Deep groove ball bearing

Abstract

The utility model relates to the technical field of deep groove ball bearings, in particular to a deep groove ball bearing, which is characterized in that an inner ring is provided with a groove for a rolling ball to roll, a plurality of air holes are symmetrically distributed on two side walls of the groove, the air holes are arrayed along the circumference of the groove, and the distance between the adjacent air holes is 4-6 times of the aperture of the air holes. When the bearing rotates, air can form ordered convection between the interior of the bearing and the external environment through the air holes. Air enters the bearing from part of the air holes, absorbs heat generated by friction and then takes the heat out of the bearing. And the structural strength of the inner ring is considered due to the 4-6-time spacing design. If the space between the air holes is too small, although heat dissipation airflow can be enhanced, the structure of the inner ring can be weakened too much, and the bearing capacity is reduced; and the proper 4-6 times of pore diameter spacing of the air holes ensures that the inner ring still has enough strength to bear pressure and friction force generated during rolling of the rolling balls and maintain normal operation of the bearing while ensuring that air flow passes through and heat dissipation is realized.

Description

Technical Field

[0001] This utility model relates to the field of deep groove ball bearing technology, and more specifically, to a deep groove ball bearing. Background Technology

[0002] Deep groove ball bearings are key components widely used in various mechanical equipment, and their performance directly affects the operational stability and reliability of the equipment. During equipment operation, deep groove ball bearings generate a large amount of heat due to friction between the rolling balls and the inner and outer rings. If this heat cannot be dissipated effectively and in a timely manner, it will cause the bearing temperature to rise, leading to a series of problems.

[0003] Currently, the most common method for cooling deep groove ball bearings is using lubricating oil. However, this traditional cooling method has several drawbacks. First, the use of lubricating oil increases equipment maintenance costs. Not only does it require regular replenishment or replacement of the lubricating oil, but it also necessitates a corresponding lubrication system and filtration device to ensure the cleanliness and performance of the lubricating oil, undoubtedly increasing the overall operating costs of the equipment. Second, lubricating oil leakage is difficult to avoid, causing environmental pollution and potentially affecting the normal operation of other components around the equipment, thus increasing the risk of equipment failure.

[0004] To address the problems associated with traditional lubricating oil cooling methods, developing novel, efficient, and environmentally friendly cooling methods has become a key research focus and development trend in the field of deep groove ball bearings. Based on this, this invention proposes a deep groove ball bearing with an innovative structure to improve its heat dissipation performance while overcoming the shortcomings of traditional cooling methods. Utility Model Content

[0005] In view of the problems existing in the prior art, this utility model proposes a deep groove ball bearing.

[0006] To solve the above-mentioned technical problems, the present invention provides a solution through the following technical method:

[0007] A deep groove ball bearing includes an inner ring, an outer ring, and a plurality of rolling balls, characterized in that: the inner ring is provided with a groove for the rolling balls to roll, and a plurality of air holes are symmetrically distributed on the two side walls of the groove, the air holes are arranged in an array along the circumference of the groove, and the spacing between adjacent air holes is 4-6 times the diameter of the air hole.

[0008] When a deep groove ball bearing is in operation, the balls roll in the grooves of the rotating inner ring, and the continuous friction generates heat, causing the internal temperature of the bearing to rise. As the bearing rotates, air can flow through these pores, creating an orderly convection between the bearing's interior and the external environment. Air enters the bearing through some of these pores, absorbs the heat generated by friction, and then carries the heat out of the bearing, thus achieving heat dissipation.

[0009] A spacing of 4-6 times the diameter ensures the structural strength of the inner ring. If the vent spacing is too small, although it may enhance the heat dissipation airflow, it will weaken the inner ring structure too much and reduce its load-bearing capacity. A suitable vent spacing of 4-6 times the diameter ensures that airflow can pass through to achieve heat dissipation while ensuring that the inner ring still has sufficient strength to withstand the pressure and friction generated when the balls roll, and maintain the normal operation of the bearing.

[0010] Preferably, the pores are located on the outer side of the groove sidewall, and the distance from the center of each pore to the edge of the groove opening is 1.5-2.0 mm.

[0011] At the same time, this position is set to minimize the impact on the structural strength of the part of the groove that directly supports the rolling ball while ensuring heat dissipation, so as to ensure that the inner ring can still stably support the rolling of the ball.

[0012] Preferably, the pores are conical in shape, with a diameter of 0.6-0.8 mm at the end near the outer side of the groove and a diameter of 0.3-0.5 mm at the end near the inner side of the groove.

