JP4372763B2 - Roller bearing and wind turbine main shaft support structure - Google Patents

Description

  The present invention relates to a roller bearing and a main shaft support structure and a spacer for a wind power generator, and in particular, a roller bearing including a split type retainer, a main shaft support structure for a wind power generator including such a roller bearing, and such a roller. The present invention relates to a spacer provided in a 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. 14 is a perspective view showing a cage segment which is a split type cage disclosed in Patent Document 1. FIG. Referring to FIG. 14, the 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.

FIG. 15 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. 14 and 15. 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 segment 101a that holds the plurality of rollers 114 is continuously arranged so that the cage segments 101b and 101c having the same shape adjacent in the circumferential direction and the outermost column 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.
European Patent Publication EP1408248A2

  One annular retainer described above is formed by arranging a plurality of retainer segments in a circumferential direction. In order to form a single annular cage by connecting a plurality of cage segments in the circumferential direction, a circumferential gap in consideration of thermal expansion or the like is required.

  Here, if this circumferential clearance is too wide, the cage segments move greatly in the circumferential direction, and adjacent cage segments collide with each other, so that abnormal noise may be generated or the cage segments may be damaged. In addition, the cage segment thermally expands as the temperature rises, but if this circumferential clearance is narrow, the thermal expansion eliminates the gap between adjacent cage segments, and the adjacent cage segments Will push each other. The circumferential stress caused by this thermal expansion causes friction and wear of the cage segment, which also causes breakage of the cage segment.

  Here, according to Patent Document 1, when the cage segments are brought into contact with each other and arranged in the circumferential direction, the dimension of the last gap generated between the first cage segment and the last cage segment is determined. A technique is disclosed in which the circumferential clearance is made appropriate by defining the circumference of the circle passing through the center of the cage segment as 0.15% or more and less than 1%.

  However, since each cage segment is manufactured independently, each cage segment has a dimensional error in the circumferential direction. When the cage segments having such dimensional errors are arranged in the circumferential direction, the dimensional errors are also accumulated. Therefore, in order to make the circumferential clearance within the above-mentioned predetermined range, each cage segment must be manufactured with high accuracy, and the productivity of the cage segment deteriorates. Bearing productivity will also deteriorate.

  An object of the present invention is to provide a roller bearing with good productivity.

  Another object of the present invention is to provide a main shaft support structure for a wind power generator with good productivity.

  Still another object of the present invention is to provide a spacer that is stably arranged.

  The roller bearing according to the present invention has an outer ring, an inner ring, a plurality of rollers arranged between the outer ring and the inner ring, and a pocket for holding the rollers, and is successively connected in the circumferential direction between the outer ring and the inner ring. And a plurality of retainer segments, and a spacer disposed between the first retainer segment and the last retainer segment that are arranged in the circumferential direction.

  By comprising in this way, a spacer can be arrange | positioned in the clearance gap between the 1st retainer segment and the last retainer segment. Then, regardless of the circumferential dimension error of each cage segment, the dimension between the first cage segment and the last cage segment can be set within a set range. Therefore, it is not necessary to manufacture each cage segment with high accuracy, and the productivity of the cage segment is improved. As a result, the productivity of the roller bearing is also improved. In this case, rollers and spacers may be arranged.

  Here, the cage segment is a unit body obtained by dividing one annular cage by a dividing line extending in a direction along the axis so as to have at least one pocket for accommodating the rollers. The first cage segment is 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 brought into contact with each other and sequentially arranged in the circumferential direction. A plurality of cage segments are connected to the roller bearing in a circumferential direction to form one annular cage. The cage segment has at least one pocket that accommodates the roller, and is different from a spacer that does not have a pocket that accommodates the roller.

  Preferably, the cage segment is provided with a pair of protrusions positioned at both ends in the axial direction and projecting in the circumferential direction, and the spacer is formed of the pair of projections provided in the first cage segment. It contacts the circumferential end surface and the circumferential end surface of the pair of protrusions provided on the last cage segment. By comprising in this way, the circumferential load from a spacer can be received by a pair of protrusion part. If it does so, a load will not be applied to the pillar part which forms the pocket contained in a cage segment from the spacer in the peripheral direction. Therefore, it is possible to prevent deformation and breakage of the column portion and locking of the rollers held in the pocket.

  More preferably, the spacer is located at both ends in the axial direction, and has an end portion sandwiched between the protrusions of the first and last retainer segments, and a central portion located between the both end portions. With this configuration, both end portions included in the spacer come into contact with the pair of protrusions of the first and last cage segments. If it does so, the pillar part of a holder | retainer segment and the edge part of a spacer will not contact | abut. Therefore, a load is not applied to the column portion from the spacer.

