Deep groove ball bearing

Abstract

A deep groove ball bearing comprises an outer ring and an inner ring, a rolling body arranged in a retainer in a sleeved mode is arranged between the outer ring and the inner ring, and the outer ring is provided with an arc-shaped first containing groove, a first backflow face arranged in an inclined mode and a first linear face from the center of the outer ring to the edge of the outer ring. The inner ring is provided with an arc-shaped second accommodating groove and an inclined second backflow surface from the center of the inner ring to the edge of the inner ring; the side, facing the outer ring, of the retainer is a first arc-shaped surface and a second linear surface from the center to the edge, and the side, facing the inner ring, of the retainer is a second arc-shaped surface from the center to the edge; the section position of the second linear surface is located between the first linear surface and the first backflow surface. The bearing has the beneficial effects that the loss of lubricating oil and the invasion of external pollution are obviously reduced, the maintenance period and the service life of the bearing are prolonged, meanwhile, the abrasion and fault risks caused by insufficient lubrication are reduced, and the overall performance and the reliability of the bearing are improved.

Description

Technical Field

[0001] The utility model relates to a deep groove ball bearing, in particular to a deep groove ball bearing. Background Art

[0002] The deep groove ball bearing with a baffle is a specially designed bearing. It adds a baffle structure on the basis of the traditional deep groove ball bearing to improve the lubrication efficiency and performance. This design reduces the wear caused by insufficient lubrication, extends the service life of the bearing, and reduces the operating noise. The deep groove ball bearing with a baffle is widely used in occasions with high speed, heavy load or special lubrication requirements, such as motors, pumps and precision instruments.

[0003] Chinese Patent Document CN108361275B discloses a high-speed deep groove ball bearing, where the radius R of the groove arc / the diameter Dw of the steel ball is 0.53 - 0.56. The two ends of the connecting arc are tangent to the groove and the rib respectively. The perpendicular line at the inner end of the outer edge protrusion of the sealing ring passes through the cage, and the protrusion is in sealing fit with the outer ring rib to form a groove.

[0004] As shown in the above solution, on the inner and outer rings of the bearing, there are accommodation grooves corresponding to the rolling elements, into which a part of the rolling elements are recessed. After the rolling elements throw up the lubricating oil during operation, the thrown lubricating oil will return to the accommodation grooves through the arc transition between the accommodation grooves and the outer surfaces of the inner and outer rings of the bearing to provide lubrication for the rolling elements. However, the above solution has the following deficiencies: To ensure the overall strength of the cage, the existing cages all require a certain thickness, and the design of the above cage will undoubtedly prevent the arc transition between the accommodation grooves and the inner and outer rings of the bearing from being expanded, thus reducing the efficiency of the lubricating oil return. Summary of the Utility Model

[0005] Aiming at the deficiencies of the prior art, the utility model provides a deep groove ball bearing that can improve the lubricating oil return efficiency and the strength of the cage.

[0006] To achieve the above purpose, the technical solution of the utility model is as follows: A deep groove ball bearing includes an outer ring and an inner ring. Between the outer ring and the inner ring, there are rolling elements sleeved in a cage. On the outer ring and the inner ring, corresponding to the positions of the rolling elements, there are a first accommodation groove and a second accommodation groove respectively. The inner diameter surface of the outer ring from its center to the edge is respectively an arc-shaped first accommodation groove, an inclined first return surface and a first straight surface. The outer diameter surface of the inner ring from its center to the edge is respectively a second accommodation groove and an inclined second return surface. On the side of the cage facing the outer ring, from its center to the edge, there are a first arc surface and a second straight surface. On the side of the cage facing the inner ring, from its center to the edge, there is a second arc surface. The cross-section position of the second straight surface is located between the first straight surface and the first return surface.

[0007] The beneficial effects of the present utility model are as follows: Through the first accommodating grooves and the second accommodating grooves on the inner and outer rings and the matching return surfaces, effective management of lubricating oil is achieved. The inner diameter surface of the outer ring transitions from the arc-shaped first accommodating groove to the inclined first return surface and then connects to the first straight surface, while the outer diameter surface of the inner ring connects from the second accommodating groove to the inclined second return surface. Such a structural layout helps to guide the lubricating oil back to the rolling elements, thereby improving the lubrication efficiency. At the same time, one side of the cage has a first arc surface and a second straight surface that match the outer ring, and the other side has a second arc surface that matches the inner ring. Such a design not only ensures the stable positioning of the rolling elements but also promotes the return of the lubricating oil along the set path to the rolling elements, ensuring continuous lubrication inside the bearing. At the same time, since the cross-sectional position of the second straight surface is located between the first straight surface and the first return surface, the gap between the cage and the outer ring can be effectively reduced, further ensuring the return effect of the lubricating oil. The above structure significantly reduces the loss of lubricating oil and the intrusion of external contamination, extends the maintenance cycle and service life of the bearing, and at the same time reduces the risk of wear and failure caused by insufficient lubrication, improving the overall performance and reliability of the bearing.

