Three-row tapered column combined rotary table bearing

Abstract

The utility model relates to a kind of three-row taper column combined rotary table bearing, comprising: first outer ring, second outer ring, inner ring and three rows of rolling body, three rows of rolling body are all set in respective cage;Annular boss is formed to outer wall of inner ring outward, first outer ring and second outer ring inner wall jointly form annular groove, annular groove and the annular boss of the outer wall of inner ring inlay cooperation, form the three annular raceways of upper, middle and lower distribution;Three annular raceways include two axial raceways and a radial raceway;Cone roller is arranged in the axial raceway in upper, cylindrical roller is arranged in the axial raceway in lower;Middle is radial raceway, cylindrical roller is arranged in radial raceway;The scheme adopts taper column combined form, not only can withstand axial force, radial force and overturning moment;Compared with the traditional cylindrical roller design mode simultaneously, the possibility of roller fragmentation can be reduced by reducing raceway wear by offsetting the tensile stress caused by the deformation of the roller transmitted by the paddle.

Description

Technical Field

[0001] This utility model relates to a three-row tapered slewing bearing, which is applied to the independent pitch control system of ultra-large megawatt onshore, coastal, floating and offshore wind turbine generator sets, and belongs to the field of bearing design technology. Background Technology

[0002] In recent years, with the increasing acceptance of clean energy, our understanding of wind power generation has deepened, and the proportion of wind turbine units has become increasingly larger. Pitch bearings are an indispensable key component in the entire wind turbine design. During operation, they simultaneously bear axial loads, radial loads, and overturning moments, exhibiting characteristics such as complex operating load conditions, harsh operating environments, and relatively low overall stiffness. Therefore, the strength of pitch bearings not only affects the overall lifespan of the bearing but also has a significant impact on the overall stability and efficient, safe operation of the wind turbine unit.

[0003] Due to the continuously harsh working environment of wind turbines, the increasing size of megawatt-class turbines, and the continuous increase in blade length, the requirements for load control capabilities are constantly increasing, posing a great challenge to the lifespan and load-bearing capacity of bearings. In particular, the axial raceway near the blade side of traditional three-row cylindrical pitch bearings not only bears axial force, radial force, and overturning moment, but also tensile stress transmitted from the wind to the blades. This causes the rollers in the axial raceway to have a certain tilt angle, which can lead to severe wear of the raceway and breakage of the rollers in severe cases. Therefore, it is urgent to design a three-row tapered slewing bearing with high load capacity, high wear resistance, and long service life. Utility Model Content

[0004] To overcome the challenges posed by the complex operating conditions, large size, and harsh environments of ultra-large megawatt offshore and deep-sea compliant wind turbine generator sets, this invention provides a three-row tapered slewing bearing with advantages such as high load capacity, high wear resistance, and long service life, greatly improving the service life of the bearing raceway and thus enhancing the bearing's reliability.

[0005] To achieve the above objectives, the technical solution adopted by this utility model is as follows: a three-row tapered roller combined slewing bearing, comprising: a first outer ring, a second outer ring, an inner ring, and three rows of rolling elements disposed between the three, each of the three rows of rolling elements being disposed in its respective cage; an annular boss is formed outward on the outer wall of the inner ring, and the inner walls of the first and second outer rings together form an annular groove, the annular groove and the annular boss on the outer wall of the inner ring being fitted together to form three annular raceways distributed at the top, middle, and bottom; the three annular raceways include two axial raceways and one radial raceway; tapered rollers are disposed in the upper axial raceway, and cylindrical rollers are disposed in the lower axial raceway; a middle radial raceway is formed between the bottom of the annular groove at the junction of the first and second outer rings and the outer diameter of the annular boss of the inner ring, and cylindrical rollers are disposed in the middle radial raceway; the cylindrical rollers in the radial raceway are embedded in the inner ring; Furthermore, the inner ring has teeth on its inner circumference, and the teeth mesh with the external drive gear; Furthermore, the first outer ring and the second outer ring are provided with corresponding connecting mounting holes, and the inner ring is provided with mounting holes that pass through the upper and lower ends. Furthermore, a stop design is provided at the junction of the first outer ring and the second outer ring.