  More preferably, the central portion of the spacer has a circumferential bulge that bulges in the circumferential direction and is received between the pair of protrusions of the cage segment. With this configuration, the movement of the spacer in the axial direction is restricted by the pair of protrusions, and the movement in the axial direction is restricted. Therefore, the displacement of the spacer in the axial direction can be suppressed.

  More preferably, the spacer is provided with a groove penetrating in the circumferential direction. By comprising in this way, the lubrication agent of oil or grease can be smoothly lubricated in the circumferential direction by the groove | channel provided in the spacer. Here, the term “through” includes not only the case of passing through the central portion of the spacer but also the case of passing through the surface on the inner diameter side or outer diameter side.

  More preferably, the circumferential dimension of the gap between the first cage segment and the spacer is 0.15% or more of the circumference of a circle passing through the coupling portion of the cage segments connected in the circumferential direction. Less than the maximum roller diameter. By comprising in this way, the clearance dimension between holder | retainer segments can be kept appropriate. Specifically, by setting it to 0.15% or more of the circumference, even when each cage segment is thermally expanded, there is no possibility that the cage segment is damaged. Here, in order to receive a larger load, it is conceivable to arrange rollers between adjacent cage segments. However, by setting the gap size to be smaller than the maximum roller diameter in the axial direction, adjacent cage segments are arranged. It is possible to smoothly guide the rollers disposed between the two.

  More preferably, the roller is a tapered roller. The roller bearing used for the main shaft of the wind power generator described above needs to receive a large thrust load, moment load, radial load and the like. Here, when the roller is a tapered roller, a large thrust load or the like can be received. Even if the tapered roller bearing is large in order to receive a large thrust load, etc., the cage is a split cage segment, so it is easy to incorporate and the cage segment productivity is good. Productivity of roller bearings is also improved.

  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. Here, the roller bearing has an outer ring, an inner ring, a plurality of rollers arranged between the outer ring and the inner ring, and a pocket for holding the rollers, and is sequentially linked in the circumferential direction between the outer ring and the inner ring. A plurality of cage segments are arranged, and a spacer is arranged between the first cage segment and the last cage segment that are arranged in the circumferential direction.

  Since the main shaft support structure of such a wind power generator includes a roller bearing with good productivity, the productivity of the main shaft support structure itself of the wind power generator is also improved.

  In still another aspect of the present invention, the spacer is disposed between the first retainer segment and the last retainer segment that are connected in the circumferential direction, and contacts the first retainer segment or the last retainer segment. It has an abutting part in contact. The spacer is an independent member, and its arrangement is unstable in the roller bearing. By configuring in this way, the contact portion of the spacer can be used as the first cage segment or the last cage. It can be placed in contact with the segment. Therefore, the arrangement of the spacers can be stabilized in the roller bearing.

  More preferably, it has a movement restricting means that is arranged between the first retainer segment and the last retainer segment that are continuous in the circumferential direction and restricts the movement in the axial direction of the retainer segment. By comprising in this way, the movement of the spacer itself in the axial direction can be restricted, and the arrangement in the axial direction can be stabilized.

  More preferably, a groove is provided between the first retainer segment and the last retainer segment that are continuous in the circumferential direction and allows the lubricant to pass therethrough. By comprising in this way, a lubrication agent can be smoothly flowed to a radial direction, an axial direction, etc. through the groove | channel provided in the spacer. Then, the lubricant can be circulated efficiently in the roller bearing. Accordingly, the rollers can be smoothly rolled.

  More preferably, it is arranged between the first cage segment and the last cage segment that are connected in the circumferential direction, and when cut along a plane orthogonal to the axial direction, the corners of the diagonal line passing through the two corners The length between them is longer than the roller diameter in the cross section. As described above, the spacer is unstablely arranged in the roller bearing, and the spacer may fall down due to the clearance in the circumferential direction. However, with this configuration, even when the spacer receives a load in the circumferential direction, the corner of the spacer is caught by the outer ring or the like. Therefore, the spacer can be prevented from falling.

  According to the present invention, the spacer can be arranged in the last gap between the first cage segment and the last cage segment. Then, regardless of the dimensional error of each cage segment, the dimension of the last gap can be within an appropriate range by the spacer. Therefore, it is not necessary to manufacture each cage segment with high accuracy, and the productivity of the cage segment is improved. As a result, the productivity of the roller bearing is also improved.

