A bearing with forced lubrication

Abstract

This invention relates to the field of bearing lubrication components, specifically to a bearing with a forced lubrication structure. The bearing with this forced lubrication structure has an inner or outer ring that is a rotating ring. At least one end of the rotating ring is provided with a guide ring. The guide ring has a structure for carrying out lubricating oil from the oil sump during rotation with the rotating ring. The guide ring also has a guide surface for throwing the lubricating oil adhering to it onto a region between the inner and outer raceways of the bearing under the centrifugal force during rotation. When the bearing operates at high speed, the guide ring also rotates at high speed, forcibly turbulently dispersing the lubricating oil remaining in the oil sump at the bottom of the bearing housing and carrying some of the lubricating oil out of the oil sump. The lubricating oil adhering to the guide ring is guided by the guide surface and splashed onto the region between the inner and outer raceways of the bearing under the centrifugal force. This ensures sufficient lubrication for the upper and middle parts of the bearing where the raceways contact the rollers.

Description

Technical Field

[0001] This invention relates to the field of bearing lubrication components, and more specifically to a bearing with a forced lubrication structure. Background Technology

[0002] Bearings used in large mineral mills in the mining and metallurgical industries generally need to withstand heavy loads and possess a certain degree of self-aligning performance; therefore, extra-large double-row self-aligning roller bearings are commonly used. The structure of a typical extra-large self-aligning roller bearing can be found in [reference needed]. Figure 1 This type of bearing consists of four parts: an outer ring (1), an inner ring (2), rollers (3), and a cage (4). The inner circumferential surface of the outer ring has an outer raceway, which is spherical. The inner ring is a double-raceway inner ring with flanges on both ends, and its outer circumferential surface has an inner raceway, which is curved. The rollers are drum-shaped with curved generatrices, and their two ends are limited by the flanges on both ends of the inner ring. The rollers are installed in the pockets of the cage and are fitted with the inner and outer raceways.

[0003] Due to the high tightness of the rollers and raceways and the curved generatrix of the rollers in extra-large self-aligning roller bearings, the bearings generate a large amount of internal heat during operation, resulting in a relatively low allowable operating speed. They are suitable for low-speed, heavy-load conditions. However, when applied to applications requiring automatic self-alignment and medium-to-high-speed heavy-load conditions, the bearings often experience severe overheating, leading to a reduction in lifespan.

[0004] In applications requiring self-aligning bearings and high-speed, heavy-load operation, oil bath lubrication or circulating oil lubrication is necessary to reduce bearing heat generation. In most cases, the bearing's central axis is horizontal. With oil bath lubrication, the lubricating oil forms a pool at the bottom of the bearing housing, immersing the lower part of the bearing in it. Lubrication of the upper raceway portion relies primarily on the lubricating oil adhering to the surfaces of the rollers and cage as they detach from the oil pool during bearing rotation. However, the amount of lubricating oil that can adhere to the rollers and cage is limited, and the oil flows away from their surfaces relatively quickly. This often results in insufficient lubrication at the contact points between the upper raceway and rollers, leading to abnormal temperature rises and even premature bearing failure.

[0005] Existing technologies include several lubrication methods, such as installing an oil slinger ring on the axial side of the bearing shaft. The ring guides the lubricating oil into the bearing housing, providing lubrication. However, the oil slinger ring is relatively far from the bearing, and the direction of the slinged oil is random, limiting its effectiveness in improving bearing lubrication and making it unsuitable for heavy-load, high-speed applications. Another method is circulating oil lubrication, directly supplying oil to the roller area. However, this requires an additional circulating oil system and auxiliary lubrication components such as a lubricating oil pump, increasing equipment size and cost. Even with circulating oil lubrication, the lubricating oil often fails to evenly reach areas requiring focused lubrication. Therefore, oil bath lubrication is often the most common method; however, oil bath lubrication suffers from the aforementioned lubrication deficiencies. Summary of the Invention

[0006] The purpose of this invention is to provide a bearing with a forced lubrication structure to solve the problem of insufficient internal lubrication in bearings that currently use oil bath lubrication.

[0007] The technical solution of the bearing with forced lubrication structure of the present invention is as follows:

[0008] A bearing with a forced lubrication structure, wherein the inner or outer ring of the bearing is a rotating ring, and at least one end of the rotating ring is provided with a drain ring. The drain ring is provided with a structure for carrying out lubricating oil in the oil sump during the rotation of the rotating ring. The drain ring is also provided with a drain surface for throwing the lubricating oil attached to it to the area between the inner and outer raceways of the bearing under the action of centrifugal force during the rotation.

