Transmission and drive device for a motor vehicle
By designing a transmission containing multiple planetary gear sets and using switching elements to achieve differential locking action, the shortcomings of existing transmissions in terms of power density, efficiency and differential locking action are solved, and higher performance and flexibility are achieved.
Patent Information
- Application Number
- CN202380071156.6
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Priority Date
- 2022-10-06
- Filing Date
- 2023-09-21
- Publication Date
- 2025-05-06
Smart Images
Figure CN119948277A_ABST
Abstract
Description
Technical Field
[0001] The invention relates to a transmission for a motor vehicle and also to a drive device having such a transmission. Background Art
[0002] For example, DE102013215877 A1 discloses a planetary gear transmission for branching the driving power present at the power input to a first power output and a second power output, while reducing the output speed to a speed level lower than the driving speed at the power input. The planetary gear transmission includes: a first transmission stage, which includes a first sun gear, a first planetary gear set, a first planet carrier and a first ring gear; a second transmission stage, which includes a second sun gear, a second planetary gear set, a second planet carrier and a second ring gear; and a third planet stage, which includes a third sun gear, a third planetary gear set and a third planet carrier. The first sun gear is configured as a power input, the first planet carrier is connected to the second sun gear in a rotationally fixed manner, the second planet carrier is fixed in a fixed manner, the first ring gear is connected to the third sun gear, the first power output occurs via the third transmission stage, and the second power output occurs via the second ring gear of the second transmission stage. Summary of the invention
[0003] The object of the invention is to provide an alternative transmission which comprises in particular an improved power density and an improved efficiency as well as a differential locking action. These objects are achieved by a transmission having the features of claim 1 and by a transmission having the features of claim 10. Advantageous embodiments are subject of the dependent claims, the following description and the drawings.
[0004] The transmission for a motor vehicle according to the invention comprises: a first planetary gear set, a second planetary gear set and a third planetary gear set, wherein each planetary gear set comprises a first element, a second element and a third element; exactly one drive shaft for connecting the transmission to a drive unit of the motor vehicle; a first output shaft and a second output shaft, each for connecting the transmission to wheels of the motor vehicle; a first coupling shaft and a second coupling shaft, each for connecting two elements of the two planetary gear sets in a rotationally fixed manner; and a switching element for transmitting torque between one of the two output shafts and the second coupling shaft,
[0005] wherein one of the elements of the second planetary gear set is connected to the drive shaft in a rotationally fixed manner, wherein another of the elements of the second planetary gear set is connected to the first coupling shaft in a rotationally fixed manner, wherein another of the elements of the second planetary gear set is connected to the second coupling shaft in a rotationally fixed manner,
[0006] wherein one of the elements of the third planetary gear set is connected to the first coupling shaft in a rotationally fixed manner, wherein another of the elements of the third planetary gear set is connected to a stationary member in a rotationally fixed manner, wherein another of the elements of the third planetary gear set is connected to the second output shaft in a rotationally fixed manner,
[0007] wherein one of the elements of the first planetary gear set is connected to the second coupling shaft in a rotationally fixed manner, wherein another of the elements of the first planetary gear set is connected to the first output shaft in a rotationally fixed manner, wherein another of the elements of the first planetary gear set is connected to the second output shaft in a rotationally fixed manner.
[0008] A "connection" of a device or element to a transmission is understood to mean that the transmission (in particular the corresponding shaft of the transmission) is connected to the device or element directly (e.g. in a rotationally fixed manner) or indirectly (e.g. via at least one further component, in particular via at least one further shaft or further gear). If two shafts are connected to one another in a rotationally fixed manner, they rotate together at a rotational speed in one direction of rotation. In particular, the connection can also take place via a switching element, whereby a drive-effective coupling and decoupling of the device or element to the corresponding shaft of the transmission is possible.
[0009] A "shaft" should not be understood to mean only a cylindrical, rotatably mounted transmission element, for example for transmitting torque, but should also be understood to mean a general connecting element which connects individual parts or elements to one another, in particular a connecting element which connects a plurality of elements to one another in a rotationally fixed manner. Two shafts which are connected to one another in a rotationally fixed manner can be formed in one piece.
[0010] "Stationary component" is understood to mean a non-rotating component of the transmission. For example, the stationary component is formed as a housing or a housing part of the transmission. Alternatively, the stationary component may be formed as a shaft fixed to the housing.
[0011] Thus, the second planetary gear set is connected or can be connected at least indirectly or directly to the drive unit via the drive shaft and is connected to the third planetary gear set via the first coupling shaft and is connected to the first planetary gear set via the second coupling shaft. Further, the third planetary gear set is connected to the housing in a rotationally fixed manner and is connected to the first planetary gear set via the second output shaft. In addition, the first planetary gear set is connected to the first output shaft. The first planetary gear set is connected or can be connected at least indirectly or directly to a first wheel of the motor vehicle via the first output shaft. In addition, the first planetary gear set and the third planetary gear set are connected or can be connected at least indirectly or directly to a second wheel of the motor vehicle via the second output shaft.
[0012] For example, the drive unit is designed as an electric motor, which can be operated as a drive motor for driving a vehicle and as a generator for recovering electrical energy. To this end, the electric motor is electrically connected to an electrical energy storage device. The electric motor comprises a rotor and a stator, wherein the rotor is connected to a rotor shaft in a rotationally fixed manner. The rotor shaft of the electric motor is at least indirectly or directly connected to a drive shaft. For example, the rotor shaft of the electric motor is connected to the drive shaft via at least one other shaft, via a plurality of gears and / or via a traction device. The electric motor can be arranged on a common rotation axis with the transmission, and can therefore be formed coaxially with respect to the drive shaft, wherein the rotor shaft is then preferably connected to the drive shaft in a rotationally fixed manner. Alternatively, the electric motor can be formed axially parallel with respect to the drive shaft, wherein the rotor shaft is then indirectly connected to the drive shaft. Alternatively, the drive unit can be formed as an internal combustion engine with a crankshaft.
[0013] A “switching element” is understood to mean a switchable device comprising at least an open state and a closed state, wherein in the open state the two shafts connected thereto are able to rotate freely and wherein in the closed state the two shafts are connected to one another in a rotationally fixed manner.
[0014] According to a preferred embodiment, the switching element in the closed state connects the third element of the first planetary gear set and the first element of the first planetary gear set to one another in a rotationally fixed manner. According to a preferred embodiment, the switching element in the closed state connects the second element of the first planetary gear set and the first element of the first planetary gear set to one another in a rotationally fixed manner.
[0015] Thus, the first planetary gear set is blocked via the switching element. In other words, two elements of the first planetary gear set, such as the sun gear and the ring gear or the sun gear and the planet carrier, are connected in a rotationally fixed manner, as a result of which the first planetary gear set rotates in a block and includes a transmission ratio of 1. Since one of these elements of the first planetary gear set is connected to the first output shaft or the second output shaft, a differential locking action is also generated by the switching element. The switching element can be switched by an actuator. "Differential locking action" is to be understood to mean a locking action between the two output shafts. The switching element can be designed as a friction locking or actively locking switching element. For example, the actively locking switching element is designed as a dog clutch. With the help of the actively locking switching element, the efficiency of the transmission can be increased due to the reduced drag losses. In particular, the actively locking switching element is designed in a more compact and efficiency-optimized manner and has a cost advantage over the friction locking switching element. However, slip operation (ie, a limited locking action at a differential speed) is not possible in the case of an actively locking switching element. For example, the friction locking switching element comprises a plurality of plates or at least one conical friction surface. In the case of a friction-locking shift element, the latter can be actuated via an actuator or mechanically, in particular by using axial forces from the helical teeth.The actuator can be arranged fixed to the housing or co-rotating.
