Spherical roller bearing having separate cages

Description

1 / 16 “SPHERICAL ROLLER BEARING HAVING SEPARATE CAGES” Technical field of the invention

[0001] The present invention relates to a spherical roller bearing. In addition, the present invention relates to a bearing arrangement comprising a spherical roller bearing. Fundamentals of the invention

[0002] Bearings are common mechanical components for many different applications. There are different types of bearings designed to meet different requirements. Depending on the specific application conditions, i.e., load level, rotational speed, temperature, etc., there are different types of bearings suitable.

[0003] A common type of bearing is a spherical roller bearing. The bearing is designed to accommodate large radial and axial loads, and is also designed to accommodate the bending of a shaft supported by the bearings, i.e., the bearing rings may be relatively misaligned. Therefore, such bearings are particularly suitable for more demanding industrial applications, such as machinery in wind turbines and the like.

[0004] In the most demanding industrial applications for spherical roller bearings, bearing failures are most commonly related to increased surface-initiated fatigue. One reason why increased surface-initiated fatigue occurs may be due to insufficient bearing lubrication. Typically, spherical roller bearings are relubricated in operation. The spherical roller bearing usually comprises two sets of rollers, and relubrication can be done through a special hole in the outer ring midway between both sets of rollers to simultaneously lubricate both sets of rollers. Furthermore, adding fresh lubricant may be able to wash away any bearing particles that might otherwise increase the risk of surface-initiated fatigue.However, in most spherical roller bearings, the spherical rollers are retained in a cage that usually has a central ring element, which can act as a... Petition 870250060403, dated 07 / 15 / 2025, p. 13 / 37 2 / 16 obstacle for the added lubricant.

[0005] It is therefore an objective of the present invention to improve the relubrication of a spherical roller bearing. Summary of the invention

[0006] This objective is solved by a spherical roller bearing according to claim 1.

[0007] Next, a spherical roller bearing is provided. Spherical roller bearings can be used to support a wind turbine main shaft.

[0008] The spherical roller bearing comprises at least an outer ring and an inner ring, and two sets of spherical rollers that are rolling along raceways formed in the outer and inner rings. The inner ring has a bore with a diameter of at least 499 mm, preferably at least 699 mm, and even more preferably at least 899 mm. The bore may be adapted to receive a component from another machine, for example, a shaft from a wind turbine.

[0009] The inner ring may be formed with or without flanges on an axial inner side and / or an axial outer side. If the inner ring is fitted with flanges, the flanges may be used as guide flanges for the roller elements. In addition, they may also serve as retaining flanges to prevent the rollers from falling out of the bearings.

[0010] In order to improve the relubrication of the spherical roller bearing, the spherical roller bearing comprises a first and a second cage, each configured to retain a set of rollers, wherein each of the first and second cages comprises the first cage ring extending in a circumferential direction of the spherical roller bearing, a second cage ring spaced from the first cage ring on an axial side and connected to it with a plurality of cage bars, thus forming closed pockets, wherein each pocket is configured to receive a spherical roller from a set of rollers.

[0011] The first and second cages can be separated from each other.

[0012] Two separate cages can allow one set of rollers to have a different rotational speed than the other row. This can reduce the forces that Petition 870250060403, dated 07 / 15 / 2025, page 14 / 37 3 / 16 of the forces act on each cage compared to a cage that couples both sets of rollers. Alternatively, the first and second cages can be separated from each other, but also arranged so close to each other that it may be possible for the first and second cages to support each other while still having relative movement.

[0013] According to another embodiment, the first and / or second cage may be made of sheet metal.

[0014] Using sheet metal as the base material for the first and / or second cage may have the advantage of reducing costs for the first and / or second cage.

[0015] Alternatively, the cage can be made from a cast material or machined from a solid material.

[0016] According to another method, the pockets can be formed by pressing and stamping and / or grinding.

