JP2007292305A - Rolling bearing and spindle support structure of wind turbine generator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rolling bearing with good productivity, which can smoothly roll a rolling element. <P>SOLUTION: A conical bearing 31 comprises an outer ring 32 which is circumferentially dividable; a plurality of conical rollers 34 disposed on the raceway surface of the outer ring 32; a plurality of retainer segments 11a, 11b and 11c having a plurality of column parts axially extending so as to form a pocket for retaining the conical rollers 34 and a connection part circumferentially extending so as to connect the plurality of column parts, the segments being successively disposed on the raceway surface of the bearing ring in the circumferential direction; and bolts 41a and 41b and bolt holes 42a and 42b as fastening means for mutually fastening divided outer ring segments 32a and 32b. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a rolling bearing and a main shaft support structure for a wind power generator, and more particularly to a large-sized rolling bearing and a main shaft support structure for a wind power generator including such a large rolling bearing.

  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. There are various types of cages for holding rollers, such as resin cages, press cages, shaving cages, and welded cages, depending on the material and manufacturing method. ing. In addition, the cage is usually composed of a single piece, that is, an 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, a technique relating to a split type retainer in which a retainer included in a roller bearing is divided by a dividing line extending in a direction along the axis is disclosed in European Patent Publication No. 1408248A2 (Patent Document 1). FIG. 11 is a perspective view showing a cage segment which is a split type cage disclosed in Patent Document 1. FIG. Referring to FIG. 11, cage segment 101a includes a plurality of pillar portions 103a, 103b, 103c, 103d, 103e extending in a direction along the axis so as to form a plurality of pockets 104 for accommodating rollers, and a plurality of pillars. It has the connection parts 102a and 102b extended in the circumferential direction so that the parts 103a-103e may be connected.

  12 is a cross-sectional view showing a part of the roller bearing including the cage segment 101a shown in FIG. The configuration of the roller bearing 111 including the cage segment 101a will be described with reference to FIGS. 11 and 12. The roller bearing 111 holds an outer ring 112, an inner ring 113, a plurality of rollers 114, and a plurality of rollers 114. A plurality of cage segments 101a, 101b, 101c and the like. The plurality of 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 that hold the plurality of rollers 114 are arranged so that the circumferentially adjacent cage segments 101b and 101c having the same shape and the outermost pillar portions 103a and 103e abut on each other. ing. A plurality of cage segments 101 a, 101 b, 101 c, etc. are connected to each other and incorporated in the roller bearing 111 to form one annular cage included in the roller bearing 111.

Further, a technology related to a split type raceway ring in which a raceway ring included in a roller bearing is divided is disclosed in Utility Model Registration No. 2521914 (Patent Document 2).
European Patent Publication EP1408248A2 Utility Model Registration No. 2521914

  As described above, if the bearing constituent members such as the outer ring, the inner ring, and the cage can be divided, the manufacture and transportation of the individual members are facilitated. In particular, the effect is great in a large-sized rolling bearing used for supporting the main shaft of the wind power generator as described above. When the race rings such as the outer ring and the inner ring are divided, it is necessary to join the divided race rings when the rolling bearing is assembled. Here, at the time of assembly, if the divided raceways are not sufficiently coupled to each other, the raceway surface may be displaced or a gap may be generated. If it does so, a rolling element cannot be rolled smoothly.

  An object of the present invention is to provide a rolling bearing having good productivity and capable of smoothly rolling a rolling element.

  Another object of the present invention is to provide a main shaft support structure of a wind power generator that has good productivity and realizes a long life.

  The rolling bearing according to the present invention includes a raceway that can be divided in a circumferential direction, a plurality of rolling elements that are arranged on a raceway surface of the raceway, and a direction along the axis so as to form a pocket that holds the rolling elements. A plurality of pillar segments, and a plurality of retainer segments that have a connecting portion that extends in the circumferential direction so as to connect the plurality of pillar portions, and that are successively arranged in the circumferential direction on the raceway surface of the raceway, Fastening means for fastening the divided race rings to each other.

  By comprising in this way, since a bearing ring and a holder | retainer are divided | segmented among the structural members of a rolling bearing, manufacture and conveyance become easy. Here, when assembling such a rolling bearing, the divided bearing rings can be coupled by fastening means for fastening the bearing rings to each other. If it does so, since the divided | segmented track ring can be couple | bonded reliably, a possibility that a track surface may shift | deviate or a clearance gap will reduce. Therefore, productivity is improved and the rolling element can be smoothly rolled.

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

  Preferably, a corner surface is provided at a corner portion where the divided raceways abut each other. When the raceway ring is divided, an acute edge is generated at the corner of the divided raceway ring. Here, when a step is generated on the raceway surface when the divided raceways are joined, the edge of the corner and the rolling element come into contact with each other at the contact portion of the raceway. If it does so, a rolling element cannot be rolled smoothly. However, with this configuration, the rolling element does not come into contact with the edge of the corner even when a step is generated on the raceway surface. Therefore, the rolling element can be smoothly rolled. Here, the surface smoothing refers to a material obtained by removing a sharp edge by cutting and rounding a corner portion having a sharp edge.