[0006] Furthermore, the axial raceway located above the bearing is an auxiliary bearing raceway, including an inclined raceway on the upper surface of the inner ring annular boss and an inclined raceway on the lower axial surface inside the first outer ring, and the outer circumferential surface of the tapered roller rolls in contact with the two inclined raceways. Furthermore, the taper of the tapered roller is between 1° and 2°, with the larger end of the tapered roller close to the first outer ring, i.e., towards the outer diameter of the bearing, and the smaller end of the tapered roller close to the inner ring, i.e., towards the inner diameter of the bearing. Furthermore, the axial raceway located below the bearing is the main load-bearing raceway, including a straight raceway located on the lower surface of the inner ring annular boss and a straight raceway on the inner axial upper surface of the second outer ring, and the outer circumferential surface of the cylindrical roller rolls in contact with the two straight raceways. Furthermore, the radial raceway located in the middle of the bearing is used to bear radial force and overturning moment, and bears a relatively small load; the radial raceway includes a boss straight raceway located on the inner radial surface of the first outer ring and a radial straight raceway in the groove opened in the outer diameter of the inner ring annular boss, the cylindrical roller is embedded in the groove opened in the outer diameter of the inner ring annular boss and the outer circumferential surface of the cylindrical roller rolls in contact with the boss straight raceway and the radial straight raceway.

[0007] Furthermore, the cage containing the tapered rollers in the auxiliary bearing raceway and the cage containing the cylindrical rollers in the main bearing raceway are both separate cages. The two cages are respectively provided with a gap of 1~2mm between themselves and the raceway. When the bearing is running, the two cages can contact the inner ring. The gap between the cage and the raceway can ensure that the parts do not jam during operation, and at the same time limit the relative position of the rolling elements and the raceway of the raceway. Furthermore, the upper and lower end faces of the cage containing the cylindrical rollers in the radial raceway are respectively separated from the sidewall of the groove opened on the outer diameter of the inner ring annular boss. This cage is a split cage, and the gap is generally 1~2mm.

[0008] In the structure described above, the bearing side closer to the auxiliary bearing raceway is the blade side of the bearing, and the bearing side closer to the main bearing raceway is the hub side of the bearing. In this bearing structure, the bearing mainly bears the overturning moment during operation. The force is transmitted from the blade to the inner ring, and from the inner ring to the outer ring through the rolling elements. During this process, since the outer ring is split, a gap tendency will be formed. That is, the two raceways of the outer ring, namely the inclined raceway on the axial lower surface of the first outer ring and the straight raceway on the axial upper surface of the second outer ring, open with a trumpet-like tendency. The design of the inclined raceway on the axial lower surface of the first outer ring can compensate for this tendency.

[0009] Seals are also provided between the first outer ring and the inner ring on the blade side near the bearing end face, and between the second outer ring and the inner ring on the hub side near the bearing end face.

[0010] The beneficial effects of this utility model are: This design adopts a conical-cylinder combination, which can withstand axial force, radial force and overturning moment. Compared with the traditional cylindrical roller design, it can also offset the deformation of the roller caused by tensile stress transmitted from the blade, thereby reducing raceway wear and the possibility of roller breakage. Finite element analysis has verified that this combination design can greatly reduce the circumferential stress concentration problem of the bearing ring and reduce the wear of the raceway on the blade side, thereby improving the bearing's life and reliability. Tapered roller bearings are designed in the axial auxiliary bearing raceway on the blade side. The large end of the tapered rollers is close to the outer diameter of the bearing, and the small end is close to the inner diameter of the bearing. This can alleviate the slippage caused by differential speed during rotation. The bearing outer ring adopts a split structure, and the tapered roller bearing design in the axial auxiliary bearing raceway on the blade side forms an inclined raceway, which allows the bearing outer ring to compensate for the clearance tendency caused by the split structure during bearing operation. Attached Figure Description

[0011] Figure 1 This is a structural diagram of the three-row conical combined turntable bearing of this utility model.

[0012] Figure 2 The stress cloud diagram of the outer ring after the three rows of conical columns are designed together in this utility model.

[0013] Figure 3 Stress cloud diagram for the outer ring of a conventional design.

[0014] In the figure, 1. First outer ring, 2. Second outer ring, 3. Inner ring, 4. Annular boss, 5. Tapered roller, 6. Cylindrical roller, 7. Inclined raceway on the upper surface of the inner ring annular boss, 8. Inclined raceway on the lower axial surface of the inner first outer ring, 9. Straight raceway on the lower surface of the inner ring annular boss, 10. Straight raceway on the upper axial surface of the inner second outer ring, 11. Straight raceway of the boss on the radial surface of the inner first outer ring, 12. Radial straight raceway, 13. Cage containing the tapered roller in the auxiliary load-bearing raceway, 14. Cage containing the cylindrical roller in the main load-bearing raceway, 15. Cage containing the cylindrical roller in the radial raceway, 16. Blade side, 17. Hub side, 18. Seal. Detailed Implementation

[0015] To make the above-mentioned objects, features, and advantages of this utility model more apparent and understandable, the specific embodiments of this utility model will be described in detail below with reference to the accompanying drawings. Many specific details are set forth in the following description to provide a full understanding of this utility model. However, this utility model can be implemented in many other ways different from those described herein, and those skilled in the art can make similar modifications without departing from the spirit of this utility model. Therefore, this utility model is not limited to the specific embodiments disclosed below.

