JP2013076441A - Turning ring bearing structure for wind turbine, and method for replacing turning ring bearing structure for wind turbine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a turning ring bearing structure for a wind turbine and a method for replacing the turning ring bearing structure for the wind turbine, by which the bearing can be replaced without removing a blade from a rotor head of the wind turbine.SOLUTION: The turning ring bearing structure for the wind turbine includes: an outer ring 2 which is bolt-connected to the rotor head; an inner ring 3 which is bolt-conncted to the wind turbine blades; and a plurality of balls 4 which are arranged in one or more rows in the circumferential direction between the outer ring 2 and the inner ring 3. At least one of the outer ring 2 and the inner ring 3 comprises a plurality of divided members 2A, 3A. Two adjacent divided members 2A, 3A are provided to be separated from each other.

Description

  The present invention relates to a wind turbine slewing ring bearing structure used in a connecting portion between a rotor head and a blade, and a method for replacing the wind turbine slewing ring bearing structure.

A windmill used in wind power generation includes a tower, a nacelle, a rotor head, and a plurality of blades. The blade is connected to the rotor head via a swirl ring bearing and can be rotated (oscillated) around a blade axis extending in the blade length direction. Thereby, the pitch angle of a wing | blade is adjusted.
Patent Documents 1 to 3 disclose inventions relating to bearings, in which an outer ring or an inner ring is divided in the circumferential direction.

JP 2007-24143 A JP 2010-91047 A JP 2010-242917 A

  By the way, among windmills used for wind power generation, offshore windmills constructed on the sea are generally larger than land windmills and are not easily accessible. For this reason, the cost for replacing parts of the offshore wind turbine is high. In particular, since replacement of important parts such as slewing ring bearings requires a great deal of cost, an offshore windmill is required to be more easily replaced than important on an offshore windmill.

  One index of the ease of replacement is whether or not the parts can be replaced on the tower top. However, the conventional slewing ring bearing has a diameter of 2 to 3 m or more and is difficult to replace on the tower top. Further, since the slewing ring bearing is a very large part, the transportation cost from the part production site to the installation site is high. Furthermore, it is desirable that the slewing ring bearing does not bend on the installation surface, and the rotor head that is a mounting counterpart component is required to have high accuracy.

  The present invention has been made in view of such circumstances, and a windmill slewing ring bearing structure and a windmill slewing ring bearing structure capable of exchanging bearings without removing blades from the rotor head in the windmill. The purpose is to provide a replacement method.

In order to solve the above-mentioned problems, the following means are employed in the wind turbine slewing ring bearing structure and the method for replacing the wind turbine slewing ring bearing structure of the present invention.
That is, the slewing ring bearing structure for wind turbines according to the present invention includes an outer ring that is bolt-coupled to the rotor head, an inner ring that is positioned inside the outer ring and is bolt-coupled to the wind turbine blades, and a circumferential direction between the outer ring and the inner ring. A plurality of rolling elements arranged in one or more rows, and at least one of the outer ring and the inner ring includes a plurality of divided members, and two adjacent divided members are provided apart from each other.

  According to this invention, a windmill blade is installed in a rotor head via the turning wheel bearing structure for windmills, and a windmill blade rotates around a blade axis | shaft and a pitch angle is adjusted. And since the adjacent two divided members of at least one of the outer ring and the inner ring are provided apart from each other, a gap is formed between the divided members. Therefore, the outer ring or inner ring can be removed and attached for each divided member without removing the entire outer ring or inner ring, and parts can be replaced while leaving some outer rings and inner rings on the rotor head and wind turbine blades. It is. The rolling elements are arranged in one row in the circumferential direction, or in two or more rows, and the rows are arranged in parallel to each other.

  In the above invention, the number of divided members of the outer ring or inner ring composed of a plurality of divided members may be four or more.

