阅读说明：本技术 轴承及风力发电机组的轴承系统 (Bearing and bearing system of wind generating set ) 是由 孙振生 古雅琦 白欢欢 于 2019-03-28 设计创作，主要内容包括：本发明提供了一种轴承及风力发电机组的轴承系统。该轴承为推力轴承,该推力轴承包括外圈和内圈,其中,外圈和内圈均为一体式结构,内圈和外圈之间形成有连续的第一环形滚道和连续的第二环形滚道,第一环形滚道中设置有第一滚动体,第二环形滚道中设置有第二滚动体,第一滚动体的结构与第二滚动体的结构不同。本发明可提高轴承的承载能力、提高轴承套圈的强度,以有效地避免套圈疲劳断裂及滚道边缘压溃等问题。(The invention provides a bearing and a bearing system of a wind generating set. The bearing is a thrust bearing and comprises an outer ring and an inner ring, wherein the outer ring and the inner ring are of an integrated structure, a continuous first annular roller path and a continuous second annular roller path are formed between the inner ring and the outer ring, a first rolling body is arranged in the first annular roller path, a second rolling body is arranged in the second annular roller path, and the structure of the first rolling body is different from that of the second rolling body. The invention can improve the bearing capacity of the bearing and the strength of the bearing ring, so as to effectively avoid the problems of fatigue fracture of the ring, crushing of the edge of the raceway and the like.)

1. The utility model provides a bearing, the bearing is thrust bearing, its characterized in that, thrust bearing includes outer lane (100) and inner circle (200), wherein, outer lane (100) with inner circle (200) are the integral type structure, inner circle (200) with be formed with continuous first annular raceway and continuous second annular raceway between outer lane (100), be provided with first rolling element in the first annular raceway, be provided with the second rolling element in the second annular raceway, the structure of first rolling element with the structure of second rolling element is different.

2. Bearing according to claim 1, wherein the first rolling element is of roller (300) construction; the second rolling body is of a ball (400) structure.

3. A bearing according to claim 2, the axes of adjacent rollers (300) within the first annular raceway being orthogonal to each other and the axis of each roller (300) intersecting the axis of the thrust bearing.

4. A bearing according to claim 3, wherein the angle between the axis of each roller (300) and the axis of the thrust bearing is 45 degrees.

5. Bearing according to claim 2, wherein the roller (300) is in contact with a first annular raceway surface; the balls (400) are in four-point contact with the second annular raceway.

6. Bearing according to claim 1, wherein the first annular raceway is provided close to a non-mounting end face of the outer ring (100) in axial direction.

7. A bearing according to claim 1, wherein the second annular raceways are arranged in one or more rows.

8. The bearing according to claim 1, wherein the thrust bearing further comprises a seal member (500), both ends of the seal member (500) in an axial direction of the thrust bearing are provided between the inner ring (200) and the outer ring (100), and an installation space of the seal member (500) is different in a deflection degree to the outer ring (100) or the inner ring (200) at the both ends in a radial direction of the thrust bearing.

9. Bearing according to claim 1, wherein the mounting blocks of the first and second rolling elements, respectively, are arranged in a radial direction of an inner ring (200) of the thrust bearing.

10. A bearing system of a wind park, the bearing system comprising a bearing according to any of claims 1-9; wherein the bearing system comprises a pitch bearing system or a yaw bearing system.

Technical Field

The invention relates to the technical field of wind power generation, in particular to a bearing and a bearing system of a wind generating set comprising the bearing.

Background

The existing bearing (such as a yaw bearing or a pitch bearing) for the wind generating set is generally provided with a double-row four-point contact ball bearing.

Taking the variable-pitch bearing as an example, two rows of rolling bodies in two rows of rolling paths arranged between the inner ring and the outer ring of the variable-pitch bearing are all steel balls with the same size, and the bearing capacities of the two rows of rolling paths are basically the same. With the continuous increase of the bearing load of the variable pitch bearing of the wind generating set with the power of 4MW and above, the bearing capacity of the variable pitch bearing of the double-row four-point contact ball structure row is limited, the phenomenon of elliptic truncation of the raceway is easy to occur, and the edge of the raceway is crushed. If the bearing capacity is improved by increasing the size of the steel ball, the bearing ring becomes thin under the condition of the same-size variable-pitch bearing, the strength of the ring is reduced, and the ring hoop stress of the ring exceeds the allowable strength of the ring, so that the fatigue fracture of the ring is caused.

Disclosure of Invention

Therefore, the bearing and the bearing system of the wind generating set comprising the bearing are provided, so that the bearing capacity of the bearing is improved.

