JP2006349032A - Double-row tapered roller bearing and spindle supporting structure of aerogenerator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a double-row tapered roller bearing capable of avoiding interference between an inner ring spacer and a small diameter side side-plate while maintaining the rigidity of the inner ring spacer to a certain value and a spindle supporting structure of an aerogenerator. <P>SOLUTION: A relief part 20 reduced in thickness is formed in the inner ring spacer 18 in an area facing the minimum inner diameter portions of the small diameter side side-plates 17a and 17b during assembly. The relief part 20 is formed in such a stepped shape that its thickness is reduced from the outer diameter part 19 of the inner ring spacer 18 to a diameter at which the small diameter side side-plates 17a and 17b are not interfered with each other, namely, the center part of the inner ring spacer 18 is formed thick and both end parts thereof are formed thin. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a double-row tapered roller bearing and a main shaft support structure of a wind power generator, and more particularly to a double-row tapered roller bearing capable of receiving a large radial load, thrust load, and moment load, and wind power generation using such a bearing. The present invention relates to the main shaft support structure of the machine.

  The bearing used for the main shaft of the wind power generator needs to receive a radial load against the weight of the blade, a thrust load against the wind force, and a moment load. Furthermore, since the main shaft of a wind power generator has a cantilever beam structure, a bearing having self-alignment with respect to the deflection of the main shaft is required, and therefore, a combination of a self-aligning roller bearing and a cylindrical roller bearing is used. It was. FIG. 8 is a schematic view when the self-aligning roller bearing 101 is used as a main shaft of a wind power generator. Referring to FIG. 8, the self-aligning roller bearing 101 holds an inner ring 102, a plurality of aligning rollers 103 a and 103 b arranged in the left and right rows, and a distance between the plurality of aligning rollers 103 a and 103 b. A container 104 and an outer ring 105. The self-aligning roller bearing 101 is mounted on a main shaft 112 provided with a blade 111 for receiving wind at one end, and is incorporated in a housing 113. The self-aligning roller bearing 101 and the cylindrical roller bearing thus mounted are combined and used for the main shaft of the wind power generator.

  However, a bearing that combines the above-mentioned two rolling bearings has a large number of parts and is required to be reduced. Moreover, it is requested | required also about size reduction of a bearing.

  In response to such requirements, double-row tapered roller bearings that can receive large radial loads, thrust loads, and moment loads with a single bearing, although inferior in alignment compared to spherical roller bearings, Used for the main shaft of the machine. FIG. 9 is an example of a cross-sectional view of the double row tapered roller bearing 121. Referring to FIG. 9, double-row tapered roller bearing 121 includes left and right inner rings 122a, 122b arranged so that the end surfaces on the small diameter side face each other, inner ring spacers 128 arranged between inner rings 122a, 122b, and outer rings. 124, a plurality of tapered rollers 123a, 123b disposed between the inner rings 122a, 122b and the outer ring 124, and left and right cages for holding the intervals between the plurality of tapered rollers 123a, 123b in the left and right rows.

  For each cage, a pin type cage that can hold more tapered rollers 123a and 123b is used in order to realize a load capacity against a large radial load. The pin type retainer holds the one end of the pins 125a and 125b penetrating the tapered rollers 123a and 123b and the plurality of pins 125a and 125b protruding to the large end face side of the tapered rollers 123a and 123b and extends in an annular shape. Large-diameter side plates 126a and 126b, and small-diameter side plates 127a and 127b that hold the other ends of the plurality of pins 125a and 125b protruding toward the small end surfaces of the tapered rollers 123a and 123b and extend annularly.

A double-row tapered roller bearing using such a pin type cage is disclosed in Japanese Patent Application Laid-Open No. 2003-49843 (Patent Document 1), and a wind turbine for wind power generation using the double-row tapered roller bearing as a main shaft. Is disclosed in Japanese Patent Laying-Open No. 2005-105917 (Patent Document 2).
JP 2003-49843 A (paragraph numbers 0008 to 0009, FIG. 1) Japanese Patent Laying-Open No. 2005-105917 (paragraph numbers 0020 to 0039, FIG. 2)

  In order to obtain a larger power generation amount, the blade 111 needs to receive a larger wind. Under such an environment, the bearing supporting the main shaft receives a larger radial load, a thrust load, and a moment load. In order to receive a larger radial load, it is necessary to make the roller lengths of the tapered rollers 123a and 123b of the double-row tapered roller bearing 121 as large as possible. Further, in order to receive a larger thrust load and moment load, it is necessary to increase a contact angle that is an angle formed by the outer ring raceway surface and the rotational axis of the double row tapered roller bearing 121.

  FIG. 10 is a cross-sectional view of the double row tapered roller bearing 121 when the contact angle is increased. Referring to FIG. 10, when the contact angle α, which is the angle formed between the outer ring raceway surface 131 and the rotation axis (not shown) of the double row tapered roller bearing 121, is increased, the minimum inner diameter portion of the small diameter side plates 127a and 127b The corner portion K may interfere with the outer diameter portion 129 of the inner ring spacer 128.