  According to the present invention, when the wind turbine blade is in a horizontal state, the outer ring and the inner ring receive a moment due to the wind turbine blade's own weight, and the rolling elements at 0 ° and 180 ° from the vertical direction support the load. The rolling elements at positions 90 ° and 270 ° from do not support the load. Therefore, the outer ring or inner ring split member corresponding to the rolling elements at 90 ° and 270 ° from the vertical direction can be easily replaced.

  In the said invention, the edge part of the division member of the side which contacts a rolling element may have elasticity compared with another part, or may be easy to carry out plastic deformation compared with another part.

  According to this invention, when a rolling element is located in the clearance gap between division members, the edge part of a division member can prevent elastically deforming or plastically deforming, and it can prevent that a load concentrates on a rolling element.

  In the above invention, the rolling elements may be arranged in two rows parallel to the circumferential direction, and may be arranged in a staggered manner.

  According to the present invention, even when one of the rolling elements is located in the gap between the divided members and does not bear the load, the rolling elements in the other rows are not located in the gap between the divided members. The increase in the load of the load can be reduced.

  In the above invention, the adjacent two divided members have a first projecting portion in which the outer peripheral side of the end of one of the divided members protrudes in the circumferential direction, and the inner peripheral side of the end of the other divided member is in the circumferential direction. The first protrusion and the second protrusion may be in contact with each other, and the division member may be positioned in the radial direction.

  According to the present invention, when the split member is installed, the split member is positioned in the radial direction simply by bringing the first projecting portion and the second projecting portion into contact with each other. Therefore, the split member can be easily installed at an accurate position. be able to.

  The said invention WHEREIN: You may further provide the filling member which has the elasticity filled with the clearance gap formed between two adjacent division members.

  According to this invention, since the filling member is provided in the gap formed between the two divided members, it is possible to prevent the divided member from moving or to prevent leakage of the lubricating oil contained therein. .

  In addition, the method for replacing the wind turbine slewing ring bearing structure according to the present invention includes an outer ring bolted to the rotor head, an inner ring positioned on the inner side of the outer ring and bolted to the wind turbine blade, and the outer ring and the inner ring. A wind turbine slewing ring bearing structure that is provided with a plurality of rolling elements arranged, at least one of the outer ring and the inner ring is composed of a plurality of divided members, and the two adjacent divided members are spaced apart from each other. A method comprising: releasing a bolt connection between an outer ring and a rotor head or a bolt connection between an inner ring and a wind turbine blade; and removing a split member of the outer ring or the inner ring from the rotor head or the wind turbine blade.

  According to this invention, it is possible to remove each divided member without removing the entire outer ring or inner ring, and it is possible to replace parts while leaving a part of the outer ring and inner ring on the rotor head and the wind turbine blade.

  In the above invention, the method may further comprise a step of attaching the outer ring or inner ring dividing member to the rotor head or the wind turbine blade, and a step of bolting the outer ring and the rotor head, or a step of bolting the inner ring and the wind turbine blade. .

  According to the present invention, the outer ring or inner ring split member can be attached to the rotor head or the outer ring portion or the inner ring portion of the wind turbine blade removed for each divided member, and can be bolted to the rotor head or the wind turbine blade. .

  According to the present invention, the bearing can be replaced without removing the blades from the rotor head by the windmill.

