A rolling bearing provided with a cage having through grooves

Abstract

The application discloses a rolling bearing with a cage provided with through grooves, wherein two through grooves penetrating through the thickness of each beam are arranged along the radial direction of the rolling bearing; one of the through grooves connects the oil film converging area on one side of the beam with the oil film diverging area on the other side, and the other through groove connects the oil film diverging area on one side of the beam with the oil film converging area on the other side. The rolling bearing can realize the self-enhancing effect of lubricating oil flow through the through grooves, effectively reduce the extrusion flow and the degree of oil film cavitation near the friction surface, more efficiently organize the lubricating oil near the friction surface, reduce the friction resistance and the wear condition, improve the heat dissipation capacity of the bearing, and avoid the problem that the abrasion powder enters the contact area of the friction surface in the flowing process to cause more serious wear of the bearing.

Description

Technical Field

[0001] This invention belongs to the field of rolling bearing technology, and specifically relates to a rolling bearing with a cage having a through groove. Background Technology

[0002] A rolling bearing is a precision mechanical component that transforms the sliding friction between a rotating shaft and its housing into rolling friction, thereby reducing frictional losses. A rolling bearing generally consists of four parts: an inner ring, an outer ring, rolling elements, and a cage. The inner ring mates with the shaft and rotates synchronously with it; the outer ring mates with the bearing housing and provides support; the cage evenly distributes the rolling elements between the inner and outer rings. The shape, size, number, and load conditions of the rolling elements directly affect the performance and lifespan of the rolling bearing; the cage ensures the even distribution of the rolling elements and guides their rotation.

[0003] Rolling bearings are widely used in automobiles, ships, aerospace and other fields due to their advantages of low frictional resistance, stable operation and reliable quality. As various machines place higher demands on the speed, load and stability of rolling bearings, the impact of frictional resistance between the bearing rolling elements and the cage on bearing performance is becoming increasingly prominent. High frictional resistance can easily lead to increased wear and increased heat load, causing lubrication failure and thermal failure problems in the bearing.

[0004] The cage primarily isolates the rolling elements and guides and limits their range of motion. According to the theory of elastohydrodynamic lubrication, variations in the pocket clearance near the friction surfaces of the rolling elements and the cage result in oil film convergence and divergence zones. In the convergence zone, the oil film pressure increases as the pocket clearance gradually decreases along the sliding direction. Some lubricating oil is forced out of the pocket due to the pressure gradient, forming a spur, preventing this portion of lubricating oil from entering the friction surfaces and being effectively utilized. In the divergence zone, the oil film pressure gradually decreases as the pocket clearance gradually increases along the sliding direction. Lower oil film pressure can cause oil film rupture and the formation of cavitation zones. The formation and rupture of cavitation bubbles easily lead to cavitation, spalling, and other wear phenomena on the friction surfaces, affecting the stability and service life of the bearing.

[0005] During actual operation, rolling bearings exhibit distinct oil film convergence and divergence zones between the rolling elements and the cage. This leads to compression and cavitation phenomena between the rolling elements and the cage, resulting in inefficient organization of lubricant flow between the friction surfaces. Existing technologies, through simple additions of oil reservoirs, weight-reduction grooves, and oil lines, cannot adequately reduce the compression and cavitation phenomena in the contact area of ​​the friction surfaces, and it is even more difficult to achieve a stable, active, self-enhancing effect of lubricant flow near the friction surfaces.

[0006] The main objective of this invention is to address the following three problems existing in rolling bearings:

[0007] 1. Traditional rolling bearings cannot improve the flow characteristics of lubricating oil: Existing rolling bearings only reduce friction by reducing the contact area or increasing the oil storage space through the cage, but cannot fundamentally change the flow characteristics of lubricating oil near the friction surface between the rolling elements and the cage. As a result, the lubricating oil cannot be efficiently organized, and the problems of friction resistance and wear are not fundamentally solved.

[0008] 2. Difficulty in overcoming dynamic defects in oil film: Although existing rolling bearings can improve oil supply capacity, they cannot effectively reduce the squeezing and cavitation of oil film caused by oil film pressure gradient on the friction surface, resulting in low lubricant utilization, high risk of cavitation and spalling, and limited optimization of lubrication effect.