  In addition, since the main shaft support structure of the wind power generator includes a roller bearing with good productivity, the productivity of the main shaft support structure itself of the wind power generator is also improved.

  Moreover, such a spacer is stably arrange | positioned in a roller bearing.

  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. FIG. 3 is a cross-sectional view of the cage segment 11a shown in FIG. 2 cut in the radial direction by arrows III-III in FIG. Moreover, FIG. 4 is sectional drawing at the time of cut | disconnecting the retainer segment 11a to an axial direction in the cross section containing the pillar part 14a. 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.

  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 includes four column portions 14a, 14b, 14c, 14d extending in the direction along the axis so as to form pockets 13a, 13b, 13c for receiving the tapered rollers 12a, 12b, 12c, A pair of connecting portions 15a and 15b extending in the circumferential direction so as to connect the four pillar portions 14a, 14b, 14c and 14d, and a pair of protrusions positioned in both ends in the axial direction and projecting in the circumferential direction Parts 16a and 16b.

  The pair of projecting portions 16a and 16b are provided so as to project in the circumferential direction from the column portions 14a and 14d located on the outermost side in the circumferential direction, in continuation with the pair of connecting portions 15a and 15b. That is, the pair of protrusions 16a and 16b has a shape in which the connecting portions 15a and 15b extend in the circumferential direction more than the column portions 14a and 14d in the circumferential direction.

  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 and the like are incorporated in the tapered roller bearing. Furthermore, it has a predetermined radius of curvature in the circumferential direction. Of the pair of connecting portions 15a and 15b and the pair of projecting portions 16a and 16b, the connecting portion 15a located on the small diameter side of the tapered roller 12a and the like, and the curvature radius of the projecting portion 16a is located on the large diameter side of the tapered roller 12a and the like. It is comprised smaller than the curvature radius of the connection part 15b and the protrusion 16b to perform. The circumferential ends of the pair of protrusions 16a and 16b have end surfaces 21a and 21b that come into contact with adjacent cage segments when a plurality of cage segments 11a and the like are arranged in the circumferential direction.

  The pair of protrusions 16a and 16b accommodate the tapered rollers between the cage segment 11a and the other cage segment when the other cage segments and the end faces 21a and 21b are arranged in contact with each other. Form a pocket.

  Guides for restricting movement of the cage segment 11a radially outward on the inner diameter side of the pillars 14a, 14b located on both sides in the circumferential direction of the pocket 13a and the pillars 14c, 14d located on both sides in the circumferential direction of the pocket 13c. Surfaces 17a, 17b, 17c, and 17d are provided. In addition, guide surfaces 18b and 18c for restricting the movement of the cage segment 11a inward in the radial direction are provided on the outer diameter side of the column portions 14b and 14c located on both sides in the circumferential direction of the pocket 13b. With such a configuration, the cage segment 11a becomes a so-called roller guide, and the radial position of the cage segment 11a can be stably arranged.

  Also, guide surfaces 18a and 18d are provided on the outer diameter side of the outer circumferential direction of the column portions 14a and 14d located on the outermost circumferential direction. The guide rollers 18a and 18d allow the tapered rollers disposed between the adjacent cage segments to guide the cage segments.

  Here, since the cage segment 11a is independent, there is a possibility that the cage segment 11a may be inclined with respect to the PCD 22 when arranged in the tapered roller bearing. However, the cage segment 11a has a total of three pockets, specifically, two inner diameter guiding pockets 13a and 13c at both ends of the cage segment 11a and one outer diameter guiding pocket 13b at the center of the cage segment 11a. Therefore, the possibility that the cage segment 11a is inclined with respect to the PCD 22 is reduced, and the stability is good.

  A groove 19 penetrating in the circumferential direction is provided on the outer diameter surface side of the pillar portions 14a, 14b, 14c, and 14d, and a groove 20 penetrating in the circumferential direction is provided on the inner diameter surface side. The groove 19 has a shape recessed toward the inner diameter side from the outer diameter surface of the column portions 14a to 14d in the central portion in the axial direction, and the groove 20 extends from the inner diameter surface of the column portions 14a to 14d in the central portion in the axial direction. The shape is recessed on the outer diameter side. By comprising in this way, a lubricant can be smoothly flowed in the circumferential direction.

  Next, the spacer 26 included in the tapered roller bearing according to the embodiment of the present invention 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.