It is a cross-sectional view showing a slewing ring bearing according to an embodiment of the present invention. It is a graph which shows the relationship between a ball surface pressure and the division | segmentation number of an outer ring | wheel or an inner ring, and the relationship between the number of volt | bolts and the division | segmentation number of an outer ring | wheel or an inner ring. It is a partial expanded cross-sectional view which shows the turning ring bearing which concerns on one Embodiment of this invention. FIG. 3 is a partially enlarged cross-sectional view showing a slewing ring bearing according to the same embodiment. It is a partial expanded cross-sectional view which shows the outer ring | wheel of the turning ring bearing which concerns on the same embodiment. It is a partial expanded cross-sectional view which shows the holder | retainer of the turning ring bearing which concerns on the same embodiment. It is a partial expanded side view which shows the turning ring bearing which concerns on the same embodiment. FIG. 3 is a partially enlarged cross-sectional view showing a slewing ring bearing according to the same embodiment. FIG. 3 is a partially enlarged cross-sectional view showing a slewing ring bearing according to the same embodiment. FIG. 3 is a partially enlarged cross-sectional view showing a slewing ring bearing according to the same embodiment. It is a flowchart which shows the replacement | exchange method of the turning ring bearing which concerns on the same embodiment. It is a perspective view which shows a windmill. 1 is a longitudinal sectional view showing a slewing ring bearing structure according to an embodiment of the present invention. It is a cross-sectional view which shows the slewing ring bearing which concerns on the same embodiment. It is a flowchart which shows another replacement | exchange method of the turning ring bearing which concerns on the same embodiment.

Hereinafter, a swirl ring bearing structure for a wind turbine according to an embodiment of the present invention will be described with reference to the drawings.
A windmill 11 used in wind power generation includes, for example, a tower 12, a nacelle 13, a rotor head 14, and a plurality of blades 15 as shown in FIG. The blade 15 is connected to the rotor head 14 via the swivel ring bearing 1 shown in FIG. 1 and can be rotated (oscillated) around the blade axis extending in the blade length direction. Thereby, the pitch angle of the wing | blade 15 is adjusted.

  FIG. 1 is a cross-sectional view showing a slewing ring bearing 1, and shows a state in which the slewing ring bearing 1 is installed on a wind turbine 11. However, the sizes of the outer ring 2 and the inner ring 3, the intervals between the gaps 6 and 7, and the number and positions of the balls 4 are schematically shown and are different from the actual ones.

  The slewing ring bearing 1 is, for example, a ball bearing (ball bearing), and includes an outer ring 2, an inner ring 3, a ball 4, and the like. The outer ring 2 is bolted by a rotor head 14 and a bolt 16 as shown in FIG. The inner ring 3 is installed inside the outer ring 2 and is bolted by a blade 15 and a bolt 17. A plurality of bolt holes corresponding to the bolts 16 and 17 are formed in each of the outer ring 2 and the inner ring 3 in parallel to the blade axis direction and in the circumferential direction. The bolts 16 and 17 are inserted into the bolt holes, and the rotor Coupled with the head 14 or the wing 15.

  The ball 4 is an example of a rolling element, and is disposed in an annular space formed between the outer ring 2 and the inner ring 3. The number of balls 4 depends on the circumferential length of the slewing wheel bearing 1 and the load per ball borne by the balls 4, but in the case of the wind turbine 11, it is about 100, for example. In addition, a rolling element is not restricted to the ball 4, A roller may be sufficient.

  The rotor head 14 rotates around the main axis with respect to the nacelle 13 together with the blades 15. The blade 15 rotates around the blade axis with respect to the rotor head 14. The rotor head 14 is a member that is fixed against rotation of the blade 15 around the blade axis. Therefore, the inner ring 3 connected to the blade 15 of the slewing ring bearing 1 rotates with respect to the outer ring 2 connected to the rotor head 14.

  The outer ring 2 and the inner ring 3 are each composed of a plurality of divided members 2A and 3A. FIG. 1 shows a case where the outer ring 2 and the inner ring 3 are each composed of four divided members 2A and 3A. And two adjacent divided members 2A or two adjacent divided members 3A are provided apart from each other. That is, a gap 6 is formed between the end 2a of one split member 2A and the end 2a of the other split member 2A. Similarly, a gap 7 is formed between the end portions 3a of the divided member 3A. The gaps 6 and 7 are, for example, 1 mm or more, and preferably 2 mm or more in consideration of deformation of the divided members 2A and 3A by about 1 mm. That is, the distance between the gaps 6 and 7 is preferably a distance that prevents the adjacent divided members 2A and 3A from coming into contact with each other in view of deformation of the divided members 2A and 3A caused by receiving a load.

