Brake disk unit

Abstract

In order to provide a brake disc unit the production and assembly of which is economically viable even with extreme mechanical and thermal load capacity, preferably without the application of intermediate elements, the disclosure proposes a brake disc unit with a friction ring and a friction ring carrier which are connected by a shaft-to-hub connection with an alignment gearing having a multitude of dogs, wherein the cross-section of the dogs provides a contour which, at least partly, runs along an extended trochoid.

Claims

1. A brake disc unit with a friction ring and a friction ring carrier which are connected by means of a shaft-to-hub connection with an alignment gearing having a multitude of dogs, wherein the cross section of the dogs has a contour which, at least partly, runs along an extended trochoid.

2. The brake disc unit according to claim 1, wherein the extended trochoid is an extended hypotrochoid.

3. The brake disc unit according to claim 1, wherein the extended trochoid is an extended epitrochoid.

4. The brake disc unit according to claim 1, wherein there are also dogs with different contours.

5. The brake disc unit according to claim 4, wherein the dogs with different contours belong to involute or parallel toothings, and/or fine serrations.

6. The brake disc unit according to claim 1, wherein non- contacting areas are formed in the contour of the dogs.

7. The brake disc unit according to claim 1, wherein the shaft and the hub are compressed.

8. The brake disc unit according to claim 7, wherein a measure for compression is selected in dependence on the maximum temperature difference to be expected between the shaft and the hub.

9. The brake disc unit according to claim 1, wherein the contour is manufactured by cam turning.

10. The brake disc unit according to claim 1, wherein dogs comprise an undercut.

11. The brake disc unit according to claim 1, wherein the friction ring and the friction ring carrier are made of different materials.

12. The brake disc unit according to claim 1, wherein the dogs are arranged in sections.

13. The brake disc unit according to claim 12, wherein each individual section constitutes an independent torque-transmitting unit.

14. The brake disc unit according to claim 1, wherein the alignment gearing comprises areas stepped in an axial direction.

15. The brake disc unit according to claim 1, wherein a locking device against axial displacement is provided.

16. The brake disc unit according to claim 1, wherein the alignment gearing is formed only over part of an axial contact ratio of the shaft and the hub.

Description

DRAWINGS

(1) The drawings described herein are for illustrative purposes only of selected embodiments and not all possible implementations, and are not intended to limit the scope of the present disclosure.

(2) Other advantages and features of the disclosure can be gathered from the following description on the basis of the figures. In these figures:

(3) FIG. 1 shows a top view of a polygonal profile of a shaft according to the state of the art;

(4) FIG. 2 shows a top view of a polygonal profile of a shaft according to the state of the art;

(5) FIG. 3 shows a sectional view (schematised) of an exemplary embodiment of a shaft-hub-profile according to the disclosure;

(6) FIG. 4 shows an illustration according to FIG. 3 with representation of the tool trajectory;

(7) FIG. 5 shows an enlarged illustration of the normal in an exemplary embodiment for a shaft-hub-profile according to the disclosure;

(8) FIG. 6 shows an illustration according to FIG. 5 of an exemplary embodiment with an undercut;

(9) FIG. 7a shows a sectional view of a shaft according to the disclosure;

(10) FIG. 7b shows a sectional view of a hub according to the disclosure, and

(11) FIG. 7c shows an illustration of the assembly.

(12) In the figures, identical elements are identified by the same reference numerals.

DETAILED DESCRIPTION

(13) Example embodiments will now be described more fully with reference to the accompanying drawing.

(14) According to FIGS. 1 and 2, there are, in addition to the standard tooth systems such as involute toothing, parallel toothing, or fine serration which are known per se, also so-called polygonal tooth systems. Polygonal contours as the ones shown have been known from the prior art. FIG. 1 shows a so-called H6 profile 1 by way of example, in which a contour with six corners 2 is formed. This cross section for torque transmission has the surface normal 4.

(15) According to FIG. 2, a so-called P3G profile is shown where the surface normal 7 is formed.

(16) In FIGS. 1 and 2, the respective normals are shown surrounding the entire perimeter. In particular, the course of the normal which is partly extremely unfavourable for force transmission or momentum transmission can be seen here.

(17) The FIGS. 3 and 4 are an exemplary embodiment of a gear tooth profile. The profile 10 comprises dogs 11 with a dog height 13 and interspaces 12, which engages with the corresponding counter-profile. The dogs have dog width 14. They are positioned between the internal functional diameter 16 and the external functional diameter 15. In the exemplary embodiment shown, the dogs have an undercut 17, which is a taper in the area of the root. The tool trajectory 18 is shown in FIG. 4.

(18) FIG. 5 shows an enlarged illustration of a dog 11 of a shaft-to-hub connection according to FIG. 3. In the shown enlarged illustration, the dog 11 is supplemented by the representation of the normal 20, illustrated by corresponding rays on the dog surface. It turns out that here, a particularly favourable course of the normal is provided, resulting in a special suitability for transmission of forces and torques.

(19) The corresponding illustration shown in FIG. 6 shows a dog 11 and the radial normal 21. In this illustration, the undercut 17 is particularly marked. It results from a deviation from an at least straight or tangential bedding-down of the dog. The undercut contour provides the correspondingly described advantages.

(20) An exemplary embodiment of a brake disc unit according to the disclosure is shown in the FIGS. 7a to 7c. A shaft 22 is provided with dogs 23 with interspaces 24 remaining between them. The dogs 23 comprise an undercut in the exemplary embodiment shown.

(21) The hub 25 shown in FIG. 7b has corresponding recesses 26 and interspaces or dogs 27.

(22) Joined together, this results in the illustration according to 7c, which shows that the transmission contacts along the normal are optimised.

(23) The illustrated exemplary embodiment shows for instance that hub 25 may be configured as a brake disc with respect to shaft 22 configured as a central hub body or pot.

(24) The described exemplary embodiments only serve a better understanding and are not restrictive.

(25) The foregoing description of the embodiments has been provided for purposes of illustration and description. It is not intended to be exhaustive or to limit the disclosure. Individual elements or features of a particular embodiment are generally not limited to that particular embodiment, but, where applicable, are interchangeable and can be used in a selected embodiment, even if not specifically shown or described. The same may also be varied in many ways. Such variations are to be regarded as a departure from the disclosure, and all such modifications are intended to be included within the scope of the disclosure.