Micromotor deep groove ball bearing with high axial load capacity and its manufacturing process

Abstract

The invention discloses a micro-motor deep groove ball bearing with high axial bearing capacity, which is composed of an inner ring, an outer ring, a rolling body, a retaining ring and a cage; the outer surface of the inner ring and the inner surface of the outer ring are both provided with a raceway for rolling of the rolling body; the rolling body is arranged between the inner ring and the outer ring, the retaining ring is arranged in pairs and is located on both sides of the rolling body, and the two retaining rings are also located between the inner ring and the outer ring; the retaining ring is located outside the retaining ring and is also located between the inner ring and the outer ring; the nominal inner diameter of the bearing is 6-8mm, and the radial clearance is 26-29μm; the inner ring groove curvature radius coefficient is 0.508-0.513; the outer ring groove curvature radius coefficient is 0.528-0.523. The invention also discloses its preparation process: the inner ring is placed in the outer ring, the rolling body is placed between the inner ring and the outer ring and the rolling body is placed on the raceway; the retaining frame is pressed toward the rolling body from both inside and outside, and then the relatively arranged retaining frames are riveted and pressed by a riveting press. The invention increases radial play, reduces groove curvature radius coefficient, and improves the axial bearing capacity of the micromotor deep groove ball bearing.

Description

Technical Field

[0001] The invention relates to high-carbon chromium, carburized, medium-carbon, stainless, high-temperature bearing steel, and in particular to a micro-motor deep groove ball bearing with high axial load-bearing capacity and a preparation process thereof. Background Art

[0002] Micro motor, full name "micro electric motor", refers to a motor with a diameter less than 160mm or a rated power less than 750mW. Micro motors are often used in control systems or transmission mechanical loads to realize the detection, analytical calculation, amplification, execution or conversion of electromechanical signals or energy. Micro deep groove ball bearings refer to various types of bearings with metric series and outer diameter less than 9mm; inch series and outer diameter less than 9.525mm. The main materials are carbon steel, bearing steel, stainless steel, plastic, ceramic, etc. It is suitable for various industrial equipment, small rotary motors and other high speed and low noise fields, such as: office equipment, micro motors, instruments, etc.

[0003] The patent with the publication number CN212584127U: An open deep groove ball bearing for a round forest electric lawn mower, belonging to the field of bearing technology, includes an outer ring, an inner ring, a steel ball and a retainer, the inner side of the outer ring is provided with an outer ring groove, the inner side of the inner ring is provided with an inner ring groove, the depth of the outer ring groove and the inner ring groove are equal; the steel ball is assembled between the outer ring and the inner ring through the retainer; the depth of the outer ring groove and the inner ring groove is 0.590-0.600mm; the groove curvature radius of the outer ring is 2.16-2.20. The axial bearing capacity of the bearing is improved by setting parameters (the depth of the outer ring groove and the inner ring groove is 0.595mm, and the flange coefficient reaches 0.3).

[0004] Zhu Liang's paper "The Influence of Groove Curvature Radius Coefficient on the Load Capacity of Wind Turbine Bearings" published in Volume 38, Issue 4 of "Journal of Huazhong University of Science and Technology (Natural Science Edition)" in April 2010 mentioned that the bearing load capacity is the highest when the inner ring groove curvature radius coefficient is 0.52 and the outer ring groove curvature radius coefficient is 0.53; at the same time, it was found that "the original contact angle of the bearing after loading increases, the maximum equivalent stress of the inner and outer rings in the circumferential direction does not coincide with the nominal contact point, and the load is different, and the contact point position is also different. Yang Xiaowei's paper "The Influence of Groove Curvature Radius Coefficient fi (e) on the Load Capacity of Deep Groove and Angular Contact Ball Bearings" published in "Bearings" Issue 6 in 1995 mentioned that if deep groove and angular contact ball bearings are to be in good working condition, the difference between the groove curvature radius and the ball radius should be greater than 2%; the difference between the outer and inner ring groove curvature radii is about 0.02. When f→0.5, as the geometric fit between the groove and the ball increases, the contact stress will naturally decrease, so as verified, the corresponding rated static load and rated dynamic load will increase. However, the higher the fit, the longer the long semi-axis of the contact ellipse, which will lead to an increase in the differential sliding and spin sliding of the ball in the groove; and under the elastic fluid dynamic lubrication state, the friction force also increases with the increase of the contact area. And so on. Therefore, under the influence of the above-mentioned comprehensive negative effects, the actual bearing load capacity is impossible to increase, and may even decrease. So as those skilled in the art are well aware: in general, the smaller the groove curvature radius coefficient, that is, the smaller the curvature radius of the groove, the greater the load capacity of the bearing. But as the prior art "The influence of the groove curvature radius coefficient on the bearing capacity of wind power bearings" states, the improvement of the axial bearing capacity of deep groove ball bearings is still limited due to many factors. And the deep groove ball bearings on micromotors are more difficult to provide axial bearing capacity because they use miniature bearings. Summary of the invention