  By forming the gaps 6 and 7, the split members 2A and 3A to be replaced can be removed from the installation position. In addition, by forming the gaps 6 and 7 in anticipation of deformation, the divided members 2A and 3A can be removed even when the adjacent divided members 2A and 3A are deformed by receiving a load.

  In the present embodiment, both the outer ring 2 and the inner ring 3 are divided, but the present invention is not limited to this example. For example, only one of the outer ring 2 and the inner ring 3 may be divided. In this case, the divided outer ring 2 or inner ring 3 can be easily replaced.

  The number of divisions of the outer ring 2 and the inner ring 3 is four in the example shown in FIG. 1, but the present invention is not limited to this example. For example, it may be divided into five or more. Conventionally, the bearing has been divided into two or at most four parts for accurate fastening, prevention of life reduction, or vibration and noise prevention. On the other hand, in this embodiment, it is divided into four or more for ease of conveyance and replacement. Further, at the connecting portion between the rotor head 14 and the blades 15 of the wind turbine 11, the blades 15 only need to be able to rotate (swing) with respect to the rotor head 14 so that the pitch angle can be adjusted without any delay. Therefore, it is only necessary to ensure the installation accuracy of the divided members 2A and 3A, and it is not necessary to ensure the accuracy over the entire circumference. Therefore, in order to ensure the accuracy of the installation surface of the rotor head 14 for installing the outer ring 2, it is not necessary to form an accurate horizontal plane over the entire circumference, and the rotor head 14 that is the mounting counterpart is highly accurate. Don't require that. This applies as the number of divisions increases.

  Further, as shown in FIG. 2, there are a relationship between the ball surface pressure and the number of divisions of the outer ring or the inner ring, and the number of front peripheral bolts of the slewing ring bearing 1 and the number of divisions of the outer ring or the inner ring. The smaller the number of divisions of the outer ring 2 or the inner ring 3 of the slewing ring bearing 1, the smaller the number of gaps 6, 7 in the slewing ring bearing 1. The larger the number of divisions of the outer ring 2 or the inner ring 3, the greater the number of gaps 6, 7. The number of places increases. And according to the number of the gaps 6 and 7, the number of balls 4 that are located in the gaps 6 and 7 and cannot bear a load changes. Therefore, the smaller the number of divisions of the outer ring 2 or the inner ring 3, the smaller the number of balls 4 positioned in the gaps 6 and 7, and the ball surface pressure per ball 4 is reduced. As the number increases, the number of balls 4 positioned in the gaps 6 and 7 increases, and the ball surface pressure received by each ball 4 increases. Therefore, for example, from the viewpoint of the ball surface pressure that affects the life of the balls 4, it is better that the number of the gaps 6 and 7 is smaller and the number of the divided members 2A and 3A is smaller.

On the other hand, the smaller the number of divisions of the outer ring 2 or the inner ring 3 and the smaller the number of division members 2A, 3A, the greater the number of bolts per division member 2A, 3A. Further, the greater the number of divisions of the outer ring 2 or the inner ring 3 and the greater the number of division members 2A, 3A, the smaller the number of bolts per division member 2A, 3A. Accordingly, since the ease of replacement of the divided members 2A and 3A is higher when the number of bolts per one is not less, from the viewpoint of ease of replacement of the divided members 2A and 3A, the greater the number of divided members 2A and 3A is, Good.
From the above, the number of the divided members 2A and 3A is determined based on a balance between the viewpoint of the ball surface pressure and the viewpoint of easy replacement.

Next, the interval between the gaps 6 and 7 will be described.
The take-out direction and attachment direction of the divided members 2A and 3A are the radial directions of the swivel ring bearing 1. When the split members 2A and 3A of the outer ring 2 and the inner ring 3 are put in and out from the outer peripheral side of the slewing ring bearing 1, the two adjacent split members 2A and 3A do not interfere with each other regardless of the gaps 6 and 7. .

