Bearing cage for roller bearing

Abstract

The invention relates to a bearing cage (1) which is designed for a roller bearing, in particular a roller bearing having a large diameter, comprising at least: a first ring element (2) which extends in the circumferential direction (u) of the bearing cage (1); the invention relates to a bearing cage (1) comprising a first ring element (2), at least one cage rod (6) extending substantially in the axial direction of the bearing cage (1), the at least one cage rod (6) being connected to the first ring element (2) at a first connection region (12), a recess (14) being provided in the first connection region (12), the recess extending into the first ring element (2), the recess (14) having a curvature, the recess (14) having a curvature, and the recess (14) having a curvature. The curvature has a predetermined radius (r).

Description

Technical Field

[0001] The present disclosure relates to a bearing cage for a roller bearing, in particular a tapered roller bearing, and to a roller bearing, in particular a tapered roller bearing, comprising such a bearing cage. Background Art

[0002] Bearing cages are often used in roller bearings to support and guide the rolling elements of the roller bearings, preferably in an evenly spaced manner. Such bearing cages can be made of metal or plastic. The cage itself usually comprises two ring elements which are offset from one another in the axial direction and which are connected to one another via cage bars, so that pockets are formed between the ring elements and the cage bars, in which pockets the rolling elements are received. However, this also means that the rolling elements received in the pockets and the elements of the cage which form the pockets interact with one another, so that the bearing cage is subjected to heavy loads.

[0003] It has been found here that, in particular in the case of roller bearings whose cages have a substantially angular shape, the structural loads of the cage in the corners (corners), i.e. in the transition area between the cage rods and the ring elements, are particularly high. In order to reduce this load concentration in the corners of the cell, it has been proposed to increase the radius of curvature in the corners of the cell. However, for roller-shaped rolling elements, this leads to interferences with edge reductions provided on the rollers, so that the radius of curvature in the corners of the cell cannot be increased arbitrarily. Furthermore, in applications in which roller bearings with large diameters are required, such as wind turbines, the loads acting on the bearing cage are increased even further.

[0004] Therefore, an object of the present invention is to provide a bearing cage for a rolling bearing, in particular a bearing cage for a tapered roller bearing, which bearing cage has a large structural load carrying capacity. Summary of the invention

[0005] This object is solved by a bearing retainer according to technical solution 1.

[0006] In the following, a bearing cage for a roller bearing, in particular a roller bearing with a large diameter, is provided. For example, the diameter of the outer ring may be greater than 1 meter. More particularly, the roller bearing may be a tapered roller bearing. For example, the roller bearing may be used in a wind turbine. The bearing cage comprises at least a first ring element extending in a circumferential direction of the bearing cage, at least one cage bar extending substantially in an axial direction of the bearing cage, wherein the at least one cage bar is connected to the first ring element at a first connection region, wherein a recess is provided in the first connection region, the recess extending into the first ring element. More particularly, if the roller bearing is a tapered roller bearing, the first ring element may be a large diameter ring element.

[0007] Furthermore, at least one retainer rod may have a predetermined retainer rod width in the circumferential direction of the bearing retainer, and the ring element may have a predetermined ring element thickness in the axial direction of the bearing retainer. In particular, the recess may be formed such that the recess extends only into the first ring element. In other words, the recess may not extend into the retainer rod. Furthermore, the width of at least one retainer rod in the circumferential direction at a position in the first connection region may be greater than the width of at least one retainer rod in the circumferential direction at a position axially spaced from the recess. That is, the width of at least one retainer rod in the circumferential direction may increase in the first connection region. Furthermore, the enlargement of the retainer rod width in the first connection region may be continuous and occur along a curvature having a radius.

[0008] In order to increase the structural load carrying capacity of the bearing cage, the recess has a curvature with a predetermined radius. In particular, the structural weakening of the bearing cage comprising recesses on the cage rod and the ring element is mainly caused by the recess on the cage rod. Therefore, by providing the recess mainly in the ring element (which may reduce the thickness of the ring element in the connection area between the ring element and the cage rod), the cage rod has an essentially uniform cage rod width or even increases the cage rod width.

