BEARING RING

Abstract

A bearing ring for a rolling-element bearing or plain bearing has at least one first region that is inductively hardened or is configured to be inductively hardened and at least one second region that is not inductively hardened and is not intended to be inductively hardened, and the at least one second region includes at least one stress-relief recess and/or at least one stress-relief projection.

Claims

1. A bearing ring for a rolling-element bearing or plain bearing comprising: at least one first region that is inductively hardened or is configured to be inductively hardened and at least one second region that is not inductively hardened and is not intended to be inductively hardened, the at least one second region including at least one stress-relief recess and/or at least one stress-relief projection.

2. The bearing ring according to claim 1, wherein each one of the at least one second regions includes at least one stress-relief recess and/or at least one stress-relief projection.

3. The bearing ring according to claim 1, wherein the at least one stress-relief recess and/or at least one stress-relief projection is disposed adjacent to the at least one first region.

4. The bearing ring according to claim 3, wherein the at least one stress-relief recess and/or stress-relief projection is spaced from the at least one first region by a distance that is less than twice an inductive hardening depth of the first region.

5. The bearing ring according to claim 1, wherein the at least one stress-relief recess and/or at least one stress-relief projection extends circumferentially around the bearing ring.

6. The bearing ring according to claim 1, wherein the at least one stress-relief recess and/or stress-relief projection comprises a plurality of discretely formed stress-relief recesses and/or stress-relief projections distributed circumferentially around the bearing ring.

7. The bearing ring according to claim 1, wherein the at least one stress-relief recess and/or stress-relief projection includes at least one side wall extending at an angle of more than 30 and less than 60 with respect to a radial direction of the bearing ring.

8. The bearing ring according to claim 1, wherein a depth of the at least one stress-relief recess and/or a height of the at least one stress-relief projection is 1 to 1.5 times that of a depth of an inductively hardened portion of the at least one first region.

9. The bearing ring according to claim 1 wherein the bearing ring is a bearing ring of a rolling-element bearing.

10. The bearing ring according to claim 1, wherein the at least one stress-relief recess and/or stress-relief projection is spaced from the at least one first region by a distance that is less than twice an inductive hardening depth of the first region, wherein the at least one stress-relief recess and/or stress-relief projection comprises a plurality of discretely formed stress-relief recesses and/or stress-relief projections distributed circumferentially around the bearing ring, wherein the at least one stress-relief recess and/or at least one stress-relief projection includes at least one side wall extending at an angle of more than 30 and less than 60 with respect to a radial direction of the bearing ring, and wherein a depth of the at least one stress-relief recess and/or a height of the at least one stress-relief projection is 1 to 1.5 times that of a depth of an inductively hardened portion of the at least one first region.

11. The bearing ring according to claim 10, wherein the plurality of stress-relief projections alternate circumferentially with the plurality of stress-relief recesses.

12. The bearing ring according to claim 1, wherein each second region is located between a pair of the first regions.

13. The bearing ring according to claim 1, wherein a first one of the at least one first regions comprises a bearing raceway and a second one of the at least one first regions does not include a bearing raceway.

14. The bearing according to claim 1, wherein the at least one first region is inductively hardened.

15. The bearing ring according to claim 6, wherein the plurality of stress-relief projections alternate circumferentially with the plurality of stress-relief recesses.

16. A bearing ring for a rolling-element bearing or plain bearing comprising: a raceway inductively hardened to a first depth; a circumferential region adjacent to the raceway that is not inductively hardened; and an annular region that is inductively hardened to a second depth less than the first depth, wherein the circumferential region is located between the raceway and the annular region, and wherein the circumferential region includes at least one circumferentially extending stress-relief recess and/or at least one circumferentially extending stress-relief projection.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0015] FIG. 1 is a sectional view through a bearing ring according to a first preferred exemplary embodiment of the disclosure.

[0016] FIG. 2 is a sectional view through a bearing ring according to a second preferred exemplary embodiment of the disclosure.

[0017] FIG. 3 is a sectional view through a bearing ring according to a third preferred exemplary embodiment of the disclosure.

DETAILED DESCRIPTION

[0018] In the following, identical or functionally equivalent elements are designated by the same reference numbers.