  On the other hand, when the divided members 2A and 3A of the outer ring 2 and the inner ring 3 are moved in and out from the inner peripheral side of the slewing ring bearing 1, the gaps 6 and 7 are formed so that the two adjacent divided members 2A and 3A do not interfere with each other. The interval needs to be adjusted.

For example, as shown in FIG. 9, when the split member 3A of the inner ring 3 is taken out in the direction of the arrow C toward the inner peripheral side of the slewing ring bearing 1, the gap 7 between the adjacent split members 3A is pointed on the outer peripheral side of the split member 3A. It must be formed so that it can pass between A and point B. Accordingly, the distance _{L 2} of the gap 7 _is larger than l 1 sin [theta. Here, L ₂ is the distance between the vertical A-B with respect to the radial direction of the straight line passing through the center of the dividing member 3A, l ₁ is the length of the radial dividing member 3A. Thereby, the center of the split member 3A of the inner ring 3 can be moved along the radial direction of the slewing ring bearing 1, and the split member 3A can be taken out in the direction of the arrow C toward the inner peripheral side.

Further, as shown in FIG. 10, when the split member 2A of the outer ring 2 is taken out in the direction of arrow D toward the inner peripheral side of the slewing ring bearing 1, the gap 7 between the adjacent split members 3A of the inner ring 3 is The outer peripheral side needs to be formed so that it can pass between point A and point B. Therefore, the distance L _{3 of the} gap 7 is set to be greater than l ₂ sin θ. Here, L ₃ is the distance between the distances AB in the direction perpendicular to the straight line in the radial direction passing through the center of the divided member 2A, and l ₂ is the radius of the divided members 2A, 3A and the ball 6 portion. The total length of the direction. Thereby, the center of the split member 2A of the outer ring 2 can be moved along the radial direction of the slewing ring bearing 1, and the split member 2A can be taken out in the direction of arrow D toward the inner peripheral side. 9 and 10 are diagrams schematically showing the slewing ring bearing 1. FIG.

Next, with reference to FIG. 11, a method for exchanging the split member 2A of the outer ring 2 or the split member 3A of the inner ring 3 will be described.
First, the blade 15 provided with the slewing ring bearing 1 to be replaced is fixed in a horizontal state as shown in an enclosure E in FIG. 12 (step S1). At this time, as shown in FIG. 13, the slewing ring bearing 1 is separated from the center of gravity of the blade 15 by a distance L _{1, and} thus receives a moment by the weight W of the blade 15. In the slewing ring bearing 1, when the vertical direction is 0 deg as indicated by the arrow in FIG. 14, the divided members 2 </ b> A and 3 </ b> A and the balls 4 positioned at 0 deg and 180 deg are subjected to a relatively large moment. On the other hand, the divided members 2A and 3A and the balls 4 positioned at 90 deg and 270 deg do not support the load or receive a relatively small moment.

  Therefore, the bolt connection between the divided member 2A and the rotor head 14 positioned at 90 deg or 270 deg or the bolt connection between the divided member 3A and the blade 15 is released (step S2). Then, the divided members 2A and 3A, which have been freed from the mating parts after the bolts have been removed, are slid in the radial direction of the swivel ring bearing 1 and removed (step S3).

  Next, a new divided member 2A, 3A (for example, a newly prepared member or a member obtained by repairing the removed divided member 2A, 3A) is slid in the radial direction of the slewing ring bearing 1 to remove the divided member 2A. , 3A (step S4). Thereafter, the divided member 2A and the rotor head 14 are bolted, or the divided member 3A and the blade 15 are bolted (step S5).

  Further, the blade 15 and the inner ring 3 are rotated around the blade axis while the blade 15 is kept in the horizontal state shown in an enclosure E in FIG. 12, so that the divided member 3A positioned at 90deg or 270deg is replaced with another divided member. It can be changed to 3A. Therefore, the replacement of the split member 3A of the inner ring 3 can be completed in a state where the blade 15 is in a horizontal state shown in an enclosure E in FIG.