[0017] According to another embodiment, the cage bars may be at least partially arranged in a position in a radial direction that is at least partially displaced by a pitch diameter.

[0018] The term pitch diameter can describe the diameter at which the center points of the spherical rollers will operate during operation.

[0019] For example, the cage bars may be at least partially arranged at a distance from the inner or outer ring raceway in the radial direction that corresponds to 10 to 40% of a spherical roller diameter or 60 to 90% of the spherical roller diameter, respectively.

[0020] Furthermore, at least one cage bar may be arranged such that more than half of a cage bar length in the axial direction, or even the entire axial cage bar length, is disposed toward the pitch diameter. For example, at least one cage bar may be arranged such that more than half of its axial length, or even its entire axial length, is on a radially inner side or a radially outer side of the pitch diameter. Furthermore, a plurality of cage bars Petition 870250060403, dated 07 / 15 / 2025, page 15 / 37 4 / 16 cage or even all cage bars can be arranged so that more than half of their axial length or even their entire axial length is on a radially inner side or a radially outer side of the pitch diameter.

[0021] Arranging the cage bars in a radial position that is offset by a pitch diameter can make it possible to decrease the distance between two adjacent rollers, so that it may be possible to increase the number of rollers in a roller assembly. Furthermore, arranging the cage bars in a radial position that is at least partially offset by a pitch diameter can make it possible to increase the cage bar width even with a very small nominal roller distance. More particularly, increasing the number of rollers in the roller assembly can have the advantage that the basic dynamic load class of the spherical roller bearing can be increased without the need to adapt the outer and / or inner ring of the bearing.

[0022] According to another embodiment, the inner ring is not provided with a flange configured to retain and / or guide the spherical rollers.

[0023] Supplying the first and second cages with closed pockets for the rollers can have the advantage of interrupting axial roller movement. This allows omitting any guide and / or retaining flanges on the inner ring. Furthermore, manufacturing time can be reduced since machining the flanges is not necessary. Additionally, stresses on the inner ring can be reduced as no bottom cut needs to be made on the inner ring to form the retaining flange. Thus, the costs and / or the required quantity of raw material for the inner ring can be reduced.

[0024] According to another embodiment, the spherical roller bearing is not equipped with a guide ring.

[0025] A guide ring or middle groove flange is generally used to limit roller inclination in an unloaded zone of the spherical roller bearing, so that the rollers enter the loaded zone of the spherical roller bearing with a limited inclination. This is particularly necessary in applications of Petition 870250060403, dated 07 / 15 / 2025, p. 16 / 37 5 / 16 high speed. Wind turbine main shaft applications are generally low-speed applications with a rotational speed of 15 rpm or less. This allows you to omit a guide ring.

[0026] According to another embodiment, at least one cage may be free of any means of retaining at least one spherical roller in at least one cage and / or in a pocket of at least one cage.

[0027] In particular, at least one cage and / or parts of the cage, such as the first cage ring, the second cage ring, the cage bars or the like, may be free of any means of holding or retaining the spherical rollers so that they cannot be lost. In other words, the at least one cage may not comprise means of fitting the spherical rollers into the at least one cage nor undulations formed on the axial end faces of the pockets to engage with recesses formed on the end faces of the spherical rollers. Due to the lack of retention means, the manufacturing costs for the at least one cage may be reduced. Furthermore, as the at least one cage may be free of any means of retaining at least one spherical roller in the cage, it may be possible to exchange individual spherical rollers, for example, during maintenance.

[0028] According to another embodiment, at least one cage and / or spherical rollers can be mounted in the spherical roller bearing without elastically and / or plastically deforming at least one cage and / or disassembling at least one cage. In particular, the term deforming at least one cage and / or disassembling at least one cage may refer to a procedure of bending, twisting, distorting, cutting or otherwise disassembling at least one cage in order to mount at least one cage and / or any of the spherical rollers in the spherical roller bearing.