[0009] 3. Wear debris accumulation and insufficient heat dissipation: Traditional rolling bearings do not optimize the flow path of lubricating oil based on the lubrication principle, and cannot actively drive the transfer of lubricating oil. As a result, wear debris on the friction surface cannot be effectively removed, and the flow of lubricating oil lacks directional organization, resulting in low heat dissipation efficiency and a significant risk of bearing thermal failure. Summary of the Invention

[0010] This invention provides a rolling bearing with a cage having a through groove. This rolling bearing can achieve a stable and self-reinforcing effect of lubricating oil flow, effectively reduce the degree of extrusion and oil film cavitation, so that the lubricating oil near the friction surface is more efficiently organized, reducing frictional resistance and wear, improving the bearing's heat dissipation capacity, and preventing wear debris from entering the contact area of ​​the friction surface during the flow process, thus preventing the bearing from experiencing more severe wear problems.

[0011] To achieve the above objectives, the present invention adopts the following specific technical solution:

[0012] A rolling bearing with a cage having a through groove, the rolling bearing including an inner ring, an outer ring, a cage and rolling elements; the cage has a plurality of crossbeams evenly arranged circumferentially, forming pockets between adjacent crossbeams;

[0013] Along the rotation direction of the rolling element, an oil film convergence zone and an oil film divergence zone of the lubricating oil film are formed sequentially between the rolling element and the side surface of the guide beam; each guide beam is provided with two through grooves that are distributed radially along the rolling bearing and penetrate through the thickness of the guide beam; one through groove connects the oil film convergence zone on one side of the guide beam with the oil film divergence zone on the other side, and the other through groove connects the oil film divergence zone on one side of the guide beam with the oil film convergence zone on the other side.

[0014] The pressure difference generated by the hydrodynamic effect and cavitation phenomenon drives the lubricating oil to flow from the oil film convergence zone on one side of the beam through a through groove to the oil film divergence zone on the other side of the beam, and from the oil film convergence zone on the other side of the beam through another through groove to the oil film divergence zone on one side of the beam, thereby reducing the squeezing and cavitation between the rolling elements and the beam and the degree of oil film cavitation.

[0015] Furthermore, two through slots are symmetrically distributed on both sides of the centerline of the contact area between the rolling element and the beam.

[0016] Furthermore, based on the principles of hydrodynamic lubrication and Hertz contact theory, the shortest distance between the through groove and the centerline of the contact area satisfies the following equation:

[0017] b>1.0w;

[0018] In the above formula, b is the shortest distance between the through groove and the centerline of the contact area; w is the nominal half-width of the contact area between the rolling element and the cage.

[0019] Furthermore, the radial width of the through slot satisfies the following formula:

[0020] a = 1.0w - 5.0w;

[0021] In the above formula, a is the radial width of the through groove; w is the nominal half-width of the contact area between the rolling element and the cage.

[0022] Furthermore, the axial width of the through groove is less than or equal to the axial width of the pocket.

[0023] Furthermore, the rolling element is a roller.

[0024] Furthermore, the through groove is a long, narrow groove.

[0025] Furthermore, the rolling element is a ball bearing.

[0026] Furthermore, the through groove is shaped like a date pit.

[0027] Compared with the prior art, the technical solution of the present invention has the following beneficial effects:

[0028] 1. Based on lubrication theory, the rolling bearing of this invention forms an oil film convergence zone and an oil film divergence zone sequentially between the friction surfaces of the rolling elements and the cage along the rotation direction of the rolling elements. A through-groove is provided on the guide beam, distributing the oil film convergence and divergence zones on the friction surfaces of the rolling elements and the guide beam. This through-groove connects the corresponding oil film convergence and divergence zones on both sides of the guide beam. The pressure difference created by the hydrodynamic effect and cavitation phenomenon drives the lubricating oil to flow from the oil film convergence zone on one side to the oil film divergence zone on the other side, thus allowing the lubricating oil to flow between the friction surfaces on both sides of the guide beam. The transfer between the oil film convergence zone and the oil film divergence zone achieves a self-enhancing effect of stable lubricating oil flow near the friction surface, resulting in more efficient organization of the lubricating oil near the friction surface. This effectively reduces the squeezing and cavitation of the oil film near the friction surface between the rolling elements and the cage, effectively utilizes the squeezing and cavitation of the oil film, reduces frictional resistance and wear, improves the lubricating oil reserve and heat exchange efficiency of the friction surface, and enhances the heat dissipation capacity of the bearing. It can be widely used in rolling bearings with rolling elements and cage structures, such as ball bearings and roller bearings.