  The circumferential dimension of the central portion 28 is configured to be smaller than the circumferential dimension of the end portions 27a and 27b. The dimension of the central portion 28 in the radial direction is slightly smaller than the dimension between the raceway surfaces when incorporated in the tapered roller bearing. By doing so, when the spacer 26 is incorporated in the tapered roller bearing, it becomes a raceway guide, and the radial position can be stabilized. End surfaces 29a and 29b are provided on the outer sides in the circumferential direction of the end portions 27a and 27b. Grooves 30 a and 30 b that penetrate in the circumferential direction are provided on the inner diameter surface side and the outer diameter surface side of the central portion 28. By configuring in this way, the lubricant can be smoothly flowed in the circumferential direction as in the grooves 19 and 20 provided in the cage segment 11a.

  Next, the configuration of the tapered roller bearing including the cage segment 11a and the spacer 26 will be described. FIG. 6 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 and a spacer 26 are arranged in the circumferential direction as seen from the axial direction. Here, since the cage segments 11b, 11c, 11d and the like 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. Here, among the plurality of cage segments 11a to 11d and the like, the cage segment arranged first is the cage segment 11a, and the cage segment arranged last is the cage segment 11d.

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

  Next, details of the cage segment 11b adjacent to the cage segments 11a and 11c will be described. FIG. 7 is an enlarged cross-sectional view of a portion indicated by VII in FIG. Referring to FIG. 7, the retainer segment 11b is configured such that the end surface 21c of the protrusion 16c of the retainer segment 11b abuts on the end surface 21a of the protrusion 16a of the retainer segment 11a, and the protrusion 16d of the retainer segment 11b It arrange | positions so that the end surface 21d and the end surface 21e of the protrusion 16e of the holder | retainer segment 11c may contact | abut.

  A pocket 35a for accommodating the tapered roller 34 is formed between the two adjacent cage segments 11b and 11c. The pocket 35a holds a tapered roller 34 disposed between adjacent cage segments 11b and 11c. Here, the pocket 35a is formed, for example, by defining the protruding amount of the protrusion 16d of the cage segment 11b and the protrusion 16e of the cage segment 11c according to the diameter of the tapered roller 34 to be held. The

  With this configuration, the tapered roller bearing 31 is provided by the tapered rollers 34 disposed between the cage segments 11b and 11c in addition to the tapered rollers 34 held by the cage segments 11a to 11d. Can also receive loads. Then, the tapered roller bearing 31 can receive a larger load. In particular, when the number of cage segments 11a to 11d and the like included in the tapered roller bearing 31 is large, the number of tapered rollers 34 disposed between the cage segments 11b and 11c and the like is also large, and the effect is remarkable. It is.

  Further, since the guide surface 36 is provided on the outer diameter side of the column portion 37 positioned on the outer side in the circumferential direction of the cage segment 11b, the cage segment 11b is also guided by the guide surface 36. Then, the radial position of the cage segment 11b can be further stabilized.

  Here, a load may be applied from the protrusion 16e of the adjacent cage segment 11c to the cage segment 11b in the circumferential direction, that is, in the direction indicated by the arrow D in FIG. Even in such a case, the protrusion 16e of the cage segment 11c and the projection 16d of the cage segment 11b come into contact with each other, so that no load is applied to the column portion 37 forming the pockets 35a and 35b. Then, deformation and breakage of the column portion 37 and locking of the tapered rollers 34 held in the pocket 35b can be prevented.

  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. 1 is an enlarged cross-sectional view of a portion indicated by I in FIG. 8 is a schematic view of the portion shown in FIG. 1 as viewed from the outside in the radial direction, that is, from the outer ring 32 side. With reference to FIG. 1 and FIG. 8, when the cage segments 11a and the like are successively arranged so as to contact each other, a gap 39 is generated between the cage segment 11a and the cage segment 11d.

  The dimension in the circumferential direction of the gap 39 is set within a certain range in consideration of the thermal expansion of the cage segments 11a to 11d and the like accompanying the temperature rise. However, in the dimension of the gap 39, circumferential dimension errors of the cage segments 11a to 11d and the like are accumulated. Therefore, it is very difficult to set the dimension of the gap 39 within the set range.

  Here, the spacer 26 is disposed so that the end faces 21f, 21g on the protrusions 16f, 16g side of the cage segment 11d abut on the end faces 29a, 29b on one side of the ends 27a, 27b of the spacer 26. Let In this case, the end portions 27a and 27b of the spacer 26 are sandwiched between the protrusions 16a and 16b of the cage segment 11a and the projections 16f and 16g of the cage segment 11d.