According to one aspect of the invention, a bearing is provided, the bearing is a thrust bearing, and comprises an outer ring and an inner ring, wherein the outer ring and the inner ring are both of an integrated structure, a continuous first annular raceway and a continuous second annular raceway are formed between the inner ring and the outer ring, a first rolling body is arranged in the first annular raceway, a second rolling body is arranged in the second annular raceway, and the structure of the first rolling body is different from that of the second rolling body, so that the bearing capacity of the bearing and the strength of a bearing ring are improved, and the problems of fatigue fracture of the bearing ring and crushing of the edge of the raceway are effectively avoided.

According to an exemplary embodiment of the present invention, the first rolling element may be a roller structure; the second rolling elements may be ball structures.

According to an exemplary embodiment of the invention, the axes of adjacent rollers within the first annular raceway may be orthogonal to each other and the axis of each roller may intersect the axis of the thrust bearing.

According to an exemplary embodiment of the present invention, an angle between an axis of each roller and an axis of the thrust bearing may be 45 degrees.

According to an exemplary embodiment of the invention, the roller may be in contact with the first endless raceway surface; the balls may be in four-point contact with the second endless raceway. The bearing capacity of the roller in the first annular raceway is larger than that of the ball in the second annular raceway, so that the actual bearing capacity of the ball in the second annular raceway is relatively reduced, and the occurrence of contact ellipse truncation of the raceways is avoided.

According to an exemplary embodiment of the present invention, the first annular raceway may be provided near a non-mounting end surface of the outer ring in the axial direction.

According to an exemplary embodiment of the invention, the second annular raceways may be arranged in one or more rows to increase the load carrying capacity of the bearing.

According to an exemplary embodiment of the present invention, the thrust bearing further includes a sealing member, both ends of which in an axial direction of the thrust bearing are disposed between the inner race and the outer race, to prevent external impurities from entering an inside of the thrust bearing while ensuring that grease inside the thrust bearing does not leak. The installation space of the seal member is different in the degree of deflection to the outer ring or the inner ring at the both ends in the radial direction of the thrust bearing.

According to an exemplary embodiment of the present invention, the mounting blocks of the first rolling element and the second rolling element are respectively provided in a radial direction of the inner ring of the thrust bearing.

According to another aspect of the present invention, there is provided a bearing system of a wind turbine generator system, the bearing system comprising a bearing as described above; wherein the bearing system comprises a pitch bearing system or a yaw bearing system.

The bearing can improve the bearing capacity of the bearing and the strength of the bearing ring so as to effectively avoid the problems of fatigue fracture of the ring, crushing of the edge of the raceway and the like, and can be applied to a high-power wind turbine generator.

Drawings

The above and other objects and features of the present invention will become more apparent from the following description of the embodiments taken in conjunction with the accompanying drawings, in which:

fig. 1 is a schematic sectional view illustrating a thrust bearing according to an exemplary embodiment of the present invention.

Fig. 2 is a schematic sectional view illustrating a thrust bearing according to another exemplary embodiment of the present invention.

The reference numbers illustrate:

100: an outer ring; 110: a first outer race groove; 120: a second outer ring groove; 200: an inner ring; 210: a first inner ring groove; 220: a second inner race groove; 300: a roller; 400: a ball bearing; 500: a sealing member; 600: a first mounting block; 700: and a second mounting block.

Detailed Description

Embodiments in accordance with the present invention will now be described in detail with reference to the drawings, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to like elements throughout.

The invention designs a bearing. According to an exemplary embodiment of the present invention, the bearing may be a thrust bearing, but embodiments of the present invention are not limited thereto. The thrust bearing according to the exemplary embodiment of the present invention adopts a combination structure of the cross roller and the four-point contact ball, that is, the thrust bearing in the exemplary embodiment is a thrust bearing of a combination of the cross roller and the four-point contact ball.

First, the structure of a thrust bearing according to an exemplary embodiment of the present invention will be described with reference to fig. 1.

As shown in fig. 1, a thrust bearing according to an exemplary embodiment of the present invention includes an outer race 100 and an inner race 200, and herein, the inner race 200 and the outer race 100 may be collectively referred to as a cage. Preferably, the outer ring 100 and the inner ring 200 are respectively of an integrated structure, and compared with a split type or split type ferrule formed by assembling a plurality of outer ring blocks on the basis of the existing outer ring 100 and/or inner ring 200, the integrated structure can maximally increase the strength of the inner ring and the outer ring, ensure the processing precision, improve the installation precision, avoid the stress concentration phenomenon caused by the bearing, and enable the bearing to be uniformly stressed integrally. It should be noted that, in the exemplary embodiments described below, the outer ring 100 of the one-piece structure may be a closed ring as a whole, and the inner ring 200 of the one-piece structure may have notches formed thereon for receiving the rolling elements.

