A method of processing a bearing to resist micromotion damage

Abstract

The application discloses a processing method of a bearing with anti-fretting damage, and belongs to the technical field of bearings. The bearing comprises rollers and raceways, and comprises the following steps: 1) the bearing rollers are designed as hollow rollers, and the geometric sizes of the rollers are obtained through three-dimensional simulation optimization of mathematical models and physical models; 2) special surface heat treatment is performed on the rollers, and the smoothness of the roller contact surface is improved through grinding; 3) a sliding parallel liquid film mixed point array liquid film rolling group composite physical model about the working motion of the bearing rollers with oil storage pits and the raceways is established, an optimal physical model and an optimal mathematical model about continuous and stable lubrication of the point array rolling liquid film group about the arrangement of the oil storage pit point array are established, and the arrangement and size of the oil storage pits on the surface of the bearing rollers are optimized; and 4) special surface heat treatment is performed on the raceways of the inner ring and the outer ring of the bearing. The bearing rollers and the bearing raceways are optimized and improved, the anti-fretting damage capacity of the bearing, the limit rotating speed of the bearing and the service life of the bearing are improved.

Description

Technical Field

[0001] This invention relates to the field of bearing technology, and more specifically to a method for processing bearings resistant to fretting damage. Background Technology

[0002] Bearings in gear transmission devices that experience frequent starts and stops, unstable operation, poor bearing bore concentricity, or over-alignment of bearings, such as those in wind turbine gearboxes and marine gearboxes, often exhibit early fretting damage during early operation, severely impacting the service life of the entire gear transmission device. For instance, some well-designed and manufactured marine gearboxes can last their entire design life, or even longer; however, some marine gearboxes require major overhauls after only 2 to 3 years, and some even less.

[0003] Fretting damage in multi-bearing support shaft systems: Bearings in shaft systems with statically indeterminate arrangements, such as those in certain gearboxes and marine stern shaft bearings, GWC high-power marine gearbox clutch component bearings, and certain industrial gearboxes. Fretting damage caused by uneven loading of bearings (rolling bearings and sliding bearings): Fretting damage in tapered roller bearings and cylindrical roller bearings is caused by excessive coaxiality between bearing bores.

[0004] To solve this problem, in addition to avoiding it in the overall design, improvements also need to be made to the bearing itself, and innovations need to be made in the bearing rollers and bearing raceways. Summary of the Invention

[0005] To address the aforementioned problems in the prior art, this invention provides a method for processing bearings resistant to fretting damage, which optimizes and improves the bearing rollers and raceways to enhance the bearing's resistance to fretting damage.

[0006] The technical solution of the present invention is as follows: A method for processing a bearing resistant to fretting damage, comprising rollers and raceways, including the following steps: 1) The bearing rollers are designed as hollow rollers, and the geometric dimensions of the rollers are obtained after three-dimensional simulation optimization through mathematical model I and physical model I; 2) The rollers undergo surface heat treatment, and the smoothness of the roller contact surface is improved by grinding; 3) A physical model and a mathematical model of the oil storage pits are established to optimize the oil storage pits on the surface of the bearing rollers; 4) Crossed oil storage pits are evenly distributed on the surface of the bearing rollers, and laser pitting is used; 5) The raceways of the inner and outer rings of the bearing undergo surface heat treatment.

[0007] The roller surface heat treatment process includes three methods: surface carburizing, surface nitriding, or surface carbonitriding. Among them, carburizing and carbonitriding require quenching treatment, followed by grinding of the bearing roller surface.

[0008] The bearing raceway heat treatment process is as follows: the bearing inner and outer ring raceways are subjected to one of four heat treatment or surface engineering methods, namely surface nitriding, surface carburizing, surface carbonitriding, and surface spraying of ceramic materials. Among them, carburizing and carbonitriding require quenching treatment, and then the bearing inner and outer ring raceways are ground.

[0009] The roller is a cylindrical roller, a tapered roller, or a self-aligning roller.

