A radial sliding roller bearing and a wind turbine generator set

Abstract

The utility model relates to a radial sliding roller bearing, comprising: a retaining ring, a supporting ring, and a nose ring, wherein the nose ring is located at the radial inner side of the retaining ring and the supporting ring, the nose ring has a nose portion protruding radially outward, and the nose portion is located between the retaining ring and the supporting ring; an upper raceway is arranged between the retaining ring and the nose portion of the nose ring to accommodate an upper row of axial rollers, and a lower raceway is arranged between the nose portion of the nose ring and the supporting ring to accommodate a lower row of axial rollers; a friction pad is arranged between the supporting ring and the nose, and the supporting ring and the nose ring can slide relative to each other by means of the friction pad.

Description

Technical Field

[0001] The utility model relates to a roller bearing, in particular to a radial sliding roller variable pitch bearing. Background Art

[0002] Wind turbines use variable pitch bearings to achieve blade pitching. Variable pitch bearings combine the blades with the hub and adjust the blade's windward angle to the best state according to the wind direction to improve wind energy utilization. Variable pitch bearings must have sufficient strength and the ability to withstand the combined effects of axial force, radial force, and overturning moment. They must also have stable operation, small starting torque, and good lubrication, corrosion resistance, and sealing properties. As a key component in wind turbines, variable pitch bearings have very low rotation speeds, usually less than 1rpm, and rolling bearings are often used in the prior art.

[0003] As the power of wind turbines increases, the dimensions of pitch bearings also increase. The current wind power market is extremely competitive, and wind turbines face enormous cost pressure. Traditional three-row roller pitch bearings are usually composed of nose rings, upper and lower rings, axial rollers, and radial rollers. To ensure the design life of the bearings, for example, sufficient distance must be ensured between the radial rollers and the mounting holes. Therefore, once the design load of the bearing is determined, the optimal values ​​of the axial and radial dimensions of the traditional pitch bearings are already determined.

[0004] To this end, the utility model provides a radial sliding roller pitch bearing with a design without radial rollers. The radial dimension of the pitch bearing is smaller, which reduces the cost of the pitch bearing. At the same time, other components of the wind turbine generator set, such as the hub, can also be designed to be relatively smaller in size, which is ultimately more conducive to reducing the cost of the entire unit.

[0005] It should be noted that the information disclosed in the background technology section of the utility model is only intended to deepen the understanding of the general background technology of the utility model, and should not be regarded as an admission or suggestion in any form that the information constitutes prior art already known to those skilled in the art. Utility Model Content

[0006] In order to overcome the above-mentioned defects, the utility model provides a radial sliding roller bearing, and in particular provides a radial sliding roller variable pitch bearing, so as to solve the technical problems of large size and complex processing technology of variable pitch bearings in the prior art.

[0007] According to one aspect of the utility model, a radial sliding roller bearing is provided, which includes: a retaining ring, a supporting ring, and a nose ring, wherein the nose ring is located radially inside the retaining ring and the supporting ring, and the nose ring has a nose protruding radially outward, and the nose is located between the retaining ring and the supporting ring; an upper raceway is provided between the retaining ring and the nose of the nose ring to accommodate an upper row of axial rollers, and a lower raceway is provided between the nose of the nose ring and the supporting ring to accommodate a lower row of axial rollers; a friction pad is provided between the supporting ring and the nose, and the supporting ring and the nose ring can slide relative to each other by means of the friction pad.

[0008] Preferably, the upper row of axial rollers and the lower row of axial rollers are evenly spaced apart by a retaining frame.

[0009] Preferably, the friction pad is fixed on the support ring, or fixed on the nose of the nose ring, and one radial side of the friction pad is a fixed surface fixed to the support ring or the nose, and the other radial side is a sliding surface.

[0010] Preferably, the sliding surface of the friction pad is an arcuate concave surface or an arcuate convex surface; and a nose ring mating surface or a support ring mating surface mating with the sliding surface is provided on the nose of the nose ring or the support ring.

[0011] Preferably, a plurality of friction pads are provided.