  As described above, the outer ring 2 or the inner ring 3 of the slewing ring bearing 1 can be replaced for each of the divided members 2A and 3A. Since the divided members 2A and 3A are smaller in size than the conventional annular slewing ring bearing, for example, the divided members 2A and 3A can be replaced on the top of the tower 12 of the wind turbine 11, for example, can be easily replaced, and the cost for replacement can be reduced. .

Next, another replacement method of the split member 2A of the outer ring 2 or the split member 3A of the inner ring 3 will be described.
The outer ring 2 is installed on the rotor head 14 whose position is fixed with respect to the rotation of the blade 15 around the blade axis. For this reason, the split member 2A of the outer ring 2 positioned at 0 deg or 180 deg cannot be replaced with the wing 15 left in the horizontal state shown in the box E in FIG.

  Therefore, for example, the blade 15 including the slewing ring bearing 1 to be replaced is fixed in a vertical state. At this time, the weight of the blade 15 is uniformly supported by all the balls 4 so that the load from the blade 15 does not act on only some of the divided members 2A and 3A, that is, the balls 4 applied to one piece. To make the pressure equal. In this state, the split member 2A of the outer ring 2 may be replaced.

This exchange method is shown in the flowchart of FIG.
First, the blade 15 provided with the slewing ring bearing 1 to be replaced is fixed in a vertical state (step S11). And in the wing | blade 15 of a vertical state, in the state which all the balls 4 are supporting the dead weight of the wing | blade 15 equally, the volt | bolt coupling | bonding of the division member 2A and the rotor head 14, or the volt | bolt of the division member 3A and the wing | blade 15 The connection is released (step S12). Thereafter, the divided members 2A and 3A that have been removed from the mating parts by removing the bolts are removed (step S13).

  Next, new divided members 2A and 3A (for example, a newly prepared member or a member obtained by repairing the removed divided members 2A and 3A) are installed at the positions of the removed divided members 2A and 3A (step S14). Then, the split member 2A and the rotor head 14 are bolted, or the split member 3A and the blade 15 are bolted (step S15).

  As a result, the split member 2A of the outer ring 2 that could not be replaced when the blade 15 is in the horizontal state can be replaced for each split member 2A in the blade 15 in the vertical state. Note that the split member 3 </ b> A of the inner ring 3 may be replaced by the above-described method for bringing the blade 15 into a vertical state.

Next, modified examples of the split member 2A of the outer ring 2 and the split member 3A of the inner ring 3 according to this embodiment will be described.
In the present embodiment, at the connecting portion between the rotor head 14 and the blade 15 of the wind turbine, the blade 15 only needs to be able to rotate (swing) with respect to the rotor head 14 to the extent that the adjustment of the pitch angle can be performed normally. Therefore, even if the gaps 6 and 7 are formed between the adjacent divided members 2A and 3A, the operation of the slewing ring bearing 1 is not affected. However, when the end portions 2a and 3a of the divided members 2A and 3A are, for example, rectangular, when the ball 4 passes through the gaps 6 and 7, the load per unit area acting on the ball 4 and the divided members 2A and 3A is increased. growing.

  Therefore, as shown in FIG. 3, a low hardness region 8 is provided in the vicinity of the gaps 6 and 7 of the divided members 2A and 3A, for example, in the end portions 2a and 3a of the divided members 2A and 3A. The low hardness region 8 is a member that is easily elastically deformed or plastically deformed when the ball 4 passes through. The low hardness region 8 is provided by, for example, providing a rubber member or not baking the metal members of the divided members 2A and 3A. Thereby, it can prevent that a load concentrates on the ball | bowl 4 and division member 2A, 3A in the clearance gap 6 and 7 vicinity.

