A bearing cage with a slot-shaped through cavity

Abstract

The application discloses a bearing retainer with slot type through cavities, each cross beam of the bearing retainer is provided with two slot type through cavities which are distributed along the radial direction of the retainer body; one slot type through cavity is used for connecting the converging area on one side of the cross beam with the diverging area on the other side, and the other slot type through cavity is used for connecting the diverging area on one side of the cross beam with the converging area on the other side. The bearing retainer can realize the stable lubricating oil flow self-enhancement effect near the friction surface through the slot type through cavities, effectively reduces the extrusion flow and the oil film cavitation degree near the friction surface between the rolling body and the retainer, makes the lubricating oil near the friction surface more efficient, reduces the friction resistance and the wear condition, improves the heat dissipation capacity of the bearing, and collects the bearing abrasion through the slot type through cavities, avoids the abrasion from entering the contact area of the friction surface in the flowing process, and makes the bearing appear more serious wear problems.

Description

Technical Field

[0001] This invention belongs to the field of bearing technology, and specifically relates to a bearing cage with a slotted cavity. Background Technology

[0002] Rolling bearings, as crucial supporting rotating components, are widely used in the automotive, marine, and aerospace industries. Their main components include an inner ring, outer ring, rolling elements, and a cage. These bearings convert the sliding friction between the shaft and its housing into rolling friction through the rolling elements, thereby reducing friction loss, improving stability, and extending the lifespan of the friction pair. With industrial upgrading and the advancement of various engineering machinery technologies, higher demands are being placed on rolling bearings in terms of speed, load capacity, and stability. The frictional resistance between the rolling elements and the cage has a growing impact on bearing performance, especially under high-speed conditions. High frictional resistance leads to increased wear and thermal load, which can easily cause lubrication and thermal failure in bearings.

[0003] As a crucial component of rolling bearings, the bearing cage primarily isolates the rolling elements and guides and limits their movement. The bearing cage features a pocket structure within which the rolling elements are mounted and rotate with the cage. Depending on the guiding method, bearings can be classified into three types: outer ring guided, cage guided, and inner ring guided. The rolling elements rotate under the guidance of the cage, and the bearing cage moves along with them. Due to the pocket clearance between the rolling elements and the cage, the rolling elements will not always be centered within the cage pocket during operation. Collisions and sliding friction may occur between the rolling elements and the cage, and this friction is a key factor causing bearing overheating and wear. According to the theory of elastohydrodynamic lubrication, the lubricating oil film exhibits convergence and divergence zones near the friction surfaces of the rolling elements and cage due to variations in the pocket clearance. In the convergence zone, the oil film pressure increases as the pocket clearance gradually decreases along the sliding direction. Some lubricating oil is squeezed out of the pocket clearance due to the pressure gradient, forming a spur, preventing this portion of lubricating oil from entering the friction surface and being effectively utilized. As the clearance in the cavitation zone gradually increases along the sliding direction, the oil film pressure gradually decreases. The lower oil film pressure will cause the oil film to rupture and form a cavitation zone. The formation and rupture of cavitation bubbles can easily cause wear phenomena such as cavitation and peeling on the friction surface, which will affect the stability and service life of the bearing.

[0004] Traditional research on the optimization of bearing cages in rolling bearings has largely focused on bearing structures and oil supply parameters, such as adding weight-reducing grooves, oil reservoirs, and oil lines. There is a lack of research that considers lubrication theory and the flow characteristics of lubricating oil near the friction surfaces. In actual operation, the friction surfaces between the rolling elements and the cage of rolling bearings exhibit distinct oil film convergence and divergence zones. This leads to phenomena such as compression jetting and oil film cavitation, limiting oil film heat dissipation efficiency and stability. The flow of lubricating oil on the friction surfaces is not efficiently organized. Existing technologies, by simply adding oil reservoirs, weight-reducing grooves, and oil lines, cannot sufficiently reduce the compression jetting and oil film 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 lubricating oil flow near the friction surfaces.