[0009] The predetermined radius may be constant along the curvature, or the radius of curvature may vary along the curvature. For example, if the radius of curvature varies along the curvature, the structural load carrying capacity of the cage may be optimized by varying the radius of curvature, such that the bearing cage is structurally stronger at locations subject to higher stress levels. Due to a consistent cage rod width or an increased cage rod width, the structural load carrying capacity of the cage may be significantly increased, while a larger radius of curvature may be provided in the transition between the cage rod and the ring element. However, due to the recess in the ring element, interference with the edge reduction of the rollers held by the cage or jamming of the rollers may be avoided. In particular, the predetermined radius may be characterized by a starting point on the cage rod (i.e., the location on the cage rod where the recess begins) and a resulting recess depth y in the axial direction. That is, a recess having a curvature of constant radius r and a recess having a curvature of radius r' varying along the curvature may have the same starting point on the cage rod and the same recess depth, but may be different in the circumferential direction with respect to the recess length x. Thus, by characterizing the predetermined radius by the starting point on the cage rod and the resulting recess depth y in the axial direction, an equivalent constant radius r may be defined for each variable radius r'.

[0010] Preferably, the radius of curvature varies such that the radius increases towards the maximum stress zone and decreases outside the maximum stress zone. This allows the use of an increasing ( / enhanced) radius in the maximum stress zone, which can reduce the stresses generated on the bearing cage, and the use of a decreasing radius outside the maximum stress zone, which allows the recess depth to be limited. For example, the radius of curvature can vary continuously along the curvature. Preferably, the radius of curvature can vary exponentially, logarithmically, linearly and / or according to a polynomial of nth grade.

[0011] According to another preferred embodiment, the bearing cage comprises a second ring element, wherein at least one cage rod is connected to the second ring element at a second connection area, wherein the width of the cage rod at a position in the second connection area in the circumferential direction of the bearing cage is smaller than the width of the at least one cage rod at a position in the first connection area in the circumferential direction of the bearing cage and / or the width of at least one cage at a position axially spaced apart from the recess in the circumferential direction of the bearing cage.

[0012] It is particularly advantageous here if the recesses on the ring elements and the cage rod widened in this area are provided not only on the first ring element of the bearing cage, but also on the second ring element of the bearing cage, which is arranged axially offset relative to the first ring element. As is known, the two ring elements are usually connected to the cage rod and together with the cage rod form pockets for receiving rolling elements. Due to the design of the recesses on the two ring elements, the structural load-bearing capacity of the cage can be further increased and jamming of the rollers in the pockets can be avoided.

[0013] According to another preferred embodiment, a cavity configured to receive a rolling element is defined between the first and second cage rods and the first and second ring elements, wherein the distance between the first and second cage rods in the circumferential direction defines a cavity width, and the distance between the first and second ring elements in the axial direction defines a cavity length, wherein the cavity width is minimum at a position spaced 20% to 60% of the cavity length from the second ring element. This can allow a structure to be created that allows the rolling element to be snapped into the cavity, which can allow the rolling element to be tilted during assembly of the roller bearing, and thus allows easier assembly of the roller bearing, particularly in the case of a roller bearing having a large diameter.

[0014] Preferably, the roller bearing is a tapered roller bearing and the second ring element has a smaller diameter than the first ring element, wherein the minimum cell width is located at a position spaced apart from the second ring element by 25% to 55% of the cell length. In this case, it may be advantageous if the width of the cage rod in the circumferential direction of the bearing cage at a position in the second connection region may be smaller than the width of the cage rod in the circumferential direction of the bearing cage at a position in the first connection region and the width of the cage rod in the circumferential direction of the bearing cage at a position spaced apart axially from the connection region. In other words, in the case where the roller bearing is a tapered roller bearing, the width of the cage rod in the circumferential direction of the bearing cage may be smallest in the connection region of the smaller ring element connecting the cage rod to the bearing cage.

[0015] The bearing cage itself can be produced in one piece, for example from sheet metal; however, the bearing cage can also be composed of individual elements.

[0016] In addition, the recess on the first ring element and / or the second ring element may define a minimum ring element thickness R min , and the cage is at the minimum ring element thickness R min The maximum cage rod width S is at maxThis means that the cage bars are preferably widened continuously in the direction of the minimum ring element thickness R min such that structural weakening that may occur, for example, due to the formation of recesses is compensated for by increasing the cage bar width.

[0017] In addition, the recess may have a specific recess length x in the circumferential direction of the first ring element and / or the second ring element and a recess depth y in the axial direction, where the ratio of the recess length x to the recess depth y falls within the range of 2 to 10 (2 < x / y < 10). Such a ratio can allow for optimal guidance of the rolling elements in the pockets, in particular an optimal abutment of the end surfaces of the rolling elements on the ring elements, and advantageously a low impact or low interference between the rolling elements and the cage in the connection region between the cage bars and the ring elements. Thus, the running and guiding behavior of the bearing cage as well as the structural integrity or load-bearing capacity of the bearing cage can also be improved.