[0029] According to another embodiment, a ratio Dm / Dw of a minimum distance Dm in the circumferential direction between the tracks of two neighboring spherical rollers of at least one set of spherical rollers for a maximum roller diameter Dw is equal to or less than 0.11, preferably 0.09, and even more Petition 870250060403, dated 07 / 15 / 2025, p. 17 / 37 6 / 16 preferred 0.075, when the spherical rollers of at least one set of spherical rollers are equally spaced in the circumferential direction.

[0030] Reducing the distance between two rollers in the circumferential direction allows increasing the number of rollers in the roller assembly. For example, it may be possible to increase the number of rollers in the roller assembly by at least one. This can allow increasing the basic dynamic load class of the spherical roller bearing. In addition, increasing the number of rollers in the roller assembly by at least one can have the advantage of significantly increasing the service life of the spherical roller bearing.Furthermore, the ratio Dm / Dw of the minimum distance Dm in the circumferential direction between the tracks of two adjacent spherical rollers of the first set of rollers to the maximum roller diameter Dw, when the spherical rollers of the first set of rollers are equally spaced in the circumferential direction, may be equal to or different from the ratio Dm / Dw of the minimum distance Dm in the circumferential direction between the tracks of two adjacent spherical rollers of the second set of rollers to the maximum roller diameter Dw, when the spherical rollers of the second set of rollers are equally spaced in the circumferential direction.

[0031] When the spherical rollers of at least one set of spherical rollers are equally spaced in the circumferential direction, a minimum distance Dm in the circumferential direction between the tracks of two adjacent spherical rollers of at least one set of spherical rollers may be equal to or less than a value obtained by the following equation: Dm < 0.0064 mm · ( ln(P · Dw + Dw) )3

[0032] where P is the pitch diameter and Dw is the maximum roller diameter, where the millimeter values ​​of P and Dw should be used as dimensionless variables. Furthermore, the minimum distance Dm in the circumferential direction between the tracks of two adjacent spherical rollers of the first roller set, when the spherical rollers of the first roller set are equally spaced in the circumferential direction, may be equal to or different from the minimum distance Dm in the circumferential direction between the tracks of two adjacent spherical rollers of the second roller set, when the spherical rollers of the second roller set are equally spaced. Petition 870250060403, dated 07 / 15 / 2025, p. 18 / 37 7 / 16 spaced in the circumferential direction.

[0033] According to another embodiment, each set of spherical rollers may comprise the same number of spherical rollers. Preferably, each set of spherical rollers may comprise the maximum number of spherical rollers.

[0034] Fitting the spherical roller bearing with the maximum number of spherical rollers can allow increasing the basic dynamic load class of the spherical roller bearing.

[0035] According to another embodiment, the first cage ring of each cage is arranged on an axially inner side of the spherical roller bearing so that a gap is formed at least partially between the first cage ring of the first cage and the first cage ring of the second cage.

[0036] Advantageously, the first cage rings of the first and second cages can act as a funnel that carries a lubricant to the inner ring of the spherical roller bearing.

[0037] Preferably, the clearance size in the axial direction can be at least 0.5 mm, preferably at least 1 mm. In particular, the clearance size can be determined under a condition in which the spherical rollers, the first cage, and the second cage of the spherical roller bearing are in a nominal position. More specifically, a nominal roller position can be a position in which a contact angle of the spherical bearing is found, and a nominal cage position can be a position in which the axis of rotation of the first and second cage axes coincides with the axis of rotation of the inner ring, and the axial clearance of the cage pockets is equally divided so that there is the same clearance between the roller side face and the cage pocket side face on the inner axial side face and the outer axial side face of each cage.

[0038] According to another embodiment, the first cage ring and / or at least one of the second cage rings includes a flange element that extends radially inward or radially outward.

[0039] Having a flange element that extends radially inward or radially outward may allow limiting cage deformations if strong forces Petition 870250060403, dated 07 / 15 / 2025, p. 19 / 37 8 / 16 act on the first and / or second cage causing the cage to become deformed.