  By comprising in this way, the dimension of the last clearance 40 of the circumferential direction produced between the holder | retainer segment 11a and the spacer 26 can be easily set as the range. Here, the last clearance is the first 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. This is the maximum clearance between the cage segment 11a and the spacer 26 disposed between the first cage segment 11a and the last cage segment 11d. Of the circles passing through the connecting portion 15a of the cage segment 11a, if the dimension of the gap 39 on the circle with the smallest diameter is C, the dimension of the end 27a is A, and the dimension of the last gap 40 is B, The dimension A of the portion 27a is arbitrarily determined so that the dimension B of the last gap 40 falls within the set range when the spacer 26 is disposed between the cage segment 11a and the cage segment 11d. It is done. Here, in order to make the dimension B within the set range, for example, the end 27a may be cut in the circumferential direction according to the dimension C, or the spacers 26 having various dimensions A are manufactured in advance. The spacer 26 may be selected and arranged in accordance with the dimension C.

  With this configuration, the tapered roller bearing 31 in which the spacer 26 is disposed between the first cage segment 11a and the last cage segment 11d has a circumferential dimension such as the cage segments 11a to 11d. Regardless of the error, the last gap 40 between the cage segments 11a and 11d can be within a set range. If it does so, it will become unnecessary to manufacture cage segments 11a-11d etc. with high precision, and productivity of cage segments 11a-11d etc. will improve. Along with this, the productivity of the tapered roller bearing 31 is also improved.

  Here, the optimal circumferential dimension of the last clearance 40 is 0.15% or more of the circumference of the circle passing through the connecting portion 15a of the cage segment 11a, and less than the maximum roller diameter in the axial direction of the tapered roller 34. To do.

  When the circumferential dimension of the last gap is 0.15% or less of the circumference, the cage segments 11a to 11d are provided between the cage segment 11a and the spacer 26 when thermally expanded. This is because the last gap 40 is eliminated and a great amount of circumferential stress may occur in the cage segments 11a to 11d. Further, when the circumferential dimension of the last clearance is equal to or larger than the maximum roller diameter in the axial direction of the tapered roller 34, the axial arrangement of the tapered rollers 34 held between the adjacent cage segments 11a to 11d is not good. This is because it may become stable and cause poor guidance.

  As described above, the spacer 26 is disposed between the first retainer segment 11a and the last retainer segment 11d connected in the circumferential direction, but the first retainer segment 11a or the last retainer segment is disposed. It has a contact portion that contacts the segment 11d. The spacer 26 is an independent member, and its arrangement is unstable in the tapered roller bearing 31. By configuring in this way, the contact portion of the spacer 26 can be used as the first cage segment 11a. Alternatively, it can be placed in contact with the last cage segment 11d. Therefore, the arrangement of the spacers 26 can be stabilized in the tapered roller bearing 31.

  Here, as described above, by using the end surfaces 29a and 29b of the spacer 26 as the contact portions and contacting the end surfaces 21f and 21g of the last cage segment 11d, the arrangement can be stabilized as described above and FIG. 1 and FIG. Here, according to another embodiment, the spacer 26 and the last cage segment 11d can be brought into contact with each other. For example, the central portion 28 of the spacer 26 may be brought into contact with the pillar portion of the last cage segment 11d. In this case, the contact portion becomes the central portion 28 of the spacer 26. Also with this configuration, the arrangement of the spacers 26 can be stabilized. In the above, from the viewpoint of easy understanding, the case where the spacer 26 and the last cage segment 11d are brought into contact with each other has been described. However, the spacer 26 and the first cage segment 11a are brought into contact with each other. The arrangement of the spacers 26 may be stabilized.

  Further, although the above description overlaps, the spacer 26 is disposed between the first retainer segment 11a and the last retainer segment 11d connected in the circumferential direction. Here, when the spacer 26 is cut along a plane perpendicular to the axial direction, the length between the corners of the diagonal line passing through the two corners is longer than the roller diameter of the tapered roller 34 in the cross section. Has been.

  As described above, the spacer 26 is unstable in the tapered roller bearing 31, and depending on the size of the last gap 40 provided between the cage segments 11 a to 11 d and the shape of the spacer 26, The spacer 26 may fall in the circumferential direction. If it does so, it will become impossible to maintain the clearance dimension of the circumferential direction in an appropriate range. However, with this configuration, the spacer 26 can be prevented from falling.