[0005] The purpose of the present invention is to overcome the defects in the prior art, provide a micromotor deep groove ball bearing with high axial load-bearing capacity, increase radial clearance, reduce the groove curvature radius coefficient, and improve the axial load-bearing capacity of the micromotor deep groove ball bearing.

[0006] To achieve the above purpose, the technical solution of the present invention is to design a micro motor deep groove ball bearing with high axial load-bearing capacity, which is composed of an inner ring, an outer ring, a rolling element, a retaining ring and a cage; the outer surface of the inner ring and the inner surface of the outer ring are both provided with a raceway for rolling of the rolling element;

[0007] The rolling body is arranged between the inner ring and the outer ring, the retaining frames are arranged in pairs and are located on both sides of the rolling body, and the two retaining frames are also located between the inner ring and the outer ring; the retaining ring is located outside the retaining frame and is also located between the inner ring and the outer ring;

[0008] The nominal inner diameter of the bearing is 6~8mm, and the radial clearance is 26~29μm; the inner ring groove curvature radius coefficient is 0.508~0.513; the outer ring groove curvature radius coefficient is 0.528~0.523. The two retainers are a retainer with rivets and a retainer without rivets; after assembly, the rivets are pressed with a riveting press, and the bearing is installed. Increasing the radial clearance and reducing the groove curvature radius coefficient, thereby improving the axial bearing capacity of the micromotor deep groove ball bearing; it is well known to those in the field that the radial clearance is: when there is no load, when one of the inner and outer rings is fixed, the other moves from one extreme position to another extreme position relative to the fixed ring in the radial direction; the groove curvature radius coefficient is the ratio of the groove curvature radius to the rolling element diameter. Due to the existence of radial clearance, the deep groove ball bearing will have an initial contact angle when it is initially installed, which is equivalent to an angular contact ball bearing with a small contact angle. The larger the contact angle, the greater the axial load it can withstand. If the bearing only bears axial load, in order to obtain a greater axial load capacity, you can consider increasing the radial clearance.

[0009] A further technical solution is to set an inner flange protruding toward the rolling body on the edge of the raceway, set a number of spaced spherical crown grooves on the edge of the inner flange, and fit a ball in the spherical crown groove; the height of the spherical crown groove is greater than the ball radius of the spherical crown groove. In the design of the raceway of the deep groove ball, the contact angle cannot be increased indefinitely. When the edge of the contact surface between the rolling body and the raceway is offset to the edge of the track, it is the limit of the axial load that can be sustained, that is, the contact area cannot exceed the raceway. If this limit is exceeded, the life of the bearing will drop sharply due to the reduction of the contact surface. The present application sets an inner flange protruding toward the rolling body on the edge of the raceway to prevent the rolling body from exceeding the raceway, and sets a number of spaced spherical crown grooves on the edge of the inner flange. Fit a ball in the spherical crown groove to avoid the problem that the rolling body is unable to roll (or rolls poorly) when the edge of the contact surface between the rolling body and the raceway is offset to the edge of the track, which also improves the axial bearing capacity of the deep groove ball bearing of the micro motor. In addition, the present application improves the deep groove ball bearing structurally to increase the axial bearing capacity, which is a clever change from the previous approach of improving the axial bearing capacity by setting parameters (baffle coefficient, groove curvature radius coefficient, groove depth, etc.).

[0010] A further technical solution is that a pair of oppositely arranged grooves are arranged on the rolling body; the center line of the two grooves is consistent with the diameter direction of the rolling body; the grooves are rectangular grooves; and the rolling body is a steel ball. The grooves are arranged on the rolling body to increase the degree of lubrication. Under the elastic fluid dynamic lubrication state, the friction force will increase with the increase of the contact area. Therefore, although the present application increases the contact angle, the friction force is increased to a certain extent. In order to reduce this effect, the grooves are arranged on the rolling body to avoid the increase of friction and ensure the degree of lubrication.