[0040] According to another embodiment, the first cage ring and at least one of the second cage rings include a radially extending flange element, wherein both flange elements extend radially inward or radially outward.

[0041] Having both cage rings fitted with a flange element that extends radially can lead to a further increase in cage stiffness. This results in less cage deformation and improved cage performance.

[0042] According to another embodiment, the first cage ring and at least one of the second cage rings may include a radially extending flange element, wherein one flange element extends radially inward and the other flange element extends radially outward.

[0043] Having one flange element that extends radially inward and the other flange element that extends radially outward can lead to a significant increase in stiffness. This allows for further reduction of cage deformation and can enable improved cage performance.

[0044] According to another embodiment, a free end of the flange element of the first cage rings is inclined towards the spherical roller. Preferably, the free ends of the flange element of the first cage rings may have an opening angle in the range between 20° and 40°. This may have the advantage that a lubricant flow towards the inner ring may be further improved.

[0045] According to another classification, a cam clearance is greater than a radial cage clearance.

[0046] In particular, the shoulder clearance can be defined as the difference between a cage ring bore diameter and an inner ring diameter at a cage ring position. By designing the cage so that the shoulder clearance is greater than the radial cage clearance, it is possible to make the cage roller-guided. Petition 870250060403, dated 07 / 15 / 2025, page 20 / 37 9 / 16

[0047] For example, the shoulder clearance can be designed to be between 1 and 15 mm larger than the radial cage clearance if the cage bore diameter is up to 1200 mm. If the cage bore diameter is greater than 1200 mm, the shoulder clearance can be designed to be between 1 and 20 mm larger than the radial cage clearance.

[0048] In addition, the radial cage clearance can be in the range of 0.2 to 5 mm, preferably between 0.5 and 3 mm. The radial cage clearance can be measured by the maximum radial movement of the first and / or second cage within the bearing.

[0049] According to another embodiment, the first and / or second cage is predominantly guided by rollers.

[0050] The term predominantly roller-guided refers to a case where the cage is generally guided by rollers, but in cases where the cage is deformed, for example, due to high forces acting on the cage, the deformation can be limited by the cage bore. This can limit extreme loads on the cage. This guiding principle can also be called mixed guidance. Alternatively, the first and / or second cage can be guided only by rollers. In other words, even if the cage deforms, the cage is designed in such a way that no contact occurs between the cage rings and the inner or outer ring. Roller-guided and / or predominantly roller-guided cages may have the advantage of suffering less wear compared to shoulder-guided cages. This can result in fewer particles in the bearing, which can lead to an increase in service life.

[0051] In another alternative design, the first and / or second cage may be predominantly guided by a shoulder in the cage bore and / or supported on an intermediate rib or inner ring guide flange.

[0052] According to another embodiment, each pocket of the first and / or second cage is adapted to limit the inclination of the spherical roller housed in the pocket.

[0053] Limiting the inclination of the spherical roller in the pocket can reduce the contact force generated by the roller contacting the cage. This can further lead to Petition 870250060403, dated 07 / 15 / 2025, page 21 / 37 10 / 16 reduced wear on the first and / or second cage.

[0054] For example, the roller inclination in the pocket can be limited by a radial cage clearance. In addition, or alternatively, the roller inclination can be limited by an axial cage pocket clearance. In particular, the axial cage pocket clearance can be between 0.2 and 2.5 mm, preferably between 0.5 and 2 mm, and even more preferably between 0.7 and 1.5 mm.

[0055] According to another embodiment, each cage bar can be provided with a contact surface configured to make contact with the spherical roller, wherein the contact surface can be positioned on a circumferential side face of each cage bar.

[0056] In addition, the contact surface can be provided with a radius. This allows that, if the roller is inclined and / or moves in the axial direction, the contact between the roller and the contact surface can still be tangential with reduced contact loads. This can result in a decrease in the risk of wear.