[0009] Furthermore, the surface where the drainage surface is located extends to intersect with the outer raceway; or the surface where the drainage surface is located extends to intersect with the inner wall surface of the cage pocket of the bearing; or there are at least two types of drainage surfaces on the drainage ring, wherein the first type of drainage surface extends to intersect with the outer raceway and the second type of drainage surface extends to intersect with the inner wall surface of the cage pocket of the bearing.

[0010] Furthermore, the contact angle of the outer raceway is defined as the contact position between the maximum diameter of the bearing roller and the outer raceway, and the surface containing the first type of drainage surface extends to intersect with the contact angle of the outer raceway.

[0011] Furthermore, the guide ring has a limiting surface opposite to the roller end face of the bearing, and a guide groove is provided on the limiting surface. One side of the groove wall forms the first type of guide surface.

[0012] Furthermore, the second type of drainage surface is located on the outer wall of the drainage ring, and the angle between the extension direction of the second type of drainage surface and the axial direction of the drainage ring is equal to the contact angle of the bearing.

[0013] Furthermore, the outer circumferential surface of the drain ring is on a conical surface, and the cone angle of the conical surface is equal to the contact angle of the bearing. The outer circumferential surface of the drain ring is provided with circumferentially distributed drain teeth. The drain teeth are straight teeth and constitute a structure for carrying out lubricating oil from the oil sump during the rotation of the rotating ring. A tooth groove is formed between any two adjacent drain teeth. The bottom of the tooth groove is inclined and the angle between the inclined direction and the axis of the drain ring is equal to the contact angle of the bearing. The groove wall surface constitutes the second type of drain surface. The drain ring has a limiting surface opposite to the roller end face of the bearing. The limiting surface extends to the drain teeth. A drain groove is provided on the limiting surface. One side of the groove wall surface constitutes the first type of drain surface.

[0014] Furthermore, the bearing is a double-row self-aligning roller bearing with a rotating inner ring. Both ends of the inner ring are provided with guide rings, which constitute retaining edges for limiting the bearing rollers.

[0015] Furthermore, the drainage ring and the inner ring are separate parts, with the drainage ring fixedly installed on the inner ring.

[0016] Furthermore, the inner ring is provided with an installation step, which includes an outer cylindrical surface surrounding the axis of the inner ring and a vertical side surface perpendicular to the axis of the inner ring. The drainage ring is fixedly installed on the installation step, and the inner circumferential surface of the drainage ring mates with the outer cylindrical surface of the installation step for radial positioning. The drainage ring also has a limiting mating surface that abuts against the vertical side surface of the installation step for axial limiting.

[0017] Furthermore, the inner wall of the bearing cage is provided with an oil groove, with the groove opening facing the inner ring.

[0018] Beneficial effects: This invention improves upon existing bearings that use oil bath lubrication by incorporating a guide ring on the rotating race of the bearing. When the bearing operates at high speed, the guide ring also rotates at high speed, forcibly turbulenting the lubricating oil remaining in the oil sump at the bottom of the bearing housing and carrying some of the lubricating oil out of the sump. The lubricating oil adhering to the guide ring is guided by the guide surface and splashed under centrifugal force into the area between the inner and outer raceways of the bearing, i.e., the bearing roller contact area. This ensures sufficient lubrication for the upper and middle parts of the bearing where the raceways and rollers contact. Furthermore, the lubricating oil is directed and thrown short distances through the guide surface of the guide ring on the bearing raceway, which is beneficial for sufficient lubrication of key areas. The structure is simple and efficient, providing good lubrication and saving costs.

[0019] It features forced lubrication, positioning lubrication, and accelerated lubricant flow within the bearing, improving internal lubrication and effectively accelerating heat radiation transfer, thus reducing bearing overheating under heavy loads and high speeds. It provides a convenient and economical solution to the problem of severe overheating caused by insufficient lubrication in self-aligning roller bearings during high-speed, heavy-load applications.

[0020] Furthermore, different parts can be positioned and lubricated through various drainage surfaces, which, in conjunction with centrifugal force, precisely direct the lubricant to the target location. The lubricant can be precisely guided to the contact angle between the roller and the raceway, and the tapered toothed outer surface of the drainage ring guides the lubricant to the cage pocket, greatly enhancing the lubrication effect at the roller contact points.

