JP5010353B2 - Roller bearings, roller bearing cage segments, and wind turbine main shaft support structure - Google Patents

Description

  The present invention relates to a roller bearing, a roller bearing cage segment, and a main shaft support structure for a wind power generator, and more particularly to a roller bearing cage segment that is arranged in the circumferential direction to form a cage, and such a roller bearing. The present invention relates to a roller bearing including a cage segment and a main shaft support structure of a wind power generator.

  The roller bearing is generally composed of an outer ring, an inner ring, a plurality of rollers disposed between the outer ring and the inner ring, and a cage that holds the plurality of rollers. The cage is usually made of a single piece, that is, a single annular part.

  A roller bearing that supports a main shaft of a wind power generator to which a blade for receiving wind is attached needs to receive a large load, so that the roller bearing itself is also large. If it does so, each structural member which comprises a roller bearing, such as a roller and a holder | retainer, will also become large sized, and production and assembly of a member will become difficult. In such a case, if each member can be divided, production and assembly are facilitated.

  Here, European Patent Publication No. 1408248A2 (Patent Document 1) discloses a technique related to a split type cage in which a cage included in a roller bearing is divided by a dividing line extending in a direction along the axis of rotation of the bearing. Referring to FIG. 9, the cage segment 101a includes a plurality of pillar portions 103a, 103b, 103c, 103d, and 103e extending in a direction along the rotation axis of the bearing so as to form a plurality of pockets 104 that accommodate the tapered rollers. And connecting portions 102a and 102b extending in the circumferential direction so as to connect the plurality of pillar portions 103a to 103e.

10 is a cross-sectional view showing a part of the tapered roller bearing including the cage segment 101a shown in FIG. The configuration of the tapered roller bearing 111 including the cage segment 101a will be described with reference to FIGS. 9 and 10. The tapered roller bearing 111 includes an outer ring 112, an inner ring 113, a plurality of tapered rollers 114, and a plurality of cones. It has a plurality of cage segments 101a, 101b, 101c, etc. for holding the rollers 114. The plurality of tapered rollers 114 are held by a plurality of cage segments 101a and the like in the vicinity of a PCD (Pitch Circle Diameter) 105 where the roller behavior is most stable. The cage segments 101a for holding the plurality of tapered rollers 114 are arranged so that the cage segments 101b and 101c having the same shape adjacent in the circumferential direction are in contact with the outermost pillar portions 103a and 103e in the circumferential direction. Has been. A plurality of cage segments 101 a, 101 b, 101 c, etc. are connected to each other and incorporated in the tapered roller bearing 111 to form one annular cage included in the tapered roller bearing 111.
European Patent Publication 1408248A2

  The cage segments 101a to 101c disclosed in Patent Document 1 are raceway guides. On the other hand, by using such a split cage segment as a roller guide, it is possible to prevent damage, collision noise, and the like during contact with the raceway.

  In order to use the cage segment as a roller guide, for example, guide pillars on the inner diameter side and the outer diameter side that restrict the movement of the cage segment are provided on the column portion so as to protrude toward the pocket side. About such a guide claw, the attitude | position of a holder | retainer segment can be stabilized by increasing the number. However, if the number is too large, the shape becomes complicated and the quality becomes excessive. Moreover, productivity will also deteriorate.

  Here, in the above-described application, the roller bearing is used on the horizontal axis. In this case, if there is a gap between the cage segments, the cage segments may fall freely and the cage segments may collide with each other. Further, when a large moment load acts on the roller bearing, there is a possibility that a non-load region of the rolling element load is partially generated regardless of whether the clearance of the roller bearing is positive or negative. Even in such a case, the cage segments freely fall and the cage segments collide with each other.

  At the time of collision, the cage segment is repelled on the outer ring side due to its shape, but if the cage segment is a roller guide, when the cage segment is repelled on the outer ring side, the inner side of the roller and the cage segment The guide claw collides. Then, a moment load acts on the guide claw on the inner diameter side at the time of collision. When such a moment load increases, stress concentrates on the base portion of the column portion provided with the guide claw on the inner diameter side. Then, the cage segment may be damaged.

  An object of the present invention is to provide a roller bearing that can reduce the risk of breakage of a cage segment.

  Another object of the present invention is to provide a roller bearing cage segment with reduced risk of breakage.

  Still another object of the present invention is to provide a main shaft support structure for a wind power generator capable of extending the life.