[0011] The present invention also provides a technical solution, which is a preparation process of a micro-motor deep groove ball bearing with high axial load-bearing capacity, which is composed of the following process steps performed in sequence:

[0012] S1: Place the inner ring in the outer ring, place the rolling element between the inner ring and the outer ring, and place the rolling element on the raceway;

[0013] S2: Press the cage toward the rolling element from both inside and outside, and then use a riveting press to rivet the cages that are arranged opposite to each other;

[0014] S3: Before installing the retaining ring, use a negative pressure pump and an air pump on both sides of the deep groove ball bearing to pump air and inhale air between the inner and outer rings of the deep groove ball bearing; after pumping air on one side and inhaling air on the other side for a period of time, install the retaining ring between the inner and outer rings. In this way, blow air between the inner and outer rings of the deep groove ball bearing before the safety retaining ring so that the dust, dirt, debris, etc. in the deep groove ball bearing can be cleaned up by the combined action of the air pump and the negative pressure pump, avoiding the failure of the micromotor deep groove ball bearing.

[0015] The advantages and beneficial effects of the present invention are: increasing radial clearance, reducing groove curvature radius coefficient, and improving the axial bearing capacity of the micro-motor deep groove ball bearing;

[0016] Due to the existence of radial clearance, deep groove ball bearings will have an initial contact angle when they are initially installed, which is equivalent to an angular contact ball bearing with a small contact angle. The larger the contact angle, the greater the axial load that can be sustained;

[0017] The present application arranges an inner flange protruding toward the rolling body on the edge of the raceway to prevent the rolling body from exceeding the raceway, and arranges a plurality of spaced spherical crown-shaped grooves on the edge of the inner flange, and fits balls in the spherical crown-shaped grooves to avoid the problem that the rolling body is unable to roll (or rolls poorly) due to the inner flange abutting against the edge of the contact surface between the rolling body and the raceway when the edge is offset to the track edge. This also improves the axial bearing capacity of the deep groove ball bearing of the micromotor.

[0018] In addition, the present application improves the deep groove ball bearing structurally to increase the axial bearing capacity, which is a clever change from the previous approach of improving the axial bearing capacity by setting parameters (baffle coefficient, groove curvature radius coefficient, groove depth, etc.).

[0019] Grooves are provided on the rolling element to increase the degree of lubrication. Under elastic fluid dynamic lubrication, friction will increase with the increase of contact area. Therefore, although the contact angle is increased in this application, the friction is increased to a certain extent. In order to reduce this effect, grooves are provided on the rolling element to avoid the increase of friction and ensure the degree of lubrication. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 Schematic diagram of a first embodiment of a micro-motor deep groove ball bearing with high axial load-bearing capacity according to the present invention;

[0021] Figure 2 yes Figure 1 CC section diagram;

[0022] Figure 3 yes Figure 2 An enlarged schematic diagram of the lower end;

[0023] Figure 4 yes Figure 1 The main view;

[0024] Figure 5 yes Figure 4 AA section view;

[0025] Figure 6 is a schematic diagram of a second embodiment of the present invention;

[0026] Figure 7 yes Figure 6 BB section diagram;

[0027] Figure 8 yes Figure 6 A partial schematic diagram of a vertical section parallel to the paper surface;

[0028] Fig. 9 yes Figure 8 The main view;

[0029] Fig.10 yes Fig. 9 A magnified schematic diagram of part A;

[0030] Fig.11 is a partial cross-sectional view of the third embodiment of the present invention;

[0031] Fig.12 yes Fig.11 Schematic diagram of the state after the rubber plug blocks the air inlet and outlet when the medium negative pressure pump stops pumping air;

[0032] Fig.13 is an enlarged schematic diagram of the lower end of the longitudinal section of the third embodiment of the present invention;

[0033] Fig.14 yes Fig.13 A front view of the end face of the middle retaining ring;

[0034] Fig.15 is a schematic diagram of a fourth embodiment of the present invention;

[0035] Fig.16 yes Fig.15 AA section view;

[0036] Fig.17 yes Fig.16 An enlarged schematic diagram of the right end after bearing axial load;

[0037] Fig.18 yes Fig.17 A partial enlarged schematic diagram of the middle arc channel and its nearby components;

[0038] Fig.19 yes Fig.18 An exploded schematic diagram of the middle arc-shaped component and the elastic sleeve;

[0039] Fig. 20 yes Fig.18 Schematic diagram of the state after no longer bearing axial load.