  More preferably, positioning means for determining the position of the divided raceway ring is included. By doing so, the positions of the race rings do not shift when the divided race rings are coupled. Then, it becomes easy to assemble the rolling bearing accurately. Therefore, productivity is improved.

  More preferably, the race ring includes an outer ring and an inner ring. The outer ring and the inner ring can be divided in the circumferential direction, and the positions in the circumferential direction of the part where the divided outer rings abut and the part where the divided inner rings abut are different positions. In the divided races, the divided parts are inferior in strength compared to other parts. When the outer ring and the inner ring can be divided, if the position in the circumferential direction of the portion with inferior strength is made the same, the strength of that portion in the circumferential direction is greatly inferior in the rolling bearing. If a load is applied to a portion of the strength that is greatly inferior, the rolling bearing may be damaged. However, by configuring in this way, the portion of the outer ring with inferior strength and the portion of the inner ring with inferior strength can be placed at different positions. Therefore, it is possible to disperse a portion of the outer ring having a low strength and a portion of the inner ring having a low strength. As a result, the risk of damage to the rolling bearing can be reduced.

  In another aspect of the present invention, the main shaft support structure of the wind power generator includes a blade that receives wind power, one end of which is fixed to the blade, the main shaft that rotates together with the blade, and a fixed member that can rotate the main shaft. And a rolling bearing to support. The rolling bearing includes a ring that can be divided in the circumferential direction, a plurality of rolling elements that are arranged on a raceway surface of the bearing ring, and a plurality of columns that extend in a direction along the axis so as to form a pocket that holds the rolling element. And a plurality of cage segments that have a connecting portion extending in the circumferential direction so as to connect the plurality of pillars, and that are sequentially arranged in the circumferential direction on the raceway surface of the raceway, and a divided raceway Fastening means for fastening the rings together.

  Such a main shaft support structure of a wind power generator has good productivity and includes a rolling bearing capable of smoothly rolling the rolling elements, so that the productivity is good and a long life can be realized. it can.

  In yet another aspect of the present invention, a rolling bearing includes a raceway that can be divided in a circumferential direction and a radial direction, a plurality of rolling elements that are arranged on a raceway surface of the raceway, and a pocket that holds the rolling elements. A plurality of pillars extending in the direction along the axis to form, and a connecting part extending in the circumferential direction so as to connect the plurality of pillars, and sequentially arranged in the circumferential direction on the raceway surface of the raceway ring A plurality of cage segments, and fastening means for fastening the raceways divided in the circumferential direction to each other.

  By comprising in this way, since a bearing ring and a holder | retainer are divided | segmented among the structural members of a rolling bearing, manufacture and conveyance become easy. In this case, since the raceway can be divided in the circumferential direction and the radial direction, each component constituting the raceway can be further reduced. Here, when assembling such a rolling bearing, the race rings divided in the circumferential direction can be coupled by fastening means for fastening the race rings divided in the circumferential direction to each other. If it does so, since the track ring divided | segmented into the circumferential direction can be couple | bonded reliably, a possibility that a track surface may slip | deviate or a clearance gap will reduce. Therefore, productivity is improved and the rolling element can be smoothly rolled.

  Preferably, the rolling bearing is a double row rolling bearing, and the race is divided in the radial direction between the left and right rows of rolling elements in the axial direction. By doing so, the race rings can be arranged and assembled from both sides in the axial direction, and the assemblability can be improved. Further, since the preload can be applied to the rolling elements from the axial direction, the rolling elements can be rolled more smoothly.

  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 rolling bearing to be supported. The rolling bearing extends in a direction along the axis so as to form a raceway ring that can be divided in a circumferential direction and a radial direction, a plurality of rolling elements disposed on a raceway surface of the bearing ring, and a pocket that holds the rolling element. A plurality of retainer segments having a plurality of pillar portions and a connecting portion extending in the circumferential direction so as to connect the plurality of pillar portions, the cage segments being sequentially arranged in the circumferential direction on the raceway surface of the bearing ring; Fastening means for fastening the race rings divided in directions to each other.

  Such a main shaft support structure of a wind power generator has good productivity and includes a rolling bearing capable of smoothly rolling the rolling elements, so that the productivity is good and a long life can be realized. it can.

  According to this invention, since the bearing ring and the cage are divided among the components of the rolling bearing, manufacture and transportation are facilitated. Here, when assembling such a rolling bearing, the divided bearing rings can be coupled by fastening means for fastening the bearing rings to each other. If it does so, since the divided | segmented track ring can be couple | bonded reliably, a possibility that a track surface may shift | deviate or a clearance gap will reduce. Therefore, productivity is improved and the rolling element can be smoothly rolled.

