Retainer of cylindrical roller bearing and cylindrical roller bearing

Abstract

The invention relates to a retainer of a cylindrical roller bearing and the cylindrical roller bearing, and the retainer comprises a plurality of cross beams which are arranged at intervals in the circumferential direction, and each cross beam is provided with a cross beam inclined plane extending in the axial direction; the two edge beams are connected to the two axial ends of the cross beam respectively, a plurality of closed-loop pockets are defined by the two edge beams and the cross beam, the pockets are used for containing cylindrical rolling bodies, protruding curved surfaces are arranged on the guide inclined faces, extend in the axial direction and protrude out of the cross beam inclined faces, and the cross beam inclined faces are provided with convex curved surfaces. And the guide rail is used for contacting and guiding with a raceway surface of the cylindrical rolling body. The convex curved surfaces are arranged on the inclined surfaces of the cross beams and used for being in contact guide with the raceway surfaces of the cylindrical rolling bodies, equivalently, the two convex curved surfaces abut against each other, so that the contact area between the cylindrical rolling bodies and the retainer is reduced, friction of the contact areas between the cylindrical rolling bodies and the convex curved surfaces is small, abrasion to coatings on the cylindrical rolling bodies is small, and the service life of the cylindrical rolling bodies is prolonged. And the service life of the cylindrical rolling body is prolonged.

Description

Technical Field

[0001] The present invention relates to the technical field of bearings, and in particular to a retaining frame of a cylindrical roller bearing and a cylindrical roller bearing. Background Art

[0002] In the related art, the pockets of the cage used in the cylindrical roller bearing are designed in the axial direction so that the entire crossbeam contacts and guides the cylindrical rolling element, making the guiding contact area between the cage and the cylindrical rolling element very long. Although the cage can better guide the cylindrical rolling element, it also causes the crossbeam of the cage and the raceway surface of the cylindrical rolling element to be too large, which increases the friction. The increased friction causes damage and scratches to the coating of the raceway surface at the corresponding position of the cylindrical rolling element, and more seriously, it can cause failure phenomena such as early peeling of the surface of the cylindrical rolling element. Summary of the invention

[0003] In order to overcome the problems existing in the related art, the present disclosure provides a retainer of a cylindrical roller bearing and a cylindrical roller bearing.

[0004] According to the first aspect of the embodiment of the present disclosure, the present disclosure provides a retaining frame of a cylindrical roller bearing, comprising: a plurality of cross beams arranged at intervals along the circumferential direction, the cross beams being provided with a cross beam inclined surface extending axially; and two side beams, respectively connected to the axial ends of the cross beam, and forming a plurality of closed-loop pockets with the cross beam, the pockets being used to place cylindrical rolling bodies, wherein a raised curved surface is provided on the cross beam inclined surface, the raised curved surface extending axially and protruding from the cross beam inclined surface, and being used for contacting and guiding the raceway surface of the cylindrical rolling body.

[0005] In some embodiments, the raised curved surface is a portion of a cylindrical curved surface, the raised curved surface is circumscribed with the raceway surface of the cylindrical rolling body, and defines a contact point and a common tangent surface including the contact point at the contact point with the raceway surface.

[0006] In some embodiments, the relationship between the radius R of the convex curved surface and the axial length Lw of the cylindrical rolling body is: R>0.09*Lw 2 .

[0007] In some embodiments, the relationship between the vertical distance H from the vertex of the convex curved surface to the inclined surface of the beam and the diameter Dw of the cylindrical rolling body is: 0.1 mm <H<0.05*Dw。

[0008] In some embodiments, on the common section surface, the ratio of the length a from the contact point to the radial inner side of the convex curved surface to the length b of the convex curved surface is: b*5% <a<b*95%。

[0009] In some embodiments, the beam inclined surfaces are symmetrically arranged on both sides of the circumference of the beam, and each of the beam inclined surfaces includes two convex curved surfaces, and the two convex curved surfaces are respectively located at two axial ends of the beam inclined surface.