[0018] To further increase the structural load-bearing capacity of the bearing cage, it is further advantageous that the minimum cage bar width S in the second connection region between the cage bar and the second ring element min and the maximum cage bar width S in the first connection region between the cage bar and the first ring element max have a ratio that falls between 0.5 and 1 (0.5 ≤ S min / S max ≤ 1), preferably between 0.8 and 0.99 (0.8 ≤ S min / S max ≤ 0.99).

[0019] As an alternative or additionally, the ratio between the maximum ring element thickness R max (especially the ring element thickness measured at the center of the pocket) and the minimum ring element thickness R measured at the lowest point of the recess min can also fall between 1.05 and 1.4 (1.05 ≤ R max / R min ≤ 1.4). A bearing cage having at least one of the above ratios has particularly good structural load-bearing capacity.

[0020] In addition, the bearing cage generally has a radially inner side and a radially outer side. Here, the inventors have recognized that when the enlargement of the cage bar follows a curvature with a radius r, the radius of curvature r a of the radially outer side can be greater than the radius of curvature r i of the radially inner side, especially when the cage is manufactured by stamping and punching. Here, in particular, the radius r of the radially outer sidea The radially inner radius r is defined by using a first tool, in particular a punching tool. i The curvature radius r of the radial inner side is defined by using a second tool, in particular a stamping tool. i and the radial outer curvature radius r a The central axis of the radial direction may not be parallel. In other words, the radius of curvature r of the radial inner side i and the radial outer curvature radius r a The central axes may be inclined relative to each other. For example, the radius of curvature r of the radially outer side a The radius of curvature r of the radial inner side may be in the direction of the punching tool, such as the radial direction, and may be generated by the angle from the punching tool. i The roller cage rod contact can be tangential. Due to this different design of the outer and inner radii, the structural integrity of the cage can be further improved. In addition, the manufacturing feasibility can be improved by having different radii.

[0021] Preferably, at least one ring element has a radial extension and an axial extension connected by a bend with a radius, wherein the recess is formed such that the recess is spaced apart from the bend. For example, if the bearing cage is made of sheet metal, the final cage profile shape is obtained by bending a flat base material into a circular shape. This can result in at least one of the ring elements having a radial extension and an axial extension connected by a bend with a radius. If the recess is, for example, positioned and / or designed in terms of size such that the recess will cut into the bend of the at least one ring element, this can lead to stress concentrations in this area. Therefore, it can be important for a stress-optimized design to separate the recess, which can be arranged in a corner of the cage cavity, from the radius of the bend of the at least one ring element.

[0022] According to a further advantageous exemplary embodiment, the bearing cage is made of sheet metal. It is particularly advantageous here if the sheet metal has a certain sheet metal thickness, wherein the radius r of the curvature along which the cage rod widens depends on the sheet metal thickness t such that the radius falls within the range defined below:

[0023] 0.12t≤r≤2t,

[0024] wherein t denotes the thickness of the metal sheet measured in units of size, and wherein r denotes the radius of curvature measured in units of size. In particular, t and r may have the same units. Please note that in case the radius of curvature is variable, r refers to the equivalent constant radius as defined above. Preferably, the radius may be between 0.25t≤r≤1t. This has the advantage that a higher radius may better optimize the structural load-bearing capacity of the bearing cage.

[0025] A further advantage of the bearing cage according to the invention is that, due to the above-described design, the structural load-bearing capacity of the bearing cage can be increased, so that even the sheet metal thickness can be reduced. This in turn leads to a reduction in material consumption and thus to a reduction in costs.

[0026] Another aspect relates to a rolling bearing, in particular a tapered roller bearing, comprising at least one inner ring, an outer ring and roller-like rolling elements arranged between the at least one inner ring and the outer ring, wherein the rolling elements are received in a bearing cage as described above.

