A super large thrust spiral conical roller bearing

Abstract

The present application belongs to the technical field of bearings, and discloses a super-large thrust spiral conical roller bearing, which comprises an axle ring, a seat ring, a retainer and a spiral conical roller, the axle ring and the seat ring are provided with raceways corresponding to the spiral conical roller, the raceways of the axle ring and the seat ring combine to form an annular groove with a taper in a cross section, the spiral conical roller is installed in the annular groove between the axle ring and the seat ring through the retainer, and the outer sides of the raceways of the axle ring and the seat ring are respectively provided with a stop edge structure matched with the two end faces of the spiral conical roller; the thrust spiral conical roller bearing has simple structure and high reliability, the spiral oil groove flow guide structure is arranged on the surface of the conical roller, the lubricating oil is continuously guided to the stop edge contact area, and the boundary lubrication condition is improved; the directional flow of the lubricating oil carries away the heat generated at the stop edge due to friction, thereby effectively reducing the temperature rise of the bearing; the large end face of the roller is a spherical surface structure, and the stop edges of the axle ring and the seat ring are conical surface structures, which is beneficial to the formation of an oil film and improves the service life of the bearing.

Description

Technical Field

[0001] This invention belongs to the field of bearing technology, and particularly relates to an extra-large thrust spiral tapered roller bearing. Background Technology

[0002] Bearings are widely used in various mechanical equipment, their main function being to support the rotation of rotating parts. Thrust tapered roller bearings are bearings where the rolling elements are tapered rollers, and the rolling generatrices and raceway generatrices both converge at a single point on the bearing's axis. They are primarily used to bear axial loads and are characterized by high rigidity and relatively small axial space requirements, allowing for a compact axial bearing configuration. These bearings can withstand heavy axial loads, are insensitive to impact loads, and possess high rigidity, good guiding accuracy, and can withstand overturning moments.

[0003] Thrust tapered roller bearings withstand extremely high axial loads during operation. The contact surfaces between the tapered rollers and the inner and outer raceways of the bearing must bear significant loads in harsh working environments. Sliding friction occurs during operation, resulting in a large contact area and high friction between the tapered rollers, raceways, and flanges. Particularly, the friction and temperature rise in the contact area between the rollers and flanges are severe, making it difficult to continuously supply lubricating oil to the flange contact area. When the axial load approaches the rated load, the stress concentrates at both ends of the tapered rollers, exceeding the allowable stress. This easily leads to overheating of the tapered rollers, causing them to roll heatedly with the inner and outer rings under pressure. Insufficient lubrication further increases friction, leading to high temperatures and severe wear, causing roller burns, deformation, and stress concentration. In severe cases, this can result in premature fatigue spalling of the bearing raceways and rollers, leading to failure. In practical use, frequent failures such as seizure and excessive stress necessitate replacement. The bearings are prone to overheating during operation, which can cause the rollers to seize and become inoperable, resulting in a high failure rate and severely limiting the operational reliability and service life of thrust tapered roller bearings. Summary of the Invention

[0004] To address the above problems, this invention provides an extra-large thrust helical tapered roller bearing, which employs tapered rollers with helical oil grooves. The direction of the helical oil grooves on the tapered rollers is matched with the bearing rotation direction, guiding the lubricating oil to flow towards the flange direction, thereby improving the lubrication capacity of the thrust tapered roller bearing during operation, reducing the friction between the tapered rollers and the flange and raceway, reducing heat generation, and giving the thrust tapered roller bearing higher reliability and service life.

[0005] The technical solution adopted by the present invention to achieve the above objectives is as follows: an extra-large thrust spiral tapered roller bearing, comprising a shaft ring, a housing ring, a cage, and spiral tapered rollers. The shaft ring and the housing ring are respectively provided with raceways adapted to the spiral tapered rollers. The shaft ring raceway and the housing ring raceway combine to form a conical annular groove. The spiral tapered rollers are installed in the annular groove between the shaft ring and the housing ring through the cage. The outer sides of the shaft ring raceway and the housing ring raceway are respectively provided with flange structures that mate with the large end face of the spiral tapered rollers. A spiral oil groove is provided on the conical rolling surface of the spiral tapered rollers.