[0012] Preferably, each of the friction pads is connected to the nose ring or the support ring via a pair of screws.

[0013] Preferably, each friction pad is provided with a pair of through holes, the hole spacing between the pair of through holes is 250-320 mm, and the hole diameter of the through hole is 15-20 mm.

[0014] Preferably, the fixing surface where the nose ring or the support ring is fixed to the friction lining is counterfaced to a plane, and the counterface depth is 1 to 2 mm.

[0015] Preferably, the thickness d at the center of the arc surface of the friction pad is 2-10 mm, and more preferably 2-7 mm; the height H along the axial direction of the bearing is 10-50 mm, and more preferably 20-40 mm; the width W of the friction pad in the radial plane is 200-600 mm, and more preferably 300-500 mm; the interval between the friction pads is 100-200 mm, and more preferably 120-180 mm; the number of friction pads is 20-30, and more preferably 24-28.

[0016] In one embodiment, the thickness d at the center of the arc surface of the friction pad is 3 mm; the height H along the axial direction of the bearing is 30 mm; the width W of the radial plane is 400 mm; the interval between the friction pads is 150 mm; and the number of friction pads is 25.

[0017] Preferably, the material of the friction pad is a metal material or a non-metal material. The metal material includes copper alloy and aluminum alloy; the non-metal material includes engineering plastic and ceramic.

[0018] In one embodiment, the roller bearing is a pitch bearing.

[0019] Preferably, a plurality of seals are provided between mutually contacting surfaces of the retaining ring and the supporting ring, and / or a first sealing band is provided between the retaining ring and the nose ring, and / or a second sealing band is provided between the supporting ring and the nose ring.

[0020] Preferably, the retaining ring and the supporting ring are provided with a first mounting hole, which is a through hole penetrating the retaining ring and the supporting ring; and the nose ring is provided with a through second mounting hole.

[0021] Preferably, a plurality of first oil filling holes and a plurality of first oil draining holes are provided on the outer cylindrical surface of the retaining ring, and a plurality of second oil filling holes and a plurality of second oil draining holes are provided on the outer cylindrical surface of the supporting ring.

[0022] According to another aspect of the utility model, a wind turbine generator set is provided, which includes the aforementioned variable pitch bearing.

[0023] The radial sliding roller bearing provided by the utility model is adopted to further optimize the size design, compensate for the concentricity error caused by processing and installation errors, have good vibration resistance, and extend the service life. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 A cross-sectional view of a variable pitch bearing of the utility model at the locations of the first mounting hole and the second mounting hole is shown;

[0025] Figure 2 A schematic diagram showing the connection between the support ring and the retaining ring of the variable pitch bearing of the utility model is shown;

[0026] Figure 3 An enlarged view showing one embodiment of the friction lining being secured to the nose ring;

[0027] Figure 4 A structural schematic diagram of a friction lining is shown;

[0028] Figure 5A top view showing one embodiment of the connection between the friction lining and the nose ring;

[0029] Figure 6 Shows Figure 5 An enlarged diagram of some details of the connection between the middle friction pad and the nose ring. DETAILED DESCRIPTION

[0030] The following is a detailed description of an embodiment of the utility model. This embodiment is implemented on the premise of the technical solution of the utility model, and a detailed implementation method and a specific operation process are given, but the protection scope of the utility model is not limited to the following embodiment.

[0031] The terms "above", "below", "upward" and "downward" in the present invention represent an upper and lower positional relationship, but are not limited to vertical above and vertical below. Those skilled in the art can understand that obliquely above and obliquely below both belong to the scope of "above" and "below" in the present invention, and obliquely upward and obliquely downward both belong to the scope of "upward" and "downward" in the present invention; it is not limited to the above and below in the installed state, but is only the above and below positional relationship in the state shown in the view in the accompanying drawings.