  A roller bearing according to the present invention includes an outer ring, an inner ring, a plurality of rollers disposed between the outer ring and the inner ring, and a plurality of columns extending in a direction along the rotation axis of the bearing so as to form a pocket for housing the roller. And a plurality of retainer segments that have a connecting portion extending in the circumferential direction so as to connect the plurality of pillars, and are sequentially arranged in the circumferential direction between the outer ring and the inner ring. The cage segment is a roller guide, and the column portion has an outer diameter side guide claw that contacts the roller accommodated in the pocket on the outer diameter side, and an inner diameter side that contacts the roller accommodated in the pocket on the inner diameter side. Guide claws are provided. Here, the number of guide claws on the inner diameter side is equal to or greater than the number of guide claws on the outer diameter side.

  With this configuration, the roller guide retainer segment has a relatively simple shape, and when the retainer segments collide with each other and the retainer segment is repelled on the outer ring side, The moment load applied to each guide claw can be reduced. If it does so, the stress which arises in the base part of each pillar part in which the guide claw of the inner diameter side was provided can be made small. Accordingly, the risk of breakage of the cage segment can be reduced.

  Here, the cage segment is a unit body obtained by dividing one annular cage by a dividing line extending in a direction along the rotation axis of the bearing so as to have at least one pocket for accommodating the rollers. A plurality of cage segments are connected to the roller bearing in a circumferential direction to constitute one annular cage.

  Preferably, the guide claw on the inner diameter side is provided on a pillar portion located on both sides of the pocket. By doing so, the moment load applied from the roller accommodated in the pocket can be received by the guide claws on the inner diameter side provided on the column portions located on both sides of the pocket. Therefore, the moment load on the guide claws on each inner diameter side can be reduced, and the risk of breakage of the cage segment can be further reduced.

  More preferably, in a cross section including a guide claw on the inner diameter side and cut along a plane orthogonal to the rotation axis of the bearing, the guide surface of the guide claw on the inner diameter side has a substantially arc shape in section and is along the rolling surface of the roller. Shape. By doing so, when the roller and the guide claw on the inner diameter side are in contact with each other, they can be brought into contact with each other and do not hit the edge. Therefore, it is possible to reduce roller damage and wear of the guide claw on the inner diameter side.

  In another aspect of the present invention, the cage segment of the roller bearing is provided in the roller bearing, and a plurality of column portions extending in a direction along the rotation axis of the bearing so as to form a pocket for accommodating the roller, and the plurality of the plurality of column portions. It has a connecting portion extending in the circumferential direction so as to connect the two pillar portions, and is successively arranged in the circumferential direction between the outer ring and the inner ring, and is made of resin. The cage segment is a roller guide. Here, the pillar portion is provided with an outer diameter side guide claw that comes into contact with the roller accommodated in the pocket on the outer diameter side, and an inner diameter side guide claw that comes into contact with the roller contained in the pocket on the inner diameter side. The number of guide claws on the inner diameter side is equal to or greater than the number of guide claws on the outer diameter side.

  The cage segments of such roller bearings have a relatively simple shape, but when the cage segments collide and are repelled on the outer ring side, a moment load is applied to each guide claw on the inner diameter side from the rollers. Can be reduced. If it does so, the stress which arises in the base part of the pillar part in which the guide claw of the inner diameter side was provided can be made small. Therefore, the risk of breakage can be reduced.

  In still another aspect of the present invention, the main shaft support structure of the wind power generator includes a blade that receives wind power, a main shaft that is fixed to the blade, one end of which is fixed to the blade, and the main shaft that rotates together with the blade. And a roller bearing to be supported. The roller bearing includes an outer ring, an inner ring, a plurality of rollers disposed between the outer ring and the inner ring, a plurality of column portions extending in a direction along the rotation axis of the bearing so as to form a pocket for housing the roller, A plurality of retainer segments that have a connecting portion extending in the circumferential direction so as to connect the plurality of pillar portions, and are sequentially arranged in the circumferential direction between the outer ring and the inner ring; The cage segment is a roller guide, and the column portion has an outer diameter side guide claw that contacts the roller accommodated in the pocket on the outer diameter side, and an inner diameter side that contacts the roller accommodated in the pocket on the inner diameter side. Guide claws are provided. Here, the number of guide claws on the inner diameter side is equal to or greater than the number of guide claws on the outer diameter side.

  Such a main shaft support structure of a wind power generator can reduce the risk of breakage of the cage segment included in the roller bearing, and thus can extend the life.