[0006] The junction of the two end faces of the spiral tapered roller with the conical surface adopts an arc transition, with the arc angle of the small end being R3~4mm and the arc angle of the large end being R7~9mm; the large end face of the spiral tapered roller has a spherical structure; the retaining edge that contacts the large end face of the spiral tapered roller has a conical structure.

[0007] The radius of the large end ball face of the spiral tapered roller is 0.95 times the radius of the flange tapered surface.

[0008] Both the shaft ring raceway and the seat ring raceway are configured with a logarithmic curve shape for raceway convexity. The convexity of the raceway is 5 to 8 μm, and the highest point of convexity is within 10% of the middle of the raceway width.

[0009] The spiral oil groove has a depth of 0.5–0.8 mm, a width of 0.7–1.5 mm, and a pitch of 10 mm.

[0010] The spiral tapered roller has a left-hand or right-hand spiral direction of rotation; a left-hand or right-hand spiral oil groove is formed on the outer conical surface of the spiral tapered roller, so that when the spiral tapered roller rotates, the lubricating oil entering the bearing flows along the spiral oil groove towards the outer flange.

[0011] The junction of the two ends of the spiral tapered roller with the conical surface is transitioned by an arc surface. The arc angle of the small end is R3-4mm, and the arc angle of the large end is R7-9mm. The large end face of the spiral tapered roller is a spherical structure. The flanges of the shaft ring and seat ring are conical structures, and the flange structure that contacts the large end face of the spiral tapered roller is a conical structure. The purpose of this design is that the tapered roller usually adopts a structural design in which the large end face, small end face and conical surface intersect or are chamfered at 45°. However, in actual use, there are the following disadvantages: (1) Due to the axial load being close to the rated load, the right-angled parts at both ends of the tapered roller generate relatively large stress and plastic deformation compared to other parts. The frictional torque increases significantly, and the stress and strain are large, making it easy to break. (2) Due to the conical angle of the tapered roller, when subjected to axial force, the entire tapered roller tends to slide towards the large end, generating a frictional torque. The large end face generates a frictional torque and adds additional axial load to the right-angled part of the large end face. To address the aforementioned shortcomings, the right-angle portions of the tapered rollers are transitioned with arc-shaped surfaces, while the large end face of the helical tapered rollers is a spherical structure. The flange structure that contacts the large end face of the helical tapered rollers is a conical structure. In other words, the right-angle raceway angular contact mode is changed to an arc-shaped raceway angular contact mode, increasing the contact angle, increasing the contact area, and improving the axial load-bearing capacity. This avoids significant stress concentration at both ends, excessive heat generation, and easy damage and failure of the rollers.

[0012] The radius of the large end ball face of the spiral tapered roller is 0.95 times the radius of the flange tapered surface. This design is based on empirical proportions derived from bearing stress analysis, contact mechanics calculations, and optimization under actual operating conditions. The aim is to address poor contact and stress concentration issues during actual operation through a slight geometric modification. By optimizing the ball end face radius to be slightly smaller than the flange tapered surface radius (0.95 times), the contact area can be controlled, stabilizing the contact point in the middle region of the roller ball end face. This effectively avoids edge contact and prevents severe localized wear or flange breakage caused by edge contact. Simultaneously, the formation of a small wedge-shaped cavity during contact facilitates lubricant storage and oil film formation, thereby improving lubrication conditions and reducing contact stress and frictional heat generation. In summary, through a reasonable radius ratio modification, the stress distribution in the contact area can be optimized, resulting in a more uniform load distribution and improved bearing capacity and service life.