[0016] like Figure 1 A three-row tapered roller combined slewing bearing is shown, comprising: a first outer ring 1, a second outer ring 2, an inner ring 3, and three rows of rolling elements disposed between them, each row of rolling elements being housed in its respective cage; an annular boss 4 is formed outwardly on the outer wall of the inner ring 3, and the inner walls of the first outer ring 1 and the second outer ring 2 together form an annular groove, which is fitted into the annular boss 4 on the outer wall of the inner ring 3 to form three annular raceways distributed at the top, middle, and bottom; the three annular raceways include two axial raceways and one radial raceway; tapered rollers 5 are arranged rolling in the upper axial raceway, and cylindrical rollers 6 are arranged rolling in the lower axial raceway; a middle radial raceway is formed between the bottom of the annular groove at the junction of the first outer ring 1 and the second outer ring 2 and the outer diameter of the annular boss 4 of the inner ring 3, and cylindrical rollers are arranged rolling in the middle radial raceway; the cylindrical rollers in the radial raceway are embedded within the inner ring; Furthermore, the inner ring 3 has teeth on its inner wall circumference, and the teeth mesh with the external drive gear. The drive gear drives the bearing to rotate through the meshing of the teeth. Furthermore, the first outer ring 1 and the second outer ring 2 are respectively provided with corresponding connecting mounting holes, and the inner ring 3 is provided with mounting holes that pass through the upper and lower ends; it is connected to the connector through the mounting holes. Furthermore, a stop design is provided at the junction of the first outer ring 1 and the second outer ring 2, which can effectively prevent radial movement of the two outer rings.

[0017] Furthermore, the axial raceway located above the bearing is an auxiliary bearing raceway, including an inclined raceway 7 located on the upper surface of the inner ring annular boss and an inclined raceway 8 located on the lower axial surface inside the first outer ring. The outer circumferential surface of the tapered roller 5 rolls in contact with the two inclined raceways. The auxiliary bearing raceway is used to withstand axial force and overturning moment. Furthermore, the taper of the tapered roller 5 is between 1° and 2°. The large end of the tapered roller 5 is close to the first outer ring 1, that is, towards the outer diameter of the bearing, and the small end of the tapered roller 5 is close to the inner ring 3, that is, towards the inner diameter of the bearing. This can alleviate the slippage caused by differential speed during rotation. Furthermore, the axial raceway located below the bearing is the main load-bearing raceway, including a straight raceway 9 located on the lower surface of the inner ring annular boss and a straight raceway 10 located on the inner axial upper surface of the second outer ring. The outer circumferential surface of the cylindrical roller 6 rolls in contact with the two straight raceways. The main load-bearing raceway is used to withstand axial force and overturning moment. Furthermore, the radial raceway located in the middle of the bearing is used to bear radial force and overturning moment, and bears a relatively small load; the radial raceway includes a boss straight raceway 11 located on the inner radial surface of the first outer ring and a radial straight raceway 12 in the groove opened on the outer diameter of the inner ring annular boss 4. The cylindrical roller 6 is embedded in the groove opened on the outer diameter of the inner ring annular boss 4 and the outer circumferential surface of the cylindrical roller 6 rolls in contact with the boss straight raceway 11 and the radial straight raceway 12.

[0018] Furthermore, the cage 13 containing the tapered rollers in the auxiliary bearing raceway and the cage 14 containing the cylindrical rollers in the main bearing raceway are both separate cages. The two cages are respectively provided with a gap of 1~2mm between themselves and the raceway. When the bearing is running, the two cages can contact the inner ring 3. The gap between the cage and the raceway can ensure that the parts do not jam during operation, and at the same time limit the relative position of the rolling elements and the raceway of the raceway. Furthermore, the upper and lower end faces of the cage 15 containing the cylindrical rollers in the radial raceway are respectively separated from the side wall of the groove opened on the outer diameter of the inner ring annular boss 4. The cage 15 is a split cage, and the gap is generally 1~2mm.

[0019] In the structure described above, the bearing side closer to the direction of the auxiliary bearing raceway is the blade side 16 of the bearing, and the bearing side closer to the direction of the main bearing raceway is the hub side 17 of the bearing. In this bearing structure, the bearing mainly bears the overturning moment during operation. The force is transmitted from the blade to the inner ring 3, and then from the inner ring 3 to the outer ring through the rolling elements. During this process, since the outer ring is split, a gap tendency will be formed. The two raceways of the outer ring, namely the inclined raceway 8 on the axial lower surface of the first outer ring and the straight raceway 10 on the axial upper surface of the second outer ring, open with a trumpet-like tendency. The design of the inclined raceway 8 on the axial lower surface of the first outer ring can compensate for this tendency.