[0010] In some embodiments, the relationship between the axial spacing L1 of the adjacent roots of the two convex curved surfaces and the axial length Lw of the cylindrical rolling body is: 0.1*Lw <L1<0.9*Lw。

[0011] In some embodiments, the beam further includes a non-guide surface, which is located radially inward of the convex curved surface and does not contact the cylindrical rolling element.

[0012] In some embodiments, the relationship between the radial dimension h of the non-guide surface and the radial thickness s of the retainer is: <h<0.5s。

[0013] In some embodiments, the crossbeam is located radially inside the pitch circle of the cylindrical roller bearing, and the raised curved surface causes the aperture of the pocket to gradually increase from the radial inside to the radial outside, and the crossbeam has no retaining force on the cylindrical rolling element in the radial direction.

[0014] According to a second aspect of an embodiment of the present disclosure, the present disclosure provides a cylindrical roller bearing, comprising a retaining cage of the cylindrical roller bearing as described in the first aspect.

[0015] The technical solution provided by the embodiments of the present disclosure may include the following beneficial effects: by arranging a raised curved surface on the inclined surface of the beam for contact and guidance with the raceway surface of the cylindrical rolling body, it is equivalent to the two convex curved surfaces abutting against each other, thereby reducing the contact area between the cylindrical rolling body and the retaining frame, so that the friction in the contact area between the cylindrical rolling body and the raised curved surface is small, and the wear on the coating on the cylindrical rolling body is also small, thereby extending the service life of the cylindrical rolling body. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the present disclosure and, together with the description, serve to explain the principles of the present disclosure.

[0017] Figure 1 is a perspective view of a retainer of a cylindrical roller bearing according to an exemplary embodiment;

[0018] Figure 2 yes Figure 1 A partial three-dimensional view of the cage of a cylindrical roller bearing;

[0019] Figure 3a yes Figure 1 A schematic diagram of the structure of the cage shown along the direction of the common section;

[0020] Figure 3b yes Figure 3a A local enlarged view of D in FIG.

[0021] Figure 4 It is the sound pressure spectrum of the bearing noise measured by the microphone array device before the cage is improved;

[0022] Figure 5 It is the sound pressure spectrum of the bearing noise measured by the microphone array device after the cage is improved;

[0023] Figure 6 It is the wear condition of the black coating on the raceway surface of the cylindrical roller in the bench test before the cage is improved;

[0024] Figure 7 The wear of the black coating on the raceway surface of the cylindrical roller in the bench test after the cage was improved;

[0025] Figure 8 yes Figure 1 A cross-sectional view of the middle cage at the contact point;

[0026] Fig. 9 yes Figure 8 A partial enlarged view of the tangent point between the middle cylindrical rolling element and the beam. DETAILED DESCRIPTION

[0027] Exemplary embodiments will be described in detail herein, examples of which are shown in the accompanying drawings. When the following description refers to the drawings, the same numbers in different drawings represent the same or similar elements unless otherwise indicated. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with the present disclosure. Instead, they are merely examples of devices and methods consistent with some aspects of the present disclosure as detailed in the appended claims.

[0028] In the present invention, unless otherwise specified, the axial direction A, radial direction R and circumferential direction W refer to the axial direction A, radial direction R and circumferential direction W of the cylindrical roller bearing respectively; the radial outer side refers to the side away from the central axis in the radial direction ( Figure 8 and Fig. 9 The radial inner side refers to the side close to the central axis in the radial direction ( Figure 8 and Fig. 9 ).

[0029] In order to solve the above technical problems, the present disclosure provides a cylindrical roller bearing cage 100, such as Figure 1As shown, it may include multiple cross beams 10, two side beams 20 and multiple pockets 30. Multiple cross beams 10 are arranged at equal intervals along the circumferential direction W, and the two side beams 20 are respectively connected to the axial ends of the cross beam 10, and together with the cross beam 10, they form multiple closed loop pockets 30, and the pockets 30 are used to contact and guide the cylindrical rolling body 200. It can be understood that the side beam 20 and the cross beam 10 can be integrally formed, and "multiple" in this disclosure refers to two or more.