[0008] Further, the cage includes a first frame body and a second frame body that are detachably connected to each other. Snap holes that can be spliced are provided at corresponding positions of the first frame body and the second frame body, and a snap member for fixing the first frame body and the second frame body is inserted into the snap holes.

[0009] The cage of a traditional deep groove ball bearing is usually fixed by riveting, which is extremely inconvenient during maintenance or replacement. The above detachable cage design realizes the rapid assembly and disassembly of the first frame body and the second frame body of the cage by introducing snap holes and snap members, significantly improving the maintenance convenience of the bearing. Therefore, it is allowed to easily assemble and maintain the cage outside the bearing, reducing the replacement of the entire bearing due to cage problems, effectively reducing the maintenance cost and equipment downtime. At the same time, this also improves the operation efficiency, making regular inspections and replacements when necessary faster and easier, enhancing the adaptability and reliability of the bearing, and is particularly suitable for application scenarios with high maintenance requirements.

[0010] Further, the snap member includes a connecting rod and snap strips located on both sides of the connecting rod. The cross-sections of the two snap strips are perpendicular to each other, and the snap holes are set corresponding to the cross-sectional shapes of the two snap strips.

[0011] As a preferred solution, the snap member can be made of an elastic material, and its self-adaptive fitting ability ensures a tight connection even in the case of slight dimensional differences in the bayonet holes. This design not only simplifies the assembly process, improves the maintenance efficiency, but also reduces the maintenance cost, because the quick-disassembly feature enables the cage to be replaced individually without having to replace the entire bearing unit. In addition, the buffering effect of the elastic snap strip helps to absorb vibrations and impacts, extending the bearing life. Meanwhile, its elastic property also helps to absorb thermal expansion and contraction under temperature changes and mechanical loads, thus ensuring the stability of the bearing performance and the accuracy of rotation. Furthermore, the cross-section of the snap strips perpendicular to each other can be in a cross shape. Correspondingly, the bayonet holes are also in a cross shape to facilitate the insertion of the snap member and also to facilitate the rotation and locking of the snap member.

[0012] Furthermore, a limiting portion is provided on the outer side of the bayonet hole corresponding to the snap strip. The limiting portion is located on both sides of the bayonet hole and the position of the limiting portion overlaps with the rotational outer diameter of the snap strip. A tightening portion for positioning in cooperation with the snap strip is provided at the end of the limiting portion.

[0013] When the snap member is inserted into the bayonet hole, since the limiting portion is located at its rotational outer diameter and on the circumferential side of the bayonet hole, it will not hinder the free insertion and rotation of the snap member, ensuring the simple installation of the cage. After rotation and locking, as a preferred solution, the tightening portion protrudes inwardly towards the rotational outer diameter of the snap strip, and can be tightly fitted and positioned with the snap strip, effectively preventing the snap member from accidentally coming out during the operation of the bearing.

[0014] Furthermore, the bayonet holes are provided on the side of the cage and are circumferentially arranged along the side surface of the cage.

[0015] The circumferential distribution of the bayonet holes along the side surface helps to evenly disperse the pressure of the snap member, enhancing the structural stability and overall rigidity of the cage. At the same time, the bayonet holes provided on the side can form strong connection points on the side surface of the cage, enhancing the local strength of the connection between the cage and the snap member. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 Isometric view of the embodiment of the present utility model;

[0017] Figure 2 Cross-sectional view of the embodiment of the present utility model;

[0018] Figure 3 Isometric view of the cage of the embodiment of the present utility model;

[0019] Figure 4 Cross-sectional view of the cage of the embodiment of the present utility model;

[0020] Figure 5 Isometric view of the snap member of the embodiment of the present utility model;

[0021] Figure 6 This is a partial enlarged view of the bayonet hole in the embodiment of the present utility model. Detailed implementation manners

[0022] An embodiment of the present utility model provides a deep groove ball bearing as Figure 1-6 shown in the figure: It includes an outer ring 1 and an inner ring 2. Between the outer ring 1 and the inner ring 2, rolling elements 4 sleeved in a cage 3 are arranged. The cage 3 is divided into a first frame body 31 and a second frame body 32. At corresponding positions on the sides of both, bayonet holes 35 that can be spliced and are in a cross shape are provided. Between the first frame body 31 and the second frame body 32, the first frame body 31 and the second frame body 32 are fixed by inserting a buckle member 5 into the bayonet hole 35 and rotating the buckle member 5.