[0016] According to a preferred embodiment, the first element of the second planetary gear set is connected to the input shaft in a rotationally fixed manner, wherein the second element of the second planetary gear set is connected to the first coupling shaft in a rotationally fixed manner, wherein the third element of the second planetary gear set is connected to the second coupling shaft in a rotationally fixed manner, wherein the first element of the third planetary gear set is connected to the first coupling shaft in a rotationally fixed manner, wherein the second element of the third planetary gear set is connected to the stationary element in a rotationally fixed manner, wherein the third element of the third planetary gear set is connected to the second output shaft in a rotationally fixed manner, wherein the first element of the first planetary gear set is connected to the second coupling shaft in a rotationally fixed manner, wherein the second element of the first planetary gear set is connected to the first output shaft in a rotationally fixed manner, wherein the third element of the first planetary gear set is connected to the second output shaft in a rotationally fixed manner. In this regard, reference is made to the embodiment according to Figure 4 , Figure 5 and Figure 6 Embodiment of the invention.
[0017] According to a preferred embodiment, the first element of the second planetary gear set is connected to the input shaft in a rotationally fixed manner, wherein the second element of the second planetary gear set is connected to the second coupling shaft in a rotationally fixed manner, wherein the third element of the second planetary gear set is connected to the first coupling shaft in a rotationally fixed manner, wherein the first element of the third planetary gear set is connected to the first coupling shaft in a rotationally fixed manner, wherein the second element of the third planetary gear set is connected to the stationary element in a rotationally fixed manner, wherein the third element of the third planetary gear set is connected to the second output shaft in a rotationally fixed manner, wherein the first element of the first planetary gear set is connected to the second output shaft in a rotationally fixed manner, wherein the second element of the first planetary gear set is connected to the first output shaft in a rotationally fixed manner, wherein the third element of the first planetary gear set is connected to the second coupling shaft in a rotationally fixed manner. In this regard, reference is made to the embodiment according to the appended claims. Figure 7 and Figure 8 Embodiment of the invention.
[0018] According to a preferred embodiment, the first element of the second planetary gear set is connected to the input shaft in a rotationally fixed manner, wherein the second element of the second planetary gear set is connected to the first coupling shaft in a rotationally fixed manner, wherein the third element of the second planetary gear set is connected to the second coupling shaft in a rotationally fixed manner, wherein the first element of the third planetary gear set is connected to the first coupling shaft in a rotationally fixed manner, wherein the second element of the third planetary gear set is connected to the stationary element in a rotationally fixed manner, wherein the third element of the third planetary gear set is connected to the second output shaft in a rotationally fixed manner, wherein the first element of the first planetary gear set is connected to the second output shaft in a rotationally fixed manner, wherein the second element of the first planetary gear set is connected to the first output shaft in a rotationally fixed manner, wherein the third element of the first planetary gear set is connected to the second coupling shaft in a rotationally fixed manner. In this regard, reference is made to the embodiment according to Fig. 9 and Fig.10 Embodiment of the invention.
[0019] According to a preferred embodiment, the first element of the second planetary gear set is connected to the input shaft in a rotationally fixed manner, wherein the second element of the second planetary gear set is connected to the first coupling shaft in a rotationally fixed manner, wherein the third element of the second planetary gear set is connected to the second coupling shaft in a rotationally fixed manner, wherein the first element of the third planetary gear set is connected to the first coupling shaft in a rotationally fixed manner, wherein the second element of the third planetary gear set is connected to the second output shaft in a rotationally fixed manner, wherein the third element of the third planetary gear set is connected to the stationary component in a rotationally fixed manner, wherein the first element of the first planetary gear set is connected to the second coupling shaft in a rotationally fixed manner, wherein the second element of the first planetary gear set is connected to the second output shaft in a rotationally fixed manner, wherein the third element of the first planetary gear set is connected to the first output shaft in a rotationally fixed manner. In this regard, reference is made to the embodiment according to Fig.11Embodiment of the invention.
[0020] According to a preferred embodiment, the first element of the second planetary gear set is connected to the input shaft in a rotationally fixed manner, wherein the second element of the second planetary gear set is connected to the second coupling shaft in a rotationally fixed manner, wherein the third element of the second planetary gear set is connected to the first coupling shaft in a rotationally fixed manner, wherein the first element of the third planetary gear set is connected to the first coupling shaft in a rotationally fixed manner, wherein the second element of the third planetary gear set is connected to the second output shaft in a rotationally fixed manner, wherein the third element of the third planetary gear set is connected to the stationary component in a rotationally fixed manner, wherein the first element of the first planetary gear set is connected to the second coupling shaft in a rotationally fixed manner, wherein the second element of the first planetary gear set is connected to the second output shaft in a rotationally fixed manner, wherein the third element of the first planetary gear set is connected to the first output shaft in a rotationally fixed manner. In this regard, reference is made to the embodiment according to Fig.12 Embodiment of the invention.
[0021] According to a preferred embodiment, two of the three planetary gear sets are arranged in a radially nested manner. In other words, the elements of the two planetary gear sets are arranged in an axially overlapping manner, so that one of the two planetary gear sets is arranged on the outside and the other of the two planetary gear sets is arranged on the inside. As a result, the transmission is formed in a more compact manner, in particular in the axial direction. Preferably, the first planetary gear set and the third planetary gear set are arranged in a radially nested manner. Alternatively, the first planetary gear set and the second planetary gear set are arranged in a radially nested manner.
[0022] According to a preferred embodiment, one of the two coupling shafts or one of the two output shafts is integrally formed with an element of the corresponding planetary gear set connected to it. For example, the coupling shaft or the output shaft can be integrally formed as an intermediate gear with two teeth, wherein the internal teeth of the intermediate gear form the ring gear for the radially internal planetary gear set, and wherein the external teeth of the intermediate gear form the sun gear for the radially external planetary gear set. Such an intermediate gear is also referred to as a sun gear ring gear. Alternatively, the coupling shaft or the output shaft can include teeth forming a common ring gear for the two planetary gear sets. Alternatively, the coupling shaft or the output shaft can include teeth forming a common sun gear for the two planetary gear sets. Alternatively, the coupling shaft or the output shaft can form a common planet carrier.
[0023] According to a preferred embodiment, at least one of the planetary gear sets is formed as a negative planetary gear set, wherein the first element of the respective planetary gear set is formed as a sun gear, wherein the second element of the respective planetary gear set is formed as a planet carrier, wherein the third element of the respective planetary gear set is formed as a ring gear. A plurality of planetary gears in toothed engagement with the sun gear and the ring gear are rotatably mounted on the planet carrier.