[0013] The larger diameter at the outer end facilitates the rapid entry of external cold air into the vent, forming the initial airflow channel. As the air flows inward towards the vent, the inner vent diameter gradually decreases to 0.3-0.5 mm, and according to the principle of fluid continuity, the airflow velocity increases accordingly. This accelerated airflow allows for more thorough contact and heat exchange with the high-temperature area inside the groove, efficiently absorbing the heat generated by the friction between the rolling ball and the inner ring. Subsequently, the heat-carrying air flows out from the inner smaller diameter end, completing the heat dissipation cycle. This conical structure creates a certain air pressure difference within the vent during bearing rotation, further promoting airflow within the vent and enhancing the heat dissipation effect. Moreover, from a structural mechanics perspective, the gradually changing vent diameter allows for a more reasonable stress distribution of the inner ring material around the vent, reducing stress concentration and ensuring the structural stability of the inner ring under dynamic rolling ball loads.

[0014] Preferably, the inlet and outlet edges of the air vents are both rounded with a radius of 0.03-0.08 mm.

[0015] The rounded corners allow for a smoother airflow transition when air enters the vent, reducing airflow separation and turbulence caused by sharp edges. Similarly, when air exits the vent, the rounded corners guide the airflow smoothly, preventing unnecessary vortices and resistance at the exit point. This not only optimizes the overall airflow within the vent but also reduces energy loss during airflow, thereby improving heat dissipation efficiency.

[0016] Preferably, the axis of the vent forms an angle of 20°-30° with the radial plane of the inner ring, and the direction of the inclination is consistent with the rotation direction of the inner ring.

[0017] When the inner ring rotates, because the vent is tilted and rotates in the same direction as the inner ring, outside air is more easily "drawn" into the vent along the tilt direction. This allows more cool outside air to quickly enter the bearing and exchange heat with the hot air generated by the friction between the balls and the inner ring, thus improving heat dissipation efficiency.

[0018] Preferably, it also includes a cage, which has receiving cavities corresponding to the rolling balls.

[0019] The cage and housing ensure that the balls are evenly distributed inside the bearing, avoiding direct contact between adjacent balls, reducing friction and local stress concentration, and extending bearing life. Attached Figure Description

[0020] Figure 1 This is a schematic diagram of the overall structure of the deep groove ball bearing in Example 1;

[0021] Figure 2 This is a schematic diagram of the inner ring structure in Example 1;

[0022] Figure 3 This is a cross-sectional view of the inner ring at the vent in Example 1;

[0023] Figure 4 This is a schematic diagram of the cage structure in Example 2.

[0024] The names of the parts referred to by the numbers in the attached diagram are as follows:

[0025] 110 Inner ring; 120 Outer ring; 130 Ball; 140 Groove; 150 Air hole; 160 Cage; 1601 Receiving cavity. Detailed Implementation

[0026] To further understand the content of this utility model, a detailed description of this utility model will be provided in conjunction with the accompanying drawings and embodiments. It should be understood that the embodiments are merely illustrative of this utility model and are not intended to limit it.

[0027] Example 1

[0028] like Figures 1-3 As shown, the deep groove ball bearing in this embodiment mainly consists of an inner ring 110, an outer ring 120, and multiple rolling balls 130.

[0029] The inner ring 110 has a groove 140 for the rolling ball 130 to roll. Several vents 150 are symmetrically distributed on both sides of the groove 140. These vents 150 are arranged in a circumferential array along the groove 140, with the spacing between adjacent vents 150 being 4-6 times the diameter of the vent 150. The vents 150 are located on the outer side of the sidewall of the groove 140, and the distance from the center of each vent 150 to the edge of the groove 140 opening is 1.5-2.0 mm. The vents 150 have a conical structure, with a diameter of 0.6-0.8 mm at the end near the outer side of the groove 140 and a diameter of 0.3-0.5 mm at the end near the inner side of the groove 140. Both the inlet and outlet edges of the vents 150 have rounded corners with a radius of 0.03-0.08 mm. Furthermore, the axis of the vent 150 forms a 20°-30° angle with the radial plane of the inner ring 110, and the direction of the angle is consistent with the rotation direction of the inner ring 110. The outer ring 120 cooperates with the inner ring 110 to provide an external support structure for the entire bearing. Multiple rolling balls 130 are placed between the groove 140 of the inner ring 110 and the outer ring 120, and are key components for realizing the rolling function of the bearing.