[0032] In order to solve the above technical problems, the utility model proposes a radial sliding roller bearing, such as Figure 1 As shown, the roller bearing comprises: a retaining ring 1, a supporting ring 2, and a nose ring 3. The nose ring 3 is located radially inside the retaining ring 1 and the supporting ring 2. At the same time, the nose ring 3 has a nose 30 protruding radially outward, and the nose 30 is located between the retaining ring 1 and the supporting ring 2. An upper raceway is arranged between the retaining ring 1 and the nose 30 of the nose ring 3 to accommodate an upper row of axial rollers 5, and a lower raceway is arranged between the nose 30 of the nose ring 3 and the supporting ring 2 to accommodate a lower row of axial rollers 6. A friction lining 7 is arranged between the supporting ring 2 and the nose 30 of the nose ring 3, and the supporting ring 2 and the nose ring 3 can slide relative to each other by means of the friction lining 7.

[0033] like Figure 2 As shown, the retaining ring 1 and the supporting ring 2 are connected and fixed by a plurality of connecting screws 13, and the upper row of axial rollers 5 and the lower row of axial rollers 6 are evenly spaced apart by the retaining frame.

[0034] The friction pad 7 can be fixed on the support ring 2 or on the nose 30 of the nose ring 3. One side of the friction pad 7 along the radial direction is a fixed surface 7-3 fixed to the support ring or the nose, and the other side is a sliding surface 7-1. Figure 3As shown, it shows the situation that the friction pad 7 is fixed on the nose 30 of the nose ring 3. The sliding surface 7-1 of the friction pad 7 can be an arcuate concave surface. At this time, the supporting ring mating surface 2-1 of the supporting ring 2 that matches the sliding surface 7-1 is made into an arcuate convex surface. In this way, the relative sliding between the supporting ring 2 and the nose ring 3 is achieved through the cooperation between the concave surface of the sliding surface 7-1 and the convex surface of the supporting ring mating surface 2-1. The concave and convex surface design has the function of aligning and adjusting the radial clearance. The friction pad 7 can also be fixed on the supporting ring 2 (not shown in the figure). At this time, the nose ring mating surface 3-1 of the nose 30 of the nose ring 3 that matches the sliding surface 7-1 of the arcuate concave surface is made into an arcuate convex surface, and the fixed surface 7-3 of the friction pad 7 is fixed to the supporting ring 2.

[0035] In addition, the sliding surface 7-1 of the friction pad 7 can also be set as an arc-shaped convex surface (not shown in the figure), and the corresponding support ring matching surface 2-1 or the nose ring matching surface 3-1 is a corresponding arc-shaped concave surface.

[0036] Further, if Figure 4 , 5 As shown, multiple friction pads 7 are arranged between the nose ring 3 and the support ring 2. The thickness d of the center of the arc surface of the friction pad 7 is 2-10mm, preferably 2-7mm; the height H along the axial direction of the bearing is 10-50mm, preferably 20-40mm; the width W of the radial plane is 200-600mm, preferably 300-500mm; the interval between the friction pads is 100-200mm, preferably 120-180mm; the number of friction pads 7 is 20-30, preferably 24-28. Further preferably, the thickness d is 3mm, the height H is 30mm, the height W is 400mm, the interval between the friction pads is 150mm, and 25 friction pads are placed.

[0037] Further, when the friction pad 7 is fixed on the nose ring 3, in order to make the friction pad 7 and the nose ring 3 fit completely, the fixing surface 7-3 where the nose ring 3 and the friction pad 7 are fixed is countersunk into a plane, such as Figure 3-5 As shown, the spot facing depth is about 1 to 2 mm. A pair of through holes 70 are provided on the friction pad 7, and a threaded hole is provided in the nose ring 3. A pair of screws 7-2 pass through the through holes 70 and are connected to the threaded holes in the nose ring 3. The hole spacing between the through holes 70 is preferably 250-320 mm, more preferably 300 mm, and the through hole diameter is preferably 15-20 mm, more preferably 18 mm. The through holes 70 are preferably through holes. When the friction pad 7 is fixed to the support ring 2, the corresponding fixed surface of the support ring 2 and the friction pad 7 is spot faced. The material of the friction pad 7 can be metal, such as copper alloy, aluminum alloy, etc., or non-metallic material, such as engineering plastics, ceramics, etc.