Wherein a first annular raceway continuous in the circumferential direction and a second annular raceway continuous in the circumferential direction are formed between the inner ring 200 and the outer ring 100, the first annular raceway and the second annular raceway being aligned along the axial direction (hereinafter simply referred to as axial direction) of the thrust bearing, and the first annular raceway and the second annular raceway may be designed to be different in shape from each other so as to be able to accommodate rolling elements of different structures (i.e., first rolling elements and second rolling elements), respectively. Specifically, the outer ring 100 is provided with two raceways arranged in the axial direction, the inner ring 200 is provided with two raceways arranged in the axial direction, and the corresponding inner and outer ring raceways form a first annular raceway and a second annular raceway, respectively. The continuous raceway arrangement can simplify processing and facilitate installation of the rolling elements.

According to an exemplary embodiment of the present invention, the first rolling element may adopt a roller 300 structure, the second rolling element may adopt a ball 400 structure, for example, a cylindrical roller may be adopted as the roller 300, and a steel ball may be adopted as the ball 400. Of course, exemplary embodiments according to the present invention are not limited thereto, and a cylindrical roller or a tapered roller may also be employed as the roller 300. For convenience of description, a cylindrical roller is shown as the roller 300 in the following exemplary embodiments.

In order that the inner ring 200 and the outer ring 100 may rotate relative to each other, rolling elements may be rollably disposed in the annular raceway, and the diameters of the rolling elements rollably disposed in the annular raceway may be selected according to the actual operating load calculation. Under the condition that the external dimensions of the bearings are the same, the bearing capacity of the crossed roller bearing is improved by about 15 percent compared with that of a four-point contact ball bearing, so that the cylindrical roller with a smaller diameter can realize the same bearing capacity as a four-point contact steel ball with a relatively larger diameter. In consideration of the fact that the strength of the race on the non-mounting end face side of the outer race of the bearing in the axial direction is a weak point of the entire race, the strength on the non-mounting end face side of the outer race 100 can be enhanced by applying the small-diameter cylindrical rollers.

For this reason, the first annular raceway for accommodating the rollers 300 may be located near the non-mounting end surface in the axial direction of the outer ring 100, and the second annular raceway for accommodating the balls 400 may be located near the mounting end surface of the outer ring 100 opposite to the non-mounting end surface in the axial direction. According to an exemplary embodiment of the present invention, as shown in fig. 1, the first annular raceway is close to and at a predetermined distance from the non-installation end surface in the axial direction of the outer ring 100, and the second annular raceway is close to and at a predetermined distance from the installation end surface opposite to the non-installation end surface in the axial direction of the outer ring 100, so that the thrust bearing can receive an axial force Fa acting in a direction parallel to the axis O of the bearing, a radial force Fr acting in the radial direction of the bearing, and an overturning moment M.

Rollers 300, such as cylindrical rollers, may be rollably disposed in the first toroidal raceway with axes between adjacent rollers 300 being orthogonal to each other. That is, the axes between adjacent rollers 300 are positioned at 90 degrees to each other, and therefore, the rollers 300 in the first toroidal raceway can be considered to be in a crossed arrangement, so the rollers 300 in the first toroidal raceway can be referred to as crossed rollers. Due to the cross arrangement between the adjacent rollers 300, the axial length dimension of the rollers 300 is slightly smaller than the radial diameter length dimension, the rollers 300 are in contact with the first toroidal raceway in the radial direction and adapted to roll, and there is a gap between the rollers 300 and the first toroidal raceway in the axial direction. In this way, the adjacent rollers 300 can abut against each other and freely rotate along their own axes without providing a roller bracket, greatly simplifying the structure of the thrust bearing.

According to an exemplary embodiment of the present invention, the inner race 200 may be formed with a notch for loading the rolling elements. The rollers 300 may be loaded through the gaps between the first inner race groove 210 of the inner race 200 and the first outer race groove 110 of the outer race 100 to be loaded into the first annular raceway, and then mounting blocks (e.g., first mounting block 600) are installed to complete the assembly.