[0019] In FIGS. 1 to 3, different bearing rings 1 are shown that are each equipped with stress-relief recesses/stress-relief projections.

[0020] FIG. 1 schematically shows a sectional representation of a bearing ring 1 that is used, for example, in a deep groove ball bearing. Here the bearing inner ring 1 includes inner ring outer surfaces 2, 4 and 6, which although inductively hardened are not subjected to any particularly increased loading. In contrast the raceway 8 is heavily loaded and therefore must be made particularly hard due to the contact with rolling elements (not shown). The penetration depth of the inductive hardening on the raceway 8 is thus significantly greater than on the side surfaces 2, 4 and 6. This is characterized by the differently thick black regions in FIG. 1.

[0021] Furthermore FIG. 1 shows that not-hardened regions 10, 12, are present laterally adjacent to the raceway 8, which not-hardened regions 10, 12 are each equipped with a stress-relief recess 14, 16 in the exemplary embodiment depicted. These stress-relief recesses 14, 16 are disposed directly adjacent to or at a very small distance A from the raceway 8, which is inductively hardened, and formed with a relatively great depth T, since the hardening depth E of the raceway 8 is particularly large. Since with a particularly deep hardening depth E the heat-influence zone is also significantly larger and the stress load of the component is particularly large due to thermal expansion, it is advantageous to dimension the stress-relief recess/projection accordingly such that the recessed or raised regions make possible a sufficient geometry change of the bearing ring without leading to crack formation.

[0022] FIG. 1 further shows that the side walls 18, 20 of the stress-absorption recess 16 are arranged with respect to a radial direction R of the bearing ring such that altogether they form an opening angle of 60. In the exemplary embodiment depicted the side walls of the recess 16 are configured symmetrically; however it is also possible to design the side walls with different inclinations. It is also depicted that the recesses 14 and 16 are configured identically. However, it is also possible that the recesses 14, 16 have different geometries, or even that one of the stress-relief recesses is configured as a stress-relief projection. Furthermore one of the stress-relief recesses 14, 16 can also be configured as a continuous groove extending circumferentially, while the other stress-relief recess is configured as a plurality of discrete circumferentially distributed stress-relief elements. Here the stress-relief elements can be configured as recesses and/or as projections, wherein projection and recess can even alternate in turn.

[0023] FIG. 2 shows a further preferred exemplary embodiment of a bearing ring 1 that is used in a roller bearing, in particular a double row tapered roller bearing. In this exemplary embodiment there are also inductively hardened bearing ring outer surfaces 2, 4, 6, which although inductively hardened need not withstand any particularly heavy loads. In contrast the raceways 8-1, 8-2 are in direct rolling-element contact and must withstand heavy loads. Not-hardened regions 10, 12, 18 are in turn provided between and laterally to the raceways 8-1, 8-2; the not-hardened regions 10, 12, 18 are each provided with stress-relief recesses 14, 16, 22. The lateral surfaces of the retaining flanges and guide flanges, which lateral surfaces face the raceways, are also inductively hardened and are defined as regions of the raceways 8-1, 8-2. The stress-relief recesses 14, 16, 22 extend essentially parallel to or at the opening angle, reduced by half, with respect to the hardened edge layer of the retaining flanges and guide flanges.

[0024] As can furthermore be seen from FIG. 2, all stress-relief recesses 14, 16, 22 are different from each other, wherein their different design is due to the specific geometric design of the bearing ring.

[0025] The opening angles of the recesses 14, 16, 22, for example, thus vary over the workpiece. As shown in FIG. 2, the opening angle on the edge-side recesses 14, 16 is significantly larger than the opening angle in the central recess 22. Furthermore FIG. 2 shows that the depth T and analogously of course also the height of the stress-relief recess/projection need not be equal for each recess/projection in a component, but rather, as shown in particular in FIG. 2, the recess 14 is significantly deeper than the recess 16, and the central recess 22 has the greatest depth T.sub.3. This is due in particular to the fact that the recess depth T depends in particular on the distance A to the hardened surface, i.e., the heat-influence zone. Thus, for example, the heat-influence zone A of the recess 14 is significantly larger than the heat-influence zone A.sub.2 of the recess 16. The depth T of the recess is preferably 1 to 1.5 times the heat-influence zone A.