[0029] 2. The rolling bearing of the present invention forms a driving pressure difference between the oil film convergence zone and the oil film divergence zone by the lubricating oil, so that the lubricating oil can actively collect the wear debris generated during the working process when flowing through the through groove, and avoid the wear debris entering the contact area of ​​the friction surface between the rolling element and the cage, so as to prevent the bearing from having more serious wear problems. Attached Figure Description

[0030] Figure 1 This is a schematic diagram of a half-section of the rolling bearing of the present invention;

[0031] Figure 2 A three-dimensional structural diagram of the cage;

[0032] Figure 3 A schematic diagram of a through groove for a cage;

[0033] Figure 4 A schematic diagram of another through-slot structure for the cage;

[0034] Figure 5 This is a schematic diagram illustrating the principle of the oil film convergence zone and oil film divergence zone between the rolling element and the beam.

[0035] Reference numerals: 1-Cage; 2-Beam; 3-Through groove; 4-Rolling element; 5-Inner ring; 6-Outer ring. Detailed Implementation

[0036] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0037] The rolling bearing of this invention reduces friction and wear based on hydrodynamic lubrication theory. Through the through-groove 3 at the crossbeam 2, which connects the oil film convergence zone and the oil film divergence zone, the pressure difference generated by the hydrodynamic effect drives the directional flow of lubricating oil, reconstructing the oil film flow behavior near the friction surface. Specifically, during the rotation of the rolling element 4, the pocket clearance of the cage 1 gradually decreases along the direction of motion, forming the oil film convergence zone, while the pocket clearance of the cage 1 gradually increases along the direction of motion, forming the oil film divergence zone. In traditional designs, the high pressure in the oil film convergence zone can squeeze the lubricating oil, causing leakage losses, while the low pressure in the oil film divergence zone can cause oil film cavitation and rupture, leading to cavitation erosion.

[0038] This invention provides a rolling bearing with a cage 1 having a through groove 3, such as... Figure 1 As shown, the rolling bearing includes an inner ring 5, an outer ring 6, a cage 1, and rolling elements 4; the cage 1 has a plurality of crossbeams 2 evenly arranged circumferentially, forming pockets between adjacent crossbeams 2; wherein:

[0039] Along the rotation direction of the rolling element 4, the side surfaces of the rolling element 4 and the beam 2 sequentially form an oil film convergence zone and an oil film divergence zone; such as Figure 5 As shown, the explanation will take one side surface of the rolling element 4 and the crossbeam 2 in the cage 1 as an example. The rolling element 4 is arranged according to... Figure 5 When the direction indicated by the middle arrow rotates at an angular velocity ω, the oil film convergence zone and oil film divergence zone are the cavities formed between the outer surface of the rolling element 4 and one side surface of the crossbeam 2. The trend of these cavities along the rotation direction of the rolling element 4 is as follows: the outer surface of the rolling element 4 and one side surface of the crossbeam 2 form cavities due to the difference in curvature. The characteristic of these cavities is that they change with the rotation direction of the rolling element 4. Figure 5Taking counterclockwise rotation as an example, the gap between the outer surface of the rolling element 4 and one side surface of the beam 2 decreases from large to small, reaching the minimum gap along the central symmetry line, and then the gap increases again. In the region where the gap decreases, a ">" shaped converging cavity is formed in space on both surfaces along the rotation direction of the rolling element 4. This cavity is called the oil film convergence zone. The gradually increasing oil film pressure P in the oil film convergence zone will squeeze out some lubricating oil and form a squeeze jet. In the region where the gap increases, a "<" shaped diverging cavity is formed in space on both surfaces along the rotation direction of the rolling element 4. This cavity is called the oil film divergence zone. The gradually decreasing oil film pressure P in the oil film divergence zone will cause the oil film to rupture, forming cavitation. It must be pointed out that the definitions of the oil film convergence zone and the oil film divergence zone are closely related to the rotation direction of the rolling element 4. If the rolling element 4 rotates in a certain direction... Figure 5 When the rotation is clockwise, the positions of the oil film convergence zone and the oil film divergence zone are reversed compared to the diagram.