  In this case, it is conceivable to avoid interference with the small-diameter side plates 127a and 127b by reducing the outer diameter of the inner ring spacer 128 and reducing the thickness. However, since a large surface pressure is applied to the inner ring spacer 128 from the end surfaces on the small diameter side of the inner rings 122a and 122b when the bearings are assembled, it is necessary to maintain the rigidity of the inner ring spacer 128 to some extent and reduce the thickness. There are also limitations.

  Further, as described above, from the viewpoint of maintaining the rigidity against the radial load, the roller lengths of the tapered rollers 123a and 123b cannot be shortened to avoid interference between the inner ring spacer 128 and the small diameter side plates 127a and 127b.

  Further, it is conceivable to change the shapes of the small diameter side plates 127a and 127b, for example, by reducing the thickness of the small diameter side plates 127a and 127b to prevent interference between the inner ring spacer 128 and the small diameter side plates 127a and 127b. However, since the small-diameter side plates 127a and 127b must hold a plurality of pins 125a and 125b, the small-diameter side plates 127a and 127b also need to maintain a certain degree of rigidity. It cannot be thinned.

  The present invention relates to a double-row tapered roller bearing capable of avoiding interference between the inner ring spacer and the small-diameter side plate while maintaining the rigidity of the inner ring spacer to some extent, and a main shaft support structure for a wind power generator using such a bearing. The purpose is to provide.

  A double row tapered roller bearing according to the present invention includes an outer ring, left and right inner rings arranged to face the end surfaces on the small diameter side, an inner ring spacer arranged between the left and right inner rings, and an outer ring and left and right inner rings. It is a double row tapered roller bearing provided with a plurality of tapered rollers arranged between them and a left and right cage for maintaining the spacing between the plurality of tapered rollers in the left and right rows. Each of the cages described above includes a pin that passes through each tapered roller, a small-diameter side plate that extends annularly while holding one end of a plurality of pins protruding to the small end face side of each tapered roller, and a large diameter for each tapered roller. A large-diameter side plate extending annularly while holding the other ends of the plurality of pins protruding to the end surface side. Here, the inner ring spacer has a relief portion with a reduced thickness in a region facing the minimum inner diameter portion of the small-diameter side plate.

  By configuring in this way, a relief portion with reduced thickness is provided in a region facing the minimum inner diameter portion of the small-diameter side plate that is a portion that interferes with the small-diameter side plate of the inner ring spacer. Interference with the small diameter side plate can be avoided. Further, since the relief portion is provided only in the interfering portion and the thickness of the inner ring spacer is not reduced in the other portions, the rigidity of the inner ring spacer can be maintained to some extent.

  Preferably, the outer diameter of the escape portion is made smaller than the minimum inner diameter of the small diameter side plate. By comprising in this way, interference with an inner ring | wheel spacer and a small diameter side plate can be avoided reliably.

  More preferably, the maximum outer diameter of the inner ring spacer is larger than the minimum inner diameter of the small-diameter side plate. By configuring in this way, the rigidity of the inner ring spacer can be sufficiently maintained while avoiding interference between the inner ring spacer and the small diameter side plate.

  More preferably, the minimum inner diameter portion of the small diameter side plate forms a cylindrical surface. For example, when the cross-sectional shape of the small-diameter side plate is a quadrangle, a rectangular corner corresponding to the minimum inner diameter portion is cut to obtain a cylindrical surface. By doing so, the minimum inner diameter of the small-diameter side plate can be increased, and accordingly, the amount of reducing the radial thickness of the escape portion provided in the inner ring spacer is reduced, and the small-diameter side plate and the inner ring spacer are respectively reduced. Stiffness can be maintained.

  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. A main shaft support structure of a wind power generator having a double row tapered roller bearing to be supported. The double-row tapered roller bearing described above includes an outer ring, left and right inner rings arranged so that the end faces on the small diameter side face each other, an inner ring spacer arranged between the left and right inner rings, and an outer ring and the left and right inner rings. A plurality of tapered rollers arranged, and left and right cages for holding the intervals between the plurality of tapered rollers in the left and right rows. Each of the cages described above includes a pin that passes through each tapered roller, a small-diameter side plate that extends annularly while holding one end of a plurality of pins protruding to the small end face side of each tapered roller, and a large diameter for each tapered roller. A large-diameter side plate extending annularly while holding the other ends of the plurality of pins protruding to the end surface side. Here, the inner ring spacer has a relief portion with a reduced thickness in a region facing the minimum inner diameter portion of the small-diameter side plate.

  By configuring in this way, while avoiding interference between the inner ring spacer and the small-diameter side plate and maintaining the rigidity of the inner ring spacer to some extent, the outer ring raceway surface and the bearing rotation axis of the double row tapered roller bearing Therefore, it is possible to provide a main shaft support structure for a wind power generator capable of receiving a larger thrust load and moment load.