[0010] A physical model of the hollow roller is established, and the geometric dimensions of the roller are optimized: the bearing roller is designed to be hollow in the middle, which increases the bearing elasticity, reduces the elastic modulus E of the bearing roller, optimizes the optimal inner diameter d1, reduces the impact of the bearing roller, reduces fretting damage, reduces the clearance between the roller and the raceway, reduces bearing roller slippage, and lowers the overall temperature of the roller. The hollow center increases the surface cooling area, lowers the overall temperature, and increases the limiting speed. The cooling area M increases, the temperature drop ΔT increases, and the limiting speed increases.

[0011] A mathematical model of the hollow roller was established, and the outer diameter and inner diameter of the hollow roller were optimized.

[0012]

[0013] Maximum compression of bearing rollers: Δd2;

[0014] The amount of cooling oil entering the rolling bearing: Q;

[0015] Minimum amount of cooling oil entering the rolling bearing: Q1;

[0016] Maximum cooling oil flow rate into the rolling bearing: Q2;

[0017] Let the inner diameter of the roller be d1;

[0018] Let the outer diameter of the roller be d2;

[0019] Roller outer diameter after deformation under stress: ;

[0020] Total surface area of ​​rollers ;

[0021] Heat exchange coefficient: C;

[0022] Temperature drop value: ΔT;

[0023] The maximum force of a solid roller: F m .

[0024] Establish a lattice model of the oil storage pits on the bearing rollers and optimize the arrangement of the oil storage pits: when the oil storage pits are arranged in a cross pattern, the lattice arrangement is the intersection of equidistant spiral lines and equidistant lines parallel to the end face of the rollers.

[0025] A physical model of the roller raceway motion is established, and the dimensions of the oil reservoir are optimized: During bearing operation, the bearing rollers roll, and at the contact point between the bearing rollers and the inner and outer ring raceways, the contact point undergoes elastic deformation, generating a narrow band of high-pressure oil film with a width of H. This narrow band of high-pressure oil film is a non-Newtonian fluid and can be considered as a rolling, elongated plane. Besides the oil inlet at the meshing point, the oil outlet at the contact point and the two roller ends with a width of B generate sealing bulges, forming a high-pressure sealed space. The oil film thickness between the rollers and the raceway is h. min The thickness of the oil film between the sealing convex points is h. mint ;

[0026] The depth of the oil pit is K when the oil is not in operation, and K is the depth of the oil pit when the oil is in operation. t Assuming the surface diameter d of the oil storage pit remains constant in both the non-working and working states, the compression amount of the oil storage pit during operation... The amount of overflowing lubricating oil The increased amount of lubricating oil on the roller surface, i.e., the increased oil film volume, reduces the coefficient of friction μ. The roller surface has numerous oil pits, and the increased surface lubricating oil reduces the friction between the roller and the raceway, thus reducing fretting damage.

[0027] A mathematical model of the oil-collecting pit lattice on the roller surface was established, and the arrangement of the oil-collecting pits was optimized.

[0028]

[0029] Roller length: B;

[0030] Contact width between the roller and the raceway: H;

[0031] Contact area between the roller and the raceway: S;

[0032] The diameter of the oil storage pit is d;

[0033] Depth of oil pit in non-working state: K;

[0034] Depth of the oil reservoir after compression: K t ;

[0035] Compression height of the oil storage pit during operation: ; ;

[0036] The amount of lubricating oil spilled (i.e., the increase in oil film volume): ;

[0037] Total amount of overflowed lubricating oil (i.e., the total increase in oil film volume): ;

[0038] Number of oil-filled pits within the contact area: n;

[0039] Oil storage pit area ratio: Ψ;

[0040] Oil storage pit arrangement helix angle: β;

[0041] Oil storage pit distribution pitch: t;

[0042] Oil storage pit spacing: x;

[0043] Raceway friction coefficient: μ.