[0005] The current design of lubrication structure for rolling bearing cages has the following limitations: (1) Existing designs reduce the friction of the friction surface by opening weight-reducing grooves or reducing the contact area, but cannot fundamentally affect the flow characteristics of lubricating oil on the friction surface between the rolling elements and the cage; (2) Although existing designs can improve the oil supply capacity of rolling bearings, they cannot effectively solve the problems of extrusion and oil film cavitation on the friction surface, and the lubricating oil cannot effectively enter the friction surface, thus greatly limiting its optimization effect; (3) Existing designs mainly optimize the lubrication effect by adding oil reservoirs, oil lines and other structures, but it is difficult to solve the defects of lubricating oil flow characteristics on the friction surface between the rolling elements and the cage. Summary of the Invention

[0006] This invention provides a bearing cage with a slotted cavity. The slotted cavity enables a stable and self-enhancing effect of lubricating oil flow near the friction surface, effectively reducing the squeezing and cavitation of the oil film near the friction surface between the rolling elements and the cage. This results in more efficient organization of the lubricating oil near the friction surface, reducing frictional resistance and wear, improving the bearing's heat dissipation capacity, and collecting bearing debris through the slotted cavity. This prevents the debris from entering the contact area of ​​the friction surface during flow, thus avoiding more severe wear problems in the bearing.

[0007] To achieve the above objectives, the present invention adopts the following specific technical solution:

[0008] A bearing cage having a slotted cavity, the bearing cage comprising an annular cage body;

[0009] The cage body has multiple pockets evenly distributed circumferentially to accommodate rolling elements, and a crossbeam is provided between adjacent pockets;

[0010] Each of the two side surfaces of each crossbeam forms a convergence zone and a divergence zone of the lubricating oil film between itself and the rolling element; each crossbeam is provided with two slotted through cavities that are radially spaced along the cage body.

[0011] One slotted cavity connects the convergence zone on one side of the beam with the divergence zone on the other side, and the other slotted cavity connects the divergence zone on one side of the beam with the convergence zone on the other side.

[0012] The pressure difference generated by the hydrodynamic effect and cavitation phenomenon drives the lubricating oil to flow from the convergence zone on one side of the crossbeam to the divergence zone on the other side of the crossbeam through a slotted cavity, and from the convergence zone on the other side of the crossbeam to the divergence zone on one side of the crossbeam through another slotted cavity, thereby reducing the squeezing and splashing between the rolling elements and the crossbeam and the degree of oil film cavitation.

[0013] Furthermore, two slotted cavities are symmetrically distributed on both sides of the centerline of the contact area between the rolling element and the beam.

[0014] Furthermore, based on the principles of hydrodynamic lubrication and Hertz contact theory, the radial width of the slotted cavity and the distance between the slotted cavity and the centerline of the contact area satisfy the following equation:

[0015] a = 1.0w - 5.0w;

[0016] b>1.0w;

[0017] In the above formula, a is the radial width of the slotted cavity; b is the shortest distance between the slotted cavity and the centerline of the contact area; and w is the nominal half-width of the contact area between the rolling element and the cage.

[0018] Furthermore, the axial width of the slotted cavity is less than or equal to the axial width of the pocket.

[0019] Furthermore, when the rolling element is a roller, the cross-sectional shape of the slotted cavity is elongated.

[0020] Furthermore, when the rolling element is a ball, the cross-sectional shape of the slotted cavity is shaped like a date pit.