[0024] The present invention also relates to a transmission for a motor vehicle, the transmission comprising: at least one first planetary gear set having a first element, a second element and a third element, wherein the first planetary gear set is formed as a negative planetary gear set having a sun gear, a ring gear and a planet carrier; a drive shaft for connecting the transmission to a drive unit of the motor vehicle; a first output shaft and a second output shaft, each for connecting the transmission to a wheel of the motor vehicle; a switching element, wherein one of the elements of the first planetary gear set is connected to the first output shaft in a rotationally fixed manner, wherein another one of the elements of the first planetary gear set is connected to the second output shaft in a rotationally fixed manner, and wherein another one of the elements of the first planetary gear set can be connected to one of the two output shafts via the switching element.
[0025] The drive device according to the invention comprises a drive unit and a transmission according to the invention. The drive unit is preferably formed as an electric motor. Alternatively, the drive unit is formed as an internal combustion engine. The drive unit can be arranged coaxially or axially parallel to the drive shaft of the transmission. The drive power of the drive unit is fed into the transmission via the drive shaft and distributed to two output shafts, wherein the respective output shaft is operatively connected to the respective drive wheels of the drive axle of the vehicle.
[0026] The motor vehicle according to the invention comprises a drive device according to the invention. In particular, the motor vehicle is designed as an electric vehicle and comprises an electric drive axle having a drive device according to the invention. The definitions and statements of the technical effects, advantages and advantageous embodiments of the transmission according to the invention described above also apply to the drive device according to the invention and the motor vehicle according to the invention. BRIEF DESCRIPTION OF THE DRAWINGS
[0027] The advantageous embodiments of the invention explained below are shown in the drawings, wherein identical elements are provided with the same reference numerals. The drawings show:
[0028] Figure 1 is a highly abstract schematic diagram of a motor vehicle having a drive device according to the invention;
[0029] Figure 2 is a highly abstract schematic diagram of a drive device according to the present invention;
[0030] Figure 3 is a highly abstract schematic diagram of a drive device according to the invention according to an alternative embodiment;
[0031] Figure 4 is a highly abstract schematic diagram of a drive device according to the present invention according to a first embodiment;
[0032] Figure 5 is a highly abstract schematic diagram of a drive device according to the present invention according to a second embodiment;
[0033] Figure 6 is a highly abstract schematic diagram of a drive device according to the present invention according to a third embodiment;
[0034] Figure 7 is a highly abstract schematic diagram of a drive device according to the present invention according to a fourth embodiment;
[0035] Figure 8 is a highly abstract schematic diagram of a drive device according to the present invention according to a fifth embodiment;
[0036] Fig. 9 is a highly abstract schematic diagram of a drive device according to the present invention according to a sixth embodiment;
[0037] Fig.10 is a highly abstract schematic diagram of a drive device according to the present invention according to a seventh embodiment;
[0038] Fig.11 is a highly abstract schematic diagram of a drive device according to the present invention according to an eighth embodiment; and
[0039] Fig.12 is a highly abstract schematic diagram of a drive device according to the present invention according to a ninth embodiment. DETAILED DESCRIPTION
[0040] Figure 1 A motor vehicle 100 is shown, which has a first wheel bridge 101 with two wheels R1, R2 and a second wheel bridge 102 with two wheels R3, R4. In the present case, the first wheel bridge 101 is designed as a rear drive bridge of the motor vehicle 100 and is equipped with a drive device according to the invention, which comprises a single drive unit 2 designed as an electric motor and a transmission 1 designed as a planetary gear transmission. Therefore, the motor vehicle 100 is designed as an electric vehicle. The drive device is arranged transversely to the longitudinal direction of the vehicle and is operably connected to the wheels R1, R2 of the first wheel bridge 101. In the present case, no additional drive device is arranged on the second wheel bridge 102, that is, on the front axle of the vehicle 100, thereby saving costs, weight and installation space. Alternatively, the drive device can also be arranged on the front axle of the motor vehicle 100 instead of the rear axle. In order to realize an all-wheel drive system, an additional drive device can be arranged on the second wheel bridge 102, which is operably connected to the wheels R3, R4 of the wheel bridge 102.
[0041] Figure 2 and Figure 3 Each schematically shows the Figure 1Schematic diagram of a drive device. The transmission 1 of the drive device comprises a first planetary gear set P1, a second planetary gear set P2 and a third planetary gear set P3, each of which is illustrated in a circle. Each planetary gear set P1, P2, P3 comprises a first element, a second element and a third element, each of which is indicated by three connection options to the corresponding planetary gear set P1, P2, P3. In addition, the transmission 1 comprises five shafts, namely a drive shaft WAn for connecting the transmission 1 to the drive unit 2, a first output shaft WAb1 and a second output shaft WAb2, each for connecting the transmission 1 to the wheels of the motor vehicle, and a first coupling shaft W1 and a second coupling shaft W2.
[0042] One of the elements of the second planetary gear set P2 is connected to the drive shaft WAn in a rotationally fixed manner. The second planetary gear set P2 is operably connected to the drive unit 2 via the drive shaft WAn. In other words, at least one further shaft, gear, switching element, etc. can be arranged in the power flow between the drive unit 2 and the drive shaft WAn. Another of the elements of the second planetary gear set P2 is connected to the first coupling shaft W1 in a rotationally fixed manner. Another of the elements of the second planetary gear set P2 is connected to the second coupling shaft W2 in a rotationally fixed manner.
[0043] One of the elements of the third planetary gear set P3 is connected to the first coupling shaft W1 in a rotationally fixed manner. Therefore, the third planetary gear set P3 is connected to the second planetary gear set P2 via the first coupling shaft W1. Another of the elements of the third planetary gear set P3 is connected to a fixed component of the transmission 1 formed as a housing G in a rotationally fixed manner and is therefore prevented from rotating. Another of the elements of the third planetary gear set P3 is connected to the second output shaft WAb2 in a rotationally fixed manner.
[0044] One of the elements of the first planetary gear set P1 is connected to the second coupling shaft W2 in a rotationally fixed manner. Therefore, the first planetary gear set P1 is connected to the second planetary gear set P2 via the second coupling shaft W2. Another of the elements of the first planetary gear set P1 is connected to the first output shaft WAb1 in a rotationally fixed manner. Another of the elements of the first planetary gear set P1 is connected to the second output shaft WAb2 in a rotationally fixed manner. Therefore, the first planetary gear set P1 is connected to the third planetary gear set P3 via the second output shaft WAb2.
[0045] according to Figure 2 The transmission 1 further includes a switching element S for transmitting torque between the second output shaft WAb2 and the second coupling shaft W2. In other words, the second coupling shaft W2 can be connected to the second output shaft WAb2 via the switching element S.
[0046] according to Figure 3, the transmission 1 includes a switching element S for transmitting torque between the first output shaft WAb1 and the second coupling shaft W2. In other words, the second coupling shaft W2 can be connected to the first output shaft WAb1 via the switching element S.
[0047] The switching element is arranged as a differential lock and is preferably formed as a friction clutch. For example, the friction clutch comprises at least two corresponding friction surfaces, i.e., a friction surface pair. For example, the friction clutch is formed as a plate clutch and comprises a plurality of friction surface pairs acting in parallel. For example, the friction surface has a planar design. Alternatively, the friction surface is of a conical design, so that the friction torque can be increased. For example, a friction element designed as a friction plate or a friction cone or a component axially adjacent thereto is used for axial clearance adjustment. Alternatively, the switching element S is formed as a claw clutch. Alternatively, the switching element is designed as a synchronizer. Preferably, the actuation of the switching element S is carried out by means of a hydraulic cylinder, which is arranged to be fixed to the housing or to rotate together. Alternatively, the actuation of the switching element S occurs electromechanically, for example, via a main shaft, a ramp or a lever. Alternatively, the actuation of the switching element S occurs electromagnetically. The force required for the actuation of the switching element S is at least partially or completely generated by the axial force of at least one helical tooth. In particular, the force flow in the first planetary gear set P1 is formed so that the force from the at least one helical tooth acts on the shift element S in both the traction and overrunning modes of the drive train.
