A bidirectional roller bearing cage and bearing

Abstract

The application discloses a kind of two-way roller bearing cage and bearing, comprising: symmetrically arranged and same structure first cage body and second cage body, the first cage body and second cage body are all included first annular support frame, the end of the first annular support frame is provided with second annular support frame away from second cage body, a plurality of first pockets are provided on the first annular support frame, the length direction of the first pocket is parallel to the axial direction of the first annular support frame, so that the cage can withstand radial load;Second annular support frame is provided with a plurality of second pockets along the circumferential direction, the length direction of the second pocket is arranged along the radial direction of the second annular support frame, and the outer side of the second annular support frame is fixedly connected with the inner side of the first annular support frame.The problem that the existing double-row roller bearing cannot simultaneously withstand axial and radial load due to uneven load distribution caused by thermal expansion is solved.

Description

Technical Field

[0001] This invention belongs to the field of bearing technology, specifically relating to a double-direction roller bearing cage and bearing. Background Technology

[0002] The statements in this section are merely background information related to the present invention and do not necessarily constitute prior art.

[0003] Double-row roller bearings are widely used in high-speed, heavy-load applications such as construction machinery, wind power, and rail transportation, where high requirements are placed on the load-bearing capacity and stability of the bearing cage. In the construction machinery field, critical components of equipment such as excavators and cranes need to withstand large radial loads and frequent impact loads, placing stringent requirements on the strength and impact resistance of the bearing cage.

[0004] In existing double-row roller bearing cages, during high-speed operation, the two rows of rollers, due to their different positions and loads, experience varying degrees of frictional heat generation. This leads to inconsistent temperature rises between the two rows, causing different thermal expansion rates in the bearing components. Consequently, the internal stress state of the bearing shifts, resulting in uneven load distribution between the two rows of rollers, exacerbating localized wear, and shortening the bearing's service life. Furthermore, existing cage structures typically only withstand loads in one direction, either radial or axial, and cannot simultaneously withstand combined radial and axial loads. When conditions require simultaneous loads in both directions, it is often necessary to combine radial and thrust bearings, increasing the number of bearings and installation space, thus limiting applications in complex operating conditions. Summary of the Invention

[0005] To address the aforementioned problems, this invention provides a double-row roller bearing cage and bearing, which solves the problems of uneven load distribution caused by thermal expansion in existing double-row roller bearings, as well as their inability to simultaneously withstand axial and radial loads.

[0006] To achieve the above objectives, the present invention is implemented through the following technical solution: In a first aspect, the present invention provides a bidirectional roller bearing cage, comprising a first cage body and a second cage body symmetrically arranged and structurally identical. Both the first and second cage bodies include a first annular support frame. A second annular support frame is disposed at the end of the first annular support frame away from the second cage body. The first annular support frame has a plurality of first pockets, the length direction of which is parallel to the axial direction of the first annular support frame, enabling the cage to withstand radial loads. The second annular support frame has a plurality of second pockets arranged circumferentially, the length direction of which is arranged radially along the second annular support frame. The outer surface of the second annular support frame is fixedly connected to the inner surface of the first annular support frame, enabling the cage to withstand axial loads. Through the bidirectional design of the first and second pockets, the first pockets, arranged axially, accommodate the first rollers to bear radial loads, while the second pockets, arranged radially, accommodate the second rollers to bear axial loads, thus achieving the cage's simultaneous bearing capacity for combined radial and axial loads.

[0007] Furthermore, the first pocket is arranged radially through the first annular support frame, so that the first roller in the first pocket can contact the inner ring of the bearing; the second pocket is arranged axially through the second annular support frame, so that the second roller in the second pocket can contact the end face of the inner ring of the bearing.

[0008] Furthermore, the length of the first pocket is greater than the length of the second pocket; the first pocket is sized to match the first roller, and the second pocket is sized to match the second roller. This sized matching design ensures stable operation of the roller within the pockets, preventing malfunctions caused by excessive looseness or tightness.

[0009] Furthermore, both ends and sides of the first pocket are flat, and the side surfaces of the two sides are provided with an inclined surface on the side of the first annular support frame, so that the first roller can be installed in the first pocket outside the first annular support frame. The inclined surface provides a friction surface with a supporting function for the first roller, and rolling friction occurs between the roller and the first roller.