  This will be described with reference to FIG. FIG. 16 is an enlarged cross-sectional view in the case where the spacer 26 is disposed between the first cage segment 11a and the last cage segment 11d, and corresponds to FIG. Referring to FIG. 16, when the length between the two corners 46a and 46b of the diagonal line 47 passing through the two corners 46a and 46b of the spacer 26 is E and the roller diameter of the tapered roller 34 is F, E > F. With this configuration, even when the spacer 26 tries to fall in the circumferential direction, the corners 46a and 46b can be caught by the outer ring 32 and the inner ring 33, and the circumferential fall of the spacer 26 can be prevented. Here, the diagonal line 47 refers to a line connecting the two corners 46a and 46b of the spacer 26, and a rounded part is included in the corners 46a and 46b.

  Here, the circumferential dimension of the central portion 28 included in the spacer 26 described above is configured to be smaller than the circumferential dimension of the end portions 27a and 27b. The size in the circumferential direction of the central portion 28 may be larger than the size in the circumferential direction of the end portions 27a and 27b.

  FIG. 9 is a perspective view of the spacer 41 in this case. Referring to FIG. 9, the spacer 41 has end portions 42a and 42b positioned at both ends in the axial direction, and a central portion 43 positioned between both end portions 42a and 42b. The central portion 43 bulges in the circumferential direction from both sides in the circumferential direction, and has a shape that is received between the pair of protrusions 16a and 16b of the cage segment 11a and the pair of projections 16f and 16g of the cage segment 11d. A bulging portion 44 is provided. Further, grooves 45a and 45b penetrating in the circumferential direction are provided on the radially outer and inner diameter surfaces.

  FIG. 10 is a view from the radially outer side when the spacer 41 is disposed between the cage segments 11a and 11d. Referring to FIG. 10, the spacer 41 is disposed between the first cage segment 11a and the last cage segment 11d. Here, the circumferential bulging portion 44 provided in the spacer 41 is received between the protrusions 16a and 16b of the cage segment 11a and the pair of projections 16f and 16g of the cage segment 11d.

  Even if the spacer 41 having such a configuration tries to move in the axial direction, the circumferential bulging portion 44 is restrained by the pair of protrusions 16a and 16b and the pair of protrusions 16f and 16g, so that the axial movement is prevented. Be regulated. Therefore, the axial displacement of the spacer 41 can be suppressed.

  Here, the circumferential bulging portion 44 has a shape that bulges from both sides of the central portion 43 in the circumferential direction, but is not limited thereto, and bulges from one side of the central portion 43 in the circumferential direction. You may make it into a shape.

  In addition, as described above, the spacer 41 and the like are disposed between the first cage segment 11a and the last cage segment 11d that are continuous in the circumferential direction. There is a movement restricting means for restricting movement.

  The spacer 26 is an independent member, and its arrangement is unstable in the tapered roller bearing 31 or the like. A circumferentially bulging portion 44 that bulges in the circumferential direction is provided at the center portion 43 of such a spacer 41, and the circumferential bulging portion 44 is received by the pair of protrusions 16f and 16g. The movement in the axial direction is restricted, the displacement in the axial direction is suppressed, and the arrangement in the axial direction is stabilized. This is apparent from the above and FIG. 9 and FIG.

  Here, according to another embodiment, the movement of the spacer 41 and the like in the axial direction can be restricted. For example, the end portions 42a and 42b of the spacer 41 are provided with connecting means for connecting to the last cage segment 11d. With this configuration, even if the spacer 41 tries to move in the axial direction, the end portions 42a and 42b are connected to the last cage segment 11d. Directional movement is restricted. Therefore, the position of the spacer 41 in the axial direction can be stabilized. In this case, for example, an engagement portion that engages with the protrusions 16f and 16g of the last cage segment 11d is provided at the end portions 42a and 42b of the spacer 41, and the engagement portions are engaged to thereby connect the You may decide to do it.

  In the above embodiment, the cage segment 11a and the like have three pockets for accommodating the rollers. However, the present invention is not limited to this and may have four or more pockets. FIG. 11A and FIG. 11B are radial cross-sectional views of the cage segment in this case. Referring to FIG. 11A, the cage segment 51 connects the pillars 53 and a plurality of pillars 53 extending in the direction along the axis so as to form four pockets 52a, 52b, 52c, and 52d. The pair of connecting portions 54 extending in the circumferential direction as described above and the pair of projecting portions 55a and 55b that are located at both ends in the axial direction and project from the connecting portion 54 in the circumferential direction are included. Guide surfaces 56 for guiding the cage segments 51 are provided on the inner diameter side and the outer diameter side of the column portion 53. Further, referring to FIG. 11B, the cage segment 61 includes a plurality of pillar portions 63 extending in the direction along the axis, and pillars so as to form five pockets 62a, 62b, 62c, 62d, 62e. A pair of connecting portions 64 extending in the circumferential direction so as to connect the portion 63 and a pair of projecting portions 65 a and 65 b that are located at both ends in the axial direction and that extend from the connecting portion 64 in the circumferential direction are included. A guide surface 66 for guiding the cage segment 61 is provided on the inner diameter side and the outer diameter side of the column part 63. Since the cage segments 51 and 61 having such a configuration have many pockets 52a provided with guide surfaces 56 and 66, the cage segments 51 and 61 are more stably arranged in the radial direction.