[0048] According to the present invention, the switching element S is provided for transmitting torque between one of the two output shafts WAb1, WAb2 and the second coupling shaft W2. In particular, one of the two output shafts WAb1, WAb2 is connected to an element of the first planetary gear set P1 formed as a planet carrier in a rotationally fixed manner. The sum of the reaction torque of the drive unit 2 and the housing support torque is oppositely equal in magnitude to the output torque at the two output shafts WAb1, WAb2. Therefore, the sum of the output torques does not occur similarly to a differential cage at a rotating part. The sum of the two output torques does not exist at any rotating part of the transmission 1. The sum of the output torques is greater in magnitude than the drive torque because it is not only a differential, but also a torque-up transmission with a differential function.
[0049] The first planetary gear set P1 rotates in a block during straight-ahead travel of the motor vehicle, with the result that the elements of the first planetary gear set P1 do not roll and therefore do not generate corresponding losses. The second planetary gear set P2 has no housing support, with the result that all three elements of the second planetary gear set P2 can rotate. The third planetary gear set P3 has a housing support, so that torque conversion is possible. The three planetary gear sets P1, P2, P3 are connected to one another so that each planetary gear set P1, P2, P3 shares exactly one rotationally fixed connection with each planetary gear set P1, P2, P3.
[0050] Figure 4 A drive device with a transmission 1 according to a first embodiment is schematically shown. For this first embodiment, the good efficiency and wide speed range of the transmission 1 are advantageous. The transmission 1 comprises a first planetary gear set P1, a second planetary gear set P2 and a third planetary gear set P3, wherein each of the three planetary gear sets P1, P2, P3 comprises a first element E11, E21, E31, a second element E12, E22, E32 and a third element E13, E23, E33. In the present case, the first element E11, E21, E31 of the respective planetary gear set P1, P2, P3 is formed as a sun gear, wherein the second element E12, E22, E32 of the respective planetary gear set P1, P2, P3 is formed as a planet carrier, wherein the third element E13, E23, E33 of the respective planetary gear set P1, P2, P3 is formed as a ring gear. Each planet carrier carries at least one planet gear which is in tooth engagement with the sun gear and the ring gear of the respective planetary gear set P1, P2, P3. Thus, each of the three planetary gear sets P1, P2, P3 is formed as a negative planetary gear set.
[0051] The first element E21 of the second planetary gear set P2 is connected to the drive shaft WAn in a rotationally fixed manner, wherein the second element E22 of the second planetary gear set P2 is connected to the first coupling shaft W1 in a rotationally fixed manner, wherein the third element E23 of the second planetary gear set P2 is connected to the second coupling shaft W2 in a rotationally fixed manner. In the present case, the drive shaft WAn is connected to the drive unit 2 in a rotationally fixed manner. Alternatively, further elements, in particular shafts, gears, switching elements or other devices can be arranged in the power flow between the drive unit 2 and the drive shaft WAn. For example, the power flow between the drive unit 2 and the drive shaft WAn can be interrupted by such a switching element.
[0052] The first element E31 of the third planetary gear set P3 is connected to the first connecting shaft W1 in a rotationally fixed manner, wherein the second element E32 of the third planetary gear set P3 is connected to the fixed component formed as the housing G in a rotationally fixed manner, wherein the third element E33 of the third planetary gear set P3 is connected to the second output shaft WAb2 in a rotationally fixed manner.
[0053] The first element E11 of the first planetary gear set P1 is connected to the second coupling shaft W2 in a rotationally fixed manner, wherein the second element E12 of the first planetary gear set P1 is connected to the first output shaft WAb1 in a rotationally fixed manner, wherein the third element E13 of the first planetary gear set P1 is connected to the second output shaft WAb2 in a rotationally fixed manner.
[0054] Therefore, the third element E13 of the first planetary gear set P1 and the third element E33 of the third planetary gear set P3 are connected to each other in a rotationally fixed manner via the second output shaft WAb2. In addition, the first coupling shaft W1 connects the second element E12 of the second planetary gear set P2 to the first element E31 of the third planetary gear set P3 in a rotationally fixed manner, wherein the second coupling shaft W2 connects the third element E23 of the second planetary gear set P2 to the first element E11 of the first planetary gear set P1 in a rotationally fixed manner.
[0055] The second planetary gear set P2 is axially arranged between the third planetary gear set P3 and the first planetary gear set P1, wherein the third planetary gear set P3 is axially adjacent to the drive unit 2. As a result, the drive device is formed in a compact manner. All three planetary gear sets P1, P2, P3 are arranged on a common rotation axis R. The drive unit 2 is arranged coaxially with respect to the rotation axis R. The drive shaft WAn is formed as a hollow shaft, wherein the first output shaft WAb1 extends axially through the drive shaft WAn and the drive unit 2. The corresponding output shafts WAb1, WAb2 are connected to the corresponding wheels of the motor vehicle, for example, in a rotationally fixed manner. Alternatively, the corresponding output shafts WAb1, WAb2 can be indirectly connected to the corresponding wheels of the motor vehicle via further transmission elements, in particular spur gear stages, chain drives or transmission shafts.
[0056] The switching element S is configured to transmit torque between the second output shaft WAb2 and the second coupling shaft W2, wherein the switching element S in the closed state connects the third element E13 of the first planetary gear set P1 and the first element E11 of the first planetary gear set P1 to each other in a rotationally fixed manner. Therefore, the first planetary gear set P1 is blocked. If the switching element S is only partially closed, only a part of the torque is transmitted between the second coupling shaft W2 and the second output shaft WAb2. Due to the arrangement of the switching element S in the power flow between the sun gear and the ring gear of the first planetary gear set P1, the first planetary gear set P1 can be at least partially or completely blocked, wherein the torque occurring in the switching element S is then lower than in the case of the arrangement of the switching element S between the two output shafts WAb1, WAb2. Therefore, the switching element S is effectively arranged between the second coupling shaft W2 and the second output shaft WAb2, and acts between the first element E11 of the first planetary gear set P1 and the third element E13 of the first planetary gear set P1. The switching element S is arranged axially adjacent to the first planetary gear set P1. The switching element S is arranged axially between the first planetary gear set P1 and the second planetary gear set P2. Alternatively and not shown in the present case, the switching element S can be arranged radially on the outside around the second planetary gear set P2. The second planetary gear set P2 can be designed with a particularly small diameter, for example, as a result of which space is generated radially between the second planetary gear set P2 and the second output shaft WAb2 in order to arrange the switching element S there. If the switching element S is arranged in a radially nested manner with the second planetary gear set P2, the overall axial length can be saved.