[0021] Specifically, the guide ring serves as a retaining edge. After assembly, the guide ring limits the movement of the rollers, allowing for roller installation before the retaining edge. This eliminates the need for roller mounting notches on the retaining edge, effectively solving the problem of scratches on the roller generatrix surface caused by roller mounting notches on conventional bearings, thus improving assembly quality. Furthermore, the guide ring and inner ring are separate structures, allowing for easy removal of the guide ring during later bearing inspection and maintenance to facilitate the inspection and analysis of the inner ring raceway surface morphology. Attached Figure Description

[0022] Figure 1 This is a cross-sectional schematic diagram of an existing double-row self-aligning roller bearing;

[0023] Figure 2 This is a cross-sectional schematic diagram of an embodiment of the bearing with a forced lubrication structure of the present invention;

[0024] Figure 3 for Figure 2 A schematic diagram of the installation structure of the drainage ring in the middle;

[0025] Figure 4 for Figure 2 A schematic diagram of the bearing from the axial side.

[0026] Figure 5 for Figure 2 A three-dimensional schematic diagram of the drainage ring in the middle;

[0027] Figure 6 for Figure 2 Enlarged view of a local structure of the drainage loop;

[0028] Figure 7 for Figure 2 A schematic diagram of the cage.

[0029] In the diagram: 1. Outer ring; 2. Inner ring; 3. Roller; 4. Cage; 41. Pocket; 42. Oil groove; 5. Draining ring; 51. First type of drainage surface; 52. Second type of drainage surface; 53. Draining groove; 54. Draining tooth; 55. Limiting surface. Detailed Implementation

[0030] The basic concept of the bearing with a forced lubrication structure of the present invention is to set a guide ring on the rotating race of the bearing. When the bearing rotates at high speed, the lubricating oil stored in the oil sump at the bottom of the bearing is forcibly turbulent, and some of the lubricating oil is carried out of the oil sump. The lubricating oil adhering to the guide ring is guided by the guide surface and splashed into the area between the inner and outer raceways of the bearing under the action of centrifugal force. In this way, the contact area between the raceway and the roller in the upper part of the bearing can also have sufficient lubrication. It has the functions of forced lubrication, positioning lubrication, and accelerating the flow of lubricating oil inside the bearing.

[0031] The following is a detailed description with reference to specific embodiments.

[0032] Embodiments of the bearing with a forced lubrication structure of the present invention:

[0033] like Figure 2 , Figure 3 , Figure 4 , Figure 5 , Figure 6 , Figure 7 As shown, the bearing includes an outer ring 1, an inner ring 2, rollers 3, a cage 4, and a guide ring 5. In this embodiment, the bearing is a self-aligning roller bearing, specifically a double-row self-aligning roller bearing. The inner circumferential surface of the outer ring 1 has an outer raceway, which is spherical. The outer circumferential surface of the inner ring 2 has an inner raceway, which is arc-shaped. The outer circumferential surface of the inner ring 2 has two arc-shaped raceways, which are the contact surfaces between the rollers 3 and the inner ring 2. Two rows of rollers 3 are respectively mounted on the two arc-shaped inner raceways. The rollers 3 have a drum-shaped structure with a curved generatrix, also an arc, and two end faces perpendicular to the axis. The diameters at both ends are small, while the diameter in the middle is large. The roller 3 is installed in the pocket 41 of the cage 4. The pocket 41 of the cage 4 is adapted to be provided with two rows. The pocket 41 extends through the wall thickness of the cage 4 and has a side opening facing one side of the axial direction. The side openings of the two rows of pockets 41 are opposite to each other. The opposite ends of the two rows of rollers 3 can extend out from the side openings of the pocket 41.

[0034] Rollers 3 are inserted between outer ring 1 and inner ring 2, and cage 4 is installed between outer ring 1 and inner ring 2 to evenly separate each roller 3. Figure 2 In the figure, A represents the contact angle of the bearing. On the cross section through the bearing axis, the contact point between the roller 3 at its maximum diameter and the raceway is the contact angle contact point. The line connecting the contact angle contact point and the bearing center point is the normal line, which is also perpendicular to the axis of roller 3. The bearing center point is also the midpoint of the bearing axial dimension on its axis. The angle between this normal line and the radial line perpendicular to the bearing axis is the contact angle A.