[0040] In the figure: 1. inner ring; 2. outer ring; 3. rolling element; 4. retaining ring; 5. raceway; 6. retaining frame; 7. inner flange; 8. ball; 9. groove; 10. annular airbag; 11. hard ring; 12. negative pressure pump; 13. air pump; 14. air inlet and outlet; 15. rubber plug; 16. second rubber plug; 17. arc channel; 18. arc component; 19. elastic sleeve. DETAILED DESCRIPTION

[0041] The specific implementation of the present invention is further described below in conjunction with the accompanying drawings and embodiments. The following embodiments are only used to more clearly illustrate the technical solution of the present invention, and cannot be used to limit the protection scope of the present invention.

[0042] Embodiment 1: Figures 1 to 5 As shown, the present invention is a micro-motor deep groove ball bearing with high axial bearing capacity, which is composed of an inner ring 1, an outer ring 2, a rolling element 3, a retaining ring 4 and a retaining frame 6; the outer surface of the inner ring 1 and the inner surface of the outer ring 2 are both provided with a raceway 5 for the rolling element 3 to roll; the rolling element is arranged between the inner ring 1 and the outer ring 2, the retaining frames 6 are arranged in pairs and are located on both sides of the rolling element, and the two retaining frames 6 are also located between the inner ring 1 and the outer ring; the retaining ring 4 is located outside the retaining frame and is also located between the inner ring and the outer ring; the nominal inner diameter of the bearing is 6~8mm, and the radial clearance is 26~29μm; the inner ring groove curvature radius coefficient is 0.508~0.513; the outer ring groove curvature radius coefficient is 0.528~0.523. The two retaining frames are a retaining frame with rivets and a retaining frame without rivets; after assembly, the rivets are pressed with a riveting press, and the bearing is installed.

[0043] Embodiment 2: The difference from Embodiment 1 is that Figures 6 to 10 As shown (for ease of illustration, Figure 8The deep groove ball bearing is properly tilted), and an inner flange 7 protruding toward the rolling element 3 is provided on the edge of the raceway 5 (the inner flange 7 has a certain thickness and the outer edge of the inner flange extends along the raceway 5, while the inner side is arranged inwardly relative to the raceway 5, one end of the inner side is arranged at a position close to the edge of the raceway 5 on the raceway 5, and the other end is arranged inwardly relative to the outer side, and the spherical crown groove is arranged between the outer side and the inner side), which can prevent the rolling element 3 from exceeding the raceway 5, and a plurality of spherical crown grooves arranged at intervals are arranged on the edge of the inner flange 7, and a ball 8 is adapted to be arranged in the spherical crown groove to avoid the problem that the rolling element 3 and the raceway 5 are pressed against the inner flange when the contact surface edge of the rolling element 3 and the raceway 5 is offset to the track side and the rolling element cannot roll (or rolls poorly); the height of the spherical crown groove is greater than the ball radius of the spherical crown groove. A pair of oppositely arranged grooves 9 are provided on the rolling element; the center line of the two grooves is consistent with the diameter direction of the rolling element; the groove 9 is in the shape of a rectangular groove; and the rolling element is a steel ball. Grooves are provided on the rolling element to increase the degree of lubrication. Under elastic fluid dynamic lubrication, friction will increase with the increase of contact area. Therefore, although the contact angle is increased in this application, the friction is increased to a certain extent. In order to reduce this effect, grooves are provided on the rolling element to avoid the increase of friction and ensure the degree of lubrication.