  Or as shown in FIG. 4, you may provide the recessed part 9 in the clearance gaps 6 and 7 vicinity of division member 2A, 3A, for example, edge part 2a, 3a of division member 2A, 3A. The recessed portion 9 is formed in a concave shape on the outer peripheral side of the slewing ring bearing 1 in the divided member 2 </ b> A of the outer ring 2, and is formed in a concave shape on the inner peripheral side of the slewing ring bearing 1 in the divided member 3 </ b> A of the inner ring 3. As a result, when the split members 2A and 3A are installed as shown in FIG. 4, the distance between the inner ring 2 and the outer ring 3 is wider in the vicinity of the gaps 6 and 7 than the other parts. Thereby, when the ball 4 passes through the gaps 6 and 7, the ball 4 is accommodated in the recessed portion 9, and the load is not concentrated on the ball 4 and the divided members 2A and 3A.

Next, a modified example of the divided members 2A and 3A having a shape capable of positioning the outer ring 2 and the inner ring 3 in the radial direction will be described with reference to FIG.
In this embodiment, since the gaps 6 and 7 are formed between the adjacent divided members 2A and 3A, positioning becomes difficult when the divided members 2A and 3A are installed.

  As shown in FIG. 5, the outer peripheral side of the end 2a of one divided member 2A has a first protruding portion 2b protruding in the circumferential direction, and the inner peripheral side of the end 2a of the other divided member 2A protrudes in the circumferential direction. The second protruding portion 2c is provided. The total length in the radial direction of the first protrusion 2b and the second protrusion 2c is equal to the length in the radial direction of the split member 2A.

  And when installing 2 A of division members, the surface of the inner peripheral side of the 1st protrusion part 2b and the surface of the outer peripheral side of the 2nd protrusion part 2c are made to contact. Thus, the radial position of one split member 2A is reliably determined with reference to the other fixed split member 2A.

Next, the arrangement of the balls 4 arranged between the outer ring 2 and the inner ring 3 will be described with reference to FIGS.
In this embodiment, since the gaps 6 and 7 are formed between the adjacent divided members 2A and 3A, the ball 4 passes through the gaps 6 and 7 when adjusting the pitch angle of the blades 15. The balls 4 positioned in the gaps 6 and 7 cannot bear the load, and the load acts on the remaining balls 4 positioned other than the gaps 6 and 7. Therefore, it is desirable to increase the number of balls 4 positioned other than the gaps 6 and 7 as much as possible to reduce the load acting on each ball.

  When the balls 4 are arranged in two rows in parallel with the circumferential direction, the balls 4 in one row and the balls 4 in the other row are not arranged on a straight line parallel to the axial direction of the swivel bearing 1, It arrange | positions in the diagonal direction with respect to the straight line parallel to a direction. For example, the balls 4 are staggered as shown in FIG. In FIG. 7, the balls 4A in one row are represented by solid lines, and the balls 4B in the other row are represented by broken lines. At this time, the relative positions of the plurality of balls 4 are fixed by the openings 5a of the cage 5 shown in FIG.

  When the gaps 6 and 7 are formed in parallel to the axial direction of the slewing ring bearing 1, if the two balls 4 are arranged on a straight line parallel to the axial direction of the slewing ring bearing 1, a load cannot be borne. Two balls 4 will be added at a time. On the other hand, when the balls 4 are arranged in a staggered manner as shown in FIG. 6 of the present embodiment, the balls 4 positioned in the gaps 6 and 7 are one by one. Can be suppressed.

  That is, when two or more balls 4 are arranged in two rows parallel to the circumferential direction, when one of the balls 4 is positioned in the gaps 6 and 7 between the divided members 2A and 3A and does not bear a load, However, since the balls 4 in the other rows are not located in the gaps 6 and 7 between the divided members 2A and 3A, a load can be borne. It is possible to reduce an increase in the load of a load per ball 4.