[0013] Both the shaft ring raceway and the seat ring raceway are configured with logarithmic curves for raceway convexity, with a convexity of 5–8 μm and the highest point of convexity within 10% of the middle of the raceway width. This configuration aims to tailor the convexity curves of the shaft ring and seat ring raceways to different operating conditions and bearing specifications. The convexity depends on the bearing load and raceway length. Excessive convexity limits the rollers to partial contact, preventing full utilization of their effective length. Insufficient convexity often results in stress peaks at the roller ends, causing stress concentration. Changing the shaft ring and seat ring raceways from straight lines to logarithmic curves with convexity effectively improves the stress distribution in the contact area between the helical tapered rollers and the raceway. This significantly reduces or eliminates edge stress concentration, facilitating fluid lubrication. Furthermore, it mitigates uneven loading caused by misalignment due to installation and machining errors, as well as spindle rotation-induced deflection, thus extending bearing life.

[0014] The spiral tapered roller has a left-hand or right-hand helix direction. A left-hand or right-hand helical oil groove is formed on the outer conical surface of the spiral tapered roller. When the spiral tapered roller rotates, the lubricating oil entering the bearing flows along the helical oil groove towards the outer flange. The purpose of this design is that the spiral tapered roller surface has a helical groove guiding structure. When the bearing rotates counterclockwise, facing the large end of the tapered roller, and the spiral tapered roller rotates clockwise, the flanges of the shaft ring and seat ring are on the outside. A left-hand helical oil groove is used, allowing the lubricating oil to move along the helical oil groove towards the flange. Conversely, when the bearing rotates clockwise, facing the large end of the tapered roller, and the spiral tapered roller rotates counterclockwise, a right-hand helical oil groove is used, allowing the lubricating oil to still move along the helical oil groove towards the flange. The main purpose is to allow lubricating oil to enter the area where the roller ball base and the flange are located when the helical tapered roller is rotating, thereby reducing the friction between the tapered roller ball base and the flange, and thus preventing problems such as burning, fatigue and stress concentration in this area, thereby extending the service life of the bearing.

[0015] Beneficial effects: The extra-large thrust spiral tapered roller bearing of this invention has a simple structure and high reliability. An optimized spiral flow guiding structure for lubricating oil is designed on the surface of the tapered rollers. When the tapered rollers rotate, the spiral oil groove structure on the outer surface of the tapered rollers generates a pumping effect, continuously guiding the lubricating oil to the flange contact area, improving boundary lubrication conditions. The directional flow of lubricating oil can remove the heat generated by friction at the flange, effectively reducing the bearing temperature rise. Through active oil supply and forced heat dissipation, wear on the flange and roller end faces is reduced, greatly improving the bearing's lubrication performance. Furthermore, the right-angle structure of the two end faces of the tapered rollers is changed to a circular arc transition structure, and the flange parts where the inner and outer rings of the bearing contact the rollers also use matching circular arcs to form arc-shaped raceways, increasing the contact angle and contact area, improving axial load capacity, and extending the bearing's service life. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of the structure of the extra-large thrust spiral tapered roller bearing of the present invention when rotated clockwise;

[0017] Figure 2 This is a schematic diagram of the structure of the extra-large thrust spiral tapered roller bearing of the present invention when it rotates counterclockwise;

[0018] Figure 3 This is a schematic diagram of the tapered rollers and flanges of the extra-large thrust spiral tapered bearing of the present invention.

[0019] Markings: 1. Shaft ring; 2. Seat ring; 3. Helical tapered roller; 4. Helical oil groove; 5. Flange; 6. Cage; 7. Shaft ring raceway; 8. Seat ring raceway. Detailed Implementation

[0020] The technical solutions in the embodiments of the present invention will be clearly and completely described below. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0021] like Figure 1-3 As shown, an extra-large thrust helical tapered roller bearing includes a shaft ring 1, a housing ring 2, a cage 6, and helical tapered rollers 3. The shaft ring 1 and the housing ring 2 are respectively provided with raceways adapted to the helical tapered rollers 3. The shaft ring raceway 7 and the housing ring raceway 8 are combined to form a conical annular groove. The helical tapered rollers 3 are installed in the annular groove between the shaft ring 1 and the housing ring 2 through the cage 6. The outer sides of the shaft ring raceway 7 and the housing ring raceway 8 are respectively provided with flange structures 5 that mate with the large end face of the helical tapered rollers 3.