[0057] According to another embodiment, a circumferential lateral face of each cage bar may be provided in the axial direction with a contact area.

[0058] For example, the circumferential side face of each cage bar can be provided with an osculation between the cage bar and the roller. The osculation, which is the radius on the cage bar divided by a crown radius of the roller, can be between 100% and 104%. This can lead to a reduction in contact stresses compared to a straight cage bar.

[0059] According to another embodiment, a circumferential side face of each cage bar may be provided in the axial direction with at least two contact areas configured to make contact with the roller.

[0060] Preferably, the contact areas can be located adjacent to the lateral faces of the roller. Having at least two contact areas can reduce the roller's inclination. Furthermore, having at least two contact areas can have the advantage of reducing the stress in the first and / or second cage. In particular, when a contact point between the roller and the cage bar is as close as possible to the cage rings, the bending moment of the cage bar can be reduced. Petition 870250060403, dated 07 / 15 / 2025, page 22 / 37 11 / 16 be reduced, resulting in reduced stress within the first and / or second cage.

[0061] According to a further aspect, a bearing arrangement is provided for a main shaft of the wind turbine, wherein the bearing arrangement includes at least one spherical roller bearing as described above.

[0062] All the characteristics described above in relation to the spherical roller bearing apply - separately or in combination - to the spherical roller bearing used in the bearing arrangement.

[0063] Additional preferred embodiments are defined in the dependent claims, as well as in the description and figures. Thus, the elements described or shown in combination with other elements may be present alone or in combination with other elements without departing from the scope of protection. Brief description of the figures

[0064] Preferred embodiments of the invention are described below in relation to the drawings, wherein the drawings are merely illustrative and are not intended to limit the scope of protection. The scope of protection is defined by the accompanying claims only.

[0065] The figures show:

[0066] Fig. 1: shows a schematic cross-section of a spherical roller bearing according to a first embodiment,

[0067] Fig. 2: shows a schematic cross-section of a spherical roller at a maximum diameter of the spherical roller in a spherical roller bearing cage according to the first embodiment,

[0068] Fig. 3: shows a schematic perspective view of a first spherical roller bearing cage according to the first embodiment,

[0069] Fig. 4: shows a section of a side view of the spherical roller bearing according to the first embodiment, and

[0070] Fig. 5: shows a schematic cross-section of a spherical roller bearing cage according to a second embodiment. Detailed description of the invention Petition 870250060403, dated 07 / 15 / 2025, p. 23 / 37 12 / 16

[0071] The following identical or similar operating elements are indicated with the same reference numbers.

[0072] Figs. 1 to 4 show a spherical roller bearing 1 to support a main shaft of the wind turbine, as well as a first cage 2-1 of the spherical roller bearing 1.

[0073] The spherical roller bearing 1 comprises an outer ring 4 and an inner ring 6, two sets of spherical rollers 8 that are rolling along raceways 9 formed in the outer ring 4 and in raceways 11 formed in the inner ring 6. The outer ring 4 comprises an opening 5 through which lubricant can be supplied to the spherical roller bearing 1. In particular, the outer ring can be stationary, while the inner ring can rotate around a rotation axis A. Furthermore, the inner ring 6 can be configured to be mounted on a main shaft of a wind turbine.

[0074] The inner ring 6 can be formed with or without flanges on an axial inner side and / or an axial outer side. The spherical roller bearing shown in Fig. 1 is formed without flanges on both the axial inner side and the axial outer side of the inner ring 6.

[0075] In addition, the spherical roller bearing comprises a first cage 2-1 configured to retain the first set of spherical rollers 8 and a second cage 2-2 configured to retain the second set of spherical rollers 8. The first and second cages 2-1, 2-2 are identical in shape. Fig. 2 shows the first cage 2-1 in detail.