  According to the present invention, the shape of the cage segments of the roller guide is made relatively simple, and when the cage segments collide with each other and the cage segments are repelled on the outer ring side, The moment load applied to the guide claw can be reduced. If it does so, the stress which arises in the base part of each pillar part in which the guide claw of the inner diameter side was provided can be made small. Accordingly, the risk of breakage of the cage segment can be reduced.

  In addition, the cage segments of such roller bearings have a relatively simple shape, and when the cage segments collide with each other and are repelled on the outer ring side, they are loaded from the rollers to the guide claws on the inner diameter side. The moment load can be reduced. If it does so, the stress which arises in the base part of the pillar part in which the guide claw of the inner diameter side was provided can be made small. Therefore, the risk of breakage can be reduced.

  Further, such a main shaft support structure of the wind power generator can reduce the risk of breakage because the risk of breakage of the cage segment included in the roller bearing is reduced.

  Embodiments of the present invention will be described below with reference to the drawings. FIG. 2 is a perspective view showing a cage segment 11a of the tapered roller bearing provided in the tapered roller bearing according to the embodiment of the present invention. 1 is a cross-sectional view of the cage segment 11a shown in FIG. 2 taken along a plane that includes the line II in FIG. 2 and that is perpendicular to the rotation axis of the bearing. FIG. 3 is a cross-sectional view of the cage segment 11a shown in FIG. 2 cut along a plane that passes through the center of the pillar portion 14a and is orthogonal to the circumferential direction. FIG. 4 is a view of a part of the cage segment 11a as seen from the direction of the arrow IV in FIG. From the viewpoint of easy understanding, in FIGS. 1 and 3, the plurality of tapered rollers 12a, 12b, 12c held by the cage segment 11a are indicated by dotted lines. Moreover, PCD22 is shown with a dashed-dotted line.

  With reference to FIGS. 1-4, the structure of the retainer segment 11a contained in a tapered roller bearing is demonstrated first. The cage segment 11a has a shape in which one annular cage is divided by a dividing line extending in a direction along the rotation axis of the bearing so as to have at least one pocket for accommodating the rollers. The cage segment 11a includes four column portions 14a, 14b, 14c, 14d extending in a direction along the rotation axis of the bearing so as to form pockets 13a, 13b, 13c for holding the tapered rollers 12a, 12b, 12c. It includes a pair of connecting portions 15a and 15b that are located at both ends in the axial direction and extend in the circumferential direction so as to connect the four column portions 14a to 14d. Here, the cage segment 11a is configured such that the column portions 14a and 14d are positioned at the outer end in the circumferential direction.

  The pair of connecting portions 15a and 15b have a predetermined radius of curvature in the circumferential direction so that when the plurality of cage segments 11a are incorporated into the tapered roller bearing, they form a single annular cage in the circumferential direction. have. Of the pair of connecting portions 15a and 15b, the radius of curvature of the connecting portion 15a located on the small diameter side of the tapered rollers 12a to 12c is smaller than the radius of curvature of the connecting portion 15b located on the large diameter side of the tapered rollers 12a to 12c. It is configured.

  Of the column portions 14a and 14b located on both sides in the circumferential direction of the pocket 13a and the column portions 14c and 14d located on both sides in the circumferential direction of the pocket 13c, the cage segment 11a is disposed on the inner diameter side of the side wall surfaces of the column portions 14a to 14d. The guide claws 17a, 17b, 17c, and 17d on the inner diameter side that restrict the movement of the outer diameter in the radial direction are provided. The guide claws 17a to 17d are in contact with the tapered rollers 12a and 12c accommodated in the pockets 13a and 13c on the inner diameter side. In addition, of the column portions 14b and 14c located on both sides in the circumferential direction of the pocket 13b, the outer diameter of the side wall surface of the column portions 14b and 14c is an outer diameter that restricts the movement of the cage segment 11a inward in the radial direction Side guide claws 18b and 18c are provided. The guide claws 18b and 18c are in contact with the tapered roller 12b accommodated in the pocket 13b on the outer diameter side. Each of the guide claws 17a to 17d, 18b, and 18c has a shape protruding toward the pockets 13a to 13c. Moreover, in the cross section shown in FIG. 1, the guide surfaces of the guide claws 17a to 17d, 18b, and 18c have a circular arc cross section and are shaped along the rolling surfaces of the tapered rollers 12a to 12c. By providing the guide claws 17a to 17d, 18b, and 18c on the inner diameter side and the outer diameter side in this way, the cage segment 11a is brought into contact with the guide surfaces of the guide claws 17a to 17d, 18b, and 18c to form roller guides. be able to. In addition, the end surfaces 21a and 21b on the outer side in the circumferential direction of the column portions 14a and 14d located on the outer side in the circumferential direction are flat.

