DIFFERENTIAL GEAR FOR A MOTOR VEHICLE

Abstract

A differential gear including a rotatably mounted differential housing and a final driven gear mounted rotationally fixed to the differential housing. The differential housing, on the outer circumferential surface thereof, includes two mating surfaces and that the final driven gear, on the inner circumferential surface thereof, includes two radially opposite mating surfaces. The mating surfaces formed on the outer circumferential surface of the differential housing and the mating surfaces formed on the inner circumferential surface of the final driven gear are each designed as separate mating surfaces which, when viewed in axial direction (a), are arranged geometrically separated from each other by a spacing.

Claims

1-12. (canceled)

13. A differential gear comprising a rotatably mounted differential housing and an final driven gear mounted rotationally fixed to the differential housing, wherein the differential housing, on the outer circumferential surface thereof, comprises two mating surfaces and that the final driven gear, on the inner circumferential surface thereof, comprises two radially opposite mating surfaces, wherein the mating surfaces formed on the outer circumferential surface of the differential housing and the mating surfaces formed on the inner circumferential surface of the final driven gear are each designed as separate mating surfaces which, when viewed in axial direction (a), are arranged geometrically separated from each other by a spacing (A), and in that the final driven gear is pressed onto the differential housing, so that the final driven gear and the differential housing are connected to one another by means of a first press fit and a second press fit which is separate therefrom and axially separated by the spacing (A).

14. The differential gear according to claim 13, wherein the in axial direction (a), the mating surfaces formed on the outer circumferential surface of the differential housing and the mating surfaces formed on the inner circumferential surface of the final driven gear are in each case separated from one another by a circumferential groove introduced into the respective circumferential surface, wherein the grooves, when viewed in axial direction (a), each have a length corresponding to the spacing (A).

15. The differential gear according to claim 14, wherein the grooves have a rectangular, triangular or semicircular basic shape.

16. The differential gear according to claim 13, wherein when viewed in the axial direction (a), the inner circumferential surface of the final driven gear has a length (L) and wherein, with respect to the length (L) of the inner circumferential surface, for the spacing (A) between the mating surfaces:
0.5≤A/L≤0.7.

17. The differential gear according to claim 13, wherein the two press fits have a radial overlap of 10 to 50 μm and in that an additional non positive or positive locking connection is formed between final driven gear and differential housing.

18. The differential gear according to claim 17, wherein the additional connection is designed in the form of a weld connection.

19. The differential gear according to claim 18, wherein the weld connection is designed as a one-sided weld seam position arranged either only in the region of the first press fit or only in the region of the second press fit.

20. The differential gear according to claim 18, wherein the weld connection is produced by electron or laser welding.

21. The differential gear according to claim 17, wherein the additional connection is designed in the form of a polygonal or mating toothing and in that, between final driven gear and differential housing, a retaining element preventing a relative movement in axial direction (a) is arranged.

22. The differential gear according to claim 21, wherein the retaining element is designed in the form of a retaining ring.

23. The differential gear according to claim 13, wherein the two press fits have a radial overlap of >200 μm, so that the final driven gear is connected in a rotationally fixed and axially fixed manner to the differential housing only via the frictional connections resulting from the press fits.

24. The differential gear according to claim 13, wherein the differential housing is made of cast iron and the final driven gear is made of a hardenable material.

25. The differential gear according to claim 14, wherein when viewed in the axial direction (a), the inner circumferential surface of the final driven gear has a length (L) and wherein, with respect to the length (L) of the inner circumferential surface, for the spacing (A) between the mating surfaces:
0.5≤A/L≤0.7.

26. The differential gear according to claim 15, wherein when viewed in the axial direction (a), the inner circumferential surface of the final driven gear has a length (L) and wherein, with respect to the length (L) of the inner circumferential surface, for the spacing (A) between the mating surfaces:
0.5≤A/L≤0.7.

27. The differential gear according to claim 14, wherein the two press fits have a radial overlap of 10 to 50 μm and in that an additional non positive or positive locking connection is formed between final driven gear and differential housing.

28. The differential gear according to claim 15, wherein the two press fits have a radial overlap of 10 to 50 μm and in that an additional non positive or positive locking connection is formed between final driven gear and differential housing.

29. The differential gear according to claim 16, wherein the two press fits have a radial overlap of 10 to 50 μm and in that an additional non positive or positive locking connection is formed between final driven gear and differential housing.

30. The differential gear according to claim 19, wherein the weld connection is produced by electron or laser welding.

31. The differential gear according to claim 14, wherein the two press fits have a radial overlap of >200 μm, so that the final driven gear is connected in a rotationally fixed and axially fixed manner to the differential housing only via the frictional connections resulting from the press fits.

