Method for operating a transmission device for a motor vehicle, and corresponding transmission device

Abstract

A transmission device and method for operating a transmission for a motor vehicle, which transmission device has an input shaft which is operatively connectable to a drive device of the motor vehicle, and has a first output shaft and a second output shaft, and has a spur gear differential transmission configured as a planetary transmission, whereby the input shaft and an intermediate shaft are coupled to the first output shaft and the second output shaft. An electric machine is coupled to the input shaft in a first shifting position of the shifting device and to the intermediate shaft in a second shifting position of the shifting device, and the electric machine is operated for applying a torque to the input shaft.

Claims

1. A method for operating a transmission device for a motor vehicle, the transmission device comprising: an input shaft which is operatively connectable to a drive device of the motor vehicle; a first output shaft and a second output shaft; and a spur gear differential transmission configured as a planetary transmission, wherein the input shaft and an intermediate shaft are coupled to the first output shaft and the second output shaft via the spur gear differential transmission, wherein the intermediate shaft is formed as a hollow shaft through which the input shaft passes, wherein an electric machine is coupled to the input shaft in a first shifting position of a shifting device and is coupled to the intermediate shaft in a second shifting position of the shifting device, wherein the electric machine is operated for applying a torque to the input shaft when in the first shifting position and for providing a differential torque and/or differential speed between the first output shaft and the second output shaft when in the second shifting position, and wherein the electric machine is operated at a speed different from zero when a differential torque is zero and/or when a differential speed is zero.

2. The method according to claim 1, wherein, before shifting from the first shifting position to the second shifting position, the electric machine is operated in a specific direction of rotation at a speed proportional to the speed of the input shaft.

3. The method according to claim 1, wherein the electric machine is set to load-free operation when shifting from the first shifting position to the second shifting position, or vice versa.

4. The method according to claim 1, wherein an intermediate position is set at the shifting device when shifting from the first shifting position to the second shifting position, or vice versa, in which intermediate position the electric machine is uncoupled from the input shaft and the intermediate shaft, and speed synchronization is performed.

5. The method according to claim 1, wherein an absolute value of the speed of the electric machine is kept permanently above a minimum speed when shifting from the first shifting position to the second shifting position, or vice versa.

6. The method according to claim 1, wherein, after shifting from the first shifting position to the second shifting position, the electric machine is operated in a specific direction of rotation at a speed proportional to the speed of the intermediate shaft.

7. The method according to claim 1, wherein, before shifting from the first shifting position to the second shifting position, a torque of the electric machine which is acting on the input shaft is reduced by a torque difference and the drive device is adjusted to compensate for the torque difference.

8. The method according to claim 1, wherein, after shifting from the second shifting position to the first shifting position, a torque of the electric machine which is acting on the input shaft is increased by a torque difference and the drive device is adjusted to compensate for the torque difference.

9. The method according to claim 1, wherein a low-voltage machine is used as the electric machine.

10. The method according to claim 1, wherein the planetary transmission of the spur gear differential transmission is configured as a double planetary gearing comprising a first and a second sun gear, a first and a second planetary gear, and a common planetary gear carrier.

11. The method according to claim 10, wherein the first planetary gear is formed as a stepped planetary gear which meshes on a first side with the second planetary gear and the first output shaft, and meshes on a second side with the intermediate shaft.

12. The method according to claim 10, wherein the input shaft rotates with the common planetary gear carrier.

13. The method according to claim 10, wherein the planetary gearing lacks an internal gear.

14. A transmission device for a motor vehicle, comprising: an input shaft which is operatively connectable to a drive device of the motor vehicle; a first output shaft and a second output shaft; and a spur gear differential transmission configured as a planetary transmission, wherein the input shaft and an intermediate shaft are coupled to the first output shaft and the second output shaft via the spur gear differential transmission, wherein the intermediate shaft is formed as a hollow shaft through which the input shaft passes, wherein an electric machine is coupled to the input shaft in a first shifting position of a shifting device and is coupled to the intermediate shaft in a second shifting position of the shifting device, wherein the electric machine is operated for applying a torque to the input shaft when in the first shifting position and for providing a differential torque and/or differential speed between the first output shaft and the second output shaft when in the second shifting position, and wherein the electric machine is operated at a speed different from zero when a differential torque is zero and/or when a differential speed is zero.

15. The transmission device according to claim 14, wherein the planetary transmission of the spur gear differential transmission is configured as a double planetary gearing comprising a first and a second sun gear, a first and a second planetary gear, and a common planetary gear carrier.

16. The transmission device according to claim 15, wherein the first planetary gear is formed as a stepped planetary gear which meshes on a first side with the second planetary gear and the first sun gear, which is rigidly connected to the first output shaft, and meshes on a second side with the intermediate shaft.

17. The transmission device according to claim 15, wherein the input shaft rotates with the common planetary gear carrier.

18. The transmission device according to claim 15, wherein the planetary gearing lacks an internal gear.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The invention will be explained in more detail below based on the exemplary embodiments shown in the drawing, but without limiting the invention in any way. Wherein:

(2) FIG. 1 shows a schematic view of a first embodiment of a transmission device for a motor vehicle;

(3) FIG. 2 shows a schematic view of a second embodiment of the transmission device; and

(4) FIG. 3 shows a schematic view of a third embodiment of the transmission device.