  Further, such a rolling bearing is easily manufactured and transported because the race and the cage are divided among the components of the rolling bearing. In this case, since the raceway can be divided in the circumferential direction and the radial direction, each component constituting the raceway can be further reduced. Here, when assembling such a rolling bearing, the race rings divided in the circumferential direction can be coupled by fastening means for fastening the race rings divided in the circumferential direction to each other. If it does so, since the track ring divided | segmented into the circumferential direction can be couple | bonded reliably, a possibility that a track surface may slip | deviate or a clearance gap will reduce. Therefore, productivity is improved and the rolling element can be smoothly rolled.

  Further, such a main shaft support structure of a wind power generator has good productivity and includes a rolling bearing capable of smoothly rolling the rolling elements, so that the productivity is good and a long life is achieved. be able to.

  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 included in the tapered roller bearing according to the embodiment of the present invention. 3 is a cross-sectional view of the cage segment 11a shown in FIG. 2 taken along a plane that includes the line III-III in FIG. 2 and is perpendicular to the axis. FIG. 4 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 column 14a and is orthogonal to the circumferential direction. From the viewpoint of easy understanding, in FIGS. 3 and 4, 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 FIG. 2, FIG. 3 and FIG. 4, first, the structure of the cage segment 11a included in the tapered roller bearing will be described. The cage segment 11a has a shape in which one annular cage is divided by a dividing line extending in the direction along the axis so as to have at least one pocket for accommodating the rollers. The cage segment 11a includes four column portions 14a, 14b, 14c, and 14d extending in the direction along the axis so as to form pockets 13a, 13b, and 13c that hold the tapered rollers 12a, 12b, and 12c. A pair of connecting portions 15a and 15b extending in the circumferential direction so as to connect the four column portions 14a to 14d, and a pair of protruding portions 16a and 16b positioned in both ends in the axial direction and protruding in the circumferential direction. Including.

  The pair of connecting portions 15a and 15b and the pair of protrusions 16a and 16b are connected in the circumferential direction to form one annular cage when the plurality of cage segments 11a are incorporated in the tapered roller bearing. , Has a predetermined radius of curvature in the circumferential direction. Of the pair of connecting portions 15a and 15b and the pair of protruding portions 16a and 16b, the connecting portion 15a located on the small diameter side of the tapered rollers 12a to 12c and the curvature radius of the protruding portion 16a are larger on the large diameter side of the tapered rollers 12a to 12c. It is comprised smaller than the curvature radius of the connection part 15b and protrusion 16b which are located in.

  When the cage segment 11a is disposed with the other cage segments and the end faces 21a and 21b in contact with each other, the pair of protrusions 16a and 16b causes the cage segment 11a to be interposed between the cage segment 11a and the other cage segment. Forming a pocket for receiving the tapered roller;

  Guide surfaces 17a, 17b, 17c, 17d, 18a, 18b, 18c, and 18d are provided on the inner diameter side and outer diameter side of the column portions 14a to 14d located on both sides in the circumferential direction of the pockets 13a to 13c. With this configuration, the cage segment serves as a roller guide, and movement of the cage segment 11a in the radial direction is restricted. On the outer diameter side and the inner diameter side of the column portions 14a to 14d, oil grooves 19 and 20 penetrating in the circumferential direction are provided in a central portion in the axial direction so as to be recessed radially inward or outward. The oil grooves 19 and 20 improve the circulation of the lubricant.

  Next, a spacer that is included in the tapered roller bearing according to the embodiment of the present invention and that adjusts the circumferential clearance such as the cage segment 11a that is continuous in the circumferential direction will be described. FIG. 5 is a perspective view of a spacer 26 included in the tapered roller bearing. The structure of the spacer 26 will be described with reference to FIG. 5. The spacer 26 includes end portions 27 a and 27 b located at both ends in the axial direction and a central portion 28 located between the end portions 27 a and 27 b. . The distance between the ends 27a and 27b in the axial direction is the same as the distance between the pair of protrusions 16a and 16b included in the cage segment 11a. Further, oil grooves 30a and 30b penetrating in the circumferential direction are provided on the inner diameter surface side and the outer diameter surface side of the central portion 28. The spacer 26 does not have a pocket for accommodating the rollers, and is different from the cage segment 11a having at least one pocket for accommodating the rollers.

  Next, the configuration of the tapered roller bearing including the cage segment 11a and the spacer 26 will be described. FIG. 1 is a schematic sectional view of a tapered roller bearing 31 in which a plurality of cage segments 11a, 11b, 11c, 11d and the like and a spacer 26 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. 6, the tapered rollers 34 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. Here, the first cage segment refers to the cage segment that is placed first when the cage segments are sequentially arranged in the circumferential direction, and the last cage segment is the adjacent cage segment. The cage segments are arranged last when they are placed in contact with each other in the circumferential direction. When arranged in this manner, the gap generated between the first cage segment and the last cage segment is adjusted by the spacer so as to have an appropriate gap size.