[0026] FIG. 3 shows an exemplary embodiment of a bearing outer ring 1 including two lateral flanges of a cylindrical roller bearing that also specifically includes hardened but not so heavily loaded outer sides 2, 4, 6, and a heavily loaded raceway 8. Here the hardened edge layer of the two flanges abuts directly against the raceway 8 or is subsumed under the term raceway. In addition to the different design as a bearing outer ring the exemplary embodiment shown includes a stress-relief recess 14 on the not-hardened region 12, and a stress-relief projection 28 on the not-hardened region 10.

[0027] In all exemplary embodiments of FIGS. 1, 2 and 3, the stress-relief recesses and/or stress-relief projections lie in a not-to-be-hardened region 10, 12, 18, 24 and 26 that abuts essentially at right angles directly against to-be-hardened regions 2, 6, 8, wherein the not-to-be-hardened region 10, 12, 18, 24 and 26 lies essentially orthogonally between two hardened regions 2 and 8, 6 and 8, 8-1, and 8-2. Here the hardened edge layers of the hardened regions 2, 6, 8 are configured essentially parallel to each other in this region of the flanges or bearing shoulders.

[0028] As mentioned above, the stress-relief recess 14, 16, 22 and the stress-relief projection 28 can extend circumferentially along the bearing rings 1 as grooves or ribs; however it is also possible to design the stress-relief recess or the stress-relief projection as discrete elements in the form of humps or holes. It is advantageous here if a plurality of stress-relief recesses or projections are distributed around the circumference of the bearing ring, so that even with discrete stress-relief recesses/projections a sufficient geometry change in the bearing ring can counteract crack formation.

[0029] Since the stress-relief recess allows for stress relief in particular in the case of an expansion of the bearing ring, the projection on the other hand counteracts crack formation in the event of a contraction, it is furthermore advantageous if both recesses and projections are present. In particular in the case of discretely formed stress-relief elements it is advantageous if these alternate in turn so that, for example, in the exemplary embodiment of FIG. 3 a projection 28 would follow the recess 14 in the circumferential direction, and a recess 14 would follow the projection 28 in the circumferential direction. Both a plurality of recesses and a plurality of projections can thus be present in alternating sequence on the not-to-be-hardened region 10, 12. Both stresses during heating and stresses during subsequent quenching can thereby be absorbed.

[0030] Overall a thermal expansion/thermal contraction of the material is promoted by the providing of stress-absorbing-recesses and/or projections in the soft material, i.e., in the not-hardened region, and stresses in the component are reduced in a targeted manner so that crack formation can be counteracted.

[0031] Representative, non-limiting examples of the present invention were described above in detail with reference to the attached drawings. This detailed description is merely intended to teach a person of skill in the art further details for practicing preferred aspects of the present teachings and is not intended to limit the scope of the invention. Furthermore, each of the additional features and teachings disclosed above may be utilized separately or in conjunction with other features and teachings to provide bearing rings.

[0032] Moreover, combinations of features and steps disclosed in the above detailed description may not be necessary to practice the invention in the broadest sense, and are instead taught merely to particularly describe representative examples of the invention. Furthermore, various features of the above-described representative examples, as well as the various independent and dependent claims below, may be combined in ways that are not specifically and explicitly enumerated in order to provide additional useful embodiments of the present teachings.

[0033] All features disclosed in the description and/or the claims are intended to be disclosed separately and independently from each other for the purpose of original written disclosure, as well as for the purpose of restricting the claimed subject matter, independent of the compositions of the features in the embodiments and/or the claims. In addition, all value ranges or indications of groups of entities are intended to disclose every possible intermediate value or intermediate entity for the purpose of original written disclosure, as well as for the purpose of restricting the claimed subject matter.

REFERENCE NUMBER LIST

[0034] 1 Bearing ring [0035] 2, 4, 6 Lightly loaded hardened regions [0036] 8 Raceway, loaded hardened region [0037] 10, 12, 18, 24, 26 Not-hardened regions [0038] 14, 16, 22, 28 Stress recess/projection [0039] E Hardening depth (current during hardening) [0040] A Heat-influence zone [0041] T Depth of the recess/height of the projection