[0027] Furthermore, it is advantageous if the roller-like rolling element comprises a running surface, by means of which the roller-like rolling element rolls on the inner ring and the outer ring, and if the roller-like rolling element is at least partially guided by a cage rod of the bearing cage, and if the roller-like rolling element comprises a first end surface and a second end surface, wherein the first end surface is associated with a first ring element of the bearing cage and the second end surface is associated with a second ring element. It is particularly advantageous here if an edge reduction is provided in a transition region between the first end surface and / or the second end surface and the running surface, such that the first end surface and / or the second end surface is offset radially inwardly from the running surface by an edge reduction value k, and in the transition region between the running surface and the first end surface or the second end surface, the running surface is shorter by the edge reduction value k than the total longitudinal extension of the roller between the first end surface and the second end surface. The edge reduction is preferably symmetrical; however, it is also possible that the edge reduction values ​​differ between the running surface and the end surface and / or at the first end side or the second end side.

[0028] Furthermore, it is advantageous if the recess depth y of the recess on the bearing cage is defined by the edge reduction value k, wherein the radius of curvature of the recess in the first connection region satisfies the inequality: ry≤k. This ensures that the edge reduction and the recess of the roller-shaped rolling element do not adversely influence or interfere with each other.

[0029] In addition, the ratio of the edge reduction value k to the recess depth y can preferably fall within the range between 0.75 and 2.33 (0.75≤k / y≤2.33), and even more preferably between 1.2 and 1.8 (1.2≤k / y≤1.8). This ensures that the edge reduction and the recess of the roller-shaped rolling element do not adversely affect or interfere with each other.

[0030] Furthermore, the inventors have found that for a continuous cage rod widened in the connection region between the cage rod and the ring element, it is advantageous if the ratio of the radius of curvature r to the edge reduction is in a specific ratio to one another, wherein the radius r holds true as follows:

[0031] 1.1k≤r≤1.4k

[0032] Note that in the case of a variable radius of curvature, r refers to the equivalent constant radius as defined above.

[0033] If the rolling bearing comprises a bearing cage, wherein the curvature of the cage rod widened in the connecting region between the cage rod and the ring element on the outer side of the cage differs from the curvature on the inner side of the cage, it is also advantageous if the radius of the outer side is as follows:

[0034] 1.1k≤r a ≤1.4k

[0035] And / or, the inner diameter is established as follows:

[0036] 0.8k≤r i ≤1.1k

[0037] Further preferred embodiments are defined in the dependent claims as well as in the description and drawings. Therefore, elements described or shown in combination with other elements may exist alone or in combination with other elements without departing from the scope of protection. BRIEF DESCRIPTION OF THE DRAWINGS

[0038] In the following, preferred embodiments of the present invention are described with respect to the accompanying drawings, which are merely exemplary and are not intended to limit the scope of protection. The scope of protection is defined solely by the appended claims.

[0039] The accompanying drawings show:

[0040] Figure 1 is a schematic cross-sectional view through a first exemplary embodiment of a bearing cage according to the present disclosure,

[0041] Figure 2 is a schematic cross-sectional view through a bearing cage including rollers received therein,

[0042] Figure 3 yes Figure 1 Detailed view of the cage pockets.

[0043] Figure 3A yes Figure 1 A detailed view of the radius of curvature of the recess of the cage cavity, the detail being identified as Figure 3 Details of Section 3A, and

[0044] Figure 4A and Figure 4B yes Figure 3 Detailed view of the cavity depicted in , with the rollers received in the cavity.

[0045] Reference numerals

[0046] 1 Bearing cage

[0047] 2 First ring element

[0048] 4 Second ring element

[0049] 6 Cage rod

[0050] 8 Cavity

[0051] 10 Roller

[0052] 12 Connection Area

[0053] 14-1 concave part

[0054] 14-2 concave part

[0055] 16-1, 16-2 Inner edge of the retaining rod

[0056] 18, 18-1, 18-2 Inner edge of ring element

[0057] 22 Transition between the recess and the inner edge of the ring element

[0058] 24 Roller running surface

[0059] 26, 28 Roller end surface

[0060] 30-1-30-4 Edge reduction

[0061] 32 Radial outer side / edge

[0062] 34 radial inside

[0063] 36 Radial extension

[0064] 38 Axial extension

[0065] 40 Bend

[0066] α Angle

[0067] r、r a 、r i , r' radius of curvature

[0068] k Edge reduction value

[0069] t Metal sheet thickness

[0070] S.S min , S max Cage rod width

[0071] R, R min , R max Ring element thickness

[0072] x, x' concave length

[0073] q starting point of concavity

[0074] y recess depth

[0075] u Circumferential direction

[0076] A Axial direction

[0077] P w Cavity width

[0078] P l Cavity length DETAILED DESCRIPTION

[0079] In the following, identical or functionally similar elements are denoted by the same reference numerals.