[0035] The inner ring 2 of this bearing is a rotating ring, and there are two guide rings 5, which are coaxially mounted at both ends of the inner ring 2, forming a forced lubrication structure. In other embodiments, if the outer ring is a rotating ring, the guide ring can also be set on the outer ring. For a single-row roller bearing, a single guide ring can also be used.

[0036] The outer ring 1 of the bearing is fixedly mounted on the bearing housing, and the inner ring 2 is mounted on the shaft and rotates with the shaft. The bearing housing can be considered as the machine casing. There is an oil sump at the bottom of the bearing housing, which contains lubricating oil. The oil sump is usually shallow. Generally, a small part of the lower part of the bearing is immersed in the oil sump, while most of the middle and upper part is above the oil level. It can be lubricated by splashing oil through the drain ring 5.

[0037] The drain ring 5 is provided with a structure for carrying out the lubricating oil in the oil sump during the rotation of the rotating ring. The drain ring 5 is also provided with a drain surface for throwing the lubricating oil attached to it to the area between the inner and outer raceways of the bearing under the action of centrifugal force during the rotation.

[0038] When the bearing operates at high speed, the guide ring 5 also rotates at high speed, forcibly turbulenting the lubricating oil remaining in the oil sump at the bottom of the bearing housing and carrying some of the lubricating oil out of the oil sump. The lubricating oil adhering to the guide ring 5 is guided by the flow of the guide surface and splashed under the action of centrifugal force to the area between the inner and outer raceways of the bearing, that is, the bearing roller contact area. In this way, the raceway and roller contact areas in the upper part of the bearing can also have sufficient lubrication. Moreover, the lubricating oil is directionally and short-distancely thrown by the guide surface of the guide ring 5 on the bearing ring, which is beneficial to sufficient lubrication of key areas. The structure is simple and efficient, with good lubrication effect and cost savings. The problem of insufficient lubrication inside the bearing, especially the heat generation caused by insufficient lubrication at the raceway contact area, is solved by changing the internal structure of the bearing.

[0039] In this embodiment, there are at least two types of drainage surfaces. The first type of drainage surface 51 extends to intersect the outer raceway, and the second type of drainage surface 52 extends to intersect the inner wall of the pocket 41 of the bearing cage 4. In the actual bearing structure, the drainage surface, the outer raceway, and the inner wall of the pocket 41 are separate surfaces. Geometrically, if the first type of drainage surface 51 is extended infinitely, it will intersect the outer raceway; similarly, if the second type of drainage surface 52 is extended infinitely, it will intersect the inner wall of the pocket 41. Thus, the lubricating oil on the first type of drainage surface 51 moves along the extension direction of the first type of drainage surface 51 under the action of centrifugal force, and after being thrown out, it continues to splash in the original direction under the action of inertia, reaching the outer raceway and lubricating the outer raceway area. Similarly, the lubricating oil on the second type of drainage surface 52 moves along the extension direction of the second type of drainage surface 52 under the action of centrifugal force, and continues to splash in the original direction under the action of inertia after being thrown out, so as to reach the inner wall surface of the pocket 41 and lubricate the inner wall area of ​​the pocket 41.

[0040] The lubricating oil on the guide ring 5 can be splashed onto the outer raceway through the gap between the rollers. The lubricating oil on the guide ring 5 can also be splashed onto the gap between the roller 3 and the inner wall of the pocket 41 of the cage 4, and then enter the inner wall surface of the pocket 41. The contact areas between the outer raceway and the roller 3, and between the roller 3 and the cage 4, are areas prone to insufficient lubrication; this method enhances their lubrication effect. However, the contact area between the inner ring 2 and the roller 3 tends to retain more lubricating oil, so the problem of insufficient lubrication is not particularly prominent.

[0041] In this embodiment, both a first type of drainage surface 51 and a second type of drainage surface 52 are provided, allowing for directional lubrication of different parts. In other embodiments, only the first type of drainage surface may be provided, only the second type of drainage surface may be provided, or drainage surfaces for directional lubrication of other parts may be provided.

[0042] The drainage ring 5 has two axial sides, an inner circumferential surface, and an outer circumferential surface. The two axial sides are also the two end faces, one of which is the inner end face facing the roller 3, and the other end face is the outer end face facing away from the roller 3. The drainage ring 5 is tightly fitted on the stepped surface of the inner ring 2, and the inner circumferential surface of the drainage ring 5 is interference-fitted with the outer cylindrical surface of the stepped surface of the inner ring 2.