In order to be able to withstand greater loads, it is preferred that the axis of each roller 300 intersects the axis O of the thrust bearing. That is, the axis of each roller 300 is inclined with respect to the axis O of the thrust bearing, i.e., the angle between the axis of each roller 300 and the axis O of the thrust bearing is greater than 0 degrees and less than 90 degrees. The provision of the axis of each roller 300 intersecting the axis O of the thrust bearing in the present example enables each roller 300 to withstand the axial force Fa, the radial force Fr, and the overturning moment M, in contrast to an arrangement in which the axis of the roller intersects the axis of the bearing at an angle of preferably 45 degrees, either parallel or perpendicular to the axis of the bearing.

Since the first toroidal raceways are arranged with the rollers 300 being crossed, it is possible to receive an axial force acting in a direction parallel to the axis O of the bearing, a radial force acting in the radial direction of the bearing, and a tilting moment. In addition, under the same condition, the bearing capacity of the roller 300 is greater than that of the ball 400, so that under the same load condition, the diameter of the roller 300 can be slightly smaller than that of the ball 400 in the original design, the bearing capacity is improved, and the problem of contact ellipse truncation of the raceway can be avoided. Compared with a double-row four-point contact ball bearing, the cross rollers are adopted in the first annular roller path, the diameter of the rolling body can be reduced, so that the space occupied by the rolling body in a bearing ring is reduced, the effective thickness of the ring is increased (namely, the radial thickness and the axial thickness of the roller path and the ring are increased), the strength of the ring is improved, the hoop stress of the ring is reduced, and the fatigue fracture of the ring is avoided.

In addition, as described above, the cross rollers in the first toroidal raceway abut against each other without interfering with each other, serving both to isolate the rollers 300 from each other and to eliminate mounting members such as a roller mount or a cage, which are additionally provided to mount the rollers. Therefore, the structure of the thrust bearing according to the exemplary embodiment of the present invention is more simplified and the production cost can be reduced, compared to the existing bearing using a cage to mount rollers.

The balls 400 are rollably disposed in the second endless raceway, and preferably, the balls 400 may be in four-point contact with the raceway. The balls 400 may be gap-fitted between the second inner ring groove 220 of the inner ring 200 and the second outer ring groove 120 of the outer ring 100, fitted into the second annular raceway, and then a mounting block (e.g., a second mounting block 700) is mounted to complete the assembly.

The rollers 300 in the first annular raceway in the crossed arrangement can withstand more than 50% of the axial force Fa, the radial force Fr, and the overturning moment M, while the balls 400 in the second annular raceway can withstand less than about 50% of the outer axial force Fa, the radial force Fr, and the overturning moment M. Since the bearing capacity of the rollers 300 in the first toroidal raceway is greater than the bearing capacity of the balls 400 in the second toroidal raceway, the actual bearing capacity of the balls 400 in the second toroidal raceway is relatively reduced, avoiding the occurrence of raceway contact ovality.

Compared with a double-row four-point contact ball bearing, the thrust bearing according to the exemplary embodiment of the invention has the advantages that the first annular roller paths are arranged in a roller crossing manner, the second annular roller paths are four-point contact balls, the sensitivity of the bearing to roller path deformation and the like can be reduced, the bearing capacity of the roller paths can be obviously improved, the contact stress is reduced, and the problem of elliptical truncation of roller path contact can be prevented.

Compared with a double-row crossed cylindrical roller structure, the thrust bearing provided by the embodiment of the invention adopts a crossed roller and four-point contact ball combined structure, so that the clamping stagnation phenomenon in the bearing operation process can be effectively avoided.

According to an exemplary embodiment of the present invention, the first and second annular raceways may be formed by: the circular outer circumferential surface of the inner ring 200 is formed with a first inner ring groove 210 and a second inner ring groove 220, the circular inner circumferential surface of the outer ring 100 is formed with a first outer ring groove 110 and a second outer ring groove 120, the first outer ring groove 110 faces the first inner ring groove 210 and forms a first annular raceway together with the first inner ring groove 210, and the second outer ring groove 120 faces the second inner ring groove 220 and forms a second annular raceway together with the second inner ring groove 220.

The first inner race groove 210 and the first outer race groove 110 may each have a V-shape in cross section, for example, the first inner race groove 210 and the second outer race groove 110 may be arranged in an isosceles right triangle; the second inner race groove 220 and the second outer race groove 120 may be arc-shaped, for example, the second inner race groove 220 and the second outer race groove 120 may be disposed in a semicircular shape.

The V-shaped first inner race groove 210 includes first and second inner race surfaces that are oppositely inclined at an angle of 45 degrees with respect to the axis O of the thrust bearing and are orthogonal to each other, and the V-shaped first outer race groove 110 includes first and second outer race surfaces that are oppositely inclined at an angle of 45 degrees with respect to the axis O of the thrust bearing and are orthogonal to each other.