[0080] Figure 1 , a cross-section through a bearing cage 1 of a tapered roller bearing is shown, which comprises a first ring element 2 and a second ring element 4 connected to one another by a plurality of cage rods 6. Thus, cavities 8 are formed between the first ring element 2, the second ring element 4 and the cage rods 6, in which cavities roller-like rolling elements ( Figure 2 and as shown in Figure 4). Figure 2 The receiving of the rolling elements 10 is depicted in FIG, wherein the ring elements 2 and the cage rods 6 (in the cross-sectional view) are also visible. Figure 2 As can further be seen in FIG. 8 , rolling elements 10 are received in cells 8. Although a tapered roller bearing is depicted in the figures, other rolling element bearings may be provided with a cage similarly configured in the transition region between the cage rods and the rings.

[0081] The bearing cage itself is usually made of sheet metal. When the flat base material of the bearing cage 1 is formed into the usually circular final contour shape of the cage 1, e.g. Figure 1 As shown, at least one ring element 2 , 4 (in the case of a bearing cage for tapered rollers 10 , usually the ring element with the smaller diameter) has a radially extending portion 36 and an axially extending portion 38 connected by a curved portion 40 with a radius.

[0082] In addition, as in Figure 1 As can be seen in the cross-sectional view of , the bearing cage 1 has a sheet metal thickness t. Due to the novel design of the bearing cage 1 described below, this sheet metal thickness t can be reduced without compromising the structural load carrying capacity of the bearing cage 1 .

[0083] For this purpose, the bearing cage 1 further comprises recesses 14-1, 14-2 in the connection region 12 between the cage rod 6 and the first ring element 2 and / or the second ring element 4. The recesses 14-1, 14-2 are configured here such that in this region, a reduction in the ring element thickness R is achieved, in particular, to a minimum ring element thickness R min , but the enlargement of the cage rod width S is specifically realized as the maximum cage rod width S max The expansion of the cage rod width S in the first connection region is continuous and occurs along a curvature having a predetermined radius r ( Figure 3 ). The predetermined radius r may be a constant radius or may vary along the curvature. In particular, the predetermined radius may be characterized by the starting point q on the cage rod 6 and the resulting recess depth y in the axial direction. Figure 3 As can be seen, a recess 14 having a curvature with a constant radius r (indicated by a solid line) and a recess 14 having a curvature with a radius r' that varies along the curvature (indicated by a dotted line) can have the same starting point q on the retainer rod 6 and the same recess depth y, but can be different in the circumferential direction relative to the recess length x or x'.

[0084] Preferably, the radius of curvature r' varies such that the radius increases towards the maximum stress zone and decreases outside the maximum stress zone. For example, the radius of curvature r' may vary continuously along the curvature. Preferably, the radius of curvature may vary non-linearly, for example exponentially, logarithmically and / or according to an nth order polynomial. Here, the ring element thickness is measured in the axial direction relative to the axis of rotation A of the bearing cage 1, while the cage rod width is measured in the circumferential direction U of the bearing cage.

[0085] Furthermore, the recesses 14-1, 14-2 are formed such that the recesses 14-1, 14-2 are spaced apart from the curved portion 40. If the recess 14 is positioned and / or designed, for example, in terms of size, such that the recess 14 would cut into and / or interfere with the curved portion 40 of the ring element 2, 4, stress concentrations may result in this area. Therefore, separating the recess 14 from the radius of the curved portion 40 of the ring element 4 may be important for stress-optimized design.

[0086] In the depicted tapered roller bearing cage, the minimum cage rod width S min Preferably measured at the second connection region at the second ring element 4, the maximum ring element thickness R max It is preferably measured at the center of the cell 8. For cages of other rolling element bearings, these values ​​can be determined at other points.

[0087] Figure 3 An example of a cavity is shown. Only one cavity is depicted here. The cage rods and ring elements are depicted only in cross-section and their inner edges 18-1, 18-2 (ring elements) or 16-1, 16-2 (cage rods) are each shown, so that the ring element thickness or the cage rod width is not visible here. In addition, Figure 3 In particular, the enlarged cutout shows that the recess 14-1 has a specific recess depth y and a recess length x in the circumferential direction. It is further proved here that it is advantageous if the ratio between the recess length x and the recess depth y falls within the range of 2 to 10:

[0088] 2≤x / y≤10

[0089] Furthermore, the enlarged cutouts show that the transition from the recess 14 to the inner edge 18 of the cell is realized such that a tangent 22 to the recess progress line forms an angle α with respect to the inner edge 18. The angle α preferably lies in the range of 10° to 40°.