[0038] Further, if Figure 1As shown, a plurality of first oil filling holes 14 and a plurality of first oil drain holes 15 may be provided on the outer cylindrical surface of the retaining ring 1, and a plurality of second oil inlet holes 16 and a plurality of second oil drain holes 17 may also be provided on the outer cylindrical surface of the supporting ring 2. Grease is injected into the bearing raceway space through the first oil inlet holes 14 and the second oil inlet holes 16 to achieve effective lubrication of the bearing, and waste grease in the bearing is discharged through the first oil drain holes 15 and the second oil drain holes 17.

[0039] In order to form a closed space in the bearing to store grease and prevent the grease from flowing out of the raceway, a plurality of seals 10 can be designed between the contacting surfaces of the retaining ring 1 and the supporting ring 2. The seals 10 can be O-type sealing strips. A first sealing strip 8 can be designed between the retaining ring 1 and the nose ring 3, and a second sealing strip 9 can be designed between the supporting ring 2 and the nose ring 3 to isolate foreign matter such as dust and oil to avoid affecting the function and life of the bearing.

[0040] The roller bearing of the utility model can be used as a variable pitch bearing, and the retaining ring 1 and the supporting ring 2 can be processed with corresponding first mounting holes 11 as required to penetrate the retaining ring 1 and the supporting ring 2, so that the bearing is connected to the fan hub. The nose ring 3 can be processed with a second mounting hole 12 as required to penetrate the bearing and the fan blade.

[0041] The radial sliding roller bearing of the utility model can also be processed with a tooth structure 4 on the inner side of the bearing or a tooth structure on the outer side of the bearing according to the needs of the wind power generation group.

[0042] Compared with the traditional three-row roller bearing, the beneficial effects of the utility model are:

[0043] 1. The radial rollers are replaced by friction pads, which effectively reduces the radial dimensions of the bearings, reduces the machining and quenching procedures of the radial raceways, improves the machining efficiency of the bearings, and thus reduces the cost of wind turbines.

[0044] 2. The radial roller adopts friction pad design, which increases the radial load capacity of the roller bearing to a certain extent.

[0045] 3. The mating surface between the friction pad and the support ring is an arc surface, which has a self-aligning effect, that is, the axis of each ring is adjusted to be concentric, and the radial clearance of the bearing can be adjusted at the same time. Correspondingly, it brings good anti-vibration performance and compensates for the concentricity error caused by processing, installation and deformation. When the bearing is subjected to the tipping force, the center of the inner and outer rings of the bearing may form a small angle. The self-aligning effect can make the bearing automatically adjust and adapt to this small angle, ensuring the normal operation of the bearing, thereby extending the life of the bearing and the wind turbine.

[0046] The foregoing disclosure of the embodiments of the present disclosure has been proposed for the purpose of illustration and description. It is not intended to be exhaustive or to limit the present disclosure to the precise form disclosed. In light of the above disclosure, many changes and modifications of the embodiments described herein will be apparent to those of ordinary skill in the art. Please note that the above examples are not intended to be restrictive. Additional embodiments of the devices and equipment that may include many of the above features may also be contemplated. After studying the accompanying drawings and detailed description, other devices, equipment, features and advantages of the present disclosure will become more apparent to those of ordinary skill in the art. It is intended that all such other devices, equipment, features and advantages be included within the scope of protection of the present utility model.

Claims

1. A radial sliding roller bearing, comprising: A retaining ring (1), a supporting ring (2), and a nose ring (3), wherein the nose ring (3) is located radially inward of the retaining ring (1) and the supporting ring (2), and is characterized in that: The nose ring (3) has a nose portion (30) protruding radially outward, and the nose portion (30) is located between the retaining ring (1) and the supporting ring (2); An upper raceway is provided between the retaining ring (1) and the nose (30) of the nose ring (3) to accommodate an upper row of axial rollers (5), and a lower raceway is provided between the nose (30) of the nose ring (3) and the support ring (2) to accommodate a lower row of axial rollers (6); A friction pad (7) is provided between the support ring (2) and the nose (30), and by means of the friction pad (7) the support ring (2) and the nose ring (3) can slide relative to each other.

