Alternative bearing construction for spherical roller bearing

Abstract

The application relates to the bearing field and discloses a bearing structure for replacing a spherical roller bearing, which comprises a bearing seat, an outer bearing sleeve is shrink-fitted on the inner side of the bearing seat, two conical roller bearings are arranged side by side on the inner side of the outer bearing sleeve, the outer ring of the conical roller bearing is shrink-fitted with the outer bearing sleeve, and the inner ring of the conical roller bearing is shrink-fitted with a shaft. The application can solve the problem that the bearing roller raceway is easily subjected to unilateral load due to the improper ratio of axial stress and radial stress when the spherical roller bearing is applied, can prevent the bearing from slipping in the application of a wind power gear box, and can customize the outer bearing sleeve to solve the wear repair problem of the bearing hole.

Description

Technical Field

[0001] This invention relates to the field of bearings, and more specifically to an alternative bearing structure for spherical roller bearings. Background Technology

[0002] Spherical roller bearings, as self-aligning locating end bearings, typically have external limiting treatments for the inner and outer rings, and the bearings bear relatively large axial loads. For example... Figure 1 As shown, in applications, spherical roller bearings are typically configured with a clearance fit on the outer ring and an interference fit on the inner ring. During use, the ratio of axial to radial forces is often small, leading to uneven load distribution on the bearing raceways and rapid wear on one side, resulting in premature failure. Wear is also common in the bearing housing's load-bearing area where the outer ring mates with the bearing, causing the actual bearing life to be far shorter than the design life. In self-aligning bearings, the movement of the outer ring often causes wear in the bearing bore of the housing. Bearing bore wear is a common failure symptom in gearboxes, significantly impacting gear meshing and further accelerating bearing failure. Summary of the Invention

[0003] This invention aims to provide an alternative bearing structure for spherical roller bearings, addressing the problem that improper axial-to-radial force ratio in spherical roller bearings can lead to uneven load distribution on the bearing raceways, resulting in rapid wear on one side of the raceway. It also prevents wear on the bearing bore walls of the housing caused by relative movement between the bearing outer ring and the housing.

[0004] To achieve the above objectives, the present invention adopts the following technical solution: a replacement bearing structure for spherical roller bearings, comprising a bearing housing, an outer bearing sleeve with an interference fit on the inner side of the bearing housing, two tapered roller bearings arranged side by side on the inner side of the outer bearing sleeve, the outer ring of the tapered roller bearings having an interference fit with the outer bearing sleeve, and the inner ring of the tapered roller bearings having an interference fit with the shaft.

[0005] Preferably, as an improvement, the outer bearing sleeve protrusion between the outer rings of the two tapered roller bearings forms an outer spacer, and an inner spacer is provided between the inner rings of the two tapered roller bearings, with a step on the inner spacer.

[0006] Preferably, as an improvement, the two tapered roller bearings are arranged asymmetrically.

[0007] Preferably, as an improvement, the outer bearing sleeve is provided with an annular groove, and the bearing housing is provided with an oil supply channel communicating with the annular groove. The width of the annular groove is greater than the width of the oil groove in the replacement spherical roller bearing. This ensures that the lubrication effect of the replacement structure is not weakened compared to the original spherical roller bearing.

[0008] Preferably, as an improvement, a hollow threaded stop nozzle is threadedly connected to the oil supply channel. The hollow threaded stop nozzle has a three-way oil passage inside, with one end of the three-way oil passage connected to the oil supply channel and the other two ends connected to the annular groove.

[0009] Preferably, as an improvement, the outer bearing sleeve is provided with a radial hole, and the hollow threaded stop nozzle includes a cylindrical end, which is inserted into the radial hole and has a clearance fit with the radial hole.

[0010] Preferably, as an improvement, four lubricating oil holes are evenly distributed along the circumference of the outer bearing sleeve. One end of the lubricating oil hole is connected to the annular groove, and the other end extends to the inner side of the outer spacer.