[0076] Furthermore, both the first cage 2-1 and the second cage 2-2 are free of any means for retaining at least one spherical roller 8 in the first cage 2-1 or in the second cage 2-2 or in a pocket 16 of the first and / or second cages 2-1, 2-2. In other words, the first cage 2-1 and the second cage 2-2 do not comprise means for fitting the spherical rollers 8 into the cages 2-1, 2-2 nor undulations formed on the axial end faces of the pockets 16 for engaging with recesses formed on the end faces of the spherical rollers 8.

[0077] In addition, the first and second 2-1, 2-2 cages can be assembled Petition 870250060403, dated 07 / 15 / 2025, page 24 / 37 13 / 16 or installed in the spherical roller bearing 1 without elastically and / or plastically deforming the first and second cages 2-1, 2-2 and / or without disassembling or cutting the first and second cages 2-1, 2-2.

[0078] Each 2-1, 2-2 cage comprises a first cage ring 10-1, 10-2 extending in a circumferential direction from the bearing, a second cage ring 12-1, 12-2 spaced axially from the first cage ring 10-1, 10-2 and connected to it with a plurality of cage bars 14, thus forming closed pockets 16. Each pocket 16 is configured to receive a spherical roller 8. In particular, each 2-1, 2-2 cage can be integrally formed.

[0079] The first cage ring 10-1, 10-2 has a flange element 18 radially outward and the second cage ring 12-1, 12-2 has a flange element 20 that extends radially inward.

[0080] The free ends of the flange elements 18 of the first cage rings 10-1, 10-2 are inclined towards the spherical roller 8 so that the free ends form an opening angle α. Preferably, the opening angle α is in the range between 20° and 40°.

[0081] Furthermore, the cage bars 14 are at least partially arranged in a position that is radially offset from a pitch diameter P of the spherical roller bearing 1. Preferably, the position corresponds to 10 to 40% of the maximum diameter Dw of the spherical roller 8 used in the spherical roller bearing 1. In the embodiment shown, the cage bar 14 is arranged so that a contact between the spherical roller 8 and the cage bar 14 is in a position that corresponds to about 30% of a maximum diameter Dw (as indicated by the dashed line 17) of the spherical roller 8. The maximum diameter Dw of the spherical roller 8 is indicated in Fig. 4.

[0082] The arrangement of the cage bars 14 offset by the pitch diameter P can make it possible to reduce a minimum distance Dm (Fig. 4) between the tracks of two neighboring rollers 8, so that it may be possible to increase the number of rollers used in a roller assembly 8. The minimum distance Dm is determined under a condition in which the spherical rollers 8 are equally spaced in the circumferential direction. Petition 870250060403, dated 07 / 15 / 2025, p. 25 / 37 14 / 16

[0083] In particular, a ratio Dm / Dw of the minimum distance in the circumferential direction between the tracks of two neighboring spherical rollers 8 of the first and / or second set of spherical rollers to the maximum roller diameter Dw is equal to or less than 0.11, preferably 0.09, and even more preferably 0.075%, when the spherical rollers 8 of the respective set of rollers 8 are equally spaced in the circumferential direction.

[0084] Alternatively or additionally, the minimum distance Dm in the circumferential direction between the tracks of two adjacent spherical rollers of the first and / or second set of spherical rollers may be equal to or less than a value obtained by the following equation: Dm < 0.0064 mm · ( ln(P · Dw + Dw) )3

[0085] when the spherical rollers 8 of the respective roller assembly 8 are equally spaced in the circumferential direction, where P is the pitch diameter and Dw is the maximum roller diameter, where the millimeter values ​​of P and Dw must be used as dimensionless variables.

[0086] The spherical roller bearing 1 is designed so that a shoulder clearance is greater than a radial cage clearance. For example, the shoulder clearance can be between 1 and 15 mm greater than the radial cage clearance if the cage bore diameter is up to 1200 mm. If the cage bore diameter is greater than 1200 mm, the shoulder clearance can be between 1 and 20 mm greater than the radial cage clearance. This allows the cage 2 to be designed predominantly by rollers.