[0010] The inclined surface of the first pocket and the planar boundary line of the side are arranged close to the inner side of the first annular support frame, so that the first roller has a large contact surface with the inclined surface in the first pocket, thereby improving the stability of the first roller rotation.

[0011] Furthermore, both ends and sides of the second pocket are flat, and a flat protrusion is provided in the middle of the flat side. The flat protrusion contacts the second roller, preventing the second roller from directly contacting the second annular support frame, thereby preventing wear of the second annular support frame.

[0012] Furthermore, the axial dimension of the first annular support frame is larger than its radial dimension, while the axial dimension of the second annular support frame is smaller than its radial dimension. The larger axial dimension of the first annular support frame is to provide sufficient space to accommodate the first pocket and the first roller arranged axially, ensuring radial load-bearing capacity; the larger radial dimension of the second annular support frame is to provide sufficient space to accommodate the second pocket and the second roller arranged radially, ensuring axial load-bearing capacity.

[0013] Furthermore, the first cage body and the second cage body are integrally formed, preferably by injection molding or stamping.

[0014] Secondly, the present invention also provides a bearing, including the above-mentioned double-direction roller bearing cage, bearing inner ring, bearing outer ring, first roller and second roller, wherein the bearing realizes simultaneous bearing of radial and axial composite loads and has good load-bearing capacity and operational stability.

[0015] Furthermore, the inner diameter of the bearing inner ring is smaller than the inner diameter of the second annular support frame. The outer wall of the bearing inner ring contacts the first roller, and both ends of the bearing inner ring contact the second roller. This design, where the inner diameter of the bearing inner ring is smaller than the inner diameter of the second annular support frame, ensures that the second annular support frame will not interfere with the installation and operation of the bearing inner ring. The first roller, in contact with the outer wall of the bearing inner ring, bears radial loads, while the second roller, in contact with both ends of the bearing inner ring, bears axial loads, achieving bidirectional load bearing.

[0016] Compared with the prior art, the advantages and positive effects of this invention are: This invention utilizes a bidirectional design with a first pocket and a second pocket. The first pocket allows the cage to withstand radial loads, while the second pocket allows it to withstand axial loads. This enables a single cage to simultaneously bear combined radial and axial loads, overcoming the limitation of existing cages that can only withstand loads in one direction, and expanding the application range of bearings under complex operating conditions. The symmetrically arranged first and second cage bodies form a double-row structure. The two rows of first rollers are independently supported by the two cage bodies, with each cage body bearing only the load and frictional heat of one row of rollers. The temperature rise of the two rows of first rollers is similar, avoiding thermal expansion differences and force misalignment caused by inconsistent temperature rises, thus improving the bearing's operating accuracy and service life. The cage can synchronously follow the movement of the two rows of first and second rollers, overcoming the limitation of existing cages that can only withstand loads in one direction, and effectively resolving the problem of uneven load distribution that is common in double-row bearings, ensuring the smooth operation of the bearing.

[0017] The first pocket of the present invention is arranged radially through the first annular support frame, and the second pocket is arranged axially through the second annular support frame, ensuring unobstructed radial and axial load transmission paths, respectively. The length of the first pocket is greater than the length of the second pocket. The first roller in the first pocket bears the main radial load and requires a larger pocket space to provide sufficient contact length and load-bearing capacity. Therefore, the length of the first pocket needs to be designed to be longer to improve the radial load-bearing capacity of the bearing. On the other hand, the second roller in the second pocket bears a smaller axial load, and the roller length is relatively shorter. The pocket size is correspondingly smaller, ensuring that the bearing can improve operational stability while effectively reducing the design redundancy of the cage.

[0018] Both the first and second cage bodies of the present invention include a first annular support frame. The first annular support frame is cylindrical, with its axial dimension larger than its radial dimension, providing sufficient axial installation space for the first pocket, allowing the first pocket to extend axially to accommodate the first roller. The first roller is installed in the first pocket, with its axis parallel to the axis of the first annular support frame. The inner surface of the first roller contacts the outer wall of the bearing inner ring through the radial penetration of the first pocket, and its outer surface contacts the inner wall of the bearing outer ring, thereby bearing radial loads. A second annular support frame is provided at the end of the first annular support frame away from the second cage body. The axial dimension of the second annular support frame is smaller than its radial dimension, and it is flat and annular, providing sufficient radial space for the installation of the second pocket, allowing the second pocket to extend radially to accommodate the second roller. The end face of the second roller contacts the end face of the bearing inner ring through the axial penetration of the second pocket, thereby bearing axial loads. Attached Figure Description

[0019] The accompanying drawings, which form part of this invention, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an improper limitation of the invention.