[0044] Embodiment 3: The difference from Embodiment 1 is that Figures 11 to 14 As shown ( Fig.11 1 is an enlarged schematic diagram of the upper end of the third embodiment of the present invention after longitudinal section; for the convenience of illustration, Fig.11 Fig.12The retaining ring in the figure does not specifically show the annular airbag and the hard ring), the retaining ring consists of an annular airbag 10 located in the middle and hard rings 11 located on the inner and outer sides of the annular airbag 10; the hard ring is fixedly connected to the annular airbag 10; a rubber ring is fixedly arranged on the inner side wall of the inner hard ring; a rubber ring is fixedly arranged on the outer side wall of the outer hard ring; an air inlet and outlet are arranged on the annular airbag 10, and an air intake pipe or an air suction pipe is arranged in conjunction with the air inlet and outlet. One of the two annular airbags is equipped with a negative pressure pump 12, and the other is equipped with an air pump 13. The negative pressure pump is connected to the air suction pipe. The pump 13 is connected to the air inlet pipe, and the air inlet pipe and the air suction pipe are connected to the air inlet and outlet respectively. The air pump inputs clean air; the air inlet and outlet are arranged on the outer surface of the annular airbag relative to the bearing; the annular airbag is also provided with an air inlet and outlet on the inner surface relative to the bearing; the air inlet and outlet on the inner surface and the air inlet and outlet 14 on the outer surface are arranged in a staggered manner (or a more preferred solution is: the line connecting the air inlet and outlet on the inner surface and the air inlet and outlet on the outer surface is located on a diameter of the bearing; in this way, the two are far enough; the annular airbag can be inflated and exhausted first during both the inflation and exhaust processes). When the annular airbag 10 is filled with air, the size of the retaining ring is slightly larger than the space between the inner ring and the outer ring; when the annular airbag is deflated, the size of the retaining ring is slightly smaller than the space between the inner ring 1 and the outer ring 2. A rubber plug 15 is provided on the air inlet and outlet of the outer surface of the annular airbag, and the rubber plug 15 is connected to the outer surface of the annular airbag 10 through a rubber rope; a second rubber plug 16 is provided on the air inlet and outlet of the inner surface of the annular airbag, and the second rubber plug 16 is fixedly connected to the inner side wall of the annular airbag close to the rolling body; the second rubber plug 16 is cylindrical, one end of the second rubber plug 16 is facing the air inlet and outlet 14 on the inner surface of the annular airbag, and the other end is fixedly connected to the inner side wall of the annular airbag 10 away from the steel ball (that is, the inner side wall of the annular airbag close to the outer surface of the bearing), and the corresponding position of the outer surface of the annular airbag 10 is protruded outward to facilitate manual operation of plugging and unplugging the second rubber plug 16 to achieve blocking or opening of the air inlet and outlet of the inner surface of the annular airbag from the outside of the annular airbag.

[0045] After the retaining frame is riveted, the retaining ring is installed while inflating (blowing) and exhausting air at the same time, so that the dust, dirt, debris, etc. in the deep groove ball bearing are removed by the combined action of the air pump and the negative pressure pump; the inflation process causes one annular airbag to expand appropriately, and the exhaust process causes the other relatively arranged annular airbag to deflate appropriately so that there is a gap between the inner ring and the retaining ring, and between the retaining ring and the outer ring, which is used to remove dust, dirt, debris, etc. After exhausting and inflating for a period of time, first operate the second rubber plug on the outside of the inflated annular airbag to block the air inlet and outlet of the inner surface of the annular airbag, and inflate it for a period of time so that the retaining ring is tightly against the inner ring and the outer ring; at this time, disconnect the suction pipe of the negative pressure pump from the air inlet and outlet of the outer surface of the annular airbag, and continue to face the retaining ring (but a little away from the retaining ring) to continue exhausting air, and operate the second rubber plug on the outside of the annular airbag to block the air inlet and outlet of the inner surface of the annular airbag (at this time, The annular airbag is in a deflated state), the air outlet of the negative pressure pump (the air outlet pipe of the negative pressure pump is provided with a filter screen or other filtering components known in the prior art that can filter and remove impurities in the air. There are many such filtering components in the prior art and they are not described in detail) is connected to the air inlet and outlet of the outer surface of the annular airbag to inflate the deflated annular airbag until the originally deflated annular airbag expands and tightly presses against the inner wall of the inner ring and the outer wall of the outer ring to seal the deep groove ball bearing, and then the negative pressure pump is closed to complete the installation of the deep groove ball bearing.