  Referring to FIGS. 1 and 6, tapered roller bearing 31 includes an outer ring 32, an inner ring 33, a plurality of tapered rollers 34, a plurality of cage segments 11 a to 11 d, and a spacer 26. The cage segments 11a to 11d are sequentially arranged in the circumferential direction. Here, first, the cage segment 11a is disposed first, and then the cage segment 11b is disposed so as to contact the cage segment 11a. Thereafter, the cage segment 11c is arranged so as to contact the cage segment 11b, the cage segments are sequentially arranged, and finally the cage segment 11d is arranged. Further, between the adjacent two cage segments 11a, 11b, etc., a tapered roller 34 is disposed in the pocket 35 to be formed, except between the first cage segment 11a and the last cage segment 11d. The

  Here, the outer ring 32 that is a raceway ring can be divided into two outer ring segments 32a and 32b. That is, the outer ring 32 has a configuration in which outer ring segments 32a and 32b divided into two in the circumferential direction are coupled. The two outer ring segments 32 a and 32 b have a shape obtained by cutting the outer ring 32 on a plane 37 that passes through the radial center 36 of the outer ring 32 and is orthogonal to the circumferential direction. The outer ring segments 32a and 32b are combined by bringing the contact surfaces 44a and 44c of the outer ring segment 32a into contact with the contact surfaces 44b and 44d of the outer ring segment 32b, respectively. Thus, by making the outer ring 32 separable, the manufacture and transportation of the individual outer ring segments 32a and 32b become easy. Here, “manufacturing is easy” means that it is easy in that the size of each member is reduced. In addition, as described above, the cage that holds the tapered roller 34 is also formed by connecting a plurality of cage segments 11a to 11d that are divided in the circumferential direction. Therefore, the productivity of the tapered roller bearing 31 can be improved.

  Here, the divided outer ring segments 32a and 32b are provided with through holes 43a and 43b and bolt holes 42a and 42b for screwing the bolts 41a and 41b that fasten each other. The bolt holes 42a, 42b and the through holes 43a, 43b are provided so as to extend in a direction orthogonal to the contact surfaces 44a, 44b, 44c, 44d. The outer ring segments 32a and 32b are provided with recesses 45a and 45b that are recessed from the outer peripheral surfaces of the outer ring segments 32a and 32b toward the inner diameter side. The through holes 43a and 43b extend from the contact surfaces 44c and 44b to the recesses 45a and 45b. The through holes 43b and 43a expose the bolt holes 42a and 42b when the outer ring segments 32a and 32b are combined. By providing such recesses 45a and 45b, the bolts 41a and 41b can be inserted into the through holes 43b and 43a, and the bolts 41a and 41b can be easily screwed into the bolt holes 42a and 42b.

  The outer ring segments 32a and 32b are provided with positioning holes 47a and 47b extending from the contact surfaces 44a and 44b to the inner side of the outer ring segments 32a and 32b. The positioning holes 47a and 47b are in contact with the contact surface 44a, the contact surface 44b, and the contact surface 44c when the outer ring segments 32a and 32b are appropriately combined, that is, so that the raceway surface forms a perfect circle. When the surfaces 44d are brought into contact with each other, they are provided at positions facing each other. The positioning holes 47a and 47b provided at the opposing positions have the same diameter, and the positioning pins 48 can be press-fitted.

  Here, a method of joining the two outer ring segments 32a and 32b will be described. The two outer ring segments 32a and 32b are combined such that the contact surfaces 44a to 44d are in contact with each other and the raceway surface formed on the inner diameter side is a perfect circle. In this case, the positioning pins 48 are press-fitted into the positioning holes 47a and 47b and combined. This facilitates accurate assembly of the outer ring segments 32a and 32b. After the combination, the bolts 41a and 41b as fastening means are screwed into the bolt holes 42a and 42b. In this manner, the two outer ring segments 32a and 32b are fastened and coupled to each other.

  By comprising in this way, the outer ring segments 32a and 32b can be reliably fastened and combined by the bolts 41a and 41b and the bolt holes 42a and 42b. This reduces the possibility that the outer ring segments 32a and 32b are misplaced and that a gap is generated between the outer ring segments 32a and 32b. Therefore, the perfect circle of the raceway surface can be maintained, and the tapered roller 34 can be smoothly rolled.

  Further, the flank portions 49a and 49b are provided at the corners of the outer ring segments 32a and 32b (see FIG. 6). That is, the sharp edges at the corners of the outer ring segments 32a and 32b are cut off. With this configuration, when the tapered roller bearing 31 is assembled, the sharp edges of the corners of the outer ring segments 32a and 32b and the tapered roller 34 are in contact with each other even when a step is generated on the raceway surface. Never do. Therefore, the tapered roller 34 can be smoothly rolled.