[0030] like Figure 2 As shown, the crossbeam 10 may be provided with an axially extending crossbeam slope 11. Furthermore, a convex curved surface 12 is provided on the crossbeam slope 11. The convex curved surface 12 is bent and extended along the axial direction A and protrudes from the crossbeam slope 11 for contacting and guiding the raceway surface 40 of the cylindrical rolling body 200.

[0031] In this embodiment, the crossbeam 10 is located radially inside the pitch circle of the cylindrical roller bearing, and the raised curved surface 12 causes the aperture of the pocket 30 to gradually increase from the radial inside to the radial outside. The crossbeam 10 has no retaining force on the cylindrical rolling element 200 in the radial direction R, that is, the retaining frame 100 does not restrict the radial movement of the cylindrical rolling element 200, but only supports the cylindrical rolling element 200 in the radial direction. Therefore, the cylindrical rolling element 200 can be easily removed from the pocket 30 of the retaining frame 100 or installed into the pocket 30.

[0032] By setting a raised curved surface 12 on the inclined surface 11 of the cross beam for contact and guidance with the raceway surface 40 of the cylindrical rolling element 200, the raceway surface 40 of the cylindrical rolling element 200 is also a curved surface, and the cross-section of the raceway surface 40 is circular. Therefore, the raised curved surface 12 abuts against the cylindrical rolling element 200, which is equivalent to the abutment of two convex curved surfaces, thereby reducing the contact area between the cylindrical rolling element 200 and the pocket 30 of the retaining frame 100, so that the friction in the contact area between the cylindrical rolling element 200 and the raised curved surface 12 is small, the wear on the coating on the cylindrical rolling element 200 is also small, and scratches on the raceway surface 40 are avoided, thereby extending the service life of the cylindrical rolling element 200 and reducing the replacement frequency.

[0033] In this embodiment, if Figure 8 As shown, the raised curved surface 12 may be a part of a cylindrical curved surface. The raised curved surface 12 is circumscribed with the raceway surface 40 of the cylindrical rolling element 200 , and defines a contact point O and a common tangent surface M including the contact point O at the contact point with the raceway surface 40 .

[0034] Specifically, the convex curved surface 12 may be a part of a cylindrical curved surface, and the convex curved surface 12 is a curved surface extending along the axial direction A. It can be seen that on the cross section of the retainer 100, the convex curved surface 12 is displayed as a straight line (such as Figure 8 and Fig. 9When the convex curved surface 12 of the cage 100 is tangent to the raceway surface 40 of the cylindrical rolling element 200, it is equivalent to the outer surfaces of the two cylinders being tangent to each other. The tangent point is the contact point O between the cage 100 and the cylindrical rolling element 200. The common tangent surface M is tangent to both the convex curved surface 12 and the raceway surface 40, and the contact point O is also located within the common tangent surface M.

[0035] It can be seen from this that when the outer surfaces of the two cylinders are in contact and tangent, the contact area of ​​the two cylinders is only one point, the contact area is small, and therefore the friction area where friction is generated is also small, which can further reduce the wear and scratches on the coating on the raceway surface 40 of the cylindrical rolling body 200.

[0036] It should be noted that in some other embodiments, the convex surface 12 may also be a part of an elliptical cylindrical surface. When the elliptical cylindrical surface abuts and is tangent to the cylindrical surface, the function and effect are the same as when the cylindrical surfaces are tangent to each other, and will not be repeated here.

[0037] Further, FIG3 is a schematic diagram of the structure of the cage 100 observed from the radial outer side of the cage 100 along the direction of the common section M. In this embodiment, the relationship between the radius R of the raised curved surface 12 and the axial length Lw of the cylindrical rolling element 200 is R>0.09*Lw 2 The radius R of the convex curved surface 12 is the radius of the arc surface where the convex curved surface 12 is located.

[0038] like Figure 4 As shown, when the structure of the retainer 100 is not optimized, that is, the radius R of the convex surface 12 is less than 0.09*Lw 2 When the cage 100 is rotated in the inner and outer rings of the cylindrical roller bearing, the bearing noise sound pressure spectrum measured by the microphone array device is obtained. Figure 4 It can be seen that the sound pressure amplitude of the vertical axis of the noise sound pressure spectrum varies greatly.