  Here, the number of guide claws 17a to 17d on the inner diameter side is greater than the number of guide claws 18b and 18c on the outer diameter side. Specifically, the guide claws 17a to 17d on the inner diameter side provided in the cage segment 11a are four, and the guide claws 18b and 18c on the outer diameter side are two. With this configuration, the stress on the root portions 23a and 23b of the pillar portions 14a to 14d can be reduced as described later, while the shape of the cage segment 11a is a relatively simple shape. Therefore, it is possible to reduce the risk of breakage of each of the pillar portions 14a to 14d and the cage segment 11a.

  Next, the configuration of the tapered roller bearing including the cage segment 11a described above will be described. FIG. 5 is a schematic cross-sectional view of a tapered roller bearing 31 in which a plurality of cage segments 11a, 11b, 11c, 11d and the like are arranged in the circumferential direction, as viewed from the axial direction. 6 is an enlarged cross-sectional view of a portion indicated by VI in FIG. Here, since the cage segments 11b, 11c, and 11d have the same shape as the cage segment 11a, description thereof is omitted. In FIG. 5, tapered rollers held by the cage segment 11a and the like are omitted. In addition, here, among the plurality of cage segments 11a to 11d, the cage segment arranged first is the cage segment 11a, and the cage segment arranged last is the cage segment 11d.

  Referring to FIGS. 5 and 6, tapered roller bearing 31 includes an outer ring 32, an inner ring 33, a plurality of tapered rollers 34, and a plurality of cage segments 11a to 11d. The cage segments 11a to 11d are sequentially connected in the circumferential direction and arranged without gaps. Here, first, the cage segment 11a is arranged first, and then the end surface 21a of the cage segment 11a and the cage segment 11b so that the cage segment 11b abuts the cage segment 11a. It arrange | positions so that the end surface 21c may contact | abut. Thereafter, the cage segment 11c is arranged so as to abut the cage segment 11b, specifically, the end surface 21d of the cage segment 11b and the end surface 21e of the cage segment 11c are abutted. The segments are arranged, and finally the cage segment 11d is arranged. In this way, the cage segments 11a to 11d are arranged in the circumferential direction. In this case, there is a circumferential gap 39 between the first cage segment 11a and the last cage segment 11d. Such a gap 39 is provided in consideration of the thermal expansion of the cage segments 11a to 11d.

  The tapered roller bearing 31 is attached to a rotating shaft (not shown) using a horizontal axis. Here, when the tapered roller bearing 31 is in operation, the cage segments 11a to 11d perform a revolving motion. In this case, the cage segments 11a to 11d freely fall and the cage segments 11a to 11d collide with each other. There is. In addition, even when a large moment load is applied to the rotating shaft and a non-load region is generated in the tapered roller bearing 31, the cage segments 11a to 11d collide with each other. Here, in FIG. 6, when the cage segment 11a and the cage segment 11b collide, the cage segment 11b is repelled in the outer ring 32 side, that is, in the direction of arrow A in FIG. In this case, the guide claw 36 on the inner diameter side provided in the cage segment 11b comes into contact with the tapered roller 34 accommodated in the pocket. Here, since the number of guide claws 36 on the inner diameter side is larger than the number of guide claws 37 on the outer diameter side, the moment load applied to each guide claw 36 on the inner diameter side can be reduced. If it does so, the stress which arises in the base part of each pillar part 35 can be made small. Therefore, the risk of breakage of the cage segment 11b can be reduced.

  In this case, the guide claw 36 on the inner diameter side is provided on both side walls of each pocket. Therefore, at the time of a collision, the moment load applied from the tapered roller 34 accommodated in the pocket can be received by the guide claws 36 on the inner diameter side located on both sides of the pocket. As a result, the load received by the guide claws 36 on each inner diameter side can be reduced, and the risk of breakage of the cage segment 11b can be further reduced.

  Further, in the cross section described above, the guide claw 36 on the inner diameter side has a substantially arcuate cross section and has a shape along the rolling surface of the tapered roller 34, so that it is brought into contact with the surface at the time of contact with the tapered roller 34. Can not be per edge. Therefore, damage to the tapered roller 34 and wear of the guide claw 36 on the inner diameter side can be reduced.