  Next, the arrangement state of the spacer 26 arranged between the first cage segment 11a and the last cage segment 11d will be described. FIG. 7 is an enlarged cross-sectional view of a portion indicated by VII in FIG. With reference to FIG. 1, FIG. 5 and FIG. 7, the cage segments 11a and the like are successively arranged so as to contact each other, and in the gap 39 generated between the cage segment 11a and the cage segment 11d, The spacer 26 is arranged. Thus, the dimension of the last clearance 40 in the circumferential direction generated between the cage segment 11a and the spacer 26 can be easily set in a range. The last gap is the first cage segment when the cage segments 11a to 11d and the like are arranged without a gap on the circumference, and the last cage segment 11d and the spacer 26 are arranged without a gap. 11a and the maximum clearance between the first retainer segment 11a and the spacer 26 disposed between the last retainer segment 11d.

  In the above-described embodiment, only the outer ring is divided among the races. However, the present invention is not limited to this, and the inner ring may be divided. FIG. 8 is a schematic sectional view of the tapered roller bearing in this case. Referring to FIG. 8, tapered roller bearing 51 includes a splittable outer ring 52 and inner ring 53, a plurality of tapered rollers 54, and a plurality of cage segments 55 that are sequentially arranged in the circumferential direction. The outer ring 52 has a configuration in which two outer ring segments 52a and 52b divided in the circumferential direction are combined, and the inner ring 53 has a configuration in which two inner ring segments 53a and 53b divided in the circumferential direction are combined. The tapered roller bearing 51 includes fastening means such as bolts 56a and 56b and bolt holes 57a and 57b that fasten and join the divided outer ring segments 52a and 52b and inner ring segments 53a and 53b to each other.

  As described above, the configuration of the raceway ring that can be divided in the circumferential direction facilitates the manufacture and transportation of each component of the tapered roller bearing and improves the productivity of the tapered roller bearing. 1 and FIG. Here, it is good also as a structure which can divide | segment a track ring into the circumferential direction and radial direction.

  FIG. 13 is an invention according to yet another embodiment of the present invention, and is a schematic cross-sectional view showing a double row tapered roller bearing when an outer ring as a bearing ring is divided in a circumferential direction and a radial direction. 14 is a perspective view showing an outer ring segment obtained by dividing the outer ring in the circumferential direction and the radial direction and an inner ring segment obtained by dividing the inner ring in the circumferential direction in the double row tapered roller bearing shown in FIG.

  Referring to FIGS. 13 and 14, double row tapered roller bearing 61 includes an outer ring 62, an inner ring 63, a plurality of tapered rollers 64a and 64b, and a plurality of cage segments 65a and 65b. The inner ring 63 has a guide portion 66 that guides the tapered rollers 64a and 64b at the center in the axial direction. The retainer segments 65a and 65b holding the tapered rollers 64a and 64b and the tapered rollers 64a and 64b are arranged in a double row so that the large end face sides of the tapered rollers 64a and 64b face each other. The large end surface sides of the tapered rollers 64a and 64b are guided by the guide surfaces 67a and 67b of the guide portion 66. The circumferential arrangement of the tapered rollers 64a and 64b, the cage segments 65a and 65b, and the spacer is the same as described above, and the description thereof is omitted.

  Here, the outer ring 62 as the raceway ring can be divided in the circumferential direction and the radial direction. Specifically, the outer ring segments 62a and 62b divided in the circumferential direction and the radial direction are configured such that the outer ring 62 passes through the center of the outer ring 62 in the radial direction and is orthogonal to the circumferential direction, and the outer ring segment passes through the center in the axial direction. This is a shape cut by a plane 69 perpendicular to the center axis 62 in the radial direction. The inner ring segment 63a is formed by cutting the inner ring 63 along a plane that passes through the radial center of the inner ring 63 and is orthogonal to the circumferential direction. The outer ring segments 62a and 62b are arranged so that the end surfaces 68a and 68b positioned on the large end surface side of the tapered rollers 64a and 64b come into contact with each other.

  Such a double-row tapered roller bearing 61 is easily manufactured and transported because the outer ring 62, the inner ring 63, and the cage are divided among the constituent members of the double-row tapered roller bearing 61. In this case, since the outer ring 62 can be divided in the circumferential direction and the radial direction, the outer ring segments 62a and 62b constituting the outer ring 62 can be further reduced. Here, when assembling such a double-row tapered roller bearing 61, the fastening means for fastening the outer ring segments 62a, the outer ring segments 62b, and the inner ring segments 63a that are divided in the circumferential direction as described above to each other. The outer ring 62 and the inner ring 63 divided in the circumferential direction can be combined. As a result, the outer ring 62 and the inner ring 63 that are divided in the circumferential direction can be reliably coupled, so that the possibility that the raceway surface is displaced or a gap is generated is reduced. Thereafter, the outer ring segments 62a and 62b coupled in the circumferential direction are assembled from the axial direction. In this way, the double row tapered roller bearing 61 is assembled. Therefore, productivity is improved and the tapered rollers 64a and 64b can be smoothly rolled.