32. The differential gear according to claim 15, wherein the two press fits have a radial overlap of >200 μm, so that the final driven gear is connected in a rotationally fixed and axially fixed manner to the differential housing only via the frictional connections resulting from the press fits.

Description

[0020] Additional advantages and application possibilities of the present invention result from the following description in connection with the embodiment example represented in the drawing.

[0021] In the drawing:

[0022] FIG. 1 represents a cross-sectional view of a first embodiment of a differential gear according to the invention;

[0023] FIG. 2 represents the differential gear from FIG. 1 in the top view;

[0024] FIG. 3 represents a second embodiment of a differential gear in a cross-sectional view;

[0025] FIG. 4 represents the differential gear from FIG. 3 in the top view;

[0026] FIG. 5 represents a cross-sectional view of a third embodiment of the differential gear according to the invention, and

[0027] FIG. 6 represents the differential gear from FIG. 5 in the top view.

[0028] In the following description and in the figures, identical parts and components are marked with identical reference numerals to avoid repetitions, to the extent that no additional differentiation is necessary or appropriate.

[0029] FIGS. 1 and 2 show a first embodiment of a differential gear of a motor vehicle, denoted overall by the reference numeral 10.

[0030] The differential gear 10 comprises a differential housing 12 and an final driven gear 14 connected in a rotationally fixed manner to the differential housing 12. The final driven gear 14, via the outer toothing 14-1 thereof, is in operative connection with a drive shaft—not represented here the sake of clarity.

[0031] Via a cruciform drive pin 16, the differential housing 12 drives four planet gears 18 which in turn mesh with two driven gears 20 which can be connected in a rotationally fixed manner to wheel shaft axles—not represented here for the sake of clarity.

[0032] As can be derived from FIGS. 1 and 2, the differential housing 12, on the outer circumferential surface thereof, has two mating surfaces, and the final driven gear 14, on the inner circumferential surface thereof, has two radially opposite mating surfaces which, when viewed in axial direction a, are each formed as separate mating surfaces arranged geometrically separated from one another by a spacing A, so that the final driven gear 14 pressed onto the differential housing 12 is connected collectively by means of a first press fit 22-1 and a second press fit 22-2 which is separate therefrom and axially separated by the spacing A.

[0033] In order to ensure a sufficient spacing for the tilt-resistant support between the press fits 22-1 and 22-2, the spacing A should be selected so that:

0.5≤A/L≤0.7,

wherein L denotes the axial length, when viewed in axial direction a, of the inner circumferential surface of the final driven gear 14.

[0034] For the geometric separation of the mating surfaces and thus of the first and second press fits 22-1, 22-2—as can also be derived from FIG. 1—, a groove 24 is milled in each case into the circumferential surface of the differential housing 12 and into the circumferential surface of the final driven gear 14. In addition to the geometric separation, a weight reduction is also achieved in particular in a particularly advantageous manner by the grooves 24.

[0035] In the present case, the grooves 24 that are introduced each have a substantially rectangular basic shape.

[0036] Due to the spaced arrangement, in axial direction a, of the two press fits 22-1, 22-2, an exceedingly tilt-resistant support is provided, which can absorb all the axial forces resulting from the meshing of the outer toothing 14-1 of the final driven gear 14 with a drive shaft—not represented here—, so that an optimal tooth contact and thus a uniform transmission of motion causing no undesired noise is ensured.

[0037] According to the embodiment represented in FIG. 1 and FIG. 2, the two press fits 22-1 and 22-2 have a radial overlap of 10 to 50 μm. Moreover, in order to ensure the torque transmission, between final driven gear 14 and differential housing 12, in the area of the first press fit 22-1, an additional positive locking connection is formed. The axial securing is ensured via a retaining ring 26.

[0038] As can be seen in particular from FIG. 2, in the present case, the positive locking connection is designed in the form of a polygonal toothing 28.

[0039] The second embodiment represented in FIGS. 3 and 4 corresponds substantially to the first embodiment represented in FIGS. 1 and 2. Compared to the first embodiment, the second embodiment differs in that the additional connection between final driven gear 14 and differential housing 12, which is used for the torque transmission, is designed in the form of a weld connection 30. Here—as FIGS. 3 and 4 show in particular—the weld connection 30 is designed as a one-sided circumferential weld seam position which is arranged only in the region of the first press fit 22-1. In addition to the torque transmission, an axial securing is also ensured by the weld seam.

[0040] The third embodiment of the differential housing according to the invention, which is represented in FIGS. 5 and 6, in comparison to the first and second embodiments, is characterized in that, for the torque transmission, instead of a positive or non positive locking connection, here only a frictional connection is provided. In order to ensure a sufficient torque transmission, the two press fits 22-1, 22-2 here have a radial overlap of >200 μm.