(5) FIG. 4 shows an exemplary process for shifting a transmission device.

DETAILED DESCRIPTION

(6) FIG. 1 shows a schematic view of a first embodiment of a transmission device 1, which is provided herein, for example, as part of a motor vehicle 2 not shown in detail. The motor vehicle 2 has a wheel axle 3 with a first partial shaft 4 and a second partial shaft 5. The wheel axle 3 or the partial shafts 4 and 5, respectively, can be driven by means of the transmission device 1 using a drive device of the motor vehicle 2. The drive device is or at least can be operatively connected to an input shaft 6 of the transmission device 1. The first partial shaft 4, on the other hand, is coupled to a first output shaft 7, the second partial shaft 5 to a second output wave 8 of the transmission device 1, or operatively connected to the output shaft 7 or 8, respectively.

(7) The operative connection between the first partial shaft 4 and the first output shaft 7 is established by means of a first transmission 9, the operative connection between the second partial shaft 5 and the second output shaft 8 is established by means of a second transmission 10. The transmissions 9 and 10 can be provided in the form of angular gears. They are preferably configured as spur gear transmissions and each have a first spur gear 11 or 12, respectively, and a second spur gear 13 or 14, respectively. According to the present embodiment of the transmission device 1, the partial shafts 4 and 5 or their axes of rotation, respectively, can be offset in the lateral or radial direction, respectively, with respect to their axes of rotation. The partial shafts 4 and 5 may alternatively be coaxially arranged, or at least be in alignment in a top view.

(8) The output shafts 7 and 8 may be at an angle with respect to the partial shafts 4 and 5 or the wheel axle 3, i.e. be at an angle greater than 0° and smaller than 180°, for example at an angle of 90° thereto. The respective deflection is implemented by means of the transmissions 9 and 10, which are provided in the form of angular gears. The transmissions 9 and 10 may of course alternatively be configured as spur gear transmissions. For example, the output shafts 7 and 8 are arranged parallel to the partial shafts 4 and 5.

(9) The transmission device 1 comprises a spur gear differential transmission 15, whereby the first output shaft 7 and the second output shaft 8 are permanently operatively connected or coupled to the input shaft 6. To this end, the spur gear differential transmission 15 is configured as a planetary gear which comprises a first sun gear 16, a second sun gear 17, and a planetary carrier 18 on which a first planetary gear 19 and a second planetary gear 20 are each pivotably mounted. The planetary carrier 18 is coupled to the input shaft 6 of the transmission device 1, particularly in a rigid and/or permanent manner. The first sun gear 16, on the other hand, is coupled to the first output shaft 7 and the second sun gear 17 is coupled to the second output shaft 8, preferably in a rigid and/or permanent manner. The first planetary gear 19 meshes with the second planetary gear 20, preferably permanently. The first planetary gear 19 also meshes with the first sun gear 16, but not with the second sun gear 17. The second planetary gear 20 on the other hand meshes with the second sun gear 17, but not with the first sun gear 16.

(10) The first planetary gear 19 is configured as the first stepped planetary gear 21, which is coupled to the second stepped planetary gear 22 in a rotationally fixed manner. The two stepped planetary gears 21 and 22 are jointly pivotably mounted onto the planetary carrier 18, wherein they are preferably provided on opposite sides of a mounting point 23 on the planetary carrier 18. The second stepped planetary gear 22 is coupled to an intermediate shaft 24 in a rotationally fixed manner, particularly in a rigid and/or permanent manner. It is clearly visible that the two output shafts 7 and 8 and the input shaft 6 and intermediate shaft 24 are arranged coaxially, that is, have the same axis of rotation. The second output shaft 8 accommodates at least sections of the first output shaft 7, and likewise the intermediate shaft 24 accommodates at least sections of the input shaft 6. It should be particularly pointed out that the spur gear differential transmission 15 is configured without an internal gear, i.e. does not have an internal gear.

(11) The transmission device 1 has an electric machine 25 which can be coupled to the input shaft 6 and/or to the intermediate shaft 24 by means of a shifting device 26. The shifting device 26 has a coupling member 27 for this purpose, which can be displaced in the axial direction as indicated by the double arrow 28. In the embodiment shown here, the shifting device 26 comprises an input gear 29, a first output gear 30, and a second output gear 31. Furthermore, an auxiliary gear 32 may be provided.

(12) The coupling member 27 is configured such that is permanently meshes with the input gear 29 of the shifting device 26. In a first shifting position, it additionally meshes with the first output gear 30, but not with the second output gear 31 and the auxiliary gear 32. In a second shifting position, it additionally meshes with the second output gear 31, but not with the first output gear 30 and the auxiliary gear 32. In a third shifting position, it additionally meshes with the first output gear 32, but not with the second output gear 30 and the auxiliary gear 31.