[0040] During the rolling process of the rolling element 4, the guide beam 2 forms an oil film convergence zone and an oil film divergence zone between itself and the rolling element 4 on both sides facing the rolling element 4. Furthermore, since all the rolling elements 4 rotate in the same direction, an oil film convergence zone is formed on one side of the guide beam 2. Figure 5 When the oil film convergence zone and oil film divergence zone are shown, a zone is formed on the other side of the crossbeam 2. Figure 5 The oil film convergence zone and oil film divergence zone are arranged in opposite directions. That is, the oil film convergence zone on one side of the beam 2 and the oil film divergence zone on the other side of the beam 2 are arranged opposite to each other in the radial direction of the bearing. At the same time, the oil film divergence zone on one side of the beam 2 and the oil film convergence zone on the other side of the beam 2 are arranged opposite to each other in the radial direction of the bearing. In other words, if the two sides of the beam 2 are defined as the first side surface and the second side surface, the beam 2 will form an oil film convergence zone and an oil film divergence zone on both the first side surface and the second side surface when the rolling element 4 rotates. In the radial direction of the bearing, if the oil film convergence zone of the first side surface is close to the outer ring 6, then the oil film divergence zone of the first side surface is close to the inner ring 5, and the oil film convergence zone of the second side surface is close to the inner ring 5 and the oil film divergence zone of the second side surface is close to the outer ring 6.

[0041] like Figure 2 As shown in the structure, each crossbeam 2 is provided with two through grooves 3 that penetrate the thickness of the crossbeam and are radially spaced along the rolling bearing; one through groove 3 connects the oil film convergence area on one side of the crossbeam 2 with the oil film divergence area on the other side, and the other through groove 3 connects the oil film divergence area on one side of the crossbeam 2 with the oil film convergence area on the other side. That is, the two through grooves 3 provided on the crossbeam 2 connect the oil film convergence area and the oil film divergence area on opposite sides of the crossbeam 2 respectively. Figure 2As shown, each crossbeam 2 is provided with two through grooves 3, namely a first through groove near the outer ring 6 (not shown in the figure) and a second through groove near the inner ring (not shown in the figure). Assuming that the rolling element 4 and the first side surface of the crossbeam 2 form an oil film convergence zone near the outer ring 6, the rolling element 4 and the first side surface of the crossbeam 2 form an oil film dispersion zone near the inner ring 5, the rolling element 4 and the second side surface of the crossbeam 2 form an oil film dispersion zone near the outer ring 6, and the rolling element 4 and the second side surface of the crossbeam 2 form an oil film convergence zone near the inner ring 5. The first through groove connects the oil film convergence zone of the first side surface and the oil film dispersion zone of the second side surface, and the second through groove connects the oil film dispersion zone of the first side surface and the oil film convergence zone of the second side surface.

[0042] Because two through grooves 3 are provided on the beam 2, the pressure difference formed by the hydrodynamic effect and cavitation phenomenon drives the lubricating oil to flow from the oil film convergence area on one side of the beam 2 through one through groove to the oil film divergence area on the other side of the beam 2, and from the oil film convergence area on the other side of the beam 2 through another through groove to the oil film divergence area on one side of the beam 2, thereby reducing the squeezing and splashing between the rolling element 4 and the beam 2 and the degree of oil film cavitation.

[0043] Based on lubrication theory, the aforementioned rolling bearing, along the rotation direction of the rolling element 4, will sequentially form an oil film convergence zone and an oil film divergence zone between the friction surfaces of the rolling element 4 and the cage. A through groove 3 corresponding to the positions of the oil film convergence zone and the oil film divergence zone is provided on the beam 2. The through groove 3 connects the corresponding oil film convergence zone and oil film divergence zone on both sides of the beam 2. Utilizing the pressure difference formed by hydrodynamic pressure effect and cavitation phenomenon, the lubricating oil flows from the oil film convergence zone to the oil film divergence zone, allowing the lubricating oil to flow between the friction surfaces on both sides of the beam 2. The transfer between the film convergence zone and the oil film divergence zone achieves a stable self-enhancing effect of lubricating oil flow near the friction surface, resulting in more efficient organization of the lubricating oil near the friction surface. This effectively reduces the squeezing and cavitation of the oil film near the friction surface between the rolling element 4 and the cage, effectively utilizes the squeezing and cavitation of the oil film, reduces frictional resistance and wear, improves the lubricating oil reserve and heat exchange efficiency of the friction surface, and enhances the heat dissipation capacity of the bearing. It can be widely used in rolling bearings with a rolling element 4 and cage structure.

