A high-precision, low-friction, low-temperature-intensity double-row tapered roller bearing for gearboxes.

Abstract

This utility model relates to the field of bearing manufacturing technology, specifically a high-precision, low-friction, low-temperature-adjustable double-row tapered roller bearing for gearboxes. It includes an outer ring, an inner spacer within the outer ring, and two inner components arranged opposite each other between the outer and inner spacers. Each inner component consists of tapered rollers and a cage. An oil groove is formed on the sidewall of the outer ring, and an oil inlet groove is formed at the contact point between the outer wall of the inner spacer and the end face of the tapered rollers. The cage window is adapted to fit the tapered rollers. To reduce friction and wear, the design of the oil inlet groove and 45° chamfer reduces the contact area between the tapered roller ball base surface and the large flange of the inner spacer, effectively reducing sliding friction between them. This directly reduces power loss during bearing operation and improves transmission efficiency. The drum-shaped cage window design reduces the friction surface between the cage and the tapered rollers, preventing tapered roller tilting and cage wobbling, further reducing friction and wear.

Description

Technical Field

[0001] This utility model relates to the field of bearing manufacturing technology, specifically a high-precision, low-friction, low-temperature-increasing double-row tapered roller bearing for gearboxes. Background Technology

[0002] In modern mechanical engineering, especially in gearbox systems, bearings are key components whose performance has a crucial impact on the reliability, accuracy, and efficiency of the entire system. With the continuous advancement of industrial technology, various mechanical equipment are developing towards higher precision, higher speed, higher load capacity, and longer service life, placing increasingly stringent requirements on gearbox bearings.

[0003] Traditional bearings are increasingly revealing a series of problems when faced with these ever-increasing demands. In terms of precision, conventional bearings struggle to meet the stringent requirements of high-precision equipment for minute displacements and angular deviations in shaft systems. For example, in the spindle gearbox of a CNC machine tool, even minute radial runout or axial movement of the bearing can lead to dimensional errors and surface roughness defects in machined parts, affecting product quality. In automotive automatic transmissions, insufficient bearing precision can cause shocks and jerks during gear shifts, reducing driving comfort.

[0004] Friction and temperature rise are also major challenges faced by traditional bearings. A high coefficient of friction not only leads to significant energy loss and reduced transmission efficiency, but also generates heat, causing excessive bearing temperature rise. Excessive temperature rise causes a decrease in lubricating oil viscosity, deteriorating lubrication and further exacerbating friction and wear, creating a vicious cycle. Simultaneously, high temperatures can cause thermal expansion of internal bearing components, altering the original fit clearances and preload, reducing the bearing's load-bearing capacity and rotational accuracy, and even triggering failure modes such as bearing seizure and fatigue spalling, shortening bearing life and increasing equipment maintenance costs and downtime. Utility Model Content

[0005] The purpose of this invention is to provide a high-precision, low-friction, low-temperature-increase double-row tapered roller bearing for gearboxes, in order to solve the problems existing in the prior art mentioned in the background section.

[0006] To achieve the above objectives, this utility model provides the following technical solution: a high-precision, low-friction, low-temperature gearbox double-row tapered roller bearing, comprising an outer ring and an inner spacer disposed within the outer ring, and two inner components arranged opposite to each other between the outer ring and the inner spacer. The inner components consist of tapered rollers and a cage. An oil groove is provided on the side wall of the outer ring, and an oil inlet groove is provided at the contact point between the outer wall of the inner spacer and the end face of the tapered roller. The cage window is adapted to the tapered roller.

[0007] Furthermore, the opening angle of the oil groove is 35° and the angle between the opening direction and the axial direction is 20°.

[0008] Furthermore, a 45° chamfer is provided at the connection between the oil inlet groove and the large flange of the inner spacer.

[0009] Furthermore, the retainer window opening has a drum-shaped surface.

[0010] Furthermore, the outer ring, inner spacer, and inner component are coated with a high-hardness coating.