[0043] The inner end face of the drainage ring 5 includes a conical surface, a cylindrical surface, and a vertical surface. The conical surface is an outer conical surface, which is spaced apart from the outer end face of the roller 3. The small end of the conical surface faces inward, and the large end faces outward. The generatrix is ​​an oblique line inclined relative to the axis. The small end of the conical surface is closer to the axis than the large end, and the small end is in contact with the cylindrical surface. The cylindrical surface corresponds to the inner raceway and can avoid the corner edges of the roller. The cylindrical surface is in contact with the vertical surface, which is a plane perpendicular to the axis. This plane abuts against the vertical side surface of the step surface of the inner ring 2. The end face of the guide ring 5 near the inner ring 2 raceway is a combination of a plane and a conical surface, with a cylindrical surface transitioning between the two. The angle of the conical surface is slightly larger than the contact angle of the bearing. The cone angle of the conical surface is 10 minutes larger than the bearing contact angle. The cone angle of the conical surface is the angle between the generatrix and the axis. The direction of the conical surface from the small end to the large end is further away from the end face of the roller 3, ensuring that the guide ring 5 does not interfere with the end face of the roller 3 during operation and plays a limiting and guiding role.

[0044] The conical surface of the inner end face of the guide ring 5 forms a limiting surface 55 opposite to the end face of the roller 3 of the bearing. A guide groove 53 is provided on this limiting surface 55, and one side wall of the guide groove 53 forms a first type of guide surface 51. The guide groove 53 is located in the middle of the conical surface and is generally a V-shaped groove, also an annular groove surrounding the axis. The guide groove 53 has two side wall surfaces forming an angle, with the side wall surface furthest from the axis being a conical surface, the larger end of which is closer to the roller 3 than the smaller end. The side wall surface of the guide groove 53 closest to the axis is a cylindrical surface. The axes of both the cylinder and the cone are the axes of the guide ring 5 and also the axis of the bearing. The guide groove 53 also has a vertical surface located at the bottom of the groove, a plane perpendicular to the axis, which connects to the two side wall surfaces. The ends of the two side wall surfaces located at the groove openings connect to the conical surface of the inner end face of the guide ring 5.

[0045] The first type of drainage surface 51 is the side of the drainage groove 53 away from the axis of the drainage ring 5. The contact angle of the outer raceway is defined by the contact point between the maximum diameter of the bearing roller 3 and the outer raceway. The surface containing the first type of drainage surface 51 extends to intersect the contact angle of the outer raceway. Figure 2 As shown in the cross-section, the extension line of the inclined side corresponding to the first drainage surface of the drainage groove 53 points to the contact point between the roller 3 at its maximum diameter and the outer raceway, and this contact point is on the extension line. This orientation allows the lubricating oil to be thrown towards the contact center between the roller 3 and the outer ring 1 due to centrifugal force when the inner ring 2 rotates at high speed, providing sufficient lubrication to the contact area.

[0046] The drainage ring 5 has a toothed structure, which is used to carry out lubricating oil from the oil sump during the rotation of the rotating ring. The toothed structure includes drainage teeth 54 distributed circumferentially on the outer circumferential surface of the drainage ring 5. Each drainage tooth 54 has a top surface, two side surfaces, and two end surfaces. The top surface is part of the outer circumferential surface of the drainage ring 5, the two side surfaces are opposite to each other in the circumferential direction of the drainage ring 5, and the two end surfaces are opposite to each other in the axial direction of the drainage ring 5. The two side surfaces of the drainage tooth 54 have an included angle, so that the drainage tooth 54 gradually tapers from the root to the top. The top surface and the end surface of the drainage tooth 54 are transitioned by a chamfer. The outward end surface is coplanar with the outer end surface of the drainage ring 5, and the inward end surface is coplanar with the conical surface of the inner end surface of the drainage ring 5.