[0044] In the aforementioned rolling bearings, such as Figure 3 and Figure 4 As shown, two through grooves 3 are symmetrically distributed on both sides of the centerline S of the contact area between the rolling element 4 and the beam 2; the axial width of the through groove 3 can be less than or equal to the axial width of the pocket; both the axial width of the through groove 3 and the axial width of the pocket are widths along the axial direction of the rolling bearing. When the rolling bearing is a roller bearing, the rolling element 4 is a roller, and the cross-sectional shape of the through groove 3 is a long strip, as shown... Figure 3As shown, the through groove 3 is an elongated groove, with its axial length much greater than its radial width. When the rolling bearing is a ball bearing, the rolling element 4 is a ball, and the cross-sectional shape of the through groove 3 is oval-shaped, as shown. Figure 4 As shown, the through groove is shaped like a date pit.

[0045] According to the principle of hydrodynamic lubrication and Hertz contact theory, the radial width of the through groove 3 and the distance between the through groove 3 and the centerline of the contact area satisfy the following formula:

[0046] a = 1.0w - 5.0w;

[0047] b>1.0w;

[0048] In the above formula, a is the radial width of the through groove 3; b is the shortest distance between the through groove 3 and the centerline of the contact area; w is the nominal half-width of the contact area between the rolling element 4 and the cage, which can be obtained through Hertz contact theory. The radial width of the through groove 3 is the width of the through groove 3 along the radial direction of the rolling bearing.

[0049] To provide an effective driving pressure differential and achieve more effective wear and drag reduction, the radial width 'a' of the through groove 3 and the shortest distance 'b' between the through groove 3 and the centerline of the contact area need to be determined based on the mechanical properties of the material and the bearing's operating conditions. By setting the radial width of the through groove 3 and the distance between the through groove 3 and the centerline of the contact area, the changes in the width of the oil film convergence zone and the oil film divergence zone caused by different local velocities can be balanced, thus more effectively utilizing the driving pressure differential generated by the hydrodynamic effect.

[0050] The aforementioned rolling bearing adopts a structural design with a through groove 3 set on the beam 2 of the cage 1, which breaks through the passive oil storage concept of traditional oil reservoirs or weight reduction grooves. A through groove 3 that penetrates the thickness of the beam 2 is set in the key area of ​​the beam 2 of the cage 1. Through the hydrodynamic pressure effect, a directional pressure difference driving mechanism is actively constructed from the oil film convergence zone to the oil film divergence zone, realizing the self-reinforcing transfer of lubricating oil from the high pressure zone to the low pressure zone, and fundamentally reconstructing the oil film flow characteristics of the friction surface.

[0051] The aforementioned rolling bearing can dynamically and collaboratively regulate oil film defects. By utilizing the connectivity of the through groove 3, the traditionally harmful extrusion flow is transformed into lubricating resources. The through groove 3 collects the lubricating oil squeezed out from the oil film convergence zone and directs it to the oil film divergence zone to suppress oil film cavitation. This simultaneously solves the two major problems of flow loss and cavitation breakage, significantly improving oil film stability and utilization.

[0052] The aforementioned rolling bearing achieves multi-functional integrated active management. The through groove 3 has both the functions of collecting wear debris and enhancing heat exchange. Under pressure differential drive, the flow containing wear debris is directed away from the friction contact area through the through groove 3, avoiding abrasive wear. In addition, the continuously flowing lubricating oil enhances the heat dissipation efficiency of the friction surface, improving the bearing reliability from both wear control and thermal management dimensions.