  In this case, since the outer ring 62 is radially divided between the left and right rows of axial rollers, such a double row tapered roller bearing 61 has outer ring segments 62a and 62b on both sides in the axial direction, that is, in the figure. 13 can be installed in the direction of the arrow in FIG. Therefore, the embeddability can be improved. In this case, a preload can be applied to the tapered rollers 64 a and 64 b further toward the inner side of the double row tapered roller bearing 61. Then, the large end surfaces of the tapered rollers 64a and 64b can be positively brought into contact with the guide surfaces 67a and 67b for guidance. Therefore, the tapered rollers 64a and 64b can be rolled more smoothly.

  In addition, about said embodiment, although the outer ring | wheel 62 was made into the shape divided | segmented radially at the center part of the axial direction, it is not restricted to this, The shape which divided | segmented the outer ring | wheel 62 radially at the other part in the axial direction Alternatively, the outer ring 62 may be divided in the radial direction at a plurality of portions in the axial direction. Further, although the end surfaces 68a and 68b in the axial direction of the outer ring segments 62a and 62b are brought into contact with each other, the present invention is not limited thereto, and the end surfaces 68a and 68b may not be in contact with each other. In addition, when the divided portion is included in the raceway surface, it is also possible to provide surface glazing at the corners of the divided surface as described above. Further, the outer ring segments 62a and 62b divided in the radial direction may be fastened. Furthermore, it is good also as a structure which can be divided | segmented into an axial direction and a circumferential direction also about an inner ring | wheel. Moreover, the said structure is applied also to a single row tapered roller bearing.

  Furthermore, in the above-described embodiment, the case where the present invention is applied to a tapered roller bearing has been described. However, the present invention is not limited to this and may be applied to a self-aligning roller bearing.

  FIG. 15 is a schematic cross-sectional view showing a self-aligning roller bearing according to still another embodiment of the present invention, which corresponds to FIG. FIG. 16 is a perspective view showing an outer ring segment obtained by dividing the outer ring in the circumferential direction and the radial direction and an inner ring segment obtained by dividing the inner ring in the circumferential direction in the self-aligning roller bearing shown in FIG.

  15 and 16, self-aligning roller bearing 91 includes an outer ring 92, an inner ring 93, a plurality of spherical rollers 94a and 94b, and a plurality of cage segments 95a and 95b. The inner ring 93 has a guide portion 96 that guides the spherical rollers 94a and 94b in the center in the axial direction. The spherical rollers 94a and 94b and the cage segments 95a and 95b that hold the spherical rollers 94a and 94b are arranged in a double row so that the large end face sides of the spherical rollers 94a and 94b face each other. The large end surface sides of the spherical rollers 94a and 94b are guided by the guide surfaces 97a and 97b of the guide portion 96. The arrangement of the spherical rollers 94a and 94b, the cage segments 95a and 95b, and the spacer in the circumferential direction is the same as in the case of the tapered roller bearing described above, and a description thereof will be omitted.

  Here, the outer ring 92 as the raceway ring can be divided in the circumferential direction and the radial direction. Specifically, the outer ring segments 92a and 92b divided in the circumferential direction and the radial direction are configured such that the outer ring 92 passes through the center of the outer ring 92 in the radial direction and is orthogonal to the circumferential direction, and the outer ring segment passes through the center in the axial direction. It is the shape cut | disconnected by the plane 99 perpendicular | vertical to the central axis of 92 radial directions. The inner ring segment 93a is formed by cutting the inner ring 93 along a plane that passes through the radial center of the inner ring 93 and is orthogonal to the circumferential direction. The outer ring segments 92a and 92b are arranged so that the end surfaces 98a and 98b positioned on the large end surface side of the spherical rollers 94a and 94b come into contact with each other.

  Also with the self-aligning roller bearing 91 having such a configuration, like the double-row tapered roller bearing 61 shown in FIG. 13, the productivity can be improved and the spherical rollers 94a and 94b can be smoothly rolled.

  9 and 10 show an example of a main shaft support structure of a wind power generator to which a tapered roller bearing according to one 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 that can be divided in the circumferential direction and a plurality of tapered rollers that are disposed on the raceway surface of the outer ring. And a plurality of pillars extending in the direction along the axis so as to form a pocket for holding the tapered rollers, and a connecting part extending in the circumferential direction so as to connect the plurality of pillars, on the raceway surface of the outer ring And a plurality of cage segments arranged sequentially in the circumferential direction and fastening means for fastening the divided outer rings to each other.

  Since the main shaft support bearing 75 supports the main shaft 76 that fixes the blade 77 that receives large wind force at one end, a large load is applied. Then, it is necessary to make the main shaft support bearing 75 itself large. Here, by comprising as mentioned above, a tapered roller can be rolled smoothly and productivity of a tapered roller bearing can be improved. If it does so, productivity can also be improved and it can be made long life also about the main shaft support structure of a wind power generator provided with such a tapered roller bearing.