[0039] like Figure 5 As shown, after the cage 100 is optimized, the radius R of the convex surface 12 is greater than 0.09*Lw 2 When the bearing noise pressure spectrum is obtained by the same test method under the same test conditions, Figure 4 and Figure 5 It can be clearly seen from the comparison that the sound pressure amplitude of the optimized retaining frame 100 changes little, which shows that the noise problem can be significantly improved. Low noise means reduced vibration and friction between the retaining frame 100 and the cylindrical rolling element 200. Therefore, the contact guidance between the retaining frame 100 and the cylindrical rolling element 200 is smoother, avoiding the coating of the raceway surface 40 of the cylindrical rolling element 200 from falling off or scratching.

[0040] In addition, as Figure 6 in the bench test, when the radius R of the convex surface 12 < 0.09 * Lw 2 is the wear condition of the blackening coating on the raceway surface 40 of the cylindrical rolling element 200. Figure 7 In the bench test, when the radius R of the convex surface 12 > 0.09 * Lw 2 is the wear condition of the blackening coating on the raceway surface 40 of the cylindrical rolling element 200. By comparison Figure 6 and Figure 7 it can be seen that Figure 6 the raceway surface 40 of the cylindrical rolling element 200 in Figure 7 is much more severely worn than the raceway surface 40 of the cylindrical rolling element 200 in 2 Therefore, when the radius R of the convex surface 12 of the cage 100 > 0.09 * Lw

[0041] Furthermore, as Figure 3b shown, the relationship between the vertical distance H from the vertex of the convex surface 12 to the crossbeam inclined surface 11 and the diameter Dw of the cylindrical rolling element 200 is: 0.1 mm < H < 0.05 * Dw. H is the vertical distance from the contact point O of the cylindrical rolling element 200 and the convex surface 12 along the direction perpendicular to the common tangent plane M (this vertical plane passes through the contact point O) to the crossbeam inclined surface 11. By setting the size of H, the spacing distance between the cylindrical rolling element 200 and the pocket 30 is ensured, unnecessary contact is avoided, and an additional contact area between the pocket 30 of the cage 100 and the raceway surface 40 of the cylindrical rolling element 200 is avoided, so as not to wear or scratch the surface of the blackening coating of the cylindrical rolling element 200.

[0042] Furthermore, as Fig. 9 shown, on the common tangent plane M, the proportional relationship between the length a from the contact point O to the radially inner side of the convex surface 12 and the length b of the convex surface 12 is: b * 5% < a < b * 95%. It can be seen from this that by setting the dimensions of the distance a and the length b, the structure at the pocket 30 of the cage 100 is further improved and perfected, so that the wear and friction of the raceway surface 40 of the cylindrical rolling element 200 by the cage 100 are minimized, and the service life of the cylindrical rolling element 200 is prolonged.

[0043] In some embodiments, as Figure 8 and Fig. 9 shown, on the cross-section of the crossbeam 10, crossbeam inclined surfaces 11 are symmetrically arranged on both sides of the circumferential direction W of the crossbeam 10. Again, as Figure 1 shown, each crossbeam inclined surface 11 includes two convex surfaces 12, and the two convex surfaces 12 are respectively located at both axial ends of the crossbeam inclined surface 11.

[0044] Each crossbeam inclined surface 11 has two convex surfaces 12. The crossbeam inclined surfaces 11 are symmetrically arranged on both sides of the circumferential direction W of the crossbeam 10, so that there are four convex surfaces 12 in each pocket 30. The four convex surfaces 12 are in contact with the raceway surface 40 of the cylindrical rolling element 200 to guide. During the contact guidance of the cylindrical rolling element 200, the cylindrical rolling element 200 is in force balance both in the axial direction A and the circumferential direction W, and the noise and vibration between the cylindrical rolling element 200 and the cage 100 are small. Therefore, the structural design of the pocket 30 of the cage 100 in this embodiment can make the cage 100 more smooth when contacting and guiding the cylindrical rolling element 200.