2. The radial sliding roller bearing according to claim 1, characterized in that: The upper row of axial rollers (5) and the lower row of axial rollers (6) are evenly spaced apart by a retaining frame.

3. The radial sliding roller bearing according to claim 2, characterized in that: The friction pad (7) is fixed on the support ring (2) or on the nose (30) of the nose ring (3); one radial side of the friction pad (7) is a fixed surface (7-3) fixed to the support ring or the nose, and the other side is a sliding surface (7-1).

4. The radial sliding roller bearing according to claim 3, characterized in that: The sliding surface (7-1) of the friction pad (7) is an arcuate concave surface or an arcuate convex surface; the nose portion (30) of the nose ring is provided with a nose ring matching surface (3-1) matching with the sliding surface (7-1), or the support ring (2) is provided with a support ring matching surface (2-1) matching with the sliding surface (7-1).

5. The radial sliding roller bearing according to any one of claims 1 to 4, characterized in that: A plurality of friction pads (7) are provided.

6. The radial sliding roller bearing according to claim 5, characterized in that: Each friction pad (7) is connected to the nose ring (3) or the support ring (2) via a pair of screws (7-2).

7. The radial sliding roller bearing according to claim 6, characterized in that: Each friction pad (7) is provided with a pair of through holes (70), the hole spacing between the pair of through holes (70) is 250-320 mm, and the hole diameter of the through hole (70) is 15-20 mm.

8. The radial sliding roller bearing according to claim 5, characterized in that: The fixing surface where the nose ring (3) or the support ring (2) is fixed to the friction pad (7) is counterfaced to form a plane, and the counterface depth is 1 to 2 mm.

9. The radial sliding roller bearing according to claim 5, characterized in that: The thickness d at the center of the arc surface of the friction pad (7) is 2-10 mm; the height H along the axial direction of the bearing is 10-50 mm; the width W of the radial plane is 200-600 mm; the interval between the friction pads (7) is 100-200 mm; and the number of friction pads (7) is 20-30.

10. The radial sliding roller bearing according to claim 9, characterized in that: The thickness d of the arc surface center of the friction pad (7) is 2-7 mm; the height H along the axial direction of the bearing is 20-40 mm; the width W of the radial plane is 300-500 mm; the interval between the friction pads (7) is 120-180 mm; and the number of friction pads (7) is 24-28.

11. The radial sliding roller bearing according to claim 10, characterized in that: The thickness d of the center of the arc surface of the friction pad (7) is 3 mm; the height H along the axial direction of the bearing is 30 mm; the width W of the radial plane is 400 mm; the interval between the friction pads (7) is 150 mm; and the number of friction pads (7) is 25.

12. The radial sliding roller bearing according to claim 11, characterized in that: The roller bearing is a pitch bearing.

13. The radial sliding roller bearing according to any one of claims 1 to 4, characterized in that: A plurality of seals (10) are arranged between the mutually contacting surfaces of the retaining ring (1) and the supporting ring (2), and / or a first sealing belt (8) is arranged between the retaining ring (1) and the nose ring (3), and / or a second sealing belt (9) is arranged between the supporting ring (2) and the nose ring (3).

14. The radial sliding roller bearing according to any one of claims 1 to 4, characterized in that: The retaining ring (1) and the supporting ring (2) are provided with a first mounting hole (11), and the first mounting hole (11) is a through hole penetrating the retaining ring (1) and the supporting ring (2); The nose ring (3) is provided with a through second mounting hole (12).

15. The radial sliding roller bearing according to any one of claims 1 to 4, characterized in that: The outer cylindrical surface of the retaining ring (1) is provided with a plurality of first oil filling holes (14) and a plurality of first oil draining holes (15), and the outer cylindrical surface of the supporting ring (2) is provided with a plurality of second oil filling holes (16) and a plurality of second oil draining holes (17).

16. A wind turbine generator set, comprising the radial sliding roller bearing according to any one of claims 1 to 15.

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