[0053] The working principle of the rolling bearing of this invention is as follows: Based on the oil film flow characteristics of the friction surface, through the through groove 3 set in the beam 2, the high-pressure lubricating oil in the oil film convergence zone on one side of the beam 2 actively flows through the through groove 3 to the low-pressure oil film dispersion zone on the other side of the beam 2 under the drive of pressure difference, achieving three synergistic effects: First, it transforms the traditionally squeezed harmful jet into lubricating resources. The through groove 3 collects the lubricating oil overflowing from the oil film convergence zone and transports it to the oil film dispersion zone to replenish the oil film, suppressing cavitation and improving the integrity and pressure stability of the oil film. Second, it reconstructs the oil film flow path. The connectivity of the through groove 3 forms a directional self-circulation from "high pressure" to "low pressure", enhancing the effective coverage and continuous renewal of lubricating oil on the friction surface, reducing boundary friction and improving heat dissipation efficiency. Third, it achieves active removal of wear debris. Wear particles in the squeeze jet are guided away from the contact area by the lubricating oil through the through groove 3, avoiding three-body wear caused by wear particle accumulation. The continuously flowing lubricating oil further enhances the convective transfer of heat and suppresses the risk of lubrication failure.

[0054] The working principle of this rolling bearing is essentially to dynamically couple the traditionally separated oil film convergence zone and oil film divergence zone through structural innovation, and to spontaneously adjust the redistribution of lubricating oil by utilizing pressure difference, thereby comprehensively solving the problems of extrusion flow loss, oil film cavitation rupture and wear debris retention, and achieving systematic optimization of tribological performance.

[0055] Obviously, those skilled in the art can make various modifications and variations to the embodiments of the present invention without departing from the spirit and scope of the invention. Therefore, if these modifications and variations fall within the scope of the claims of the present invention and their equivalents, the present invention also intends to include these modifications and variations.

Claims

1. A rolling bearing with a cage having a through groove, comprising an inner ring, an outer ring, a cage, and rolling elements; the cage having a plurality of crossbeams evenly arranged circumferentially, forming pockets between adjacent crossbeams; characterized in that, Along the rotation direction of the rolling element, an oil film convergence zone and an oil film divergence zone of the lubricating oil film are formed sequentially between the rolling element and the side surface of the guide beam; each guide beam is provided with two through grooves that are distributed radially along the rolling bearing and penetrate through the thickness of the guide beam; one through groove connects the oil film convergence zone on one side of the guide beam with the oil film divergence zone on the other side, and the other through groove connects the oil film divergence zone on one side of the guide beam with the oil film convergence zone on the other side. The pressure difference generated by the hydrodynamic effect and cavitation phenomenon drives the lubricating oil to flow from the oil film convergence zone on one side of the beam through a through groove to the oil film divergence zone on the other side of the beam, and from the oil film convergence zone on the other side of the beam through another through groove to the oil film divergence zone on one side of the beam, thereby reducing the squeezing and cavitation between the rolling elements and the beam and the degree of oil film cavitation.

2. The rolling bearing as described in claim 1, characterized in that, Two through slots are symmetrically distributed on both sides of the centerline of the contact area between the rolling element and the beam.

3. The rolling bearing as described in claim 2, characterized in that, According to the principle of hydrodynamic lubrication and Hertz contact theory, the shortest distance between the through groove and the centerline of the contact area satisfies the following equation: b>1.0w; In the above formula, b is the shortest distance between the through groove and the centerline of the contact area; w is the nominal half-width of the contact area between the rolling element and the cage.

4. The rolling bearing as described in claim 2, characterized in that, The radial width of the through slot satisfies the following formula: a = 1.0w - 5.0w; In the above formula, a is the radial width of the through groove; w is the nominal half-width of the contact area between the rolling element and the cage.

5. The rolling bearing as described in claim 1, characterized in that, The axial width of the through groove is less than or equal to the axial width of the pocket.

6. The rolling bearing according to any one of claims 1-5, characterized in that, The rolling element is a roller.

7. The rolling bearing as described in claim 6, characterized in that, The through groove is a long, narrow groove.

8. The rolling bearing according to any one of claims 1-5, characterized in that, The rolling element is a ball bearing.

9. The rolling bearing as described in claim 8, characterized in that, The through groove is shaped like a date pit.

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