When the rollers 300 are fitted into the first toroidal raceway, the axis of each roller 300 may be at an angle of 45 degrees to the axis O of the thrust bearing, and the axes of two adjacent rollers 300 are inclined in opposite directions with respect to the axis O of the thrust bearing. The roller 300 is in contact with the first toroidal raceway surface, that is, the outer circumferential surface of the roller 300 in the circumferential direction is in contact with the first toroidal raceway surface. One of the adjacent two rollers 300 is in contact with the first inner ring surface and the second outer ring surface (i.e., two opposite sides of the square of the first annular raceway which is square in cross section), and the other is in contact with the second inner ring surface and the first outer ring surface (i.e., the other two opposite sides of the square of the first annular raceway which is square in cross section). However, embodiments of the present invention are not limited thereto, and in the case of making the axes of the adjacent rollers 300 orthogonal to each other, the angle between the axes of the rollers 300 and the axis O of the thrust bearing may be appropriately changed, for example, the axes of the adjacent two rollers 300 may be at 30 degrees and 60 degrees to the axis O of the thrust bearing, respectively. This, of course, would make the processing of the raceway more difficult and the production cost higher.

As shown in fig. 1, according to an exemplary embodiment of the present invention, the first annular raceways are arranged in a row, and the second annular raceways are arranged in a row. The thrust bearing according to the exemplary embodiment of the present invention is not limited to the single-row cross roller 300 and the single-row four-point contact ball structure shown in fig. 1, but may be designed as a single-row cross roller 300 and multi-row four-point contact ball combined structure according to the loaded condition of the bearing. As shown in fig. 2, according to another exemplary embodiment of the present invention, the first annular raceways are arranged in one row and the second annular raceways are arranged in two rows to further increase the load carrying capacity of the bearing. However, the embodiments of the present invention are not limited thereto, and the second annular raceway may be designed in more than two rows as the actual need may be, in the case where the radial dimension of the bearing is fixed and the axial dimension of the bearing may be increased.

In consideration of the fact that the use environment of the bearing system of the wind turbine generator set is generally severe, the thrust bearing according to the exemplary embodiment of the present invention may be further provided with a sealing member 500, both ends of the sealing member 500 in the axial direction of the thrust bearing being disposed between the inner race 200 and the outer race 100 to seal. For example, the sealing member 500 may be provided as a sealing ring. As shown in fig. 1 and 2, the installation space of the seal member 500 is different in the degree of deflection toward the outer ring 100 or the inner ring 200 at both ends of the thrust bearing in the radial direction of the thrust bearing. Specifically, the seal member 500 forms an installation space, in the radial direction, disposed biased toward the inner ring 200 at one of both ends of the thrust bearing, and disposed biased toward the outer ring 100 at the other end of the thrust bearing. Preferably, the installation space of the sealing member 500 is provided to be offset to the inner ring 200 in the radial direction at the end of the roller 300, and the installation space of the sealing member 500 is provided to be offset to the outer ring 100 in the radial direction at the end of the ball 400, further enhancing the outer ring strength of the roller 300 at the non-installation side of the outer ring.

By providing the sealing member 500, on the one hand, external impurities can be prevented from entering the inside of the thrust bearing, protecting the internal components from the external environment. On the other hand, the lubricating grease in the thrust bearing can be prevented from leaking, the lubricating grease required by good lubrication of the bearing is ensured, the pollution caused by leakage is prevented, the good lubrication of the bearing is promoted, the service life is prolonged, the operation and maintenance cost is reduced, and the operation stability is improved.

According to an exemplary embodiment of the invention, a bearing system of a wind park is provided, the bearing system comprising a bearing as described above. Wherein the bearing system comprises a pitch bearing system or a yaw bearing system.

According to an exemplary embodiment of the invention, a wind park is provided, comprising a pitch bearing system or a yaw bearing system as described above. The wind generating set may be a high power wind generating set such as 4MW and above.

According to the bearing and the bearing system of the wind generating set comprising the bearing, the bearing capacity of the bearing can be improved, the strength of the bearing ring can be improved, the problems of fatigue fracture of the bearing ring, crushing of the edge of the raceway and the like can be effectively solved, the operation and maintenance cost of the wind generating set can be reduced, and the operation stability of the wind generating set can be improved.

Although the embodiments of the present invention have been described in detail above, those skilled in the art may make various modifications and alterations to the embodiments of the present invention without departing from the spirit and scope of the present invention. It will be understood that modifications and variations may occur to those skilled in the art, which modifications and variations may be within the spirit and scope of the embodiments of the invention as defined by the appended claims.