[0044] The roller of this invention is a hollow roller, and physical and mathematical models have been established to optimize the roller size. Special heat treatment is applied to the roller surface and inner and outer raceways to improve the hardness and strength of the roller surface and raceway surface. A composite physical model of sliding parallel liquid film mixed lattice liquid film rolling agglomerate for the working motion of the roller and raceway of the bearing with oil pits has been established. An optimal physical model and optimal mathematical model for continuous and stable lubrication of the lattice rolling liquid film for the arrangement of oil pits have also been established to optimize the arrangement and size of the oil pits on the roller surface, thereby improving the bearing's resistance to fretting damage, as well as the bearing's limiting speed and service life. Attached Figure Description

[0045] Figure 1 A flowchart illustrating the manufacturing process for bearing rollers;

[0046] Figure 2 A flowchart illustrating the manufacturing process of the inner and outer ring raceways of a bearing.

[0047] Figure 3 A schematic diagram of the cross-section of a rolling bearing (physical model I);

[0048] Figure 4 Schematic diagrams of three types of rollers (physical model I);

[0049] Figure 5 A schematic diagram of the deformation of a roller under stress (physical model I);

[0050] Figure 6 A schematic diagram of the roller oil reservoir lattice model (physical model II) (taking a cylindrical bearing as an example);

[0051] Figure 7 A partial schematic diagram of the bearing roller lubrication oil reservoir (physical model III) (taking a cylindrical bearing as an example);

[0052] Figure 8 A partial schematic diagram of the bearing roller lubrication oil reservoir (physical model III) (taking a cylindrical bearing as an example);

[0053] Figure 9 A partial schematic diagram of a carbonitriding oil storage pit roller (physical model III) (taking a cylindrical bearing as an example);

[0054] Figure 10A partial schematic diagram of a carbonitriding oil storage pit roller (physical model III) (taking a cylindrical bearing as an example). Detailed Implementation

[0055] The present invention will be further described below with reference to the accompanying drawings.

[0056] Based on existing cylindrical roller bearings, tapered roller bearings, and self-aligning roller bearings, the following methods can be used to address bearing fretting damage: a. Design the bearing rollers as hollow rollers to reduce roller stiffness, decrease impact force between the rollers and raceways, and increase the bearing's limiting speed; this also increases resistance to fretting damage. b. Increase the hardness and strength of the roller and raceway surfaces. Carburizing, nitriding, or carbonitriding can be applied to the roller surfaces. Carburizing and carbonitriding require quenching, and grinding can further improve the surface finish of the roller contact surfaces; this increases the limiting speed and reduces resistance to fretting damage. c. Improve the lubricity and load-bearing capacity of the roller and raceway surfaces. Increase the thickness of the lubricating oil film between the roller and raceway surfaces. Laser-drilled grooves are used to evenly distribute cross-shaped oil-retaining pits on the bearing roller surface. These uniformly distributed pits are suitable for repeated starts and starts. When the bearing is subjected to vibration, the elasticity of the oil-retaining pits causes lubricating oil to be squeezed out, increasing the volume of the oil film between the rollers and raceways. This improves lubrication of the bearing rollers and raceways, increases the limiting speed, and reduces resistance to fretting damage. d. Nitriding, carburizing, and carbonitriding (carburizing requires quenching) are applied to the inner and outer raceways, followed by spraying with ceramic materials (such as silicon carbide mirror coating) to increase the hardness and strength of the bearing raceway friction surface and resist fretting damage. e. Physical and mathematical models of the roller geometry and oil pits on the roller surface are established to optimize the roller geometry and the arrangement and size of the oil pits on the roller surface.