  In the above-described embodiment, the grooves 30a and 30b that penetrate in the circumferential direction are provided on the outer diameter surface and inner diameter surface of the spacer 26 and the like. A groove 30a or the like may be provided on any one of the upper surfaces, or a central portion in the radial direction such as the central portion 28 may be penetrated in the circumferential direction. In this case, the lubricant can flow more efficiently by matching the radial positions of the grooves 19 and 20 provided in the cage segments 11a and 11d with the grooves 30a provided in the spacer 26 and the like. Can do.

  Further, as described above, the spacers 26 and the like are disposed between the first cage segment 11a and the last cage segment 11d that are continuous in the circumferential direction. A groove for allowing oil to pass therethrough is provided. The spacer 26 and the like are provided with grooves 30a and 30b that penetrate in the circumferential direction. This is apparent with reference to the above and FIGS. 5 and 8 to 10. Here, not only the circumferential direction but also a groove penetrating in the axial direction or a groove penetrating in the radial direction may be provided.

  By comprising in this way, a lubrication agent can be smoothly flowed in an axial direction and a radial direction. Then, in the tapered roller bearing 31 or the like, the lubricant can be efficiently circulated through a groove provided in the spacer 26 for passing the lubricant. Therefore, the tapered roller 34 can be smoothly rolled. In this case, as described above, the surface of the spacer 26 or the like may be penetrated, or the center part of the spacer 26 or the like may be penetrated. A plurality of grooves may be provided in the axial direction, radial direction, and circumferential direction.

  12 and 13 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 roller bearing according to an embodiment of the present invention, and includes an outer ring, an inner ring, a plurality of rollers disposed between the outer ring and the inner ring, and a roller. A plurality of cage segments having pockets for holding and sequentially arranged in the circumferential direction between the outer ring and the inner ring, and between the first cage segment and the last cage segment arranged in the circumferential direction And a spacer to be arranged.

  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 making a roller bearing provided with a cage segment having a shape obtained by dividing one annular cage, the productivity, handling and assembly of the cage are improved, so the productivity of the roller bearing itself is also improved. It becomes good. Further, since the last gap 40 between the cage segments arranged in the circumferential direction is within the range set by the spacer, the cage segment is thermally expanded due to the temperature rise or the cage segment is damaged due to the collision between the cage segments. The possibility of abnormal noise is reduced.

  In the above embodiment, the cage segment has a protrusion protruding in the circumferential direction. However, the present invention is not limited to this, and a type having no protrusion, that is, a column part on the outer side in the circumferential direction. The present invention is also applied to a cage segment having a configuration in which is arranged.

  The spacer 26 and the like included in the tapered roller bearing 31 is small and has a simple shape. Therefore, the material is made of resin such as engineer plastic, and is easily manufactured by injection molding or the like. can do. By doing so, productivity is further improved.

  In the above embodiment, the tapered roller is used as the roller accommodated in the cage segment 11a. 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 can be effectively used for a roller bearing with improved productivity because the last gap between the cage segments can be set within a set range regardless of the dimensional accuracy of the cage segments. The

  Further, the main shaft support structure of the wind power generator according to the present invention can be effectively used for the main shaft support structure of the wind power generator with improved productivity because the roller bearing can be easily manufactured.

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 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 retainer segment shown in FIG. 2 to radial direction. It is sectional drawing at the time of cut | disconnecting the retainer segment shown in FIG. 2 to an axial direction. It is a perspective view which shows the spacer contained in a tapered roller bearing. It is a schematic sectional drawing of a tapered roller bearing at the time of arranging a plurality of cage segments and spacers in the circumferential direction. It is an expanded sectional view which shows the adjacent retainer segment. It is the schematic which looked at the part shown in FIG. 1 from the radial direction outer side. It is a perspective view of the spacer containing a circumferential bulge part. It is the figure which looked at the spacer shown in FIG. 9 from the radial direction outer side. FIG. 4 is a cross-sectional view of another embodiment of a cage segment included in a tapered roller bearing, (A) a cage segment having four pockets, and (B) a cage segment having five pockets. 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. 13 is an illustrative side view of the main shaft support structure of the wind power generator shown in FIG. 12. It is a perspective view of the retainer segment in the past. It is sectional drawing at the time of cut | disconnecting the retainer segment shown in FIG. 14 to radial direction. It is an expanded sectional view at the time of arranging a spacer between the first cage segment and the last cage segment, and shows the relationship between the length between two corners and the roller diameter of the tapered roller is there.