[0021] Compared with the prior art, the technical solution of the present invention has the following beneficial effects:

[0022] 1. Based on lubrication theory, the bearing cage of this invention forms an oil film convergence zone and a divergence zone sequentially between the friction surfaces of the rolling elements and the cage along the rotation direction of the rolling elements. A slotted cavity is provided on the guide beam, distributed between the oil film convergence and divergence zones on the friction surfaces of the rolling elements and the guide beam. This slotted cavity 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 enhances the flow of lubricating oil from the convergence zone to the divergence zone, allowing the lubricating oil to transfer between the oil film convergence and divergence zones on both sides of the guide beam. This achieves a stable, self-enhancing effect of lubricating oil flow near the friction surfaces, resulting in more efficient organization of the lubricating oil near the friction surfaces. It effectively reduces the squeezing and cavitation degree of the oil film near the friction surfaces between the rolling elements and the cage, effectively utilizing squeezing and cavitation to alleviate oil film cavitation, reducing frictional resistance and wear, improving the lubricating oil reserve and heat exchange efficiency of the friction surfaces, and enhancing the bearing's heat dissipation capacity. It can be widely applied to rolling bearings with a rolling element and cage structure.

[0023] 2. The bearing cage of the present invention can effectively collect the squeezed and gushing lubricating oil through the slotted cavity provided in the beam. Driven by the pressure gradient, the lubricating oil flows stably from the oil film convergence zone to the divergence zone through the slotted cavity. Compared with the traditional design, it can store and provide more lubricating oil for the friction surface and remove the heat of the related structure.

[0024] 3. The bearing cage of the present invention, by creating a driving pressure difference through slotted cavities distributed in the oil film convergence and divergence zones on both sides of the guide beam, can actively collect the wear debris generated during bearing operation, preventing it from entering the friction surfaces of the rolling elements and the cage. The extruded flow contains wear debris, and the slotted cavities can guide the extruded flow from the oil film convergence zone on one side of the guide beam to the oil film divergence zone on the other side, preventing wear debris from entering the contact area of ​​the friction surfaces during flow and causing more severe bearing wear.

[0025] 4. The bearing cage of the present invention has wide applicability to rolling bearings and is mainly used to reduce the frictional resistance and wear of the friction surfaces between the rolling elements and the bearing cage; by utilizing the driving pressure difference, it can also collect the extruded flow near the friction surface and use it to reduce the degree of cavitation. Attached Figure Description

[0026] Figure 1 This is a three-dimensional structural diagram of the bearing cage of the present invention;

[0027] Figure 2 A half-sectional schematic diagram of a rolling bearing having the bearing cage of the present invention;

[0028] Figure 3This is a schematic diagram of a slotted cavity structure of the bearing cage of the present invention;

[0029] Figure 4 This is a schematic diagram of another slotted cavity structure of the bearing cage of the present invention;

[0030] Figure 5 This is a schematic diagram illustrating the convergence and divergence zones between the rolling element and the beam.

[0031] Reference numerals: 1-Bearing cage; 2-Beam; 3-Groove cavity; 4-Rolling element; 5-Bearing inner ring; 6-Bearing outer ring. Detailed Implementation

[0032] 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.

[0033] The present invention aims to solve the following three technical problems:

[0034] 1. Traditional cages cannot improve the flow characteristics of lubricating oil: Existing cage designs only reduce friction by reducing the contact area or increasing the oil storage space, but cannot fundamentally change the flow characteristics of lubricating oil near the friction surface between the rolling element 4 and the bearing cage 1. This results in the lubricating oil not being efficiently organized, and the problems of friction resistance and wear are not fundamentally solved.

[0035] 2. Difficulty in overcoming dynamic defects of oil film: Although the existing design improves the oil supply capacity, it cannot effectively reduce the squeezing and cavitation of oil film caused by the 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.

[0036] 3. Wear debris accumulation and insufficient heat dissipation: Traditional methods do not optimize the flow path based on the lubrication principle and cannot actively use pressure difference to 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.

[0037] The bearing cage 1 of this invention reduces friction and wear based on hydrodynamic lubrication theory. Through a slotted cavity 3 at the crossbeam 2 connecting the oil film convergence and divergence zones, 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 cage's pocket clearance forms a gradually decreasing convergence zone and a gradually increasing divergence zone along the direction of motion. In traditional designs, the high pressure in the convergence zone squeezes the lubricating oil, causing leakage losses, while the low pressure in the divergence zone triggers oil film cavitation and rupture, leading to cavitation erosion.