[0057] Figure 5 A second embodiment of the drive device according to the present invention is shown. Figure 5 The drive device basically corresponds to Figure 4Drive device, wherein there are differences between the two embodiments with respect to the arrangement and connection of the switching element S. In the present case, the switching element S is configured to transmit torque between the first output shaft WAb1 and the second coupling shaft W2, wherein the switching element S in the closed state connects the second element E12 of the first planetary gear set P1 and the first element E11 of the first planetary gear set P1 in a rotationally fixed manner. Therefore, the switching element S acts between the first element E11 of the first planetary gear set P1 and the second element E12 of the first planetary gear set P1. The switching element S is arranged axially adjacent to the first planetary gear set P1. Due to the arrangement of the switching element S in the power flow between the sun gear and the planet carrier of the first planetary gear set P1, the first planetary gear set P1 can be at least partially or completely blocked, wherein the torque occurring in the switching element S is then lower than in the case of the arrangement of the switching element S between the two output shafts WAb1, WAb2. Although the torque in the switching element S is higher than in the case of an arrangement of the switching element S in the power flow between the sun gear and the ring gear of the first planetary gear set P1, structural advantages can be generated due to the coupling capability, especially if the arrangement of the switching element S in the power flow between the sun gear and the ring gear of the first planetary gear set P1 is structurally impossible. Figure 5 The exemplary embodiment corresponds to the reference according to Figure 4 An exemplary embodiment of .
[0058] Figure 6 A third embodiment of the drive device according to the present invention is shown. Figure 6 The drive device basically corresponds to Figure 4A drive device, wherein there are differences between the two embodiments in terms of the arrangement of the first planetary gear set P1 and the second planetary gear set P2. The short axial total length of the transmission 1 of this third embodiment is advantageous compared to the first embodiment. In the present case, the first planetary gear set P1 and the second planetary gear set P2 are arranged in a radially nested manner, wherein the second planetary gear set P2 is arranged radially on the inside, and wherein the first planetary gear set P1 is arranged radially on the outside. Therefore, the second planetary gear set P2 is arranged closer to the rotation axis R than the second planetary gear set P2. The elements E11, E12, E13 of the first planetary gear set P1 and the elements E21, E22, E23 of the second planetary gear set P2 overlap in the axial direction. The second coupling shaft W2 is configured as an intermediate gear with internal and external teeth, and connects the first planetary gear set P1 and the second planetary gear set P2. In other words, the third element E23 of the second planetary gear set P2, the first element E11 of the first planetary gear set P1 and the second coupling shaft W2 are formed as a common component in one piece. The inner teeth of the intermediate gear form a ring gear for the radially inner second planetary gear set P2. The outer teeth of the intermediate gear form a sun gear for the radially outer first planetary gear set P1. The intermediate gear makes the transmission 1 more compact and lighter. In addition, the first planetary gear set P1 and the third planetary gear set P3 have a common ring gear. In other words, the third element E13 of the first planetary gear set P1 and the third element E33 of the third planetary gear set P3 are formed as a common component with a single tooth. As a result, the assembly complexity is reduced and the compactness is increased. In particular, the second output shaft WAb2 is formed integrally with the common ring gear. The switching element S is effectively arranged between the second coupling shaft W2 and the second output shaft WAb2. Therefore, the switching element S acts between the first element E11 of the first planetary gear set P1 and the third element E13 of the first planetary gear set P1. The switching element S is arranged axially adjacent to the third planetary gear set P3. The switching element S is axially arranged between the first planetary gear set P1 and the third planetary gear set P3. In other aspects, according to Figure 6 The exemplary embodiment corresponds to the reference according to Figure 4 An exemplary embodiment of .
[0059] Figure 7 A fourth embodiment of the drive device according to the present invention is shown. Figure 7 The drive device basically corresponds to Figure 4A drive device, wherein there is a difference between the two embodiments in terms of the connection between the first planetary gear set P1 and the second planetary gear set P2. In the present case, the first element E21 of the second planetary gear set P2 is connected to the drive shaft WAn in a rotationally fixed manner, wherein the second element E22 of the second planetary gear set P2 is connected to the second coupling shaft W2 in a rotationally fixed manner, wherein the third element E23 of the second planetary gear set P2 is connected to the first coupling shaft W1 in a rotationally fixed manner. The first element E31 of the third planetary gear set P3 is connected to the first coupling shaft W1 in a rotationally fixed manner, wherein the second element E32 of the third planetary gear set P3 is connected to the fixed component formed as the housing G in a rotationally fixed manner, wherein the third element E33 of the third planetary gear set P3 is connected to the second output shaft WAb2 in a rotationally fixed manner. In addition, the first element E11 of the first planetary gear set P1 is connected to the second output shaft WAb2 in a rotationally fixed manner, wherein the second element E12 of the first planetary gear set P1 is connected to the first output shaft WAb1 in a rotationally fixed manner, wherein the third element E13 of the first planetary gear set P1 is connected to the second coupling shaft W2 in a rotationally fixed manner. The switching element S is effectively arranged between the second coupling shaft W2 and the second output shaft WAb2. The switching element S therefore acts between the first element E11 of the first planetary gear set P1 and the third element E13 of the first planetary gear set P1. The switching element S is arranged axially adjacent to the first planetary gear set P1. The switching element S is arranged axially between the first planetary gear set P1 and the second planetary gear set P2. Alternatively and not shown in the present case, the switching element S can be arranged radially on the outside around the second planetary gear set P2. The second planetary gear set P2 can be designed with a particularly small diameter, for example, as a result of which space is created radially between the second planetary gear set P2 and the second output shaft WAb2 in order to arrange the switching element S there. If the switching element S is arranged in a radially nested manner with the second planetary gear set P2, the total axial length can be saved. In other respects, according to Figure 7 The exemplary embodiment corresponds to the reference according to Figure 4 An exemplary embodiment of .
[0060] Figure 8 A fifth embodiment of the drive device according to the present invention is shown. Figure 8 The drive device basically corresponds to Figure 7A drive device, wherein there is a difference between the two embodiments in the arrangement of the first planetary gear set P1 and the third planetary gear set P3. The short axial total length of the transmission 1 of this fifth embodiment is advantageous compared to the fourth embodiment. In the present case, the first planetary gear set P1 and the third planetary gear set P3 are arranged in a radially nested manner, wherein the third planetary gear set P3 is arranged radially on the inside, and wherein the first planetary gear set P1 is arranged radially on the outside. Therefore, the third planetary gear set P3 is arranged closer to the rotation axis R than the first planetary gear set P1. The elements E11, E12, E13 of the first planetary gear set P1 and the elements E31, E32, E33 of the third planetary gear set P3 overlap in the axial direction. An intermediate gear with internal and external teeth is arranged in the power flow between the first planetary gear set P1 and the third planetary gear set P3. The third element E33 of the third planetary gear set P3, the first element E11 of the first planetary gear set P1 and the second output shaft WAb2 are formed as a common component. The internal teeth form the ring gear for the radially inner third planetary gearset P3. The external teeth form the sun gear for the radially outer first planetary gearset P1. The intermediate gear makes the transmission 1 more compact and lighter. The switching element S is effectively arranged between the second coupling shaft W2 and the second output shaft WAb2. The switching element S thus acts between the first element E11 of the first planetary gearset P1 and the third element E13 of the first planetary gearset P1. The switching element S is arranged axially adjacent to the first planetary gearset P1. In other respects, according to Figure 8 The exemplary embodiment corresponds to the reference according to Figure 7 An exemplary embodiment of .