[0057] Mathematical Model I is established to optimize roller dimensions: For cylindrical roller bearings, tapered roller bearings, and self-aligning roller bearings, the bearing rollers are designed with a hollow center (see attached diagram). This increases bearing elasticity, reduces the elastic modulus E of the bearing rollers, optimizes the optimal inner diameter d1, reduces the impact on the bearing rollers, and minimizes fretting damage. It also reduces the clearance between the rollers and raceways, decreasing the possibility of roller slippage. Furthermore, it lowers the overall roller temperature; the hollow center increases the surface cooling area, thus lowering the overall temperature and increasing the limiting speed. An increased cooling area M leads to a larger temperature drop ΔT and a larger limiting speed. The inner diameter of the roller is related to the outer diameter and the load-bearing capacity. Under a given operating temperature (related to the limiting speed V), it can dissipate more heat. F represents the bearing load-bearing capacity, which is a vector number, F1, F2, ... F. m ...F n These represent the forces exerted by the bearing rollers on the inner ring of the bearing. Taking a cylindrical roller bearing as an example (see attached diagram), this can reduce fretting damage to the bearing.

[0058] The bearing roller surface is carburized and quenched or carbonitrided and quenched, or directly nitrided. Then it is ground according to the design requirements, and then oil pits are laser-cut on the surface. The roller is then placed in a fine abrasive grain and vibrated to remove the burrs and sharp corners of the roller surface after laser processing.

[0059] like Figure 1 As shown, the process flow for designing and manufacturing bearing rollers is as follows: The geometric dimensions of cylindrical rollers, tapered rollers, and self-aligning rollers are obtained through 3D simulation optimization using mathematical model I and physical model I. Rollers undergo three heat treatment methods: surface carburizing, surface nitriding, and carbonitriding. Surface carburizing and carbonitriding require quenching, followed by surface grinding. Then, the geometric arrangement and dimensions of the oil storage pits are optimized using mathematical model II, physical model II (through lattice optimization), and physical model III (through 3D simulation and fluid simulation). Finally, laser drilling and finishing are performed to eliminate the peaks after laser processing.

[0060] like Figure 2 As shown, the characteristics of the friction surfaces of the inner and outer raceways of the bearing are changed: (1) The bearing roller surface is nitrided, carburized, and carbonitrided, then quenched, and the bearing roller surface is ground; because the hardness of the alloy nitrided layer and the carburized layer is greater than that of bearing steel. (2) The inner and outer raceways are nitrided, carburized, and carbonitrided (carburizing requires quenching), and ceramic materials (such as silicon carbide mirror spraying) are sprayed to increase the hardness and strength of the bearing raceway friction surfaces, and the inner and outer raceways of the bearing are ground. This can reduce fretting damage.

[0061] Physical Model I (Hollow Roller Bearing Model):

[0062] like Figure 3 , Figure 4 , Figure 5 As shown, for cylindrical roller bearings, tapered roller bearings, and self-aligning roller bearings, the bearing rollers are designed with a hollow center (see attached diagram). This increases bearing elasticity, reduces the elastic modulus E of the bearing rollers, optimizes the inner bore diameter d1, reduces impact on the bearing rollers, and minimizes fretting damage. It also reduces the clearance between the rollers and raceways, decreasing the possibility of roller slippage. Furthermore, it lowers the overall roller temperature; the hollow center increases the surface cooling area, thus lowering the overall temperature and increasing the limiting speed. An increased cooling area M leads to a larger temperature drop ΔT and a larger limiting speed. The inner bore diameter of the roller is related to the outer diameter and the load-carrying capacity. Under a constant operating temperature (related to the limiting speed V), it can dissipate more heat. F represents the bearing load-carrying capacity, which is a vector number, F1, F2, ... F. m ...F n These represent the forces exerted by the bearing rollers on the inner ring of the bearing.

[0063] Physical Model II (Oil Pit Lattice Model):

[0064] like Figure 6 As shown, the bearing roller oil reservoir lattice model has the following arrangement: When the oil reservoirs are arranged in an intersecting (helix angle β) pattern, the oil reservoir spacing x and oil reservoir depth t have optimal values. The lattice arrangement (intersection of equidistant helical lines and equidistant lines parallel to the roller end face) is related to the uniformity and continuity of the oil reservoirs when the roller contacts the raceway. This optimizes the overall load-bearing, friction-reducing, and lubrication performance of the rolling bearing. It is also related to the width H of the contact point between the bearing roller and the raceway (calculated using the Hertzian stress formula).