[0038] The working principle of the bearing cage 1 of the present invention is as follows: Based on the oil film flow characteristics of the friction surface, through the slotted cavity 3 set in the beam 2, the high-pressure lubricating oil in the convergence zone on one side of the beam 2 actively flows through the slotted cavity 3 to the low-pressure divergence zone on the other side of the beam 2 under the pressure difference drive, realizing three synergistic effects: First, it transforms the traditionally squeezed harmful jet into lubricating resources. The slotted cavity 3 collects the lubricating oil overflowing from the convergence zone and transports it to the divergence 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 cavity 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 realizes the active removal of wear debris. Wear particles in the squeezed jet are guided away from the contact area with the lubricating oil through the slotted cavity 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.

[0039] The working principle of the bearing cage 1 is essentially to dynamically couple the traditionally separated convergence and divergence regions through structural innovation, and to spontaneously adjust the redistribution of lubricating oil by utilizing pressure difference, thereby comprehensively solving the problems of extrusion loss, cavitation fracture and wear debris retention, and achieving systematic optimization of tribological performance.

[0040] This invention provides a bearing cage 1 with a slotted cavity 3, such as... Figure 2 As shown, taking a rolling bearing as an example, the rolling bearing includes an inner ring 5 and an outer ring 6 arranged radially at intervals, a bearing cage 1 installed between the inner ring 5 and the outer ring 6, and rolling elements 4 installed in the bearing cage 1 and rolling between the inner ring 5 and the outer ring 6. The bearing cage 1 is used to separate and limit the rolling elements 4, and the rolling friction between the inner ring 5 and the outer ring 6 is achieved by the rolling of the rolling elements 4.

[0041] like Figure 1 As shown in the structure, the bearing cage 1 includes an annular cage body; the cage body has a plurality of pockets evenly distributed circumferentially for accommodating the rolling elements 4, and a crossbeam 2 is provided between adjacent pockets to separate the pockets.

[0042] Along the rotation direction of the rolling element 4, the two side surfaces of each beam 2 sequentially form a convergence zone and a divergence zone of the lubricating oil film between themselves and the rolling element 4; Reference Figure 5 Taking the rolling element 4 and one side surface of the crossbeam 2 in the bearing cage 1 as an example, when the rolling element 4 rotates at an angular velocity ω in the direction indicated by the arrow, the convergence region and divergence region are defined as the changing trend of the cavity formed between the outer surface of the rolling element 4 and one side surface of the crossbeam 2 along the rotor rotation direction: the outer surface of the rolling element 4 and one side surface of the crossbeam 2 form a cavity due to the difference in curvature. The characteristic of this cavity is that it changes with the rotation direction of the rolling element 4 ( Figure 5 (Taking 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 convergence zone. The oil film pressure P in the convergence zone gradually increases, squeezing out some lubricating oil and forming 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 divergence zone. The oil film pressure P in the divergence zone gradually decreases, causing the oil film to rupture and form cavitation. It must be pointed out that the definitions of the convergence zone and the 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 diagram is rotated clockwise, the positions of the convergence and divergence regions are reversed compared to the diagram.

[0043] During the rolling process of the rolling element 4, the crossbeam 2 forms a convergence zone and a divergence zone with the rolling element 4 on both sides facing the rolling element 4. Furthermore, since all the rolling elements 4 rotate in the same direction, a [missing information - likely a specific region or area] is formed on one side of the crossbeam 2. Figure 5 When the convergence and divergence regions are shown, a region is formed on the other side of the lintel 2 that is similar to... Figure 5 The converging and diverging regions are arranged in opposite directions. That is, the converging region on one side of the beam 2 and the diverging region on the other side of the beam 2 are arranged opposite to each other along the radial direction of the bearing. At the same time, the diverging region on one side of the beam 2 and the converging region on the other side of the beam 2 are arranged opposite to each other along 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 a converging region and a diverging region with the rolling element 4 on both the first side surface and the second side surface. Along the radial direction of the bearing, if the converging region of the first side surface is close to the outer ring 6 of the bearing, then the diverging region of the first side surface is close to the inner ring 5 of the bearing, and the converging region of the second side surface is close to the inner ring 5 of the bearing, and the diverging region of the second side surface is close to the outer ring 6 of the bearing.