[0047] The outer circumferential surface of the guide ring 5 is on a conical surface and the cone angle of the conical surface is equal to the contact angle of the bearing. The guide teeth 54 are straight teeth. Any two adjacent guide teeth 54 form a tooth groove. The bottom of the tooth groove is inclined and the angle between the inclined direction and the axis of the guide ring 5 is equal to the contact angle of the bearing. The groove wall surface forms a second type of guide surface 52. The tooth groove is inclined and extends in the direction towards the roller 3 and away from the roller 3, with a certain angle to the axial direction, and towards the center of the end face of the roller 3. The lubricating oil in the tooth groove can be guided by the second type of guide surface 52 in the tooth groove and thrown along the second type of guide surface 52 to the space between the rollers 3, and then enters the gap between the inner wall of the pocket 41 of the cage 4 and the roller 3 to provide directional positioning lubrication for the inner wall of the pocket 41 of the cage 4.

[0048] The limiting surface 55 of the guide ring 5, which is opposite to the end face of the roller 3 of the bearing, extends to the guide tooth 54. That is, the inner end face of the guide tooth 54 is coplanar with the conical surface of the inner end face of the guide ring 5. The groove wall surface between any two adjacent guide teeth 54 belongs to the outer wall of the guide ring 5. The second type of guide surface 52 is provided on the outer wall of the guide ring 5. The angle between the extension direction of the second type of guide surface 52 and the axial direction of the guide ring 5 is equal to the contact angle of the bearing. The extension direction of the second type of guide surface 52 is the direction of groove inclination.

[0049] The outer circumferential surface of the drainage ring 5 is a conical surface. In this embodiment, the angle of the conical surface is the same as the contact angle of the bearing; in other embodiments, it can be close to it. When the angle of the conical surface containing the outer circumferential surface of the drainage ring 5 is equal to the bearing contact angle, the extension direction of the second drainage surface 52 is consistent with the axis direction of the roller 3, pointing towards the center of the roller 3. The direction of this conical surface is with the small end facing outward and the large end facing inward. This direction setting can guide the lubricating oil along the tooth surface and into the pocket 41 of the cage 4 due to the centrifugal force when the bearing rotates at high speed, providing sufficient lubrication and friction reduction for the friction pair between the roller 3 and the cage 4. The maximum outer diameter of the drainage ring 5 is not less than the distribution circle diameter of the center point of the outer end face of the roller 3, and the pitch circle diameter of the drainage teeth 54 on the drainage ring 5 is the same as or close to the distribution circle diameter of the center point of the outer end face of the roller 3. The distribution circle of the center point of the outer end face of the roller 3 is also the circle containing the center point of the outer end face of each roller 3.

[0050] Multiple drainage surfaces enable targeted lubrication at different locations, using centrifugal force to precisely direct lubricant to the target position. Lubricating oil is accurately guided to the contact angle between the roller 3 and the raceway. The tapered toothed outer surface of the drainage ring 5 further guides the oil to the pocket 41 of the cage 4, significantly enhancing lubrication at the contact points of the roller 3. This system provides forced lubrication, targeted lubrication, and accelerates the flow of lubricating oil within the bearing. It not only improves internal bearing lubrication but also effectively accelerates heat radiation transfer within the bearing, reducing heat generation under heavy loads and high speeds. This provides a convenient and economical solution to the problem of severe overheating due to insufficient lubrication in self-aligning roller bearings under high-speed, heavy-load conditions.

[0051] In this embodiment, the outer diameter of the guide ring 5 is larger than the outer diameter of the inner ring 2. The guide ring 5 constitutes a retaining edge for limiting the roller 3 of the bearing. That is, the setting position of the guide ring 5 meets the functional requirements of the retaining edge. The gap between the guide ring 5 and the roller 3 meets the function of straightening the roller 3, and does not rely on the guide ring 5 to bear the load.

[0052] The drainage ring 5 and the inner ring 2 are two separate parts, with the drainage ring 5 fixedly mounted on the inner ring 2. To position the drainage ring 5 during installation, the inner ring 2 has a mounting step at its end. The mounting step includes an outer cylindrical surface surrounding the axis of the inner ring 2 and a vertical side surface perpendicular to the axis of the inner ring 2. The drainage ring 5 is fixedly mounted on the mounting step. The inner circumferential surface of the drainage ring 5 mates with the outer cylindrical surface of the mounting step for radial positioning. The drainage ring 5 also has a limiting mating surface that abuts against the vertical side surface of the mounting step for axial positioning; this limiting mating surface is the vertical surface of the inner end face of the drainage ring 5. The vertical side surface of the mounting step of the inner ring 2 serves as the axial positioning surface for the drainage ring 5, and the outer cylindrical surface serves as the radial positioning surface for the drainage ring 5.