  A main shaft support bearing 75 incorporated in the bearing housing 74 is a double row tapered roller bearing according to still another embodiment of the present invention, and includes an outer ring that can be divided in the axial direction and the circumferential direction, and a raceway of the outer ring. A plurality of tapered rollers arranged on the surface, a plurality of pillars extending in a direction along the axis so as to form a pocket for holding the tapered rollers, and a connection extending in the circumferential direction so as to connect the plurality of pillars And a plurality of cage segments that are sequentially arranged in the circumferential direction on the raceway surface of the outer ring, and fastening means for fastening the outer rings divided in the circumferential direction to each other.

  Also with this configuration, the tapered roller can be smoothly rolled and the productivity of the tapered roller bearing can be improved. If it does so, productivity can also be improved and it can be made long life also about the main shaft support structure of a wind power generator provided with such a tapered roller bearing.

  Further, the main shaft support bearing 75 incorporated in the bearing housing 74 is a self-aligning roller bearing according to still another embodiment of the present invention, and includes an outer ring that can be divided in the axial direction and the circumferential direction, and a raceway surface of the outer ring. A plurality of spherical rollers arranged above, a plurality of pillars extending in a direction along the axis so as to form a pocket for holding the spherical rollers, and a connecting part extending in the circumferential direction so as to connect the plurality of pillars And a plurality of cage segments sequentially arranged in the circumferential direction on the raceway surface of the outer ring, and fastening means for fastening the outer rings divided in the circumferential direction to each other.

  Also with this configuration, the spherical roller can be smoothly rolled, and the productivity of the self-aligning roller bearing can be improved. If it does so, productivity can also be improved and it can be made a long life also about the spindle support structure of a wind power generator provided with such a self-aligning roller bearing.

  In the above embodiment, the bolt and the bolt hole are used as the fastening means for fastening the two outer ring segments. However, the present invention is not limited to this, and the outer ring segments are fastened by other fastening means. It may be. For example, it may be fastened with an adhesive having strong adhesiveness, or an annular groove is provided on the outer diameter surface of the outer ring, and the outer ring segments are constrained by fitting a ring-shaped member into the groove from the outer diameter side. However, it may be concluded.

  Moreover, in embodiment mentioned above in FIGS. 1-8, although the outer ring | wheel and the inner ring | wheel were made into the shape cut | disconnected in two by the plane orthogonal to an axis | shaft, respectively passing through the center of an outer ring | wheel or an inner ring | wheel, it does not restrict to this. For example, in the above-described embodiment, a configuration that can be divided into four portions of 90 degrees in the circumferential direction may be used, or a configuration that can be divided into a larger number may be used. Further, the divided race rings may have different shapes.

  In the above embodiment, as the positioning means, the positioning pins are press-fitted into the positioning holes to position the raceways. However, the present invention is not limited to this, and positioning may be performed by other means. Good. For example, positioning may be performed by providing concave and convex engaging portions that engage with each other on the contact surfaces of the raceways and engaging the engaging portions.

  In the above embodiment, the cage segments 11a to 11d have the protrusions 16a and 16b protruding in the circumferential direction. However, the present invention is not limited thereto, and the type does not have the protrusions 16a and 16b. That is, the present invention is also applied to a cage segment having a configuration in which a pillar portion is disposed on the outer side in the circumferential direction.

  In the above embodiment, the tapered roller bearing includes a spacer. However, the present invention is not limited to this, and the present invention can be applied to a tapered roller bearing of a type that does not include such a spacer. Also, the shape of the spacer may be, for example, a substantially rectangular parallelepiped shape or a shape in which the central portion bulges in the circumferential direction. Furthermore, it is not necessary to arrange a roller between adjacent cage segments, or a roller may be arranged between the spacer and the cage segment.

  In the above embodiment, the tapered roller is used as the rolling element provided in the rolling bearing. However, the present invention is not limited to this, and a cylindrical roller, a needle roller, a rod roller, a ball, a spherical roller, or the like may be used. Good.

  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 rolling bearing according to the present invention is effectively used when good productivity and long life are required.

  The main shaft support structure for a wind power generator according to the present invention can also be effectively used for the main shaft support structure for a wind power generator that requires good productivity and long life.

It is a schematic sectional drawing at the time of cut | disconnecting the tapered roller bearing which concerns on one Embodiment of this invention by the plane orthogonal to an axis | shaft. 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 by the plane orthogonal to an axis | shaft including line III-III in FIG. 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 a perspective view which shows the spacer contained in a tapered roller bearing. It is an expanded sectional view which shows the adjacent retainer segment. It is an expanded sectional view at the time of arrange | positioning a spacer between the 1st retainer segment and the last retainer segment. It is a schematic sectional drawing of the tapered roller bearing which concerns on other embodiment of this invention. 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. 10 is a schematic side view of the main shaft support structure of the wind power generator shown in FIG. 9. It is a perspective view of the retainer segment in the past. It is sectional drawing at the time of cut | disconnecting the holder | retainer segment shown in FIG. 11 by the plane orthogonal to an axis | shaft including a pillar part. It is a schematic sectional drawing of the double row tapered roller bearing which concerns on other embodiment of this invention. FIG. 14 is a perspective view showing an outer ring segment and an inner ring segment provided in the double row tapered roller bearing shown in FIG. 13. It is a schematic sectional drawing of the self-aligning roller bearing which concerns on other embodiment of this invention. FIG. 16 is a perspective view showing an outer ring segment and an inner ring segment provided in the self-aligning roller bearing shown in FIG. 15.