[0065] Physical Model III (Roller Raceway Motion Model):

[0066] like Figure 7 , Figure 8 , Figure 9 , Figure 10 As shown, during bearing operation, the bearing rollers roll, and at the contact point between the bearing rollers and the raceways of the inner and outer rings, the contact point undergoes elastic deformation, generating a narrow band of high-pressure oil film with a width of H. This narrow band of high-pressure oil film is a non-Newtonian fluid and can be considered as a rolling, elongated plane. Except for the oil inlet at the contact point, the oil outlet at the contact point and the ends of the two rollers at width B form sealing bulges, creating a high-pressure, sealed space; the oil film thickness between the rollers and the raceways is h. min The thickness of the oil film between the sealing convex points is h. mint .

[0067] Because the bearing rollers have optimally arranged oil pits with specific diameters and depths, high-pressure oil accumulation points are generated during bearing operation. Through laser processing, tiny oil pits are distributed across the roller surface. As the rollers run, the mating surface deforms, forming a narrow, elongated plane. The depth of these tiny oil pits decreases, causing the lubricating oil to overflow. This generates high pressure within the lubricating oil, and the rolling of the bearing rollers produces a high-pressure oil film. Since this is a non-Newtonian fluid, it can be considered a rolling, elongated plane. A rotating, high-pressure oil mass is generated within the oil pit, which can be viewed as a rolling "steel ball." This improves the anti-galling and anti-pitting properties of the mating surface, especially during low-speed bearing operation.

[0068] The depth of the oil pit is K when the oil is not in operation, and K is the depth of the oil pit when the oil is in operation. t Assuming the surface diameter d of the oil storage pit remains constant in both the non-working and working states (the diameter of the oil storage pit is related to the diameter of the bearing rollers), the compression amount of the oil storage pit during operation... The amount of overflowing lubricating oil As the amount of lubricating oil on the roller surface increases, i.e., the oil film volume increases, the coefficient of friction μ decreases. The roller surface has numerous oil pits; increased surface lubrication reduces the friction between the roller and the raceway, thus minimizing fretting damage. During operation, the roller surface temperature decreases, which can improve the limiting speed.

[0069] Mathematical Model I:

[0070]

[0071] Maximum compression of bearing rollers: Δd2;

[0072] The amount of cooling oil entering the rolling bearing: Q;

[0073] Minimum amount of cooling oil entering the rolling bearing: Q1;

[0074] Maximum cooling oil flow rate into the rolling bearing: Q2;

[0075] Let the inner diameter of the roller be d1;

[0076] Let the outer diameter of the roller be d2;

[0077] Roller outer diameter after deformation under stress: ;

[0078] Total surface area of ​​rollers ;

[0079] Heat exchange coefficient: C;

[0080] Temperature drop value: ΔT;

[0081] The maximum force of a solid roller: F m .

[0082] Design, effectiveness, and mathematical model of oil reservoirs on bearing roller surfaces: Oil reservoirs are uniformly distributed on the surface of the rollers using methods such as laser processing, according to design requirements. The uniformly distributed oil reservoirs are suitable for repeated starts and vibrations of the bearing. The elasticity of the oil reservoirs causes lubricating oil to be squeezed out. This improves the lubrication of the bearing rollers and raceways, reduces fretting damage, increases bearing fatigue life, extends bearing service life, and improves the bearing's limiting speed.

[0083] The shape, density, size, and depth of the oil storage pits were determined. According to mathematical model II, the depth and spacing of the cylindrical micro-pit oil storage holes have a significant impact on the oil film pressure distribution, load-bearing capacity, and friction of the rolling bearing rollers. (e.g.) Figure 5 As shown). Oil storage pit arrangement: When oil storage pits are arranged in a cross (helix angle β) configuration, (as shown) Figure 6 As shown), the optimal values ​​for the oil pit spacing x and oil pit depth t are determined by the lattice arrangement (intersection of equidistant spirals and equidistant lines parallel to the roller end face). This is related to the uniformity and continuity of the oil pits when the roller contacts the raceway, thus optimizing the overall load-bearing capacity, friction reduction, and lubrication performance of the rolling bearing. It is also related to the width H of the contact point between the bearing roller and the raceway (calculated using the Hertzian stress formula).