[0090] As in Figure 3 As can be seen in the figure, the cavity 8 has a cavity width P w and cavity length P l , where the cavity width P w In the cavity length P l For example, in the case of a tapered roller bearing, the minimum cell width P w Located at a distance of cavity length P from the second ring element 4 lThus, for a tapered roller bearing, the width of the cage rod 6 is smallest in the connection region where it connects the smaller ring element 4 to the bearing cage 1 .

[0091] In addition, Figure 3 It can be seen from the minimum ring element thickness R min The transition to the increased cage rod width S occurs continuously and along a curvature having a radius r. As mentioned above, the radius r varies along the recess.

[0092] also, Figure 4A It shows that Figure 3 An exemplary embodiment of a cage in which the rollers 10 are received in the cage. Figure 4A and Figure 4B As can be further seen in FIG, the roller 10 comprises a running surface 24, via which the roller 10 rolls on the inner or outer ring of a rolling bearing (not depicted) and is guided by the cage rod 6. Furthermore, the roller 10 comprises a first end surface 26 associated with the first ring element 2 and a second end surface 28 associated with the second ring element 4. The two end surfaces 26, 28 interact with the inner side 18 of the ring elements 2, 4. As can be seen from FIG. Figure 4A and Figure 4B As can be further seen in FIG. 1 , each roller 10 comprises an edge reduction 30 - 1 , 30 - 2 , 30 - 3 , 30 - 4 at the transition region between the running surface 24 and the end surfaces 26 , 28 . Figure 4B One of these edge reductions 30-1 is depicted in an enlarged manner in FIG. Here, the running surface or the first end surface or the second end surface, respectively, is reduced by an edge reduction value k. As depicted, the edge reduction is preferably symmetrical.

[0093] The edge reduction value k in turn determines the recess depth y, wherein the radius r of the curvature of the recess in the connecting region satisfies the inequality: r−y≤k.

[0094] In addition, the ratio of the edge reduction value k to the recess depth y preferably falls within the range between 0.75 and 2.33, 0.75≤k / y≤2.33, and more preferably between 1.2 and 1.8, 1.2≤k / y≤1.8.

[0095] This relationship ensures an optimal balance between the edge reduction k and the recess y, so that no interference occurs between the roller 10 and the cage 1. It can also be ensured that a sufficiently large radius of curvature r, r' or an enlargement of the cage rod width S can be achieved without causing the roller 10 to jam in the cage 1.

[0096] Furthermore, if the retainer is provided on its radially outer surface 32 (see Figure 1 ) on the radially inner surface 34 (see Figure 1 ) on the surface of the substrate. These different radii r i 、r a exist Figure 3A shown Figure 3 However, if the outer radius of curvature r a Generally larger than the inner radius of curvature r i , and the outer radius r a Usually provided by the first tool and the inner radius r i More specifically, the bearing cage 1 has a radial inner side 34 and a radial outer side 32, wherein the curvature radius r of the radial outer side 32 is a is greater than the radius of curvature r located radially inside 34 i , and wherein the radius of curvature r located at the radially outer side 32 a The curvature radius r formed by using a punching tool and located at the radial inner side 34 i formed by applying a second punching tool. Therefore, it is advantageous; for example, if the outer radius r a Provided by punching a hole in the metal sheet, the inner radius r i It is formed by a subsequent stamping process of the bearing cage.

[0097] In summary, with the disclosed bearing cage design, a bearing cage can be provided, the structural load-bearing capacity of which is increased, so that even a bearing cage for large-diameter bearings, in particular for wind turbines, can be formed from sheet metal. In addition, despite the increased radius of curvature r between the cage rod 6 and the ring elements 2, 4, interference and resulting jamming of the rollers 10 in the cage pocket 8 can be reliably prevented. At the same time, by adjusting the recess length x and the recess depth y, the cage 1 can be optimally adapted to the desired properties.