[0011] Compared with the prior art, the beneficial effects of this utility model are as follows:

[0012] 1. Reduce friction and wear: The design of the oil inlet groove and 45° chamfer reduces the contact area between the tapered roller ball base surface and the large flange of the inner spacer, effectively reducing the sliding friction between the two. This directly reduces the power loss of the bearing during operation and improves the transmission efficiency.

[0013] 2. The cage window design with a drum-shaped surface reduces the friction surface between the cage and the tapered rollers, preventing the tapered rollers from tilting and the cage from wobbling, further reducing friction and wear.

[0014] 3. The presence of a high-hardness coating reduces direct contact between bearing components, lowers frictional losses, and improves the bearing's wear resistance, extending its service life. The high-hardness coating not only has lubricating properties but also assists in heat dissipation to a certain extent. The coating reduces heat generation and, once heat is generated, helps with heat conduction and dissipation, further controlling the bearing's temperature rise.

[0015] 4. The optimized design of the oil groove, oil inlet groove, and cage window works together to ensure that the lubricating oil is distributed more fully and evenly to all key parts of the bearing. The good lubrication effect reduces frictional heat generation, thereby reducing the temperature rise of the bearing during operation. The design of the oil groove and oil inlet groove ensures that the lubricating oil can circulate effectively inside the bearing. The oil groove stores and guides the lubricating oil, while the oil inlet groove accurately delivers the lubricating oil to the key friction parts, forming a good lubrication system.

[0016] 5. The axial slope of the oil groove is 20°, which improves the contact angle and contact pressure distribution, making the contact between the roller and the raceway more stable. This stable contact reduces impact and vibration, and improves the bearing capacity under dynamic load, enabling it to adapt to higher load requirements.

[0017] 6. The 35° opening angle of the oil groove ensures uniform stress distribution and avoids local fatigue failure. The drum-shaped surface design of the retainer window hole ensures the correct position of the rollers and the smooth operation of the bearing. These designs together improve the overall structural stability of the bearing and enhance its load-bearing capacity. Attached Figure Description

[0018] Figure 1 This is a cross-sectional view of the overall structure of this utility model;

[0019] Figure 2 This is a cross-sectional view of the outer ring portion of this utility model;

[0020] Figure 3 This is an enlarged view of the oil trench of this utility model;

[0021] Figure 4 This is an enlarged view of the oil inlet groove of this utility model;

[0022] Figure 5 This is a front view of the cage of this utility model;

[0023] Figure 6 This is an enlarged view of the drum-shaped surface of this utility model.

[0024] In the picture:

[0025] 1. Outer ring; 2. Inner spacer ring; 3. Inner component; 4. Oil groove; 5. Oil inlet groove; 6. Tapered roller; 7. Cage; 8. Drum-shaped surface. Detailed Implementation

[0026] Please see Figures 1 to 6 A high-precision, low-friction, low-temperature double-row tapered roller bearing for gearboxes includes an outer ring 1, an inner spacer 2 disposed within the outer ring 1, and two inner components 3 arranged opposite to each other between the outer ring 1 and the inner spacer 2. The inner components 3 consist of tapered rollers 6 and cages 7. An oil groove 4 is formed on the side wall of the outer ring 1. The opening angle of the oil groove 4 is 35° and the opening direction is 20° from the axial direction. The outer ring flange adopts a shallow oil groove with a smooth transition, which avoids the oil groove 4 from local fatigue failure due to large stress when the bearing is under load. The 20° axial slope can improve the contact angle and contact pressure distribution to a certain extent, making the contact more stable, reducing impact and vibration, thereby improving the bearing capacity under dynamic load. The 35° opening of the oil groove 4 can make the stress distribution of the oil groove 4 and its surrounding area more uniform, reducing the risk of failure due to stress concentration.

