft 5 by means of the first planetary gear set 15, wherein a support torque of the first planetary gear set 15 can be converted in the second planetary gear set 16 such that a second output torque corresponding to the first output torque can be transmitted to the second output shaft 6.

[0035] The first and second planetary gear sets 15, 16 are each designed as minus planetary gear sets and are radially nested, i.e., lying in a common plane, with the common plane running perpendicular to the first axis 10a. This saves axial installation space of the transmission 3. The first planetary gear set 15 is arranged radially inside the second planetary gear set 16. On the first planetary gear set 15, the first gear set element is a first sun gear 17a, the second gear set element is a first planet carrier 18a, and the third gear set element is a first ring gear 19a, with several first planet gears 20a being rotatably mounted on planetary pins (not shown here) on the first planet carrier 18a. The first planet gears 20a mesh with the first sun gear 17a and the first ring gear 19a.

[0036] The first output shaft 5 extends axially through the transmission 3, in particular through the integral differential 7, as well as through the drive unit 12. Accordingly, the first output shaft 5 also extends axially through the first sun gear 17a of the first planetary gear set 15. Thus, the first sun gear 17a is designed as an internally hollow gear, and the input shaft 4, which is connected to it in a rotationally fixed manner, is designed as a hollow shaft.

[0037] On the second planetary gear set 16, the first gear set element is a second sun gear 17b, the second gear set element is a second planet carrier 18b, and the third gear set element is a second ring gear 19b. Several planet gears 20b are rotatably mounted on planetary pins (not shown) on the second planet carrier 18b. The second planet gears 20b mesh with the second sun gear 17b and the second ring gear 19b.

[0038] The first sun gear 17a of the first planetary gear set 15 is configured to be rotationally fixedly connected to the input shaft 4 when the drive train 2 is assembled. The first planet carrier 18a of the first planetary gear set 15 is configured to be rotationally fixedly connected to the first output shaft 5 via a spline 22 when the drive train 2 is assembled. The first ring gear 19a of the first planetary gear set 15 is rotationally fixedly connected, here in one piece, to the second sun gear 17b of the second planetary gear set 16. The second ring gear 19b of the second planetary gear set 16 is also rotationally fixedly connected to the second output shaft 6 via an annular disk-shaped carrier element 8, which is designed here as a ring gear carrier. It should be explicitly noted that the assignment of the gear set elements to the elements of the respective planetary gear set 15, 16 can be interchanged as desired.The respective connection of the gear set elements sun gear, planet carrier, and ring gear is made depending on the gear ratio requirements, including the sign. Instead of a negative planetary gear set, the respective planetary gear set 15, 16 can always be designed as a positive planetary gear set by swapping the connection of the first planet carrier and the first ring gear and increasing the value of the stationary gear ratio by one. The reverse is also possible. It is also conceivable to arrange an additional gear ratio stage between the drive unit 12 and the transmission 3, for example, designed as a spur gear stage or as a planetary gear with one or more planetary gear sets, in order to increase the overall gear ratio of the drive.

[0039] Fig. 3 shows the planet carrier 18b of the second planetary gear set 16 according to Fig. 2. The planet carrier 18b has a circumferential and segmented spline 9. In the present case, the spline 9 on the planet carrier 18b consists of a total of six segments 22, which are evenly distributed in the circumferential direction on an outer circumference of the planet carrier 18b. Due to the perspective view, only five of the six segments 22 of the spline 9 on the planet carrier 18b are shown. In the circumferential direction, exactly one bore 26 for receiving a planet gear bolt is arranged on the planet carrier 18b between each two segments 22 of the spline 9. In the assembled state, the planet gears are arranged in the pockets 27 provided for them on the planet carrier 18b. The bores 26 run centrally through the pockets 27 on the planet carrier 18b.Thus, in the circumferential direction, exactly one pocket 27 is arranged between each two segments 22 of the spline 9 for accommodating a planetary gear on the planet carrier 18b. Due to the perspective view, only four of the six pockets 27 are shown.

[0040] Fig. 4 shows a schematic sectional view of a section of the transmission 3 according to the invention. The cross section according to Fig. 4 is guided through the spline 9 on the planet carrier 18b of the transmission 3. As can be seen from Fig. 4, the spline 9 on the planet carrier 18b engages with a spline 11 on the housing 21 of the transmission 3 in order to torsionally connect the planet carrier 18b and the housing 21. In the circumferential direction between two segments 22 of the spline 9 on the planet carrier 18b, exactly two bores 23 are formed on the housing 21, wherein these bores 23 are designed to receive screw elements 24 shown in Fig. 5 and to fix a housing cover 25 shown in Fig. 5 to the housing 21. The longitudinal section according to Fig. 5 runs through a planetary gear bolt of the gearbox 3, so that only the screw elements 24 located behind the cutting plane are visible.

[0041] The housing 21 of the transmission 3 is shown in a highly simplified manner in Fig. 6. In a first section of the housing 3, an electric machine 29 is arranged with a stator fixed to the housing and an internal rotor. In this region, the housing 3 has a first inner diameter D1. Axially adjacent to this, the inner diameter of the housing 21 increases to a second inner diameter D2, wherein this region of the housing 21 is designed to accommodate a seal (not shown in detail). Axially adjacent to this, the spline 11 is formed on the housing 21, wherein a tip circle diameter 30 of the spline 11 on the housing 21 is larger than the second inner diameter D2 on the housing 21. A root circle diameter 28 of the spline 11 on the housing 21 is larger than the tip circle diameter 30 of the spline 11 on the housing 21.Furthermore, a bore 23 is formed on the housing 21, which is designed to receive the screw elements 24 and to fix the housing cover 25 to the housing 21. The sectional view according to Fig. 6 runs, on the one hand, through the spline 11 on the housing 21 and, on the other hand, rotated in the circumferential direction, through one of the bores 23 on the housing 21.