Claims

1. A bearing cage (1) configured for a roller bearing, in particular a roller bearing with a large diameter, the bearing cage (1) comprising at least: A first ring element (2) extending in a circumferential direction (u) of the bearing cage (1), at least one cage rod (6) extending substantially in the axial direction of the bearing cage (1), wherein the at least one cage rod (6) is connected to the first ring element (2) at a first connection region (12), A recess (14) is provided in the first connection region (12), the recess (14) extending into the first ring element (2), characterized in that the recess (14) has a curvature with a predetermined radius (r, r').

2. The bearing retainer (1) according to claim 1, characterized in that: The predetermined radius (r) is constant along the curvature, or the radius of the curvature (r') varies along the curvature.

3. The bearing retainer (1) according to claim 2, characterized in that: The radius (r') of the curvature varies such that the radius (r') increases towards the maximum stress zone and decreases outside the maximum stress zone.

4. The bearing retainer (1) according to claim 2 or 3, characterized in that: The radius of curvature (r') varies continuously along the curvature, preferably, the radius of curvature (r') varies exponentially, logarithmically and / or according to an nth-order polynomial.

5. The bearing cage (1) according to any one of the preceding claims, characterized in that The bearing retainer (1) comprises a second ring element (4), wherein the at least one retainer rod (6) is connected to the second ring element (4) at a second connection area (12), and the width (S) of the retainer rod (6) in the circumferential direction (u) of the bearing retainer (1) at a position in the second connection area (12) is smaller than the width (S) of the at least one retainer rod (6) in the circumferential direction (u) of the bearing retainer (1) at a position in the first connection area (12) and / or the width (S) of the at least one retainer in the circumferential direction (u) of the bearing retainer (1) at a position axially spaced apart from the recess (14).

6. The bearing retainer (1) according to claim 5, characterized in that: A cavity (8) configured to receive a rolling element (10) is defined between a first cage rod (6) and a second cage rod (6) and between the first ring element (2) and the second ring element (4), wherein a distance between the first cage rod (6) and the second cage rod (6) in the circumferential direction (u) defines a cavity width (P w ), the distance between the first ring element and the second ring element in the axial direction defines a cavity length (P l ), where the cavity width (P w ) is spaced apart from the second ring element (4) by the cavity length (P l ) is smallest at 20% to 60% of the value.

7. The bearing retainer (1) according to claim 6, characterized in that: The roller bearing is a tapered roller bearing, the second ring element (4) has a smaller diameter than the first ring element (2), and the minimum cell width (P w ) is located at a distance of the cavity length (P from the second ring element (4) l ) is between 25% and 55%.

8. Bearing cage (1) according to any one of the preceding claims, It is characterized in that The bearing retainer (1) has a radial inner side and a radial outer side, The radius of curvature (r a ) is greater than the radius of curvature located on the radial inner side (r i ),and The radius of curvature located on the radially outer side is formed by using a punching tool, and the radius of curvature located on the radially inner side is formed by using a second punching tool. Preferably, the radius of curvature located on the radially inner side (r i ) and the radius of curvature of the radial outer side (r a )’s central axes are inclined to each other.

9. Bearing cage (1) according to any one of the preceding claims, characterized in that The bearing retainer (1) is made of metal plate.

10. Bearing cage (1) according to any one of the preceding claims, characterized in that At least one ring element (2, 4) has a radially extending portion (36) and an axially extending portion (38) connected by a curved portion (40) having a radius, the recess (14) being formed such that the recess (14) is spaced apart from the curved portion (40).

11. A roller bearing, comprising: At least one inner circle, an outer ring, and a roller element (10) arranged between the at least one inner ring and the outer ring, Characterized in that the rolling elements are received in a bearing cage (1) according to any one of the preceding claims.

12. The roller bearing according to claim 11, It is characterized in that The roller element (10) has a running surface (24) and a first end surface (26) and a second end surface (28), the running surface (24) being configured to roll on the inner ring and the outer ring and at least partially contacting the first cage rod (6), The first end surface faces the first ring element (2), and the second end surface faces the second ring element (4), An edge reduction (30) is provided at a transition region (22) between the first end surface and the running surface, so that the first end surface is radially offset inwardly by an edge reduction value (k) of the running surface and so that the running surface is shorter by the edge reduction value (k) than the total longitudinal extension of the roller element (10) between the first end surface (26) and the second end surface (28), The recess depth (y) of the recess (14) on the bearing retainer (1) is defined by the edge reduction value (k), and The radius of curvature of the concave portion in the first connection area (12) satisfies the inequality: r - y ≤ k.

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