[0011] The principle and advantages of this solution are as follows: In practical applications, two asymmetrically arranged tapered roller bearings are paired, resulting in more sufficient contact between the roller raceways and a more suitable bearing for axial forces. This effectively avoids the situation where the contact is biased towards one side of the bearing when the ratio of axial load to radial load is small, thus preventing premature failure caused by wear on one side of the raceway. It is particularly suitable for gearboxes with unidirectional motion. The asymmetrical arrangement can strengthen the rollers on the side subjected to axial load, thereby maximizing the overall load-bearing capacity of the bearing assembly. In addition, the outer diameter fit dimension deviation of the outer bearing sleeve is positive, which is larger than the outer diameter fit tolerance of spherical roller bearings under the same conditions. Usually, self-aligning bearings have a clearance fit when the outer ring is stationary. However, this solution ensures radial interference after assembly. When the outer bearing sleeve tends to slip in the circumferential direction due to impact loads or other reasons, the interference between it and the bearing housing will prevent slippage. Furthermore, the cylindrical end of the hollow threaded stop oil nozzle and the insertion fit with the radial hole can also prevent circumferential slippage of the bearing outer sleeve, serving both the functions of oil supply and stopping. This solution, utilizing interference fit and hollow threaded stop valves, can completely eliminate bearing slippage in wind turbine gearbox applications. During maintenance, a custom-made outer bearing sleeve can be used to repair wear on the bearing bore; the hollow threaded stop valves prevent rotation of the outer bearing sleeve, thus avoiding wear on the bearing bore and preventing bearing bore wear caused by bearing slippage. Attached Figure Description

[0012] Figure 1 This is a schematic diagram illustrating the application of existing technologies.

[0013] Figure 2 This is a cross-sectional view of an embodiment of the present invention.

[0014] Figure 3 for Figure 2 A magnified view of point A in the middle. Detailed Implementation

[0015] The following detailed description illustrates the specific implementation method:

[0016] The reference numerals in the accompanying drawings include: bearing housing 1, outer bearing sleeve 2, outer spacer 3, shaft end baffle 4, tapered roller bearing 5, inner spacer 6, lubricating oil hole 7, annular groove 8, limit baffle 9, rotating shaft 10, oil supply channel 11, hollow threaded stop grease nipple 12, cylindrical end 13, radial hole 14, tee oil passage 15.

[0017] The basic implementation examples are as follows: Figure 2 , Figure 3 The diagram shows a replacement bearing structure for a spherical roller bearing, comprising a bearing housing 1. The bearing housing 1 has a positioning step and a limiting annular groove 8 on its inner side. An outer bearing sleeve 2 is interference-fitted onto the bearing housing 1 between the positioning step and the limiting annular groove 8. A limiting baffle 9 is embedded within the limiting annular groove 8, limiting the end face of the outer bearing sleeve 2 away from the positioning step. The outer bearing sleeve 2 has the annular groove 8, and the bearing housing 1 has an oil supply channel 11 communicating with the annular groove 8. The width of the annular groove 8 is greater than the width of the oil groove in the replacement spherical roller bearing. A hollow threaded stop grease nipple 12 is threadedly connected to the oil supply channel 11. The hollow threaded stop grease nipple 12 has a three-way oil passage 15 inside, one end of which communicates with the oil supply channel 11, and the other two ends communicate with the annular groove 8. The outer bearing sleeve 2 has a radial hole 14. A hollow threaded stop grease nipple 12 includes a cylindrical end 13, which is inserted into the radial hole 14 and has a clearance fit. Two tapered roller bearings 5 ​​are arranged side-by-side on the inner side of the outer bearing sleeve 2. The two tapered roller bearings 5 ​​are asymmetrically arranged, and their outer rings are interference-fitted with the outer bearing sleeve 2. An outer spacer 3 is formed by a protrusion on the outer bearing sleeve 2 between the outer rings of the two tapered roller bearings 5. An inner spacer 6 is provided between the inner rings of the two tapered roller bearings 5, and the inner spacer 6 has a step. Four lubrication holes 7 are evenly distributed along the circumference of the outer bearing sleeve 2. One end of each lubrication hole 7 communicates with an annular groove 8, and the other end extends to the inner side of the outer spacer 3.