[0044] like Figure 1As shown, each lintel 2 is provided with two slotted cavities 3 distributed radially along the cage body; one slotted cavity 3 connects the convergent region on one side of the lintel 2 with the divergent region on the other side, and the other slotted cavity 3 connects the divergent region on one side of the lintel 2 with the convergent region on the other side. That is, the two slotted cavities 3 provided on the lintel 2 connect the opposite convergent and divergent regions on both sides of the lintel 2 respectively. Figure 2 As shown, each guide beam 2 is provided with two slotted cavities 3, namely a first slotted cavity 3 near the outer ring 6 of the bearing and a second slotted cavity 3 near the inner ring. Assuming that the rolling element 4 and the first side surface of the guide beam 2 form a convergence zone near the outer ring 6 of the bearing, the rolling element 4 and the first side surface of the guide beam 2 form a divergence zone near the inner ring 5 of the bearing, the rolling element 4 and the second side surface of the guide beam 2 form a divergence zone near the outer ring 6 of the bearing, and the rolling element 4 and the second side surface of the guide beam 2 form a convergence zone near the inner ring 5 of the bearing. The first slotted cavity 3 connects the convergence zone of the first side surface and the divergence zone of the second side surface, and the second slotted cavity 3 connects the divergence zone of the first side surface and the convergence zone of the second side surface.

[0045] Because two slotted cavities 3 are provided on the crossbeam 2, the pressure difference formed by the hydrodynamic effect and cavitation phenomenon drives the lubricating oil to flow from the convergence zone on one side of the crossbeam 2 to the divergence zone on the other side of the crossbeam 2 through one slotted cavity 3, and from the convergence zone on the other side of the crossbeam 2 to the divergence zone on one side of the crossbeam 2 through the other slotted cavity 3, thereby reducing the squeezing and splashing between the rolling element 4 and the crossbeam 2 and the degree of oil film cavitation.

[0046] Based on lubrication theory, the bearing cage 1 described above forms an oil film convergence zone and a divergence zone sequentially between the friction surfaces of the rolling element 4 and the cage along the rotation direction of the rolling element 4. A slotted cavity 3 is provided on the guide beam 2, distributed between the oil film convergence and divergence zones on the friction surfaces of the rolling element 4 and the guide beam 2. The slotted cavity 3 connects the corresponding oil film convergence and divergence zones on both sides of the guide beam 2. The pressure difference created by the hydrodynamic effect and cavitation enhances the flow of lubricating oil from the convergence zone to the divergence zone, allowing the lubricating oil to flow smoothly across the friction surfaces on both sides of the guide beam 2. The transfer between the oil film convergence zone and the oil film divergence zone on the surface achieves a stable self-enhancing effect of lubricating oil flow near the friction surface, resulting in more efficient organization of 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.

[0047] In the aforementioned bearing cage 1, as Figure 3 and Figure 4 As shown, two slotted cavities 3 are symmetrically distributed on both sides of the centerline s of the contact area between the rolling element 4 and the crossbeam 2. The axial width of the slotted cavity 3 is less than or equal to the axial width of the pocket. Both the axial width of the slotted cavity 3 and the axial width of the pocket are widths along the axial direction of the bearing cage 1. When the rolling element 4 is a roller, the cross-sectional shape of the slotted cavity 3 is elongated, as shown in the figure. Figure 3 As shown. When the rolling element 4 is a ball, the cross-sectional shape of the slotted cavity 3 is shaped like a date pit, as shown. Figure 4 As shown. According to the principle of hydrodynamic lubrication and Hertz contact theory, the radial width of the slotted cavity 3 and the distance between the slotted cavity 3 and the centerline of the contact area satisfy the following equation:

[0048] a = 1.0w - 5.0w;

[0049] b>1.0w;

[0050] In the above formula, a is the radial width of the slotted cavity 3; b is the shortest distance between the slotted cavity 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 slotted cavity 3 is the width of the slotted cavity 3 along the radial direction of the bearing cage 1.