[0046] This reasonable installation can avoid the erosion of the micro motor deep groove ball bearing and prevent the failure of the deep groove ball bearing. About 40% of the failed miniature deep groove ball bearings are caused by dust, dirt, debris and corrosion. Contamination is usually caused by improper use and poor use environment, which can also cause torque and noise problems. Miniature bearing failure caused by environment and pollution is preventable, and the cause of such failure can be determined by simple visual observation. As long as it is used and installed properly, the erosion of miniature bearings is easy to avoid. The characteristic of erosion is that the indentation caused by impact load or improper installation is left on the raceway of the miniature bearing ring. Erosion usually occurs when the load exceeds the yield limit of the material. If the installation is incorrect so that a load crosses the miniature bearing ring, erosion will also occur. The indentation on the miniature bearing ring will also produce noise, vibration and additional torque.

[0047] Embodiment 4: The difference from Embodiment 1 is that Figures 15 to 20As shown, an arc-shaped channel 17 is arranged in the wall of the inner ring 1, one end of the arc-shaped channel 17 is located on the raceway 5, and the other end is located on the outer surface of the inner ring 1 (and located outside the edge of the raceway 5), an arc-shaped component 18 is arranged in the arc-shaped channel 17, and an elastic sleeve 19 is fixedly arranged at one end of the arc-shaped channel close to the rolling element 3, and the end of the arc-shaped component 18 close to the rolling element 3 passes through the middle of the elastic sleeve 19 and its side surface is fixedly connected to the inner side wall of the elastic sleeve 19, so that when the arc-shaped component 18 is squeezed by the rolling element 3 (that is, when the micro motor deep groove ball bearing is subjected to axial load, the rolling element is close to When the arc-shaped component 18 reaches the edge of the raceway, the elastic sleeve 19 is stretched. However, since the arc-shaped component 18 passes through the elastic sleeve and only a small part of the outer side surface is fixedly connected to the inner side wall of the elastic sleeve 19, the arc-shaped component 18 is squeezed by the rolling body, and the other end of the arc-shaped component abuts against the rolling body 3 from the outer surface of the inner ring 1, that is, the outer side of the edge of the raceway 5, and contacts the rolling body. When the micro motor deep groove ball bearing is subjected to axial load, the rolling body and the raceway form a similar angular contact bearing. The arc-shaped component is squeezed by the rolling body and extends from the outer side of the raceway edge to abut the rolling body, preventing the contact area between the rolling body and the raceway from exceeding the raceway. When the axial load is no longer applied, the arc-shaped component 18 is reset due to the elasticity of the elastic sleeve 19 and is therefore pulled to reset.

[0048] A similar structure is also provided on the outer ring 2: that is, an arc-shaped channel is also provided in the wall of the outer ring, one end of the arc-shaped channel is located on the raceway, and the other end is located on the outer surface of the outer ring (and located outside the edge of the raceway), an arc-shaped component is provided in the arc-shaped channel, and an elastic sleeve is fixedly provided at one end of the arc-shaped channel close to the rolling body, and the end of the arc-shaped component close to the rolling body passes through the middle of the elastic sleeve and its side surface is fixedly connected to the inner wall of the elastic sleeve, so that when the arc-shaped component is squeezed by the rolling body (that is, when the micro motor deep groove ball bearing is subjected to axial load, the rolling body is close to When the arc-shaped component reaches the edge of the raceway, the elastic sleeve is stretched. However, since the arc-shaped component passes through the elastic sleeve and only a small part of the outer side surface is fixedly connected to the inner wall of the elastic sleeve, the arc-shaped component is squeezed by the rolling body and the other end of the arc-shaped component contacts the rolling body from the outer surface of the outer ring, that is, the outer side of the raceway edge. When the micro motor deep groove ball bearing is subjected to axial load, the rolling body and the raceway form a similar angular contact bearing. The arc-shaped component is squeezed by the rolling body and extends from the outer side of the raceway edge to resist the rolling body, preventing the contact area between the rolling body and the raceway from exceeding the raceway. When it is no longer subjected to axial load, the arc-shaped component is pulled and reset due to the reset of the elastic sleeve.

[0049] The present application is designed to prevent the contact area between the rolling element and the raceway from exceeding the raceway. When the rolling element is about to exceed the raceway, the arc-shaped component automatically moves over to press against the rolling element, thereby avoiding the reduction of the contact surface and reducing the problem of a sharp decrease in the life of the bearing. In addition, the moving arc-shaped component plays a role in forcing the rolling element to return to its original position, thereby ensuring that the contact area between the rolling element and the raceway does not exceed the raceway at all times.