[0087] In addition, each cage bar 14 of the cages 2-1, 2-2 of the spherical roller bearing 1 according to the first embodiment is provided with at least one contact area 24 configured to contact the spherical roller 8, wherein the contact area 24 is positioned on a circumferential side face 22 of each cage bar 14.

[0088] The contact surface or area 24 is at least partially provided with a radius such that an osculation is formed between the cage bar 14 and the roller 8 along the axis of the roller. The osculation, which is the radius in the cage bar 14 Petition 870250060403, dated 07 / 15 / 2025, page 26 / 37 15 / 16 divided by a crowning radius of the roller, can be between 100% and 104%. Furthermore, each cage bar 14 of the spherical roller bearing 1 according to the first embodiment has a contact area 24 in the axial direction.

[0089] Fig. 5 shows a cross-section of a cage 2 for a spherical roller bearing 1 according to a second embodiment. The cage 2 of the second embodiment differs from the cage 2 of the first embodiment in that a circumferential side face 22 of each cage bar 14 is provided in the axial direction with two contact areas 24-1,24-2 configured to contact the roller.

[0090] Although Fig. 5 shows a embodiment with two contact areas 24-1, 24-2, it may also be possible to provide more than two contact areas.

[0091] In summary, providing two separate cages 2-1,2-2 may have the advantage that lubricant flow to the inner ring 6 can be improved. In particular, a gap formed between the first cage rings 10-1, 10-2 of the first and second cages 2-1, 2-2 can act as a funnel that transports lubricant to the inner ring 6 of the spherical roller bearing 1. Furthermore, having two separate cages 2-1, 2-2 can allow the first row of spherical rollers 8 retained in the first cage 2-1 to have a different rotational speed than the second row of spherical rollers 8 retained by the second cage 2-2. This can reduce the forces acting on the cages 2-1, 2-2 compared to a design in which only one cage is used. Reference numbers

[0092] 1. spherical roller bearing

[0093] 2-1 first cage

[0094] 2-2 second cage

[0095] 4 outer ring

[0096] 5 opening

[0097] 6 inner ring

[0098] 8 spherical roller

[0099] 9 outer track

[0100] 10-1, 10-2 first cage ring Petition 870250060403, dated 07 / 15 / 2025, page 27 / 37 16 / 16

[0101] 11 inner track

[0102] 12-1, 12-2 second cage ring

[0103] 14 cage bar

[0104] 16 pocket

[0105] 18 flange element

[0106] 20 flange element

[0107] 22 circumferential side face

[0108] 24 contact area

[0109] α opening angle

[0110] A axis of rotation Petition 870250060403, dated 07 / 15 / 2025, pp. 28 / 37

Claims

1 / 4 CLAIMS 1.Spherical roller bearing (1), in particular for supporting a wind turbine main shaft, comprising: at least one outer ring (4) and one inner ring (6), wherein the inner ring (6) has a diameter of at least 499 mm, two sets of spherical rollers (8) rolling along tracks formed in the outer and inner rings (4, 6), characterized in that a first and a second cage (2-1, 2-2), each configured to retain a set of spherical rollers (8), wherein each of the first and second cages (2-1, 2-2) comprises the first cage ring (10-1, 10-2) extending in a circumferential direction from the spherical roller bearing (1), a second cage ring (12-1, 12-2) spaced from the first cage ring (10-1, 10-2) on an axial side and connected to it with a plurality of cage bars (14), thus forming closed pockets (16), wherein each pocket (16) is configured to receive a spherical roller (8) from a set of spherical rollers.

2. Spherical roller bearing (1), according to claim 1, characterized in that the inner ring (6) is not provided with a flange configured to retain and / or guide the spherical rollers and / or in that the spherical roller bearing (1) is not equipped with a guide ring.