[0053] The vertical surface of the inner end face of the drainage ring 5 is connected to its inner circumferential surface, and the outer end face is connected to the inner circumferential surface. The mounting step of the inner ring 2 is located in the area of ​​the inner raceway near the end face of the inner ring 2. The axial width of the mounting step should ensure a suitable distance between the drainage ring 5 and the end face of the roller 3 after installation. The outer end face of the drainage ring 5 is flush with the outer end face of the inner ring 2, or does not protrude from the end face of the inner ring 2. The inward and outward directions of the end faces are axial.

[0054] In this embodiment, the drainage ring 5 and the inner ring 2 are interference-fitted. In other embodiments, the drainage ring 5 and the inner ring 2 can also be connected by a thread, and the thread is a fine thread.

[0055] The outer circumferential surface of the inner ring 2 also includes a cylindrical surface located between the two inner raceways, which is in contact with the inner raceways. The inner circumferential surface of the cage 4 has an annular boss protruding towards the inner ring 2 at its center. This annular boss is opposite to the cylindrical surface at the center of the outer circumferential surface of the inner ring 2. The top surface of the annular boss facing the inner ring 2 is a composite surface, composed of two types of surfaces: a cylindrical surface in the middle and outer arc surfaces on both sides. The cylindrical surface on the top surface of the annular boss is located at the center axially, while the two sides are connected arc surfaces. This reduces the sliding friction and heat generation between the top surface of the boss in the middle of the cage 4 and the largest outer cylindrical surface of the inner ring 2, while also preventing interference between the cage 4 and the outer cylindrical surface of the inner ring 2 when the cage 4 is tilted due to uneven force.

[0056] An oil groove 42 is provided on the annular boss on the inner circumferential surface of the cage 4. The annular boss belongs to the inner wall of the cage 4 of the bearing. The oil groove 42 is located on the inner wall of the cage 4 and the groove opening faces the inner ring 2. A certain amount of lubricating oil can be stored in the oil groove 42 to lubricate the two friction pairs.

[0057] The grooves between the drainage teeth 54 can also carry out and temporarily store some lubricating oil, and the drainage groove 53 can also carry out and temporarily store some lubricating oil, which can ensure that there is enough lubricating oil on the drainage surface to be thrown to the target area.

[0058] During bearing assembly, the cage 4 is first fitted onto the inner ring 2, then the rollers 3 are installed into the cage 4. Afterwards, the guide ring 5 is heat-fitted onto the inner ring 2. Since the guide ring 5 is installed after the rollers 3 are installed into the inner ring 2, it has no impact on the assembly of the rollers 3. This avoids the scratches caused to the rollers 3 by the notch on the inner ring flange when the rollers pass through the flange with the roller mounting notch in a conventional bearing. The remaining assembly steps are the same as for conventional bearings. Conventional bearings have an integral flange on the inner ring 2. To allow the rollers 3 to be installed into the raceway, the flange needs to have a roller mounting notch. However, this notch can easily scratch the rollers 3 during installation.

[0059] This bearing features a compact structure, convenient assembly, and economic efficiency. By incorporating a guide ring 5, the lubricating oil remaining in the oil sump at the bottom of the bearing is forced to turbulently and splashed by centrifugal force to the contact area between the bearing rollers, especially the raceway and roller 3 in the upper middle part of the bearing. The V-groove design precisely guides the lubricating oil to the contact angle between the roller 3 and the raceway. The tapered toothed outer surface of the guide ring 5 further directs the lubricating oil to the cage pocket, achieving forced lubrication, positioning lubrication, and accelerated lubricating oil flow within the bearing. This not only improves internal lubrication but also effectively accelerates heat radiation transfer within the bearing, reducing heat generation under heavy loads and high speeds. It effectively solves the problem of insufficient lubrication and overheating in self-aligning roller bearings under high-speed, heavy-load conditions in a convenient and economical manner.

[0060] The bearing inner ring has stepped surfaces at both ends, with the outer diameter of the stepped surfaces smaller than the inner ring raceway diameter. This facilitates the positioning and assembly of the guide ring, simplifying bearing assembly. Furthermore, it avoids scratches on the roller generatrix surface caused by the notches on the flanges when the rollers enter the inner ring raceway through the flanges at both ends of the original structure during assembly, thus improving assembly quality. The guide ring and inner ring are separate structures; during later inspection and maintenance of the bearing, the guide ring can be removed to allow for inspection and analysis of the inner ring raceway surface morphology.