[0020] Figure 1 This is a schematic diagram of the bidirectional roller bearing cage structure of the present invention. Figure 2 This is a schematic diagram of the first cage body structure of the present invention. Figure 3 This is a schematic diagram of the cage structure of the present invention, in which the first roller and the second roller are mounted. Figure 4 This is a partially enlarged schematic diagram of the first pocket and the second pocket of the present invention. In the figure: 1. First cage body; 2. Second cage body; 3. First pocket; 4. Second pocket; 5. First annular support frame; 6. Second annular support frame; 7. First roller; 8. Second roller; 9. Inner ring of bearing; 10. Inclined surface; 11. Planar protrusion. Detailed Implementation

[0021] It should be noted that the following detailed description is illustrative and intended to provide further explanation of the invention. Unless otherwise specified, all technical and scientific terms used in this invention have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains.

[0022] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the scope of exemplary embodiments according to the invention. As used herein, unless otherwise expressly indicated by the invention, the singular form is intended to include the plural form as well. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0023] Example 1 This embodiment provides a bidirectional roller bearing cage structure, such as... Figures 1-4 As shown, the bearing includes a first cage body 1 and a second cage body 2 that are symmetrically arranged and structurally identical. The first cage body 1 and the second cage body 2 are mirror-symmetrically distributed with the bearing's axial center plane as the plane of symmetry. Both have identical structures, differing only in their spatial position about the plane of symmetry. This symmetrical arrangement allows the cage to distribute the load evenly when bearing loads, avoiding load shifts caused by structural asymmetry due to the structure itself or thermal expansion, thus improving the overall operational stability of the bearing.

[0024] Both the first cage body 1 and the second cage body 2 include a first annular support frame 5. The first annular support frame 5 is cylindrical, with its axial dimension larger than its radial dimension. This slender cylindrical structure provides sufficient axial space for the first pocket 3, allowing the first pocket 3 to extend axially to accommodate the first roller 7. The first roller 7 is installed in the first pocket 3, with its axis parallel to the axis of the first annular support frame 5. The inner surface of the first roller 7 contacts the outer wall of the bearing inner ring 9 through the radial penetration of the first pocket 3, and its outer surface contacts the inner wall of the bearing outer ring, thereby bearing radial loads.

[0025] A second annular support 6 is provided at the end of the first annular support 5 away from the second cage body. The axial dimension of the second annular support 6 is smaller than its radial dimension, and it is in the shape of a flat annulus. This flat annular structure provides sufficient radial space for the second pocket 4, allowing the second pocket 4 to extend radially to accommodate the second roller 8. The second roller 8 is installed in the second pocket 4, and the axis of the second roller 8 is arranged radially along the second annular support 6. The end face of the second roller 8 passes through the second pocket 4 axially and contacts the end face of the bearing inner ring 9, thereby bearing the axial load.

[0026] The first annular support frame 5 has several first pockets 3 evenly distributed circumferentially. The length direction of the first pockets 3 is parallel to the axial direction of the first annular support frame 5, allowing the first roller 7 to transmit radial loads through contact with the inner ring 9 and the outer ring of the bearing. The second annular support frame 6 has several second pockets 4 evenly distributed circumferentially. The length direction of the second pockets 4 is arranged along the radial direction of the second annular support frame 6, allowing the second roller 8 to transmit axial loads through contact with the end face of the inner ring 9 of the bearing. Through the bidirectional design of the first pockets 3 and the second pockets 4, the cage can simultaneously withstand radial and axial loads.

[0027] The first cage body 1 and the second cage body 2 are preferably made by injection molding or stamping. The one-piece molding process makes the cage body structure strong and has no welding or assembly seams, which improves strength and reliability and reduces production costs.