[0030] Its specific operating principle is as follows:

[0031] When the deep groove ball bearing is working, the inner ring 110 rotates with the shaft, and the balls 130 roll in the grooves 140 of the inner ring 110. The friction between the balls 130 and the grooves 140 of the inner ring 110 generates heat, causing the internal temperature of the bearing to rise.

[0032] At this point, the vent 150 begins to function as a heat dissipation device. Due to the inclined design of the vent 150, whose axis aligns with the rotation direction of the inner ring 110, the relatively cool outside air is more easily drawn into the vent 150 along its inclined direction. Air enters from the outer end of the vent 150 with its larger diameter, and as it flows inward, the air velocity increases due to the gradually narrowing inner diameter, according to the principle of fluid continuity. This accelerated airflow comes into full contact with the high-temperature area inside the groove 140, exchanging heat and absorbing the heat generated by the friction between the rolling ball 130 and the inner ring 110.

[0033] In this process, the rounded corners at the inlet and outlet edges of the vent 150 facilitate smoother airflow, reducing airflow separation, turbulence, vortices, and resistance. This minimizes energy loss from airflow, optimizes the overall flow of cooling air within the vent 150, and further improves heat dissipation efficiency. Simultaneously, the vents 150 are arranged in a circumferential array along the groove 140 with a specific spacing. This ensures airflow for heat dissipation while also maintaining the structural strength of the inner ring 110, enabling it to withstand the pressure and friction generated by the rolling balls 130 and maintain normal bearing operation.

[0034] The aforementioned design, through its unique vent 150 design, including the distribution of the vents, their tapered structure, tilt angle, and rounded corners, significantly improves heat dissipation efficiency. This allows for rapid dissipation of heat generated internally by friction, effectively reducing the bearing's operating temperature and ensuring optimal performance under various operating conditions, thus extending its service life.

[0035] The reasonable spacing of the pores 150 and the optimized distribution of stress around the pores 150 by the conical pore structure ensure heat dissipation while minimizing the impact on the structural strength of the part of the groove 140 that directly supports the rolling ball 130.

[0036] Example 2

[0037] Compared to Embodiment 1, an additional retainer 160 is added. The retainer 160 has a receiving cavity 1601 corresponding to the rolling ball 130, which is used to separate and position the rolling ball 130 in a suitable position.

[0038] The cage 160 and its housing cavity 1601 ensure that the balls 130 are evenly distributed inside the bearing, avoiding direct contact between adjacent balls 130 and reducing friction and local stress concentration between the balls 130. This not only ensures that each ball 130 can stably bear the load, but also makes the force distribution of the entire bearing more balanced, and also helps to maintain the stable flow of heat dissipation airflow formed by the vent 150 inside the bearing.

[0039] In summary, the above are merely preferred embodiments of this embodiment. All equivalent changes and modifications made in accordance with the scope of the patent application of this embodiment shall fall within the scope of the patent of this embodiment.

Claims

1. A deep groove ball bearing comprising an inner ring (110), an outer ring (120) and a plurality of balls (130), characterized in that: The inner ring (110) is provided with a groove (140) for rolling of the rolling ball (130), and a plurality of air holes (150) are symmetrically distributed on the two side walls of the groove (140), the air holes (150) are arranged in a circumferential array along the groove (140), and the spacing between adjacent air holes (150) is 4-6 times the aperture of the air hole (150).

2. A deep groove ball bearing according to claim 1, characterized in that: The air hole (150) is arranged on the outer side of the side wall of the groove (140), and the distance from the center of each air hole (150) to the opening edge of the groove (140) is 1.5-2.0 mm.

3. A deep groove ball bearing according to claim 2, characterized in that: The air hole (150) has a conical structure, the aperture of one end close to the outer side of the groove (140) is 0.6-0.8 mm, and the aperture of the other end close to the inner side of the groove (140) is 0.3-0.5 mm.

4. A deep groove ball bearing according to claim 3, characterized in that: The inlet edge and the outlet edge of the air hole (150) are both provided with a fillet with a radius of 0.03-0.08 mm.

5. The deep groove ball bearing of claim 1, wherein: The axis of the air hole (150) forms an inclination angle of 20°-30° with the radial plane of the inner ring (110), and the inclination direction is consistent with the rotation direction of the inner ring (110).

6. A deep groove ball bearing according to any one of claims 1 to 5, characterized in that: Further comprising a retainer (160), the retainer (160) is provided with a receiving cavity (1601) corresponding to the rolling ball (130) one by one.

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