[0061] Fig. 9 A sixth embodiment of the drive device according to the present invention is shown. Fig. 9 The drive device basically corresponds to Figure 4A drive device, wherein there is a difference between the two embodiments in terms of the connection of the third planetary gear set P3. In the present case, the first element E21 of the second planetary gear set P2 is connected to the drive shaft WAn in a rotationally fixed manner, wherein the second element E22 of the second planetary gear set P2 is connected to the first coupling shaft W1 in a rotationally fixed manner, wherein the third element E23 of the second planetary gear set P2 is connected to the second coupling shaft W2 in a rotationally fixed manner. The first element E31 of the third planetary gear set P3 is connected to the first coupling shaft W1 in a rotationally fixed manner, wherein the second element E32 of the third planetary gear set P3 is connected to a fixed component formed as a housing G in a rotationally fixed manner, wherein the third element E33 of the third planetary gear set P3 is connected to the second output shaft WAb2 in a rotationally fixed manner. In addition, the first element E11 of the first planetary gear set P1 is connected to the second output shaft WAb2 in a rotationally fixed manner, wherein the second element E12 of the first planetary gear set P1 is connected to the first output shaft WAb1 in a rotationally fixed manner, wherein the third element E13 of the first planetary gear set P1 is connected to the second coupling shaft W2 in a rotationally fixed manner. In addition, the first planetary gear set P1 and the second planetary gear set P2 have a common ring gear with a single tooth. In other words, the third element E13 of the first planetary gear set P1, the third element E23 of the second planetary gear set P2 and the second connecting shaft W2 are formed as a common component. As a result, the assembly complexity is reduced and the compactness is increased. The switching element S is effectively arranged between the second connecting shaft W2 and the second output shaft WAb2. Therefore, the switching element S acts between the first element E11 of the first planetary gear set P1 and the third element E13 of the first planetary gear set P1. The switching element S is arranged axially adjacent to the first planetary gear set P1. In other aspects, according to Fig. 9 The exemplary embodiment corresponds to the reference according to Figure 4 An exemplary embodiment of .
[0062] Fig.10 A seventh embodiment of the drive device according to the present invention is shown. Fig.10 The drive device basically corresponds to Fig. 9A drive device, wherein there is a difference between the two embodiments in the arrangement of the first planetary gear set P1 and the third planetary gear set P3. The short axial total length of the transmission 1 of this seventh embodiment is advantageous compared to the sixth embodiment. In the present case, the first planetary gear set P1 and the third planetary gear set P3 are arranged in a radially nested manner, wherein the third planetary gear set P3 is arranged radially on the inside, and wherein the first planetary gear set P1 is arranged radially on the outside. Therefore, the third planetary gear set P3 is arranged closer to the axis of rotation R than the first planetary gear set P1. The elements E11, E12, E13 of the first planetary gear set P1 and the elements E31, E32, E33 of the third planetary gear set P3 overlap in the axial direction. An intermediate gear with internal and external teeth is arranged in the power flow between the first planetary gear set P1 and the third planetary gear set P3. In the present case, the third element E33 of the third planetary gear set P3 and the first element E11 of the first planetary gear set P1 form a common component. The internal teeth of the intermediate gear form a ring gear for the radially internal third planetary gear set P3. The external teeth of the intermediate gear form a sun gear for the radially external first planetary gear set P1. The intermediate gear makes the transmission 1 more compact and lighter. In addition, the first planetary gear set P1 and the second planetary gear set P2 have a common ring gear with a single tooth. In other words, the third element E13 of the first planetary gear set P1, the third element E23 of the second planetary gear set P2 and the second connecting shaft W2 are formed as a common component. As a result, the assembly complexity is reduced and the compactness is increased. The switching element S is effectively arranged between the second connecting shaft W2 and the second output shaft WAb2. Therefore, the switching element S acts between the first element E11 of the first planetary gear set P1 and the third element E13 of the first planetary gear set P1. The switching element S is arranged axially adjacent to the second planetary gear set P2. The switching element S is axially arranged between the first planetary gear set P1 and the second planetary gear set P2. In other aspects, according to Fig.10 The exemplary embodiment corresponds to the reference according to Fig. 9 An exemplary embodiment of .
[0063] Fig.11 An eighth embodiment of the drive device according to the present invention is shown. Fig.11 The drive device basically corresponds to Figure 4A drive device, wherein there is a difference between the two embodiments in terms of the connection of the planetary gear sets P1, P2, P3. In the present case, the first element E21 of the second planetary gear set P2 is connected to the drive shaft WAn in a rotationally fixed manner, wherein the second element E22 of the second planetary gear set P2 is connected to the first coupling shaft W1 in a rotationally fixed manner, wherein the third element E23 of the second planetary gear set P2 is connected to the second coupling shaft W2 in a rotationally fixed manner. The first element E31 of the third planetary gear set P3 is connected to the first coupling shaft W1 in a rotationally fixed manner, wherein the second element E32 of the third planetary gear set P3 is connected to the second output shaft WAb2 in a rotationally fixed manner, wherein the third element E33 of the third planetary gear set P3 is connected to the fixed component formed as the housing G in a rotationally fixed manner. Furthermore, the first element E11 of the first planetary gear set P1 is connected to the second coupling shaft W2 in a rotationally fixed manner, wherein the second element E12 of the first planetary gear set P1 is connected to the second output shaft WAb2 in a rotationally fixed manner, wherein the third element E13 of the first planetary gear set P1 is connected to the first output shaft WAb1 in a rotationally fixed manner. The drive shaft WAn is formed as a hollow shaft, wherein the second output shaft WAb2 extends axially through the drive shaft WAn and the drive unit 2. The switching element S is effectively arranged between the second coupling shaft W2 and the second output shaft WAb2. Therefore, the switching element S acts between the first element E11 of the first planetary gear set P1 and the second element E12 of the first planetary gear set P1. The switching element S is arranged axially adjacent to the first planetary gear set P1. The switching element S is arranged axially between the first planetary gear set P1 and the second planetary gear set P2. Alternatively and not shown in the present case, the switching element S can be arranged radially on the outside around the second planetary gear set P2. The second planetary gear set P2 can be designed with a particularly small diameter, for example, as a result of which space is radially created between the second planetary gear set P2 and the second output shaft WAb2 in order to arrange the switching element S there. If the switching element S is arranged in a radially nested manner with the second planetary gear set P2, the total axial length can be saved. In other respects, according to Fig.11 The exemplary embodiment corresponds to the reference according to Figure 4 An exemplary embodiment of .