Next, with reference to FIG. 8, a description will be given of the absorption of the displacement of the split members 2A and 3A of the slewing ring bearing 1 and the prevention of grease leakage of the slewing ring bearing 1.
As shown in FIG. 8, a filling member 10 may be provided between two adjacent divided members 2A and 3A. The filling member 10 is a member having elasticity such as rubber. The filling member 10 is provided on the outer peripheral side of the slewing ring bearing 1 in the gap 6 of the outer ring 2, and is provided on the inner peripheral side of the slewing ring bearing 1 in the gap 7 of the inner ring 3.

  By providing the filling member 10, the divided members 2 </ b> A and 3 </ b> A are difficult to move, and the outer ring 2 and the inner ring can be prevented from moving. Further, since the gaps 6 and 7 are closed with respect to the outside, leakage of the lubricant (grease) used inside the slewing ring bearing 1 can be prevented.

  In the above embodiment, the cage 5 that holds the balls 4 may be annular, or may have a divided structure like the outer ring 2 and the inner ring 3. When the cage 5 is divided, it can be exchanged for each divided member of the cage 5 in the same manner as the divided members 2A and 3A of the outer ring 2 and the inner ring 3, and the ease of component replacement of the slewing ring bearing 1 is improved. be able to.

DESCRIPTION OF SYMBOLS 1 slewing ring bearing 2 outer ring | wheel 2A, 3A division | segmentation member 2a, 3a end part 2b 1st protrusion part 2c 2nd protrusion part 3 inner ring 4, 4A, 4B ball (rolling element)
5 Cage 6, 7 Clearance 8 Low Hardness Area 9 Recessed Part 10 Filling Member 11 Windmill 12 Tower 13 Nacelle 14 Rotor Head 15 Wings

Claims (8)

An outer ring bolted to the rotor head;
An inner ring located inside the outer ring and bolted to the windmill blade;
A plurality of rolling elements arranged in one or more rows in the circumferential direction between the outer ring and the inner ring;
With
At least one of the outer ring and the inner ring is composed of a plurality of divided members,
The two adjacent divided members are provided with a slewing ring bearing structure for a wind turbine provided to be separated from each other.   The slewing ring bearing structure for a wind turbine according to claim 1, wherein the number of the divided members of the outer ring or the inner ring including the plurality of divided members is four or more.   The slewing ring bearing structure for a wind turbine according to claim 1, wherein an end portion of the divided member on a side in contact with the rolling element has elasticity compared to other portions or is more easily plastically deformed than other portions.   The slewing ring bearing structure for a wind turbine according to claim 1, wherein the rolling elements are arranged in two rows parallel to the circumferential direction and arranged in a staggered manner.   Two adjacent divided members have a first protruding portion in which the outer peripheral side of the end of one of the divided members protrudes in the circumferential direction, and the inner peripheral side of the end of the other divided member extends in the circumferential direction. The slewing ring bearing structure for a wind turbine according to claim 1, further comprising a protruding second protruding portion, wherein the first protruding portion and the second protruding portion are in contact with each other to position the divided member in a radial direction.   The slewing ring bearing structure for wind turbines according to claim 1, further comprising a filling member having elasticity that fills a gap formed between two adjacent divided members. An outer ring that is bolt-coupled to the rotor head, an inner ring that is positioned inside the outer ring and is bolt-coupled to a wind turbine blade, and a plurality of rolling elements that are disposed between the outer ring and the inner ring, the outer ring and At least one of the inner rings is composed of a plurality of divided members, and the two adjacent divided members are an exchange method of a slewing ring bearing structure for a windmill provided separately from each other,
Releasing the bolt connection between the outer ring and the rotor head, or the bolt connection between the inner ring and the wind turbine blade;
Removing the split member of the outer ring or the inner ring from the rotor head or the wind turbine blade;
A method for replacing a slewing ring bearing structure for a windmill. Attaching the split member of the outer ring or the inner ring to the rotor head or the wind turbine blade;
Bolting the outer ring and the rotor head, or bolting the inner ring and the wind turbine blade;
The method for replacing a wind turbine slewing ring bearing structure according to claim 7, further comprising:

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