[0084] The depth of the oil pit is K when the oil is not in operation, and K is the depth of the oil pit when the oil is in operation.t Assuming the surface diameter d of the oil storage pit remains constant in both the non-working and working states (the diameter of the oil storage pit is related to the diameter of the bearing rollers), the compression amount of the oil storage pit during operation... The amount of overflowing lubricating oil As the amount of lubricating oil on the roller surface increases, i.e., the oil film volume increases, the coefficient of friction μ decreases. The roller surface has numerous oil pits; increased surface lubrication reduces the friction between the roller and the raceway, thus minimizing fretting damage. During operation, the roller surface temperature decreases, which can improve the limiting speed.

[0085] Mathematical Model II:

[0086]

[0087] Roller length: B;

[0088] Contact width between the roller and the raceway: H;

[0089] Contact area between the roller and the raceway: S;

[0090] The diameter of the oil storage pit is d;

[0091] Depth of oil pit in non-working state: K;

[0092] Depth of the oil reservoir after compression: K t ;

[0093] Compression height of the oil storage pit during operation: ;

[0094] The amount of lubricating oil spilled (i.e., the increase in oil film volume): ;

[0095] Total amount of overflowed lubricating oil (i.e., the total increase in oil film volume): ;

[0096] Number of oil-filled pits within the contact area: n;

[0097] Oil storage pit area ratio: Ψ;

[0098] The helix angle of the oil storage pit arrangement is β; there is an optimal value, which is the minimum value of the raceway friction coefficient.

[0099] The pitch of the oil storage pit distribution is t; it is related to the uniformity and continuity of the oil storage holes during contact.

[0100] Oil pit spacing: x; there is an optimal value, which is the minimum value of the raceway friction coefficient, because it is related to the uniformity and continuity of the oil pits during contact;

[0101] Raceway friction coefficient: μ.

[0102] The roller of this invention is a hollow roller, and physical and mathematical models have been established to optimize the roller size. Special heat treatment is applied to the roller surface and inner and outer raceways to improve the hardness and strength of the roller surface and raceway surface. A composite physical model (physical model II, III) of the sliding parallel liquid film mixed lattice liquid film rolling agglomerate regarding the working motion of the roller and raceway of the bearing with oil pits has been established. An optimal physical model and optimal mathematical model (mathematical model II) for continuous and stable lubrication of the lattice rolling liquid film with oil pit lattice arrangement have been established. The arrangement and size of the oil pits on the roller surface have been optimized, which improves the bearing's resistance to fretting damage, as well as the bearing's limiting speed and service life.