[0064] Fig.12 A ninth embodiment of the drive device according to the present invention is shown. Fig.12 The drive device basically corresponds to Figure 4A drive device, wherein there is a difference between the two embodiments in terms of the connection of the planetary gear sets P1, P2, P3. In the present case, the first element E21 of the second planetary gear set P2 is connected to the drive shaft WAn in a rotationally fixed manner, wherein the second element E22 of the second planetary gear set P2 is connected to the second coupling shaft W2 in a rotationally fixed manner, wherein the third element E23 of the second planetary gear set P2 is connected to the first coupling shaft W1 in a rotationally fixed manner. The first element E31 of the third planetary gear set P3 is connected to the first coupling shaft W1 in a rotationally fixed manner, wherein the second element E32 of the third planetary gear set P3 is connected to the second output shaft WAb2 in a rotationally fixed manner, wherein the third element E33 of the third planetary gear set P3 is connected to the fixed component formed as the housing G in a rotationally fixed manner. Furthermore, the first element E11 of the first planetary gear set P1 is connected to the second coupling shaft W2 in a rotationally fixed manner, wherein the second element E12 of the first planetary gear set P1 is connected to the second output shaft WAb2 in a rotationally fixed manner, wherein the third element E13 of the first planetary gear set P1 is connected to the first output shaft WAb1 in a rotationally fixed manner. The drive shaft WAn is formed as a hollow shaft, wherein the second output shaft WAb2 extends axially through the drive shaft WAn and the drive unit 2. The switching element S is effectively arranged between the second coupling shaft W2 and the second output shaft WAb2. Therefore, the switching element S acts between the first element E11 of the first planetary gear set P1 and the second element E12 of the first planetary gear set P1. The switching element S is arranged axially adjacent to the first planetary gear set P1. The switching element S is arranged axially between the first planetary gear set P1 and the second planetary gear set P2. Alternatively and not shown in the present case, the switching element S can be arranged radially on the outside around the second planetary gear set P2. The second planetary gear set P2 can be designed with a particularly small diameter, for example, as a result of which space is radially created between the second planetary gear set P2 and the second output shaft WAb2 in order to arrange the switching element S there. If the switching element S is arranged in a radially nested manner with the second planetary gear set P2, the total axial length can be saved. In other respects, according to Fig.12 The exemplary embodiment corresponds to the reference according to Figure 4 An exemplary embodiment of .
[0065] According to all nine exemplary embodiments, the transmission 1 includes: a first planetary gear set P1, which is formed as a negative planetary gear set having a sun gear, a ring gear and a planet carrier; a drive shaft WAn, which is configured to connect the transmission 1 to the drive unit 2; a first output shaft WAb1 and a second output shaft WAb2, each of which is configured to connect the transmission 1 to wheels of a motor vehicle; and a switching element S. One of the elements E11, E12, E13 of the first planetary gear set P1 is always connected to the first output shaft WAb1 in a rotationally fixed manner, wherein the other of the elements E11, E12, E13 of the first planetary gear set P1 is always connected to the second output shaft WAb2 in a rotationally fixed manner, and wherein the other of the elements E11, E12, E13 of the first planetary gear set P1 can always be connected to one of the two output shafts WAb1, WAb2 via the switching element S.
[0066] Reference numerals
[0067] 1 Transmission
[0068] 2 drive units
[0069] W1 first connecting shaft
[0070] W2 Second connecting shaft
[0071] WAN input axis
[0072] WAb1 first output shaft
[0073] WAb2 second output shaft
[0074] G housing
[0075] S switching element
[0076] RRotation axis
[0077] P1 first planetary gear set
[0078] E11 The first element of the first planetary gear set
[0079] E12 The second element of the first planetary gear set
[0080] E13 The third element of the first planetary gear set
[0081] P2 Second planetary gear set
[0082] E21 The first element of the second planetary gear set
[0083] E22 The second element of the second planetary gear set
[0084] E23 The third element of the second planetary gear set
[0085] P3 third planetary gear set
[0086] E31 The first element of the third planetary gear set
[0087] E32 The second element of the third planetary gear set
[0088] E33 The third element of the third planetary gear set
[0089] 100 Motor Vehicles
[0090] 101 First Wheel Bridge
[0091] 102 Second wheel bridge
[0092] R1 Wheels
[0093] R2 Wheels
[0094] R3 Wheels
[0095] R4 wheels.
Claims
1. A transmission (1) for a motor vehicle (100), comprising: a first planetary gear set (P1), a second planetary gear set (P2) and a third planetary gear set (P3), wherein each planetary gear set (P1, P2, P3) includes a first element (E11, E21, E31), a second element (E12, E22, E32) and a third element (E13, E23, E33), Exactly one drive shaft (WAn) for connecting the transmission (1) to a drive unit (2) of the motor vehicle (100), a first output shaft (WAb1) and a second output shaft (WAb2), each output shaft being used to connect the transmission (1) to wheels (R1, R2) of the motor vehicle (100), a first coupling shaft (W1) and a second coupling shaft (W2), each coupling shaft being used to connect two elements of two planetary gear sets (P1, P2, P3) in a rotationally fixed manner, a switching element (S) for transmitting torque between one of the two output shafts (WAb1, WAb2) and the second coupling shaft (W2), wherein one of the elements (E21, E22, E23) of the second planetary gear set (P2) is connected to the drive shaft (WAn) in a rotationally fixed manner, wherein another of the elements (E21, E22, E23) of the second planetary gear set (P2) is connected to the first coupling shaft (W1) in a rotationally fixed manner, wherein another of the elements (E21, E22, E23) of the second planetary gear set (P2) is connected to the second coupling shaft (W2) in a rotationally fixed manner, wherein one of the elements (E31, E32, E33) of the third planetary gear set (P3) is connected to the first coupling shaft (W1) in a rotationally fixed manner, wherein another of the elements (E31, E32, E33) of the third planetary gear set (P3) is connected to a fixed component in a rotationally fixed manner, wherein another of the elements (E31, E32, E33) of the third planetary gear set (P3) is connected to the second output shaft (WAb2) in a rotationally fixed manner, wherein one of the elements (E11, E12, E13) of the first planetary gear set (P1) is connected to the second connecting shaft (W2) in a rotationally fixed manner, wherein another of the elements (E11, E12, E13) of the first planetary gear set (P1) is connected to the first output shaft (WAb1) in a rotationally fixed manner, wherein another of the elements (E11, E12, E13) of the first planetary gear set (P1) is connected to the second output shaft (WAb2) in a rotationally fixed manner.
2. The transmission according to claim 1, in, The first element (E21) of the second planetary gear set (P2) is connected to the drive shaft (WAn) in a rotationally fixed manner, wherein the second element (E22) of the second planetary gear set (P2) is connected to the first coupling shaft (W1) in a rotationally fixed manner, wherein the third element (E23) of the second planetary gear set (P2) is connected to the second coupling shaft (W2) in a rotationally fixed manner, wherein the first element (E31) of the third planetary gear set (P3) is connected to the first coupling shaft (W1) in a rotationally fixed manner, wherein the second element (E32) of the third planetary gear set (P3) is connected to the fixed component in a rotationally fixed manner, wherein the third element (E33) of the third planetary gear set (P3) is connected to the second output shaft (WAb2) in a rotationally fixed manner, wherein the first element (E11) of the first planetary gear set (P1) is connected to the second connecting shaft (W2) in a rotationally fixed manner, wherein the second element (E12) of the first planetary gear set (P1) is connected to the first output shaft (WAb1) in a rotationally fixed manner, and wherein the third element (E13) of the first planetary gear set (P1) is connected to the second output shaft (WAb2) in a rotationally fixed manner.