(13) The input gear 29 is coupled to the electric machine 25, particularly in a rigid and/or permanent manner. The first output gear 30 is firmly coupled to the input shaft 6, and the second output gear 31 is firmly coupled to the intermediate shaft 24, preferably likewise in a rigid and/or permanent manner. The auxiliary gear 32, on the other hand, is uncoupled from both the input shaft 6 and the intermediate shaft 24 and thus mounted for free rotation.

(14) The connection between the electric machine 25 and the shifting device 26 or the input gear 29, respectively, is provided by means of a coupled planetary transmission 33. It comprises a sun gear 34, a planetary carrier 35 with a planetary gear 36 pivotably mounted thereto, and an internal gear 37. The sun gear is coupled to the electric machine 25, particularly in a rigid and/or permanent manner. The internal gear 37 is stationary, however. The planetary gear 36 now meshes with both the sun gear 34 and the internal gear 37. The planetary carrier 35 is coupled to the shifting device 26, particularly to the input gear 29, particularly in a rigid and/or permanent manner.

(15) The shifting device 26 can be used to couple the electric machine 25 either to the input shaft 6 or to the intermediate shaft 24. In the former case, the electric machine 25 can provide a torque which is superimposed on a torque provided by the drive device to the input shaft 6. This means that the electric machine 25 can be used to either increase or reduce the drive torque.

(16) In the second shifting position of the shifting device 26, the electric machine 25 can be used for providing a torque vectoring functionality. This functionality allows splitting the drive torque applied to the input shaft 6 by providing an additional torque between the two partial shafts 4 and 5 using the electric machine 25, such that a desired torque distribution between these shafts is achieved. This means that the electric machine 25 can be used to split the drive torque freely between the output shafts 7 and 8 and thus between the partial shafts 4 and 5.

(17) FIG. 2 shows a schematic view of a second embodiment of the transmission device 1. It is in principle constructed like the first embodiment, such that we will only discuss the differences hereinafter and otherwise refer to the description above. The differences are in the design of the shifting device 26. While the input gear 29 was configured as an internal gear in the first embodiment, it is now present as a spur gear and is arranged between the first output gear 30 and the second output gear 31 when viewed in an axial direction. The functionality is not identical with the shifting device 26 of the first embodiment described above, however. Compared to that embodiment, the auxiliary gear 32 can be eliminated, which is the case here.

(18) FIG. 3 shows a schematic view of a third embodiment of the transmission device 1. Once again we refer to the preceding description, particularly regarding the first embodiment, and will point out the difference below. These differences include that the coupled planetary transmission 33 is two-stage, such that the electric machine 25 is coupled to both the input gear 29 and to another input gear 38 by means of the coupled planetary transmission 33, preferably in a rigid and/or permanent manner. To this end, the coupled planetary transmission 33 comprises another sun gear 39, another planetary gear 40, and another internal gear 41.

(19) The sun gear 39 is coupled to the sun gear 34 and thus to the electric machine 25, particularly in a rigid and/or permanent manner. The planetary gear 40 is pivotably mounted to the planetary carrier 35, but independent of the planetary gear 36. The planetary gear 40 meshes with the sun gear 39 on the one hand and with the internal gear 41 on the other. The internal gear is pivotably mounted and coupled to the input gear 38, preferably in a rigid and/or permanent manner. The planetary gears 36 and 40 preferably comprises different numbers of teeth, such that a first gear ratio is established between the electric machine 25 and the input gear 29 and a second gear ratio is established between the electric machine 25 and the other input gear 38, wherein the two gear ratios are different from each other.

(20) In addition to the shifting positions already described above, a fourth shifting position of the shifting device 26 can be provided in which the coupling member 27 meshes with the input gear 38 instead of the input gear 29, while it meshes at the same time with the first output gear 30. Accordingly, a different gear ratio than in the first shifting position is set here between the electric machine 25 and the input shaft 6.

(21) The described transmission device 1 has the particular advantage that the spur gear differential transmission 15 is configured without an internal gear and can thus be implemented in a small axial installation space. In addition, the shifting device 26 allows a flexible coupling of the electric machine 25 either for driving the input shaft 6 or for providing the torque vectoring functionality by driving the intermediate shaft 24.

(22) The transmission device 1 described above is used to implement a method in which the electric machine 25 is operated for applying a torque to the input shaft 6 when in the first shifting position and for providing a differential torque and/or differential speed between the first output shaft 7 and the second output shaft 8 when in the second position, wherein the electric machine 25 is operated at a speed different from zero when a differential torque is zero and/or when a differential speed is zero. This on the one hand allows improved propulsion of the motor vehicle 2 even in the second shifting position and on the other hand faster shifting between the shifting positions.

(23) FIG. 4 shows a process by which a speed and torque of the electric machine 25 might be managed when shifting the shifting device 26. When shifting from the first shifting position to the second shifting position (or vice versa), an absolute value of the speed of the electric machine 25 is kept above a minimum speed in S1. Before shifting from the first shifting position to the second shifting position in S3, a torque of the electric machine 25 is reduced by a torque difference in S2 and the drive device is adjusted to compensate for the torque difference. After shifting from the first shifting position to the second shifting position in S3, a torque of the electric machine 25 is increased by a torque difference in S4 and the drive device is adjusted to compensate for the torque difference.