[0023] On the inner diameter surface of the outer ring 1, that is, on the side facing the cage 3, from the center of its inner diameter surface towards the edge, there are respectively an arc-shaped first accommodation groove 11, an inclined first return surface 12, and a first straight surface 13; on the outer diameter surface of the inner ring 2, also on the side facing the cage 3, from the center of its outer diameter surface towards the edge, there are respectively a second accommodation groove 21 and an inclined second return surface 22. And on the side of the cage 3 facing the outer ring 1, from the center of it towards the edge, there are a first arc surface 33 and a second straight surface 34, and on the side facing the inner ring 2, from the center of it towards the edge, there is a second arc surface 35. At the same time, the cross-sectional position of the second straight surface 34 of the cage 3 is located between the first straight surface 13 and the first return surface 12, and the cross-sectional position of the second arc surface 35 of the cage 3 is located at the second return surface 22. In this way, while ensuring the width of the cage 3 to ensure its strength, the distance between the edge of the cage 3 and the outer ring 1 and the inner ring 2 can be minimized as much as possible, improving the oil return effect of the lubricating oil and preventing it from flowing out of the cage 3.

[0024] The buckle member 5 includes a connecting rod 52 and buckle strips 51 located on both sides of the connecting rod. The cross-sectional positions of the two buckle strips 51 intersect to form a cross shape. At corresponding positions on the periphery of the bayonet hole 36, a limiting portion 37 is provided. The limiting portion 37 is located at the rotation outer diameter of the buckle strip 51, that is, it overlaps with the rotation outer diameter of the buckle strip 51. At the end of the limiting portion 37 (this end refers to the end where the buckle strip 51 rotates and is clamped), a tightening portion 371 protruding towards the inner side of the rotation outer diameter of the buckle strip 51 is provided.

[0025] The installation process of this embodiment is as follows: Place the rolling elements 4 between the first frame 31 and the second frame 32, and insert the buckle member 5 into the bayonet holes 36 provided circumferentially on both of them. After the buckle strip 51 on one side passes through the bayonet hole 36 on the other side, grasp the buckle strip 51 and rotate it so that the buckle strip 51 cooperates with the expansion part 371 on the limiting part 37 to complete the locking and positioning. Subsequently, install the completed cage 3 and the rolling elements 4 therein into the inner ring 2, and install the outer ring 1 to complete the installation of the bearing.

[0026] The above embodiments are only one of the preferred specific embodiments of the present invention, and the ordinary changes and substitutions made by those skilled in the art within the scope of the technical solution of the present invention are included in the protection scope of the present invention.

Claims

1. A deep groove ball bearing, comprising an outer ring and an inner ring, with rolling elements sleeved in a cage disposed between the outer ring and the inner ring, and a first accommodation groove and a second accommodation groove are respectively arranged at positions corresponding to the rolling elements on the outer ring and the inner ring, characterized in that: The inner diameter surface of the outer ring is respectively an arc-shaped first accommodation groove, an inclined first return surface, and a first straight surface from its center towards the edge. The outer diameter surface of the inner ring is respectively a second accommodation groove and an inclined second return surface from its center towards the edge. The side of the cage facing the outer ring is a first arc surface and a second straight surface from its center towards the edge, and the side of the cage facing the inner ring is a second arc surface from its center towards the edge. The cross-sectional position of the second straight surface is located between the first straight surface and the first return surface.

2. The deep groove ball bearing according to claim 1, wherein: The cage includes a first frame body and a second frame body that are detachable from each other. Snap holes that can be spliced are provided at corresponding positions of the first frame body and the second frame body, and a buckle is inserted into the snap holes for fixing the first frame body and the second frame body.

3. The deep groove ball bearing according to claim 2, characterized in that: The buckle includes a connecting rod and buckle strips on both sides of the connecting rod. The cross-sections of the two buckle strips are perpendicular to each other, and the snap holes are set according to the cross-sectional shapes of the two buckle strips.

4. The deep groove ball bearing according to claim 3, characterized in that: Limit parts are provided on the outer side of the snap holes corresponding to the buckle strips. The limit parts are located on both sides of the snap holes, and the positions of the limit parts overlap with the rotational outer diameters of the buckle strips. Tightening parts that cooperate with the buckle strips to form positioning are provided at the ends of the limit parts.

5. The deep groove ball bearing according to claim 4, characterized in that: The snap holes are provided on the side of the cage and are circumferentially arranged along the side surface of the cage.

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