[0018] The specific implementation process is as follows: In application, a positioning shoulder is machined on the rotating shaft 10, and a shaft end plate 4 is bolted to the end of the rotating shaft 10. Two tapered roller bearings 5 ​​and an inner spacer 6 are located on the rotating shaft 10 between the positioning shoulder and the shaft end plate 4. The inner ring of the tapered roller bearing 5 has an interference fit with the shaft. During the operation of the rotating shaft 10, the two asymmetrically arranged tapered roller bearings 5 ​​are paired, resulting in more sufficient contact between the roller raceways and a more suitable bearing for axial force. This effectively avoids the situation where the contact is biased towards one side of the bearing when the ratio of axial load to radial load is small, thus preventing premature failure caused by wear on one side of the raceway. The asymmetrical arrangement is particularly suitable for unidirectional gearboxes, using a wider row of rollers to bear the axial force. The life distribution of the two rows of rollers is more uniform, significantly improving the actual service life of the bearings compared to symmetrically arranged double-row self-aligning or tapered roller bearings. Furthermore, the outer diameter fit dimension deviation of the outer bearing sleeve 2 is positive, and its outer diameter is larger than that of a spherical roller bearing under the same conditions. After assembly, it can ensure radial interference. When the outer bearing sleeve 2 tends to slip or slide in the circumferential direction due to impact load or other reasons, its interference with the bearing housing 1 will prevent slippage. In addition, the insertion fit between the cylindrical end 13 and the radial hole 14 can also prevent circumferential slippage of the bearing outer sleeve. Lubricating oil enters from the oil supply channel 11, enters the annular groove 8 through the three-way oil passage 15 inside the hollow threaded stop oil nozzle 12, and then enters the lubricating oil hole 7 through the annular groove 8. From the lubricating oil hole 7, it enters between the two tapered roller bearings 5 ​​for lubrication. The hollow threaded stop oil nozzle 12 has both positioning and lubrication functions.

[0019] The above descriptions are merely embodiments of the present invention, and common knowledge regarding specific technical solutions or characteristics is not elaborated upon here. It should be noted that those skilled in the art can make various modifications and improvements without departing from the technical solutions of the present invention, and these should also be considered within the scope of protection of the present invention. These modifications and improvements will not affect the effectiveness of the implementation of the present invention or the practicality of the patent. The scope of protection claimed in this application should be determined by the content of its claims, and the specific embodiments described in the specification can be used to interpret the content of the claims.

Claims

1. A replacement bearing structure for spherical roller bearings, characterized in that: The bearing housing includes an outer bearing sleeve with an interference fit on the inner side of the bearing housing. Two tapered roller bearings are arranged side by side on the inner side of the outer bearing sleeve. The outer ring of the tapered roller bearing is interference fitted with the outer bearing sleeve, and the inner ring of the tapered roller bearing is interference fitted with the shaft. The outer bearing sleeve is provided with an annular groove, and the bearing seat is provided with an oil supply channel communicating with the annular groove. A hollow threaded stop oil nozzle is threadedly connected in the oil supply channel. The outer bearing sleeve is provided with a radial hole. The hollow threaded stop oil nozzle includes a cylindrical end. The cylindrical end is inserted into the radial hole and is clearance-fitted with the radial hole. When the outer bearing sleeve has a tendency to rotate, and the hole wall and the cylindrical end come into contact, the movement will be stopped.

2. The alternative bearing structure for a spherical roller bearing according to claim 1, characterized in that: An outer bearing sleeve protrusion between the outer rings of two tapered roller bearings forms an outer spacer, and an inner spacer is provided between the inner rings of the two tapered roller bearings, with a step on the inner spacer.

3. The alternative bearing structure for a spherical roller bearing according to claim 2, characterized in that: The two tapered roller bearings are arranged asymmetrically.

4. The alternative bearing structure for a spherical roller bearing according to claim 3, characterized in that: The width of the annular groove is greater than the width of the oil groove in the alternative spherical roller bearing.

5. The alternative bearing structure for a spherical roller bearing according to claim 4, characterized in that: The hollow threaded stop nozzle has a three-way oil passage inside, with one end of the three-way oil passage connected to the oil supply channel and the other two ends connected to the annular groove.

6. The alternative bearing structure for a spherical roller bearing according to claim 5, characterized in that: The radial hole size is 0.05 mm larger than the cylindrical end.

7. The alternative bearing structure for a spherical roller bearing according to claim 6, characterized in that: The outer bearing sleeve has four lubricating oil holes evenly distributed along the circumference. One end of the lubricating oil hole is connected to the annular groove, and the other end extends to the inner side of the outer spacer.

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