[0022] The junction of the two end faces of the helical tapered roller 3 with the conical surface is a rounded transition, with an arc angle of R3-4mm at the small end and R7-9mm at the large end. The large end face of the helical tapered roller has a spherical structure, while the flanges 5 of the shaft ring and seat ring have conical structures. The flange 5 that contacts the large end face of the helical tapered roller 3 also has a conical structure. The radius of the spherical end face of the large end of the helical tapered roller 3 is 0.95 times the radius of the conical surface of the flange. Figure 3 As shown, R 滚子 =0.95R. The right-angle portions of the two ends of the spiral tapered roller 3 are transitioned with arc surfaces, and the flange 5 that contacts the roller is also formed with a corresponding arc to create an arc-shaped raceway. This changes the right-angle raceway angular contact mode to an arc-shaped raceway angular contact mode, increasing the contact angle, increasing the contact area, and improving the axial load-bearing capacity. It also avoids the obvious stress concentration at both ends of the original structure, which leads to excessive heat generation and easy damage and failure of the rollers.

[0023] Both the shaft ring raceway 7 and the seat ring raceway 8 are set as logarithmic curves with a crown of 5-8 μm, and the highest point of crown is within 10% of the middle of the raceway width. Changing the shaft ring raceway 7 and the seat ring raceway 8 from straight lines to logarithmic curves with crown can effectively improve the stress distribution in the contact area between the helical tapered roller 3 and the raceway. This can reduce or eliminate edge stress concentration of the helical tapered roller 3 to a large extent, which is beneficial to fluid lubrication. It can also improve the roller off-center loading phenomenon caused by eccentricity due to installation and machining errors of the helical tapered roller 3 and deflection caused by spindle rotation, thereby improving bearing life.

[0024] The spiral tapered roller 3 has a spiral oil groove 4 on its conical rolling surface. The spiral oil groove 4 has a depth of 0.5-0.8 mm, a width of 0.7-1.5 mm, and a pitch of 10 mm. The spiral oil groove of the present invention has a clear directional guiding function, which directs the lubricating oil to the contact area of ​​the flange. This has unique application value in the lubrication and heat dissipation scenarios of large thrust bearings that bear axial loads. The spiral direction and dimensional parameters of the spiral oil groove have been optimized for the working conditions of large thrust bearings.

[0025] The spiral tapered roller 3 has a left-hand or right-hand spiral direction; the outer conical surface of the spiral tapered roller 3 forms a left-hand or right-hand spiral oil groove, which causes the lubricating oil entering the bearing to flow along the spiral oil groove 4 towards the outer flange 5 when the spiral tapered roller 3 rotates.

[0026] The direction of rotation of the rollers is crucial for determining the direction of rotation of the spiral oil groove 4. When the spiral tapered roller 3 rotates, the movement of its surface relative to the lubricating oil is similar to that of a rotating screw. This rotation generates a pumping effect, pushing the lubricating oil towards the outer end face. According to the wedge effect principle of hydrodynamic lubrication, the rotational motion should bring the lubricating oil in from the wider side of the wedge gap and compress it to the narrower side, thus forming a hydrodynamic oil film. Under a specific direction of rotation, in order for the lubricating oil to move axially towards the large end face of the spiral tapered roller 3, the direction of rotation of the spiral oil groove 4 must match the direction of rotation.