Explanation of symbols

  11a, 11b, 11c, 11d, 51, 61 Cage segment, 12a, 12b, 12c, 34 Tapered roller, 13a, 13b, 13c, 35a, 35b, 52a, 52b, 52c, 52d, 62a, 62b, 62c, 62d , 62e pockets, 14a, 14b, 14c, 14d, 37, 53, 63 pillars, 15a, 15b, 15c, 15d, 54, 64 connecting parts, 16a, 16b, 16c, 16d, 16e, 16f, 16g, 55a, 55b, 65a, 65b Projection, 17a, 17b, 17c, 17d, 18a, 18b, 18c, 18d, 36, 56, 66 Guide surface, 19, 20, 30a, 30b, 45a, 45b Groove, 21a, 21b, 21c , 21d, 21e, 21f, 21g, 29a, 29b end face, 22 PCD, 26, 41 spacer, 27a, 27b, 42a, 42b End, 28, 43 Center, 31 Tapered roller bearing, 32 Outer ring, 33 Inner ring, 39 Clearance, 40 Final clearance, 44 Circumferential bulge, 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 speed reducer, 46a, 46b corner, 47 diagonal.

Claims (10)

Outer ring,
Inner ring,
A plurality of rollers disposed between the outer ring and the inner ring;
A plurality of pillars extending in the direction along the axis so as to form the pockets, and a plurality of pillars positioned at both ends in the axial direction and connected in the circumferential direction to connect the plurality of pillars; A plurality of retainer segments arranged in series so as to sequentially contact each other in the circumferential direction between the outer ring and the inner ring,
A spacer that is arranged between the first cage segment and the last cage segment that are connected in the circumferential direction and is an independent member;
The cage segment is provided with a pair of protrusions located at both ends in the axial direction and protruding in the circumferential direction,
The spacer is in contact with a circumferential end surface of a pair of protrusions provided on the first cage segment and a circumferential end surface of a pair of projections provided on the last cage segment. . The said spacer is located in the both ends of an axial direction, and has the edge part pinched | interposed into the protrusion of the said 1st and last retainer segment, and the center part located between this both edge parts. Roller bearing. The roller bearing according to claim 2, wherein a central portion of the spacer has a circumferential bulge that bulges in the circumferential direction and is received between a pair of protrusions of the cage segment. The roller bearing according to claim 1, wherein the spacer is provided with a groove penetrating in a circumferential direction. The circumferential dimension of the gap between the first cage segment and the spacer is not less than 0.15% of the circumference of a circle passing through the coupling portion of the cage segment connected in the circumferential direction. The roller bearing in any one of Claims 1-4 which is less than a largest roller diameter. The roller bearing according to claim 1, wherein the roller is a tapered roller. The roller bearing according to any one of claims 1 to 6, wherein the spacer has movement restricting means for restricting movement in the axial direction of the spacer. The roller bearing according to claim 1, wherein the spacer is provided with a groove through which a lubricant is allowed to pass. When the spacer is cut along a plane orthogonal to the axial direction, the length between the corners of the diagonal passing through the two corners of the spacer is longer than the roller diameter in the cross section. The roller bearing according to any one of 8. 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 having a roller bearing incorporated in a fixing member and rotatably supporting the main shaft,
The roller bearing has an outer ring, an inner ring, a plurality of rollers disposed between the outer ring and the inner ring, and a pocket for holding the roller, and in a direction along the axis so as to form the pocket. A plurality of pillars extending in the axial direction, and a pair of connecting parts extending in the circumferential direction so as to connect the plurality of pillars, and sequentially in the circumferential direction between the outer ring and the inner ring. A plurality of cage segments arranged in series so as to contact each other, and a spacer that is arranged between the first cage segment and the last cage segment arranged in the circumferential direction and is an independent member;
The cage segment is provided with a pair of protrusions located at both ends in the axial direction and protruding in the circumferential direction,
The spacer is in contact with a circumferential end surface of a pair of protrusions provided on the first cage segment and a circumferential end surface of a pair of projections provided on the last cage segment. Main shaft support structure of the machine.

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