[0027] Please see Figure 4Oil inlet grooves 5 are provided on the outer wall of the inner spacer 2 and the end face of the tapered roller 6. A 45° chamfer is provided at the connection between the oil inlet groove 5 and the large flange of the inner spacer 2. The sliding friction between the ball base surface of the tapered roller 6 and the large flange of the inner spacer 2 accounts for a large proportion of the total friction of the tapered roller bearing and has a significant impact on the power loss of the bearing. This structure reduces friction by optimizing the contact area between the two. The tapered flange of the tapered roller bearing and the ball base surface of the tapered roller 6 are in point contact, but they become surface contact after being subjected to force. Therefore, by reducing the contact area between the two, friction can be effectively reduced. Therefore, while ensuring the minimum contact size of the flange, a 45° chamfer is adopted for the large flange of the inner ring to reduce the contact area and form an oil wedge, so that the lubricating oil can fully enter the working surface, thereby playing a good lubrication role, achieving the functions of heat dissipation and reducing friction.

[0028] Please see Figure 5 and Figure 6 The cage 7 aperture is adapted to the tapered roller 6. The cage 7 aperture has a drum-shaped surface 8. This bearing adopts a drum-shaped cage 7 aperture structure. In order to make the bearing run more smoothly and the lubricating oil can be evenly lubricated to the surface of the tapered roller 6, the cage 7 aperture is designed as a concave arc shape similar to the convex shape of the tapered roller 6. This effectively reduces the friction surface between the cage 7 and the tapered roller 6, and avoids the highest part of the tapered roller 6 from contacting the pressure slope surface of the cage 7, which would cause the tapered roller 6 to tilt and the cage 7 to wobble. During operation, only the two ends of the tapered roller 6 are in contact with the pressure slope surface of the cage. This design can make the bearing run more smoothly and the lubricating oil is more evenly distributed to the surface of the tapered roller 6 without affecting the overall strength of the cage 7, effectively reducing the friction between the cage 7 and the tapered roller 6.

[0029] The outer ring 1, inner spacer 2, and inner component 3 are coated with a high-hardness coating. The high-hardness coating is deposited using PVD technology to enhance the lubrication performance of the bearing and reduce bearing wear and friction loss. This modification is done on the surface of bearing components that traditionally only have a metal substrate. By reasonably coating the surfaces of the outer ring 1, inner spacer 2, and inner component 3 (DLC1 coating), the bearing's corrosion resistance, wear resistance, and self-lubrication properties are improved. This greatly enhances the wear performance of the bearing base material while reducing friction loss.

[0030] The working principle of this invention is as follows: Inside the bearing, the shallow oil groove at the flange of the outer ring 1 creates a smooth transition structure, preventing localized fatigue failure. Friction is reduced by decreasing the contact area between the large flange of the inner spacer 2 and the ball base of the tapered roller 6, and by using a 45° chamfer on the large flange to form an oil wedge. The use of a drum-shaped surface 8 for the cage window structure prevents the convexity of the highest point of the tapered roller 6 from contacting the slope of the cage 7, resulting in smoother bearing operation. Wear and friction loss are reduced by applying a high-hardness coating to the bearing surface using PVD technology. This bearing design reduces heat and wear generated by friction, decreases energy loss, extends the bearing's service life, and improves the transmission efficiency of mechanical equipment such as gearboxes.

Claims

1. A high-precision, low-friction, low-temperature-intensity double-row tapered roller bearing for gearboxes, characterized in that, It includes an outer ring (1) and an inner spacer (2) disposed inside the outer ring (1), as well as two inner components (3) arranged opposite to each other between the outer ring (1) and the inner spacer (2). The inner components (3) are composed of tapered rollers (6) and cages (7). The outer ring (1) has an oil groove (4) on its side wall. The inner spacer (2) has an oil inlet groove (5) at the contact point between its outer wall and the end face of the tapered roller (6). The oil inlet groove (5) and the large flange of the inner spacer (2) are connected by a 45° chamfer. The window of the cage (7) is adapted to the tapered roller (6).

2. The double-row tapered roller bearing as described in claim 1, characterized in that, The opening angle of the oil groove (4) is 35° and the angle between the opening direction and the axial direction is 20°.

3. The double-row tapered roller bearing as described in claim 1, characterized in that, The retainer (7) has a bulging window (8).

4. The double-row tapered roller bearing as described in claim 1, characterized in that, The outer ring (1), inner spacer (2), and inner component (3) are coated with a high-hardness coating.

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