[0028] like Figures 1-2 As shown, the first pocket 3 is arranged radially through the first annular support frame 5, that is, the first pocket 3 extends from the outer side to the inner side of the first annular support frame 5, so that the first roller 7 in the first pocket 3 can contact the outer side wall of the inner ring 9 of the bearing. The length of the first pocket 3 is greater than the length of the second pocket 4 because the first roller 7 bears the main radial load and requires a larger pocket space to provide sufficient contact length and load-bearing capacity. Therefore, the length of the first roller 7 needs to be designed to be longer to improve the radial load-bearing capacity of the bearing. On the other hand, the second roller 8 in the second pocket 4 bears a smaller axial load, the roller length is relatively shorter, and the pocket size is correspondingly smaller.

[0029] The first pocket 3 is sized to match the first roller 7, with the width of the first pocket 3 being slightly larger than the diameter of the first roller 7. This allows the first roller 7 to rotate freely within the first pocket 3 while preventing excessive clearance that could cause wobbling. The second pocket 4 is sized to match the second roller 8, with the width of the second pocket 4 being slightly larger than the diameter of the second roller 8. This allows the second roller 8 to rotate freely within the second pocket 4 while preventing excessive clearance that could cause wobbling.

[0030] like Figure 4 As shown, both ends and sides of the first pocket 3 are flat. An inclined surface 10 is provided on the side of the flat surface of the two sides that is close to the outer side of the first annular support frame 5. The inclined surface 10 is a friction surface that contacts the first roller 7. The inclination angle of the inclined surface 10 relative to the flat surface of the two sides is usually 15 degrees to 45 degrees, preferably 30 degrees.

[0031] During bearing operation, the inclined surface 10 acts as a friction surface, maintaining contact with the first roller 7 and providing guidance and support. The boundary line between the inclined surface 10 of the first pocket 3 and the side plane is positioned close to the inner side of the first annular support frame 5, increasing the contact area between the first roller 7 and the inclined surface 10, reducing contact stress, improving contact stiffness, and minimizing elastic deformation and vibration of the first roller 7 during high-speed operation. This makes the rotation of the first roller 7 more stable, improving the bearing's operating accuracy and service life. The radial load transmission path for the first roller 7 is as follows: the external radial load is transmitted through the outer ring of the bearing to the outer surface of the first roller 7, then through the inner surface of the first roller 7 to the outer wall of the inner ring 9 of the bearing, and finally to the shaft.

[0032] like Figure 3 As shown, the second pocket 4 is arranged axially through the second annular support frame 6, that is, the second pocket 4 extends from one end face of the second annular support frame 6 to the other end face, so that the second roller 8 in the second pocket 4 can contact the end face of the bearing inner ring 9. The dimensions of the second pocket 4 and the second roller 8 are adapted; both ends and both sides of the second pocket 4 are flat, and a flat protrusion 11 is provided in the middle of the flat surface of both sides, which contacts the second roller 8. The shape of the flat protrusion 11 can be a rectangular boss or an arc-shaped boss.

[0033] The planar protrusion 11 forms point or line contact with the second roller 8, which greatly reduces the contact area between the second roller 8 and the second annular support frame 6, significantly reducing the friction. This prevents the second roller 8 from directly contacting the side wall plane of the second annular support frame 6, preventing wear on the side wall plane and extending the service life of the second annular support frame 6.

[0034] The transmission path of the axial load on the second roller 8 is as follows: the external axial load is transmitted to the side of the second roller 8, then to the end face of the inner ring 9 of the bearing, and finally to the shaft. When the bearing is subjected to impact load or sudden change in axial force, the second roller 8 bears the impact first, buffering the direct impact on the first roller 7, reducing the collision intensity between the first roller 7 and the inner ring 9 and outer ring of the bearing, effectively suppressing operating noise, making the synchronous operation of the double-row first rollers 7 smoother, and less prone to problems such as abnormal noise and vibration in a single row.

[0035] Example 2 This embodiment provides a bearing, including the aforementioned double-direction roller bearing cage, inner ring 9, outer ring, first roller 7, and second roller 8. The inner diameter of the inner ring 9 is smaller than the inner diameter of the second annular support 6, ensuring sufficient clearance between the cage and the inner ring 9, allowing the cage to rotate freely without being constrained by the inner ring 9. The outer wall of the inner ring 9 has an inner ring raceway. Under radial load, the first roller 7 forms line contact with the inner ring raceway, transmitting the radial load to the inner ring 9. Both end faces of the inner ring 9 have flanges. Under axial load, the second roller 8 contacts the flanges, transmitting the axial load to the end face of the inner ring 9, and then to the shaft.