[0020] Furthermore, seals 18 are respectively provided between the first outer ring 1 and the inner ring 3 near the bearing end face on the blade side 16, and between the second outer ring 2 and the inner ring 3 near the bearing end face on the hub side 17, for sealing at both ends of the bearing, so that the bearing has a better sealing effect.

[0021] The design of the 16-axis tapered roller bearing on the blade side of this bearing is compared with the conventional cylindrical roller bearing design. Finite element analysis is used to illustrate the differences. Figure 2 The stress cloud diagram of the outer ring after the three-row conical column joint design of this scheme is shown below. Figure 3 The stress cloud diagram of the outer ring in the conventional design shows that the tapered roller design of the axial raceway on the blade side in this scheme can greatly reduce the circumferential stress concentration problem of the raceway, reduce the wear of the blade side raceway, and thus improve the bearing's life and reliability.

[0022] In the description of this utility model, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this utility model and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model.

[0023] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this utility model, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0024] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0025] In this utility model, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0026] It should be noted that when an element is referred to as being "fixed to" or "set on" another element, it can be directly on the other element or there may be an intervening element. When an element is considered to be "connected to" another element, it can be directly connected to the other element or there may be an intervening element. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used herein are for illustrative purposes only and do not represent the only possible implementation.

Claims

1. A three-row tapered spool bearing, characterized in that, include: Three rows of rolling elements are arranged between the first outer ring, the second outer ring, and the inner ring, with each row of rolling elements housed in its respective cage. An annular boss is formed on the outer wall of the inner ring, and the inner walls of the first and second outer rings together form an annular groove. This groove engages with the annular boss on the outer wall of the inner ring, forming three annular raceways distributed at the top, middle, and bottom. These three annular raceways include two axial raceways and one radial raceway. Conical rollers roll in the upper axial raceway, while cylindrical rollers roll in the lower axial raceway. A central radial raceway is formed between the bottom of the annular groove at the junction of the first and second outer rings and the outer diameter of the annular boss on the inner ring. Cylindrical rollers roll in this central radial raceway. The cylindrical rollers in the radial raceway are embedded within the inner ring.

2. The three-row tapered spool bearing according to claim 1, characterized in that: The first outer ring and the second outer ring are provided with corresponding connecting mounting holes, and the inner ring is provided with mounting holes that pass through the upper and lower ends.

3. The three-row tapered slewing bearing according to claim 1, characterized in that: A stop design is provided at the junction of the first outer ring and the second outer ring.

4. The three-row tapered spool bearing according to claim 1, characterized in that: The axial raceway located above the bearing is the auxiliary load-bearing raceway, which includes the inclined raceway on the upper surface of the inner ring annular boss and the inclined raceway on the lower axial surface inside the first outer ring. The outer circumferential surface of the tapered roller makes rolling contact with the two inclined raceways.

5. A three-row tapered spool bearing according to claim 4, characterized in that: The taper of the tapered roller is between 1° and 2°. The larger end of the tapered roller is close to the first outer ring, i.e., towards the outer diameter of the bearing, and the smaller end of the tapered roller is close to the inner ring, i.e., towards the inner diameter of the bearing.

6. A three-row tapered spool bearing according to claim 4, characterized in that: The axial raceway located below the bearing is the main load-bearing raceway, including a straight raceway on the lower surface of the inner ring annular boss and a straight raceway on the inner axial upper surface of the second outer ring. The outer circumferential surface of the cylindrical rollers makes rolling contact with these two straight raceways.

7. A three-row tapered spool bearing according to claim 1, characterized in that: The radial raceway includes a boss straight raceway located on the inner radial surface of the first outer ring and a radial straight raceway in a groove opened in the outer diameter of the inner ring annular boss. The cylindrical roller is embedded in the groove opened in the outer diameter of the inner ring annular boss and the outer circumferential surface of the cylindrical roller rolls in contact with the boss straight raceway and the radial straight raceway.

8. A three-row tapered spool bearing according to claim 6, characterized in that: The cage containing the tapered rollers in the auxiliary bearing raceway and the cage containing the cylindrical rollers in the main bearing raceway are both separate cages. The two cages are respectively provided with a gap between themselves and the raceway, and the gap is 1~2mm.

9. A three-row tapered spool bearing according to claim 7, characterized in that: The upper and lower ends of the cage containing the cylindrical rollers in the radial raceway are respectively spaced apart from the sidewall of the groove opened on the outer diameter of the inner ring annular boss.

10. A three-row tapered spool bearing according to claim 6, characterized in that: The bearing side closer to the direction of the auxiliary load-bearing raceway is the blade side of the bearing, and the bearing side closer to the direction of the main load-bearing raceway is the hub side of the bearing. Seals are also provided between the first outer ring and the inner ring near the bearing end face on the blade side, and between the second outer ring and the inner ring near the bearing end face on the hub side.

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