[0061] This bearing structure is suitable for extra-large double-row self-aligning roller bearings with built-in turbulence and flow diversion functions used under heavy-load, high-speed conditions. It can effectively provide sufficient lubrication to target areas in the upper part of the bearing that are far from the oil sump. In other embodiments, this bearing structure can also be used on other suitable types of bearings, such as double-row tapered roller bearings. Of course, it can also be used on ordinary single-row roller bearings, such as cylindrical bearings and ball bearings, to achieve the same enhanced lubrication effect.

[0062] Finally, it should be noted that the above descriptions are merely preferred embodiments of the present invention and are not intended to limit the present invention. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art can still make modifications to the technical solutions described in the foregoing embodiments without creative effort, or make equivalent substitutions for some of the technical features. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A bearing with a forced lubrication structure, wherein the inner or outer ring of the bearing is a rotating ring, characterized in that, At least one end of the rotating ring is provided with a drainage ring, and the outer circumferential surface of the drainage ring is provided with various drainage teeth distributed in a circle. The drainage teeth form a structure for carrying out the lubricating oil in the oil sump during the rotation of the rotating ring. The drainage ring is also provided with a drainage surface for throwing the lubricating oil attached to it into the area between the inner and outer raceways of the bearing under the action of centrifugal force during the rotation. A tooth groove is formed between any two adjacent drainage teeth. The bottom of the tooth groove is inclined and the inclination direction is at an angle to the axis of the drainage ring. The groove wall surface forms a drainage surface and the surface where the drainage surface is located extends to intersect the inner wall surface of the cage pocket of the bearing.

2. The bearing with a forced lubrication structure according to claim 1, characterized in that, There are at least two types of drainage surfaces on the drainage ring. The drainage surface formed by the extension of the first drainage surface and its intersection with the outer raceway and the groove wall of the tooth groove is the second drainage surface.

3. The bearing with a forced lubrication structure according to claim 2, characterized in that, The contact angle of the outer raceway is defined as the position where the maximum diameter of the bearing roller contacts the outer raceway. The surface containing the first type of drainage surface extends and intersects with the contact angle of the outer raceway.

4. The bearing with a forced lubrication structure according to claim 3, characterized in that, The guide ring has a limiting surface opposite to the roller end face of the bearing, and a guide groove is provided on the limiting surface. One side of the groove wall forms the first type of guide surface.

5. The bearing with a forced lubrication structure according to claim 2, characterized in that, The second type of drainage surface is located on the outer wall of the drainage ring, and the angle between the extension direction of the second type of drainage surface and the axis of the drainage ring is equal to the contact angle of the bearing.

6. The bearing with a forced lubrication structure according to claim 5, characterized in that, The outer circumferential surface of the drainage ring is on a conical surface and the cone angle of the conical surface is equal to the contact angle of the bearing. The drainage teeth are straight teeth, and the angle between the bottom inclination direction of the tooth groove and the axis of the drainage ring is equal to the contact angle of the bearing. The drainage ring has a limiting surface opposite to the roller end face of the bearing. The limiting surface extends to the drainage teeth. A drainage groove is provided on the limiting surface. One side of the groove wall of the drainage groove constitutes the first type of drainage surface.

7. The bearing with a forced lubrication structure according to any one of claims 1-6, characterized in that, This bearing is a double-row self-aligning roller bearing with a rotating inner ring. Both ends of the inner ring are equipped with guide rings, which serve as retaining edges for limiting the position of the bearing rollers.

8. The bearing with a forced lubrication structure according to any one of claims 1-6, characterized in that, The drainage ring and the inner ring are separate parts, with the drainage ring fixedly installed on the inner ring.

9. The bearing with a forced lubrication structure according to claim 8, characterized in that, The inner ring is provided with an installation step, which includes an outer cylindrical surface surrounding the axis of the inner ring and a vertical side surface perpendicular to the axis of the inner ring. The drainage ring is fixedly installed on the installation step. The inner circumferential surface of the drainage ring mates with the outer cylindrical surface of the installation step for radial positioning. The drainage ring also has a limiting mating surface that abuts against the vertical side surface of the installation step for axial limiting.

10. The bearing with a forced lubrication structure according to any one of claims 1-6, characterized in that, The inner wall of the bearing cage is provided with an oil groove, with the groove opening facing the inner ring.

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