  In the above embodiment, a spacer for adjusting the dimension of the circumferential clearance 39 is brought into contact with the last cage segment 11d between the first cage segment 11a and the last cage segment 11d. You may decide to arrange in this way. In this case, a gap 39 is generated between the spacer and the first cage segment 11a. By configuring in this way, it is easier to adjust the dimensions of the first retainer segment 11a, the last retainer segment 11d, and the circumferential clearance 39. In this case, the spacer should be interpreted as a cage segment.

  7 and 8 show an example of a main shaft support structure of a wind power generator in which a roller bearing according to an embodiment of the present invention is applied as a main shaft support bearing 75. FIG. The casing 73 of the nacelle 72 that supports the main components of the main shaft support structure is installed on the support base 70 via a swivel bearing 71 at a high position so as to be horizontally rotatable. A main shaft 76 that fixes a blade 77 that receives wind power to one end is rotatably supported in a casing 73 of the nacelle 72 via a main shaft support bearing 75 incorporated in a bearing housing 74. Is connected to a speed increaser 78, and the output shaft of the speed increaser 78 is coupled to the rotor shaft of the generator 79. The nacelle 72 is turned at an arbitrary angle by the turning motor 80 via the speed reducer 81.

  The main shaft support bearing 75 incorporated in the bearing housing 74 is a tapered roller bearing according to an embodiment of the present invention, and includes an outer ring, an inner ring, a plurality of tapered rollers disposed between the outer ring and the inner ring, and a cone. A plurality of pillars extending in the direction along the rotation axis of the bearing so as to form a pocket for accommodating the rollers, and a connecting part extending in the circumferential direction so as to connect the plurality of pillars, and between the outer ring and the inner ring And a plurality of cage segments arranged in series in the circumferential direction. The cage segment is a roller guide, and the column part is in contact with the tapered roller accommodated in the pocket on the outer diameter side, and the outer diameter side guide claw is in contact with the tapered roller accommodated in the pocket on the inner diameter side. A guide claw on the inner diameter side is provided. Here, the number of guide claws on the inner diameter side is larger than the number of guide claws on the outer diameter side.

  The main shaft support bearing 75 needs to receive a large moment load, a thrust load, a radial load, and the like in order to support the main shaft 76 that fixes the blade 77 that receives a large wind force at one end. Here, when the roller is a tapered roller, a large moment load or the like can be received.

  In addition, such a main shaft support structure of the wind power generator can reduce the risk of breakage because the risk of breakage of the cage segment included in the tapered roller bearing is reduced.

  In the above embodiment, the number of guide claws on the inner diameter side is larger than the number of guide claws on the outer diameter side. However, the number of guide claws on the inner diameter side and the outer diameter are not limited thereto. The number of guide claws on the side may be the same. In this way, the cage segments of the roller guides have a relatively simple shape, and when the cage segments collide with each other and the cage segments are repelled on the outer ring side, The applied moment load can be reduced.

  In the above embodiment, the tapered roller is used as the roller accommodated in the cage segment. However, the present invention is not limited to this, and a cylindrical roller, a needle roller, a rod roller, or the like may be used.

  As mentioned above, although embodiment of this invention was described with reference to drawings, this invention is not limited to the thing of embodiment shown in figure. Various modifications and variations can be made to the illustrated embodiment within the same range or equivalent range as the present invention.

  The roller bearing according to the present invention is effectively used when reduction of the risk of breakage is required.

  Further, the cage segment of the roller bearing according to the present invention is effectively used when reduction of the risk of breakage is required.

  In addition, the main shaft support structure for a wind power generator according to the present invention can be effectively used when a long life is required.

It is sectional drawing at the time of cut | disconnecting the retainer segment which concerns on the tapered roller bearing which concerns on one Embodiment of this invention by the plane orthogonal to the rotating shaft line of a bearing. It is a perspective view of a cage segment included in a tapered roller bearing according to an embodiment of the present invention. It is sectional drawing at the time of cut | disconnecting the holder | retainer segment shown in FIG. 2 with the plane which passes along the center of a pillar part and is orthogonal to the circumferential direction. It is the figure which looked at the retainer segment contained in the tapered roller bearing which concerns on one Embodiment of this invention from the direction of arrow IV in FIG. It is a schematic sectional drawing of a tapered roller bearing at the time of arranging a plurality of cage segments in the peripheral direction. It is an expanded sectional view which shows the adjacent retainer segment. It is a figure which shows an example of the main shaft support structure of the wind power generator using the tapered roller bearing which concerns on this invention. FIG. 8 is a schematic side view of the main shaft support structure of the wind power generator shown in FIG. 7. It is a perspective view of the retainer segment in the past. It is sectional drawing at the time of cut | disconnecting the cage | basket segment shown in FIG. 9 by the plane orthogonal to the rotating shaft line of a bearing.