[0036] Under high-speed and heavy-load conditions, the first roller 7 bears the radial load through the constraint of the first pocket 3, and the second roller 8 bears the axial load through the constraint of the second pocket 4. The two work together to jointly bear the external axial and radial loads, avoiding stress concentration and overload caused by a single roller bearing loads in two directions at the same time, thus improving the bearing capacity and service life of the bearing.

[0037] Under conditions of sudden changes in axial force, the second roller 8 responds quickly to changes in axial load, ensuring smooth transmission of axial load and reducing the impact on the first roller 7. Compared with existing unidirectional bearings, this invention, through the bidirectional design of the first pocket 3 and the second pocket 4, simultaneously achieves radial and axial load-bearing functions within a single bearing, eliminating the need for other bearings and reducing the number of bearings required. By having the first roller 7 and the second roller 8 bear the radial and axial loads respectively, the load is distributed, reducing the load level of a single roller, reducing frictional heat generation, and extending the bearing's service life. The buffering effect of the second roller 8 and the rapid response capability of the lightweight cage improve shock resistance, reduce vibration and noise, and enhance operational stability.

[0038] While the specific embodiments of the present invention have been described above in conjunction with the accompanying drawings, this is not intended to limit the scope of protection of the present invention. Those skilled in the art should understand that various modifications or variations that can be made by those skilled in the art without creative effort based on the technical solutions of the present invention are still within the scope of protection of the present invention.

Claims

1. A double-direction roller bearing cage and bearing, characterized in that, include: A first retainer body and a second retainer body are symmetrically arranged and have identical structures. Both the first retainer body and the second retainer body include a first annular support frame. A second annular support frame is provided at the end of the first annular support frame away from the second retainer body. The first annular support frame is provided with a plurality of first pockets, the length direction of which is parallel to the axial direction of the first annular support frame, so that the retainer can withstand radial loads. The second annular support frame is provided with a plurality of second pockets along the circumferential direction, the length direction of which is arranged along the radial direction of the second annular support frame. The outer side of the second annular support frame is fixedly connected to the inner side of the first annular support frame, so that the retainer can withstand axial loads.

2. The bidirectional roller bearing cage as described in claim 1, characterized in that, The first pocket is arranged radially through the first annular support frame, so that the first roller in the first pocket can contact the inner ring of the bearing; the second pocket is arranged axially through the second annular support frame, so that the second roller in the second pocket can contact the end face of the inner ring of the bearing.

3. A bidirectional roller bearing cage as described in claim 2, characterized in that, The length of the first pocket is greater than the length of the second pocket; the first pocket is adapted to the size of the first roller, and the second pocket is adapted to the size of the second roller.

4. A bidirectional roller bearing cage as described in claim 3, characterized in that, Both ends and sides of the first pocket are flat. The side of the flat side near the outer side of the first annular support frame is provided with an inclined surface. The inclined surface contacts the first roller, so that the first roller can be inserted into the first pocket outside the first annular support frame.

5. A bidirectional roller bearing cage as described in claim 3, characterized in that, The inclined surface of the first pocket and the planar boundary line of the side are arranged close to the inner side of the first annular support frame.

6. A bidirectional roller bearing cage as described in claim 1, characterized in that, The two ends and two sides of the second pocket are flat, and a flat protrusion is provided in the middle of the flat part of the two sides, and the flat protrusion contacts the second roller.

7. A bidirectional roller bearing cage as described in claim 1, characterized in that, The axial dimension of the first annular support frame is greater than its radial dimension, and the axial dimension of the second annular support frame is less than its radial dimension.

8. A bidirectional roller bearing cage as described in claim 1, characterized in that, Both the first cage body and the second cage body are integrally formed.

9. A bearing, characterized in that, It includes a bidirectional roller bearing cage, an inner bearing ring, an outer bearing ring, a first roller, and a second roller as described in any one of claims 2-8.

10. A bearing as described in claim 9, characterized in that, The inner diameter of the bearing inner ring is smaller than the inner diameter of the second annular support frame. The outer wall of the bearing inner ring is in contact with the first roller, and both ends of the bearing inner ring are in contact with the second roller.

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