Claims

1. A method for machining a bearing resistant to fretting damage, comprising roller machining and raceway machining, characterized in that: The process includes the following steps: 1) Designing the bearing rollers as hollow rollers, and obtaining the geometric dimensions of the rollers through three-dimensional simulation optimization using mathematical model I and physical model I; 2) Performing surface heat treatment on the rollers, and improving the smoothness of the roller contact surfaces through grinding; 3) Establishing physical and mathematical models of the oil storage pits, and optimizing the oil storage pits on the surface of the bearing rollers; 4) Distributing cross-shaped oil storage pits evenly on the surface of the bearing rollers using laser drilling; 5) Performing surface heat treatment on the raceways of the inner and outer rings of the bearing. A mathematical model of the hollow roller was established, and the outer diameter and inner diameter of the hollow roller were optimized. ； Maximum compression of bearing rollers: Δd2; The amount of cooling oil entering the rolling bearing: Q; Minimum amount of cooling oil entering the rolling bearing: Q1; Maximum cooling oil flow rate into the rolling bearing: Q2; Let the inner diameter of the roller be d1; Let the outer diameter of the roller be d2; Roller outer diameter after deformation under stress: ; Total surface area of ​​rollers ; Heat exchange coefficient: C; Temperature drop value: ΔT; The maximum force of a solid roller: F m ; Establish a lattice model of the oil storage pits on the bearing rollers and optimize the arrangement of the oil storage pits: when the oil storage pits are arranged in a cross pattern, the lattice arrangement is the intersection of equidistant spiral lines and equidistant lines parallel to the end face of the rollers. A physical model of the roller raceway motion is established, and the dimensions of the oil reservoir are optimized: During bearing operation, the bearing rollers roll, and at the contact point between the bearing rollers and the inner and outer ring raceways, the contact point undergoes elastic deformation, generating a narrow band of high-pressure oil film with a width of H. This narrow band of high-pressure oil film is a non-Newtonian fluid and can be considered as a rolling, elongated plane. Besides the oil inlet at the meshing point, the oil outlet at the contact point and the two roller ends with a width of B generate sealing bulges, forming a high-pressure sealed space. The oil film thickness between the rollers and the raceway is h. min The thickness of the oil film between the sealing convex points is h. mint ; The depth of the oil pit is K when the oil is not in operation, and K is the depth of the oil pit when the oil is in operation. t Assuming the surface diameter d of the oil storage pit remains constant in both the non-working and working states, the compression amount of the oil storage pit during operation... The amount of overflowing lubricating oil The amount of lubricating oil on the surface of the roller increases, that is, the oil film volume increases, the friction coefficient μ decreases, there are many oil pits on the surface of the roller, the surface lubricating oil increases, the friction between the roller and the raceway decreases, and the fretting damage is reduced. A mathematical model of the oil-collecting pit lattice on the roller surface was established, and the arrangement of the oil-collecting pits was optimized. ； Roller length: B; Contact width between the roller and the raceway: H; Contact area between the roller and the raceway: S; The diameter of the oil storage pit is d; Depth of oil pit in non-working state: K; Depth of the oil reservoir after compression: K t ; Compression height of the oil storage pit during operation: ; ; The amount of lubricating oil spilled (i.e., the increase in oil film volume): ; Total amount of overflowed lubricating oil (i.e., the total increase in oil film volume): ; Number of oil-filled pits within the contact area: n; Oil storage pit area ratio: Ψ; Oil storage pit arrangement helix angle: β; Oil storage pit distribution pitch: t; Oil storage pit spacing: x; Raceway friction coefficient: μ.

2. The method for processing a bearing resistant to fretting damage as described in claim 1, characterized in that: The roller surface heat treatment process includes three methods: surface carburizing, surface nitriding, or surface carbonitriding. Among them, carburizing and carbonitriding require quenching treatment, followed by grinding of the bearing roller surface.

3. The method for processing a bearing resistant to fretting damage as described in claim 1, characterized in that: The bearing raceway heat treatment process is as follows: the bearing inner and outer ring raceways are subjected to one of four heat treatment or surface engineering methods, namely surface nitriding, surface carburizing, surface carbonitriding, and surface spraying of ceramic materials. Among them, carburizing and carbonitriding require quenching treatment, and then the bearing inner and outer ring raceways are ground.

4. The method for processing a bearing resistant to fretting damage as described in claim 1, characterized in that: A physical model of the hollow roller is established, and the geometric dimensions of the roller are optimized: the bearing roller is designed to be hollow in the middle, which increases the bearing elasticity, reduces the elastic modulus E of the bearing roller, optimizes the optimal inner diameter d1, reduces the impact of the bearing roller, reduces fretting damage, reduces the clearance between the roller and the raceway, reduces bearing roller slippage, and lowers the overall temperature of the roller. The hollow center increases the surface cooling area, lowers the overall temperature, and increases the limiting speed. The cooling area M increases, the temperature drop ΔT increases, and the limiting speed increases.

5. The method for processing a bearing resistant to fretting damage as described in claim 1, characterized in that: The roller is a cylindrical roller, a tapered roller, or a self-aligning roller.

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