Explanation of symbols

  11a, 11b, 11c, 11d Cage segment, 12a, 12b, 12c, 34 Tapered roller, 13a, 13b, 13c pocket, 14a, 14b, 14c, 14d, 35 Column part, 15a, 15b Connecting part, 17a, 17b, 17c, 17d, 18b, 18c, 36, 37 Guide claw, 21a, 21b, 21c, 21d, 21e End face, 22 PCD, 23a, 23b Root part, 31 Tapered roller bearing, 32 Outer ring, 33 Inner ring, 39 Clearance, 70 Support Pedestal, 71 swivel seat bearing, 72 nacelle, 73 casing, 74 bearing housing, 75 spindle support bearing, 76 spindle, 77 blade, 78 speed increaser, 79 generator, 80 turning motor, 81 speed reducer.

Claims (5)

An outer ring, an inner ring, a plurality of rollers disposed between the outer ring and the inner ring, a plurality of pillars extending in a direction along the axis of rotation of the bearing so as to form a pocket for accommodating the rollers, and the plurality A roller bearing having a connecting portion extending in the circumferential direction so as to connect the pillar portions, and a plurality of cage segments sequentially arranged in the circumferential direction between the outer ring and the inner ring,
The cage segment is a roller guide;
The column portion is provided with an outer diameter side guide claw that comes into contact with the roller accommodated in the pocket on the outer diameter side, and an inner diameter side guide claw that comes into contact with the roller contained in the pocket on the inner diameter side. And
The pocket provided with the guide claw on the outer diameter side that contacts the roller on the outer diameter side is different from the pocket provided with the guide claw on the inner diameter side that contacts the roller on the inner diameter side ,
The roller bearing, wherein the number of guide claws on the inner diameter side is equal to or greater than the number of guide claws on the outer diameter side. The roller bearing according to claim 1, wherein the guide claw on the inner diameter side is provided on a pillar portion located on both sides of the pocket. In the cross section including the guide claw on the inner diameter side and cut along a plane orthogonal to the rotation axis of the bearing, the guide surface of the guide claw on the inner diameter side is substantially arc-shaped in cross section and has a shape along the rolling surface of the roller The roller bearing according to claim 1 or 2, wherein The roller bearing includes a plurality of column portions extending in a direction along the rotation axis of the bearing so as to form a pocket for accommodating the roller, and a connecting portion extending in the circumferential direction so as to connect the plurality of column portions. , A cage segment of a resin roller bearing arranged sequentially in the circumferential direction between the outer ring and the inner ring,
It is roller guidance,
The column portion is provided with an outer diameter side guide claw that comes into contact with the roller accommodated in the pocket on the outer diameter side, and an inner diameter side guide claw that comes into contact with the roller contained in the pocket on the inner diameter side. And
The pocket provided with the guide claw on the outer diameter side that contacts the roller on the outer diameter side is different from the pocket provided with the guide claw on the inner diameter side that contacts the roller on the inner diameter side ,
The cage segment of a roller bearing, wherein the number of guide claws on the inner diameter side is equal to or greater than the number of guide claws on the outer diameter side. A blade that receives wind,
One end of which is fixed to the blade and rotates with the blade;
A main shaft support structure for a wind power generator, including a roller bearing that is incorporated in a fixed member and rotatably supports the main shaft,
The roller bearing includes an outer ring, an inner ring, a plurality of rollers disposed between the outer ring and the inner ring, and a plurality of columns extending in a direction along a rotation axis of the bearing so as to form a pocket for housing the roller. And a plurality of cage segments having a connecting portion extending in the circumferential direction so as to connect the plurality of column portions and sequentially arranged in the circumferential direction between the outer ring and the inner ring. Because
The cage segment is a roller guide;
The column portion is provided with an outer diameter side guide claw that comes into contact with the roller accommodated in the pocket on the outer diameter side, and an inner diameter side guide claw that comes into contact with the roller contained in the pocket on the inner diameter side. And
The pocket provided with the guide claw on the outer diameter side that contacts the roller on the outer diameter side is different from the pocket provided with the guide claw on the inner diameter side that contacts the roller on the inner diameter side ,
The number of guide claws on the inner diameter side is equal to or greater than the number of guide claws on the outer diameter side.

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