[0045] In some embodiments, the relationship between the axial A spacing L1 between the adjacent roots of the two convex surfaces 12 and the axial length Lw of the cylindrical rolling element 200 is: 0.1*Lw < L1 < 0.9*Lw. Wherein, as Figure 3a shown, the root of the convex surface 12 refers to the position where the convex surface 12 intersects the crossbeam inclined surface 11 in the axial direction A, which is also the lowest point of the convex surface 12. By improving the distance between the roots of the convex surfaces 12, the axial distance between the two contact points O where the two convex surfaces 12 on the axial A contact the raceway surface 40 of the cylindrical rolling element 200 is improved, so as to finally improve the wear condition of the raceway surface 40 of the cylindrical rolling element 200 when the cylindrical rolling element 200 contacts and guides with the cage 100.

[0046] In some embodiments, as Figure 8 and Fig. 9 shown, the crossbeam 10 further includes a non-guiding surface 13, and the non-guiding surface 13 is located radially inside the crossbeam inclined surface 11 and does not contact the cylindrical rolling element 200.

[0047] On the one hand, after the cylindrical rolling element 200 is installed in the bearing inner ring, outer ring and cage 100, in the case of the accumulation of tolerance limits, the design of the non-guiding surface 13 can make the contact point O between the cylindrical rolling element 200 and the cage 100 always remain on the crossbeam inclined surface 11, more precisely, always remain on the convex surface 12. The structural design of the pocket 30 can better ensure the contact guidance of the cylindrical rolling element 200 and reduce the friction and wear on the raceway surface 40 of the cylindrical rolling element 200, and ensure that the cylindrical rolling element 200 does not roll out of the crossbeam inclined surface 11 of the pocket 30 of the cage 100.

[0048] On the other hand, the non-guiding surface 13 can reduce the radial thickness of the crossbeam inclined surface 11, save materials and reduce the weight of the cage 100. The non-guiding surface 13 can be a plane extending along the radial R, or an inclined surface or a curved surface inclined relative to the radial R.

[0049] Furthermore, the relationship between the length h of the non-guide surface 13 in the radial direction and the radial thickness s of the retainer 100 can be 0 <h<0.5s。

[0050] Further, it can be known from the above content that the beam 10 is provided with a beam inclined surface 11 and a non-guide surface 13 on both sides of the circumferential direction W, respectively. Therefore, the design of the non-guide surface 13 enables the cross section of the beam 10 to be hexagonal.

[0051] It should be noted that when the non-guide surface 13 is a plane, the sides of the hexagon formed by the cross section of the non-guide surface 13 are straight lines. When the non-guide surface 13 is a curved surface, two sides of the hexagon formed by the cross section of the non-guide surface 13 may be arcs. In addition, the non-guide surface 13 on each side of the beam 10 may also be composed of two or more faces. When the non-guide surface 13 includes two faces, the cross section of the beam 10 is an octagon. The shapes of the cross section of the beam 10 are not listed here one by one, and can be changed according to design requirements.

[0052] Furthermore, if Figure 1 As shown in FIG. 3 , the pocket 30 further includes roller pockets 31 , and the roller pockets 31 are distributed at the four corners of the pocket 30 .

[0053] Based on the same inventive concept, the present disclosure provides a cylindrical roller bearing, including an outer ring (not shown in the figure), an inner ring (not shown in the figure), a cylindrical rolling element 200, and the cylindrical roller bearing cage 100. The specific manner in which the functions of the cylindrical roller bearing in the above-mentioned embodiment are realized has been described in detail in the embodiment of the cylindrical roller bearing cage 100, and will not be described in detail here.

[0054] It is further understood that the terms "first", "second", etc. are used to describe various structures, but these structures should not be limited to these terms. These terms are only used to distinguish structures of the same type from each other, and do not indicate a specific order or importance. In fact, the expressions "first", "second", etc. can be used interchangeably. For example, without departing from the scope of the present disclosure, a first structure can also be referred to as a second structure, and similarly, a second structure can also be referred to as a first structure.

[0055] It should be further understood that the orientation or positional relationship indicated by the terms "center", "axial", "lateral", etc. is based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing the present embodiment and simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation.