[0051] To provide an effective driving pressure difference and achieve more effective wear and drag reduction, the radial width 'a' of the slotted cavity 3 and the shortest distance 'b' between the slotted cavity 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 slotted cavity 3 and the distance between the slotted cavity 3 and the centerline of the contact area, the changes in the width of the convergence and divergence zones caused by different local velocities can be balanced, thus more effectively utilizing the driving pressure difference generated by the dynamic pressure effect.

[0052] The slotted cavity 3 structure design adopted by the bearing cage 1 breaks through the passive oil storage concept of traditional oil storage tanks or weight reduction tanks. A through cavity is set in the key area of ​​the cage beam 2. Through the hydrodynamic pressure effect, a directional pressure difference driving mechanism from the convergence zone to the divergence zone is actively constructed to realize the self-reinforcing transfer of lubricating oil from the high pressure zone to the low pressure zone, and the oil film flow characteristics of the friction surface are fundamentally reconstructed.

[0053] The aforementioned bearing cage 1 can dynamically and collaboratively regulate oil film defects. By utilizing the connectivity of the cavity, it transforms the traditionally harmful extrusion flow into lubricating resources. The cavity collects the lubricating oil extruded from the convergence zone and directs it to the 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.

[0054] The aforementioned bearing cage 1 achieves multi-functional integrated active management. The cavity serves both as a wear debris collection point and an enhanced heat exchanger. Under differential pressure, the flow containing wear debris is directed away from the friction contact area through the cavity, preventing abrasive wear. Furthermore, the continuously flowing lubricating oil enhances the heat dissipation efficiency of the friction surface, thereby improving bearing reliability from both wear control and thermal management perspectives.

[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 bearing cage having a slotted cavity, characterized in that, Includes a circular cage body; The cage body has multiple pockets evenly distributed circumferentially to accommodate rolling elements, and a crossbeam is provided between adjacent pockets; Each of the two side surfaces of each crossbeam forms a convergence zone and a divergence zone of the lubricating oil film between itself and the rolling element; each crossbeam is provided with two slotted through cavities that are radially spaced along the cage body; One slotted cavity connects the convergence zone on one side of the beam with the divergence zone on the other side, and the other slotted cavity connects the divergence zone on one side of the beam with the 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 convergence zone on one side of the crossbeam to the divergence zone on the other side of the crossbeam through a slotted cavity, and from the convergence zone on the other side of the crossbeam to the divergence zone on one side of the crossbeam through another slotted cavity, thereby reducing the squeezing and splashing between the rolling elements and the crossbeam and the degree of oil film cavitation.

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

3. The bearing cage as described in claim 2, characterized in that, According to the principles of hydrodynamic lubrication and Hertz contact theory, the radial width of the slotted cavity and the distance between the slotted cavity and the centerline of the contact area satisfy the following equation: a = 1.0w - 5.0w; b>1.0w; In the above formula, a is the radial width of the slotted cavity; b is the shortest distance between the slotted cavity 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 bearing cage as described in claim 1, characterized in that, The axial width of the slotted cavity is less than or equal to the axial width of the pocket.

5. The bearing cage as described in any one of claims 1-4, characterized in that, When the rolling element is a roller, the cross-sectional shape of the slotted cavity is elongated.

6. The bearing cage as described in any one of claims 1-4, characterized in that, When the rolling element is a ball, the cross-sectional shape of the slotted cavity is shaped like a date pit.

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