[0042] Fig. 6 shows that the root diameter 28 of the spline 11 on the housing 21 has an overlap in the radial direction with the bores 23 for receiving screw elements 24 and for fixing the housing cover 25 to the housing 21. In the present case, the root diameter 28 of the spline 11 on the housing 21 and the bores 23 for receiving screw elements 24 and for fixing the housing cover 25 to the housing 21 are arranged essentially on a common circular path. Due to the radial overlap of the root diameter 28 of the spline 11 on the housing 21 and the bores 23 for receiving screw elements 24 on the housing 21, the gear 3 is designed to be more compact in the radial direction. This is because the bores 23 for receiving the screw elements 24 on the housing 21 are shifted radially further inward than previously known. The outer diameter of the housing 21 decreases without affecting the axial dimension of the housing 21.The production and assembly of the transmission 3 are simplified. The entire drive unit can be designed with a smaller diameter, as the reduced diameter of the housing 21 saves installation space. Furthermore, the weight of the transmission 3 can be reduced. Another advantage is that the power electronics integrated in the drive unit (not shown here) can be positioned closer to the planetary gear set and thus installed deeper in the vehicle.

[0043] Reference symbol

[0044] vehicle

[0045] Powertrain

[0046] Gearbox

[0047] input shaft

[0048] First output wave

[0049] Second output shaft

[0050] differential

[0051] Support element

[0052] Spline on the planet carrier a First axis b Second axis

[0053] Spline on the housing

[0054] drive unit

[0055] wheel

[0056] joint

[0057] First planetary gear set

[0058] Second planetary gear set a First sun gear of the first planetary gear set b Second sun gear of the second planetary gear set a First planet carrier of the first planetary gear set b Second planet carrier of the second planetary gear set a First ring gear of the first planetary gear set b Second ring gear of the second planetary gear set a First planet gear of the first planetary gear set b Second planet gear of the second planetary gear set

[0059] Housing

[0060] Segment of the spline on the planet carrier

[0061] Hole on the housing

[0062] screw element

[0063] Housing cover

[0064] Hole on the planet carrier 27 pocket

[0065] 28 root diameter

[0066] 29 electric machine

[0067] 30 head circle diameter

[0068] 31 strokes

[0069] D1 first inner diameter

[0070] D2 second inner diameter

Claims

Patent claims 1. A transmission (3) for a drive train (2) of a vehicle (1), comprising a differential (7) which is designed to distribute drive power between a first output shaft (5) and a second output shaft (6), wherein the differential (7) has a planetary carrier (18b) with an at least partially circumferential and segmented spline (9), wherein the spline (9) on the planetary carrier (18b) engages in a spline (11) on a housing (21) of the transmission (3) and is connected thereto in a rotationally fixed manner, wherein in the circumferential direction between two segments (22) of the spline (9) on the planetary carrier (18b) at least one bore (23) is formed on the housing (21), said bores (23) being designed to receive screw elements (24) and to fix a housing cover (25) on the housing (21).

2. Gearbox (3) according to claim 1, wherein a root circle diameter (28) of the spline (11) on the housing (21) has an overlap in the radial direction with the bores (23) for receiving screw elements (24) and fixing the housing cover (25) on the housing (21).

3. Gearbox (3) according to claim 2, wherein the root circle diameter (28) of the spline (11) on the housing (21) and the bores (23) for receiving screw elements (24) and fixing the housing cover (25) on the housing (21) are arranged substantially on a common circular path.

4. Gearbox (3) according to one of the preceding claims, wherein in the circumferential direction between two segments (22) of the spline (9) on the planet carrier (18b) exactly two bores (23) are formed for receiving screw elements (24) and fixing the housing cover (25) to the housing (21).

5. Gearbox (3) according to one of the preceding claims, wherein in the circumferential direction between each two segments (22) of the spline (9) exactly one bore (26) for receiving a planetary gear bolt on the planet carrier (18b) is arranged.

6. Gearbox (3) according to one of the preceding claims, wherein the spline (9) on the planet carrier (18b) has at least three segments (22) evenly distributed in the circumferential direction.

7. Transmission (3) according to one of the preceding claims, wherein the differential (7) comprises a first planetary gear set (29) and at least one second planetary gear set (30) operatively connected thereto, wherein a first output torque can be transmitted at least indirectly to the first output shaft (5) by means of the first planetary gear set of the differential (7), wherein a support torque of the first planetary gear set (29) in the second planetary gear set (30) can be converted such that a second output torque corresponding to the first output torque can be transmitted to the second output shaft (6).

8. Drive train (2) for a vehicle (1), comprising a transmission (3) according to one of the preceding claims, an input shaft (4), a first output shaft (5) and a second output shaft (6), wherein the differential (7) of the transmission (3) is effectively arranged between the input shaft (4) and the two output shafts (5, 6) and divides a drive power applied to the input shaft (4) between the two output shafts (5, 6).

9. Vehicle with a drive train (2) according to claim 8.

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