[0056] Those skilled in the art will readily appreciate other embodiments of the present disclosure after considering the specification and practicing the invention disclosed herein. This application is intended to cover any modification, use or adaptation of the present disclosure, which follows the general principles of the present disclosure and includes common knowledge or customary techniques in the art that are not disclosed in the present disclosure. The specification and examples are intended to be exemplary only, and the true scope and spirit of the present disclosure are indicated by the following scope of rights.

[0057] It should be understood that the present disclosure is not limited to the precise structures that have been described above and shown in the drawings, and that various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the scope of the appended claims.

Claims

1. A cylindrical roller bearing retainer (100), characterized in that: include: A plurality of cross beams (10) are arranged at intervals along a circumferential direction (W), wherein the cross beams (10) are provided with cross beam inclined surfaces (11) extending in an axial direction (A); and Two side beams (20) are respectively connected to the two axial ends (A) of the cross beam (10) and are combined with the cross beam (10) to form a plurality of closed loop pockets (30), wherein the pockets (30) are used to place cylindrical rolling bodies (200). The cross beam inclined surface (11) is provided with a raised curved surface (12), which is bent and extended along the axial direction (A) and protrudes from the cross beam inclined surface (11) and is used for contacting and guiding the raceway surface (40) of the cylindrical rolling body (200).

2. The cylindrical roller bearing cage (100) according to claim 1, characterized in that: The convex curved surface (12) is a part of a cylindrical curved surface. The convex curved surface (12) is circumscribed with the raceway surface (40) of the cylindrical rolling body (200), and defines a contact point (O) and a common tangent surface including the contact point (O) at the contact point with the raceway surface (40).

3. The cylindrical roller bearing cage (100) according to claim 2, characterized in that: The relationship between the radius R of the convex curved surface (12) and the axial (A) length Lw of the cylindrical rolling body (200) is: R>0.09*Lw 2 .

4. The cylindrical roller bearing cage (100) according to claim 2, characterized in that: The relationship between the vertical distance (H) from the vertex of the convex curved surface (12) to the crossbeam inclined surface (11) and the diameter (Dw) of the cylindrical rolling body (200) is: 0.1 mm <H<0.05*Dw。 5. The cylindrical roller bearing cage (100) according to claim 2, characterized in that: On the common section, the ratio of the length (a) from the contact point (O) to the radial inner side of the convex curved surface (12) to the length (b) of the convex curved surface (12) is: b*5% <a<b*95%。 6. The cylindrical roller bearing cage (100) according to claim 1, characterized in that: The crossbeam inclined surfaces (11) are symmetrically arranged on both sides of the circumferential direction (W) of the crossbeam (10), and each of the crossbeam inclined surfaces (11) includes two convex curved surfaces (12), and the two convex curved surfaces (12) are respectively located at two axial ends of the crossbeam inclined surface (11).

7. The cylindrical roller bearing cage (100) according to claim 6, characterized in that: The relationship between the axial spacing (L1) of the adjacent roots of the two convex curved surfaces (12) and the axial length (Lw) of the cylindrical rolling body (200) is: 0.1*Lw <L1<0.9*Lw。 8. The cylindrical roller bearing cage (100) according to claim 6, characterized in that: The cross beam (10) further comprises a non-guide surface (13), wherein the non-guide surface (13) is located radially inside the convex curved surface (12) and does not contact the cylindrical rolling element (200).

9. The cylindrical roller bearing cage (100) according to claim 6, characterized in that: The relationship between the length (h) of the non-guide surface (13) in the radial direction and the radial thickness (s) of the retainer is: <h<0.5s。 10. The cylindrical roller bearing cage (100) according to claim 1, characterized in that: The crossbeam (10) is located radially inside the pitch circle of the cylindrical roller bearing, and the convex curved surface (12) causes the aperture of the pocket (30) to gradually increase from the radial inside to the radial outside, and the crossbeam (10) has no retaining force on the cylindrical rolling body (200) in the radial direction.

11. A cylindrical roller bearing, characterized in that: A cage (100) comprising a cylindrical roller bearing according to any one of claims 1 to 10.

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