3. The transmission (1) according to claim 1, in, The first element (E21) of the second planetary gear set (P2) is connected to the drive shaft (WAn) in a rotationally fixed manner, wherein the second element (E22) of the second planetary gear set (P2) is connected to the second coupling shaft (W2) in a rotationally fixed manner, wherein the third element (E23) of the second planetary gear set (P2) is connected to the first coupling shaft (W1) in a rotationally fixed manner, wherein the first element (E31) of the third planetary gear set (P3) is connected to the first coupling shaft (W1) in a rotationally fixed manner, wherein the second element (E32) of the third planetary gear set (P3) is connected to the fixed component in a rotationally fixed manner, wherein the third element (E33) of the third planetary gear set (P3) is connected to the second output shaft (WAb2) in a rotationally fixed manner, wherein the first element (E11) of the first planetary gear set (P1) is connected to the second output shaft (WAb2) in a rotationally fixed manner, wherein the second element (E12) of the first planetary gear set (P1) is connected to the first output shaft (WAb1) in a rotationally fixed manner, and wherein the third element (E13) of the first planetary gear set (P1) is connected to the second connecting shaft (W2) in a rotationally fixed manner.
4. The transmission (1) according to claim 1, in, The first element (E21) of the second planetary gear set (P2) is connected to the drive shaft (WAn) in a rotationally fixed manner, wherein the second element (E22) of the second planetary gear set (P2) is connected to the first coupling shaft (W1) in a rotationally fixed manner, wherein the third element (E23) of the second planetary gear set (P2) is connected to the second coupling shaft (W2) in a rotationally fixed manner, wherein the first element (E31) of the third planetary gear set (P3) is connected to the first coupling shaft (W1) in a rotationally fixed manner, wherein the second element (E32) of the third planetary gear set (P3) is connected to the fixed component in a rotationally fixed manner, wherein the third element (E33) of the third planetary gear set (P3) is connected to the second output shaft (WAb2) in a rotationally fixed manner, wherein the first element (E11) of the first planetary gear set (P1) is connected to the second output shaft (WAb2) in a rotationally fixed manner, wherein the second element (E12) of the first planetary gear set (P1) is connected to the first output shaft (WAb1) in a rotationally fixed manner, and wherein the third element (E13) of the first planetary gear set (P1) is connected to the second connecting shaft (W2) in a rotationally fixed manner.
5. The transmission (1) according to claim 1, in, The first element (E21) of the second planetary gear set (P2) is connected to the drive shaft (WAn) in a rotationally fixed manner, wherein the second element (E22) of the second planetary gear set (P2) is connected to the first coupling shaft (W1) in a rotationally fixed manner, wherein the third element (E23) of the second planetary gear set (P2) is connected to the second coupling shaft (W2) in a rotationally fixed manner, wherein the first element (E31) of the third planetary gear set (P3) is connected to the first coupling shaft (W1) in a rotationally fixed manner, wherein the second element (E32) of the third planetary gear set (P3) is connected to the second output shaft (WAb2) in a rotationally fixed manner, wherein the third element (E33) of the third planetary gear set (P3) is connected to a fixed component in a rotationally fixed manner, wherein the first element (E11) of the first planetary gear set (P1) is connected to the second connecting shaft (W2) in a rotationally fixed manner, wherein the second element (E12) of the first planetary gear set (P1) is connected to the second output shaft (WAb2) in a rotationally fixed manner, and wherein the third element (E13) of the first planetary gear set (P1) is connected to the first output shaft (WAb1) in a rotationally fixed manner.
6. The transmission (1) according to claim 1, in, The first element (E21) of the second planetary gear set (P2) is connected to the drive shaft (WAn) in a rotationally fixed manner, wherein the second element (E22) of the second planetary gear set (P2) is connected to the second coupling shaft (W2) in a rotationally fixed manner, wherein the third element (E23) of the second planetary gear set (P2) is connected to the first coupling shaft (W1) in a rotationally fixed manner, wherein the first element (E31) of the third planetary gear set (P3) is connected to the first coupling shaft (W1) in a rotationally fixed manner, wherein the second element (E32) of the third planetary gear set (P3) is connected to the second output shaft (WAb2) in a rotationally fixed manner, wherein the third element (E33) of the third planetary gear set (P3) is connected to a fixed component in a rotationally fixed manner, wherein the first element (E11) of the first planetary gear set (P1) is connected to the second connecting shaft (W2) in a rotationally fixed manner, wherein the second element (E12) of the first planetary gear set (P1) is connected to the second output shaft (WAb2) in a rotationally fixed manner, and wherein the third element (E13) of the first planetary gear set (P1) is connected to the first output shaft (WAb1) in a rotationally fixed manner.
7. A transmission (1) according to any one of the preceding claims, wherein: Two of the three planetary gear sets (P1, P2, P3) are arranged in a radially nested manner.
8. A transmission (1) according to any one of the preceding claims, wherein: One of the two coupling shafts (W1, W2) or one of the two output shafts (WAb1, WAb2) is integrally formed with an element of a corresponding planetary gear set (P1, P2, P3) connected thereto.
9. A transmission (1) according to any one of the preceding claims, wherein: At least one of the planetary gear sets (P1, P2, P3) is formed as a negative planetary gear set, wherein the first element (E11, E21, E31) of the corresponding planetary gear set (P1, P2, P3) is formed as a sun gear, The second element (E12, E22, E32) of the corresponding planetary gear set (P1, P2, P3) is formed as a planet carrier. Therein, the third element (E13, E23, E33) of the corresponding planetary gear set (P1, P2, P3) is formed as a ring gear.
10. A transmission (1) for a motor vehicle (100), comprising: at least one first planetary gear set (P1) having a first element (E11), a second element (E12) and a third element (E13), wherein the first planetary gear set (P1) is formed as a negative planetary gear set having a sun gear, a ring gear and a planet carrier, a drive shaft (WAn) for connecting the transmission (1) to a drive unit (2) of the motor vehicle (100), a first output shaft (WAb1) and a second output shaft (WAb2), each output shaft being used to connect the transmission (1) to wheels (R1, R2) of the motor vehicle (100), Switching element(s), wherein one of the elements (E11, E12, E13) of the first planetary gear set (P1) is connected to the first output shaft (WAb1) in a rotationally fixed manner, wherein another element (E11, E12, E13) of the first planetary gear set (P1) is connected to the second output shaft (WAb2) in a rotationally fixed manner, and Another one of the elements (E11, E12, E13) of the first planetary gear set (P1) is connectable to one of the two output shafts (WAb1, WAb2) via the switching element (S).
11. A transmission (1) according to any one of the preceding claims, wherein: The shift element (S) is designed as a friction clutch or a dog clutch.
12. A transmission (1) according to any one of the preceding claims, wherein: The actuation of the switching element (S) takes place at least partially by means of an axial force generated by the helical teeth.
13. A transmission (1) according to any one of the preceding claims, wherein: The switching element (S) in the closed state connects the third element (E13) of the first planetary gear set (P1) and the first element (E11) of the first planetary gear set (P1) in a rotationally fixed manner.
14. The transmission (1) according to any one of claims 1 to 12, wherein: The switching element (S) in the closed state connects the second element (E12) of the first planetary gear set (P1) and the first element (E11) of the first planetary gear set (P1) in a rotationally fixed manner.
15. A drive device comprising a drive unit (2) and a transmission (1) according to any one of claims 1 to 14.
Citation Information
Patent Citations
Planetary gear transmissions, in particular axle transmissions for a motor vehicle
DE102013215877A1