[0027] like Figure 1As shown, the thrust bearing rotates clockwise, meaning the bearing's central ring rotates clockwise. In this case, the motion of the helical tapered roller includes both revolution and rotation: the roller, along with the cage, revolves clockwise around the bearing axis. Due to friction between the roller and the rotating ring, the roller itself rotates around its axis, and its rotation direction is opposite to its revolution direction. Viewed from the large end of the helical tapered roller 3, its rotation is counter-clockwise, and the helical oil groove 4 on its outer conical surface should be right-handed. When the roller rotates counter-clockwise, the right-handed helical oil groove generates an axial hydrodynamic pressure component towards the large end spherical surface of the roller. This helps pump lubricating oil to the critical friction area between the large end spherical surface and the flange.

[0028] like Figure 2 As shown, the thrust bearing rotates counterclockwise, meaning the rotating shaft ring in the bearing rotates counterclockwise. At this time, the helical tapered roller rotates clockwise, opposite to its revolution direction. Viewed from the large end of the helical tapered roller 3, its rotation is clockwise, and the helical oil groove 4 on its outer conical surface should be left-handed. When the roller rotates clockwise, the left-handed helical oil groove generates an axial hydrodynamic pressure component towards the spherical surface of the large end of the roller. This helps to pump lubricating oil to the critical friction area between the spherical surface of the large end and the flange.

[0029] The extra-large thrust spiral tapered roller bearing of this invention features a simple structure and high reliability. An optimized spiral guide structure is incorporated on the surface of the tapered rollers. As the tapered rollers rotate, the spiral oil groove structure on the outer surface generates a pumping effect, continuously pushing lubricating oil towards the flange contact area, improving boundary lubrication conditions. The directional flow of lubricating oil removes heat generated by friction at the flange, effectively reducing bearing temperature rise. Active oil supply and forced heat dissipation reduce wear on the flange and roller end faces, significantly improving bearing lubrication performance. Furthermore, the right-angle structure of the two end faces of the tapered rollers is replaced with a circular arc transition structure. The flange areas where the inner and outer rings contact the rollers also utilize matching circular arcs to form arc-shaped raceways, increasing the contact angle and contact area, improving axial load capacity, and extending bearing service life.

Claims

1. A super-large thrust spiral tapered roller bearing, characterized in that: It includes a shaft ring, a seat ring, a cage, and a helical tapered roller. The shaft ring and the seat ring are respectively provided with raceways adapted to the helical tapered roller. The raceways of the shaft ring and the seat ring combine to form a conical annular groove. The helical tapered roller is installed in the annular groove between the shaft ring and the seat ring through the cage. The outer sides of the shaft ring raceway and the seat ring raceway are respectively provided with flange structures that mate with the large end face of the helical tapered roller. A helical oil groove is provided on the conical rolling surface of the helical tapered roller.

2. The extra-large thrust spiral tapered roller bearing according to claim 1, characterized in that: The junction of the two end faces of the spiral tapered roller with the conical surface is transitioned by an arc surface. The arc angle of the small end is R3-4mm, and the arc angle of the large end is R7-9mm. The large end face of the spiral tapered roller has a spherical structure. The flange that contacts the large end face of the spiral tapered roller has a conical structure.

3. The extra-large thrust spiral tapered roller bearing according to claim 1, characterized in that: The radius of the large end ball face of the spiral tapered roller is 0.95 times the radius of the flange cone face.

4. The extra-large thrust spiral tapered roller bearing according to claim 1, characterized in that: Both the shaft ring raceway and the seat ring raceway are set as logarithmic curves with a convexity of 5 to 8 μm and the highest point of convexity is within 10% of the middle of the raceway width.

5. A super-large thrust spiral tapered roller bearing according to claim 1, characterized in that: The depth of the spiral oil groove is 0.5–0.8 mm, the width of the spiral oil groove is 0.7–1.5 mm, and the pitch is 10 mm.

6. A super-large thrust spiral tapered roller bearing according to claim 1, characterized in that: The spiral tapered roller has a left-hand or right-hand spiral direction of rotation. The outer conical surface of the spiral tapered roller forms a left-hand or right-hand spiral oil groove, which allows the lubricating oil entering the bearing to flow along the spiral oil groove towards the outer flange when the spiral tapered roller rotates.

Images