Explanation of symbols

  11a, 11b, 11c, 11d, 55, 65a, 65b, 95a, 95b Cage segment, 12a, 12b, 12c, 34, 54, 64a, 64b tapered rollers, 13a, 13b, 13c, 35 pockets, 14a, 14b, 14c, 14d Pillar part, 15a, 15b Connecting part, 16a, 16b Protruding part, 17a, 17b, 17c, 17d, 18a, 18b, 18c, 18d, 67a, 67b, 97a, 97b Guide surface, 19, 20, 30a, 30b oil groove, 21a, 21b, 68a, 68b, 98a, 98b end face, 22 PCD, 26 spacer, 27a, 27b end part, 28 center part, 31, 51, 61 tapered roller bearing, 32, 52, 62, 92 Outer ring, 32a, 32b, 52a, 52b, 62a, 62b, 92a, 92b Outer ring segment, 33, 3, 63, 93 Inner ring, 36 center, 37, 69, 99 plane, 39 clearance, 40 last clearance, 41a, 41b, 56a, 56b bolt, 42a, 42b, 57a, 57b bolt hole, 43a, 43b through hole, 44a , 44b, 44c, 44d, contact surface, 45a, 45b recess, 47a, 47b positioning hole, 48 positioning pin, 49a, 49b splay, 53a, 53b, 63a, 93a inner ring segment, 58a, 58b contact portion, 66 , 96 Guide section, 70 Support base, 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 Reducer, 91 spherical roller bearing, 94a, 94b spherical roller.

Claims (7)

A ring that can be divided in the circumferential direction;
A plurality of rolling elements disposed on a raceway surface of the raceway,
A plurality of pillar portions extending in a direction along the axis so as to form a pocket for holding the rolling elements, and a connecting portion extending in the circumferential direction so as to connect the plurality of pillar portions; A plurality of cage segments arranged sequentially in the circumferential direction above,
A rolling bearing comprising fastening means for fastening the divided race rings to each other. The rolling bearing according to claim 1, wherein a flat surface is provided at a corner of a portion where the divided race rings abut against each other. The rolling bearing according to claim 1, further comprising positioning means for determining a position of the divided raceway ring. A blade that receives wind,
One end of which is fixed to the blade and rotates with the blade;
A main shaft support structure of a wind power generator, which is incorporated in a fixed member and has a rolling bearing that rotatably supports the main shaft,
The rolling bearing extends in a direction along an axis so as to form a raceway that can be divided in a circumferential direction, a plurality of rolling elements disposed on a raceway surface of the raceway, and a pocket that holds the rolling element. A plurality of retainer segments having a plurality of pillar portions and a connecting portion extending in the circumferential direction so as to connect the plurality of pillar portions, and sequentially arranged in the circumferential direction on the raceway surface of the raceway; A main shaft support structure for a wind power generator, comprising fastening means for fastening the divided raceways to each other. A raceway ring that can be divided in a circumferential direction and a radial direction;
A plurality of rolling elements disposed on a raceway surface of the raceway,
A plurality of pillar portions extending in a direction along the axis so as to form a pocket for holding the rolling elements, and a connecting portion extending in the circumferential direction so as to connect the plurality of pillar portions; A plurality of cage segments arranged sequentially in the circumferential direction above,
A rolling bearing comprising fastening means for fastening the raceways divided in the circumferential direction to each other. The rolling bearing is a double row rolling bearing,
The rolling bearing according to claim 5, wherein the bearing ring is divided in a radial direction between left and right rows of axial rolling elements. A blade that receives wind,
One end of which is fixed to the blade and rotates with the blade;
A main shaft support structure of a wind power generator, which is incorporated in a fixed member and has a rolling bearing that rotatably supports the main shaft,
The rolling bearing follows an axis so as to form a raceway ring that can be divided in a circumferential direction and a radial direction, a plurality of rolling elements disposed on a raceway surface of the raceway, and a pocket that holds the rolling element. A plurality of retainers which have a plurality of pillar portions extending in the direction and a connecting portion extending in the circumferential direction so as to connect the plurality of pillar portions and are successively arranged in the circumferential direction on the raceway surface of the raceway. A main shaft support structure for a wind power generator, comprising: a segment; and fastening means for fastening the raceway rings divided in the circumferential direction to each other.

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