[0050] The above is only a preferred embodiment of the present invention. It should be pointed out that for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the technical principles of the present invention. These improvements and modifications should also be regarded as the scope of protection of the present invention.

Claims

1. Micromotor deep groove ball bearing with high axial load capacity, characterized by: It is composed of an inner ring, an outer ring, rolling elements, a retaining ring and a cage; the outer surface of the inner ring and the inner surface of the outer ring are both provided with raceways for rolling elements; The rolling body is arranged between the inner ring and the outer ring, the retaining frames are arranged in pairs and are located on both sides of the rolling body, and the two retaining frames are also located between the inner ring and the outer ring; the retaining ring is located outside the retaining frame and is also located between the inner ring and the outer ring; The bearing has a nominal inner diameter of 6-8 mm, a radial clearance of 26-29 μm, an inner ring groove curvature radius coefficient of 0.508-0.513, and an outer ring groove curvature radius coefficient of 0.528-0.

523. The retaining ring is composed of an annular airbag located in the middle and hard rings located on the inner and outer sides of the annular airbag; the hard ring is fixedly connected to the annular airbag; a rubber ring is fixedly arranged on the inner wall of the inner hard ring; a rubber ring is fixedly arranged on the outer wall of the outer hard ring; an air port is arranged on the outer surface of the two annular airbags relative to the bearing, and an air port is also arranged on the inner surface of each annular airbag relative to the bearing; the air port on the inner surface is staggered with the air port on the outer surface; an air inlet pipe is adapted to be arranged with the air port on the outer surface of one annular airbag, and an air suction pipe is adapted to be arranged with the air port on the outer surface of the other annular airbag, one of the two annular airbags is equipped with a negative pressure pump, and the other is equipped with an air pump, the negative pressure pump is connected to the suction pipe, and the air pump is connected to the air inlet pipe, and the air pump inputs clean air; the annular airbag is filled with air When the annular airbag is deflated, the size of the retaining ring is slightly larger than the space between the inner ring and the outer ring; when the annular airbag is deflated, the size of the retaining ring is slightly smaller than the space between the inner ring and the outer ring; a rubber plug is provided on the air port on the outer surface of the annular airbag, and the rubber plug is connected to the outer surface of the annular airbag through a rubber rope; a second rubber plug is provided on the air port on the inner surface of the annular airbag, and the second rubber plug is fixedly connected to the inner side wall of the annular airbag close to the rolling body; the second rubber plug is cylindrical, one end of the second rubber plug is directly facing the air port on the inner surface of the annular airbag, and the other end is fixedly connected to the inner side wall of the annular airbag away from the steel ball and close to the outer surface of the bearing, and the corresponding position on the outer surface of the annular airbag is protruding outward to facilitate manual operation of plugging and unplugging the second rubber plug to achieve blocking or opening of the air port on the inner surface of the annular airbag from the outside of the annular airbag; An inner flange protruding toward the rolling body is arranged at the edge of the raceway, and a plurality of spaced spherical crown-shaped grooves are arranged at the edge of the inner flange. Balls are adapted to be arranged in the spherical crown-shaped grooves. The height of the spherical crown-shaped grooves is greater than the ball radius of the spherical crown-shaped grooves.

2. The micromotor deep groove ball bearing with high axial load capacity according to claim 1, characterized in that: The rolling body is provided with a pair of grooves arranged opposite to each other; the center line of the two grooves is consistent with the diameter direction of the rolling body; the grooves are rectangular groove-shaped; and the rolling body is a steel ball.

3. A process for preparing a micromotor deep groove ball bearing with high axial load-bearing capacity, wherein the micromotor deep groove ball bearing with high axial load-bearing capacity as claimed in any one of claims 1 or 2 is prepared, characterized in that: It consists of the following process steps performed in sequence: S1: Place the inner ring in the outer ring, place the rolling element between the inner ring and the outer ring, and place the rolling element on the raceway; S2: Press the cage toward the rolling element from both inside and outside, and then use a riveting press to rivet the cages that are arranged opposite to each other; S3: Before installing the retaining ring, use a negative pressure pump and an air pump on both sides of the deep groove ball bearing to evacuate and inhale air between the inner ring and the outer ring of the deep groove ball bearing; after evacuating air on one side and inhaling air on the other side for a period of time, install the retaining ring between the inner ring and the outer ring.

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