3. Spherical roller bearing (1), according to claim 1 or 2, characterized in that a ratio Dm / Dw of a minimum distance Dm in the circumferential direction between the raceways of two adjacent spherical rollers (8) of at least one set of spherical rollers (8) for a maximum roller diameter (Dw) is equal to or less than 0.11, preferably 0.09, and even more preferably 0.075, when the spherical rollers (8) of at least one set of rollers (8) are equally spaced in the circumferential direction.

4. Spherical roller bearing (1), according to any of the preceding claims, characterized in that a minimum distance Dm in the circumferential direction between the raceways of two neighboring spherical rollers (8) of at least one set of spherical rollers (8) is equal to or less than a value obtained by the following equation: Dm < 0.0064 mm · ( 1 n ( P · Dw + Dw) ) 3, when the spherical rollers (8) of at least one set of spherical rollers (8) are equally spaced in the circumferential direction, wherein P is the pitch diameter and Dw is the maximum roller diameter, wherein the millimeter values ​​of P and Dw are to be used as dimensionless variables.

5. Spherical roller bearing (1), according to any of the preceding claims, characterized in that the first cage ring (10-1, 10-2) of each cage (2-1, 2-2) is disposed on an axially inner side of the spherical roller bearing (1) such that a clearance is formed at least partially between the first cage ring (10-1) of the first cage (2-1) and the first cage ring (10-2) of the second cage (2-2).

6. Spherical roller bearing (1), according to claim 5, characterized in that the clearance size in the axial direction is at least 0.5 mm, preferably at least 1 mm.

7. Spherical roller bearing (1), according to any of the preceding claims, characterized in that the first cage ring (10-1, 10-2) and / or at least one of the second cage rings (12-1, 12-2) includes a flange element (18, 20) extending radially inward or radially outward, or the first cage ring (10-1, 10-2) and at least one of the second cage rings (12-1, 12-2) include a flange element extending radially (18, 20), wherein both flange elements (18, 20) extend radially inward or radially outward, or the first cage ring (10-1, 10-2) and at least one of the second cage rings (12-1, 12-2) include a flange element extending radially (18, 20), wherein a flange element (18, 20) extends radially inwardly and the other flange element (18, 20) extends radially outwardly.

8. Spherical roller bearing (1), according to claim 7, characterized in that a free end of the flange element (18) of the first cage ring (10-1, 10-2) is inclined in the direction of the spherical roller (8).

9. Spherical roller bearing (1), according to claim 8, characterized in that the free ends of the flange element (18) of the first cage rings (10-1, 10-2) have an opening angle (α) in the range between 2° and 40°.

10. Spherical roller bearing (1), according to any of the preceding claims, characterized in that the first and / or second cage (2-1, 2-2) are predominantly roller guided.

11. Spherical roller bearing (1), according to any of the preceding claims, characterized in that a shoulder clearance is greater than a radial cage clearance.

12. Spherical roller bearing (1), according to any of the preceding claims, characterized in that a circumferential side face (22) of the cage bars (14) is provided in the axial direction with a contact area (24) or at least two contact areas (24-1, 24-2) configured to contact the spherical roller (8).

13. Spherical roller bearing (1), according to any of the preceding claims, characterized in that at least one of the first and second cages (2-1, 2-2) is made of sheet metal.

14. Spherical roller bearing (1), according to any of the preceding claims, characterized in that at least one cage (2) is free of any means for retaining at least one spherical roller (8) in at least one cage (2) and / or in a pocket (16) of at least one cage (2), and / or in that at least one cage (2) and / or the spherical rollers (8) are mountable in the spherical roller bearing (1) without elastically and / or plastically deforming at least one cage (2) and / or without disassembling at least one cage (2).

15. Bearing arrangement for a wind turbine main shaft, characterized in that the bearing arrangement includes at least one spherical roller bearing (1) as defined in any of the preceding claims. Petition 870260028064, dated 03 / 25 / 2026, p. 8 / 15 4 / 4

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