  According to this invention, the rigidity of the inner ring spacer can be favorably maintained while avoiding interference between the inner ring spacer and the small-diameter side plate.

  If such a double-row tapered roller bearing is used for the main shaft of a wind power generator, the contact angle is avoided while avoiding interference between the inner ring spacer and the small-diameter side plate and maintaining the rigidity of the inner ring spacer. Therefore, it is possible to receive a larger thrust load and moment load.

  Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a view showing a double row tapered roller bearing 11 according to an embodiment of the present invention. Referring to FIG. 1, double-row tapered roller bearing 11 includes left and right inner rings 12a and 12b arranged so that the end faces on the small diameter side face each other, inner ring spacers 18 arranged between inner rings 12a and 12b, An outer ring 14 having a raceway surface corresponding to the inner rings 12a and 12b, a plurality of tapered rollers 13a and 13b disposed between the inner rings 12a and 12b and the outer ring 14, and a distance between the plurality of tapered rollers 13a and 13b in the left and right rows Left and right cages.

  Since the inner rings 12a and 12b receive a large thrust load and moment load, a contact angle that is an angle formed between the outer ring raceway surface and the rotation axis (not shown) of the double row tapered roller bearing 11 is configured to be large. Preferably, the contact angle is set within a range of 40 ° to 47 °.

  An inner ring spacer 18 having a shape capable of avoiding interference with the small-diameter side plates 17a and 17b is disposed between the inner rings 12a and 12b. Both end surfaces of the inner ring spacer 18 are in contact with the small diameter side end surfaces of the left and right inner rings 12a and 12b, respectively, and pressure is applied from the inner rings 12a and 12b when the bearings are assembled. Therefore, the inner ring spacer 18 needs to be rigid enough to withstand the pressure. In order to ensure rigidity, it is necessary to increase the radial sectional area, that is, to increase the radial thickness of the inner ring spacer 18.

  The outer ring 14 has a cross-sectional shape whose central portion is convex in the radial direction, and holds a plurality of tapered rollers 13a and 13b between the inner rings 12a and 12b. In the present embodiment, one outer ring 14 is configured, but separate outer rings may be provided for the inner rings 12a and 12b, respectively.

  The tapered rollers 13a and 13b are disposed between the outer ring 14 and the inner rings 12a and 12b. Further, in order to enable holding by a pin type cage, which will be described later, the tapered rollers 13a and 13b are provided with through holes for inserting pins from the small end surface to the large end surface.

  As the cage, a pin type cage that can hold more tapered rollers 13a and 13b is used. Each of the left and right cages includes a pin 15a, 15b that passes through each of the tapered rollers 13a, 13b, and a small-diameter side plate that holds one end of the plurality of pins 15a, 15b protruding toward the small end surface of each of the tapered rollers 13a, 13b. 17a, 17b and large-diameter side plates 16a, 16b that hold the other ends of the plurality of pins 15a, 15b protruding to the large end face side of the tapered rollers 13a, 13b.

  Each of the small-diameter side plates 17a and 17b and the large-diameter side plates 16a and 16b extends annularly around the rotation axis and has a ring shape. The small-diameter side plates 17a and 17b are disposed on the small flange side of the inner rings 12a and 12b, and the inner diameter is smaller than the large-diameter side plates 16a and 16b disposed on the large collar side. In addition, the small-diameter side plates 17a and 17b and the large-diameter side plates 16a and 16b both hold a large amount of pins 15a and 15b, and therefore need a certain rigidity. From the viewpoint of rigidity, productivity, and the like, it is preferable that the cross-sectional shapes of the small-diameter side plates 17a and 17b and the large-diameter side plates 16a and 16b are rectangular. Here, there is no particular problem even if the small-diameter side plates 17a and 17b and the large-diameter side plates 16a and 16b have other shapes such as a circular shape and an elliptical shape as long as rigidity can be ensured.

  The inner ring spacer 18 is provided with a relief portion 20 having a reduced thickness in a region facing the minimum inner diameter portion of the small diameter side plates 17a and 17b when assembled. The escape portion 20 has a stepped shape in which the thickness is reduced from the outer diameter portion 19 of the inner ring spacer 18 to a diameter at which the small diameter side plates 17a and 17b do not interfere, that is, the central portion of the inner ring spacer 18 is thicker and both ends are thin. It has a shape. The region that faces the minimum inner diameter portion is a region that is shifted to both ends from at least the central portion of the inner ring spacer 18. Therefore, about the center part, the thickness of the inner ring spacer 18 is not reduced, and the thickness is such that the rigidity of the inner ring spacer 18 can be maintained.

  By configuring in this way, the interference between the region of the inner ring spacer 18 facing the minimum inner diameter portion of the small diameter side plates 17a and 17b and the corner portion K which is the minimum inner diameter portion of the small diameter side plates 17a and 17b when assembled. Can be avoided. Further, since the thickness of the central portion of the inner ring spacer 18 is not reduced, the rigidity of the inner ring spacer 18 can be maintained to some extent.

  FIG. 2 is an enlarged view of the escape portion 20 and the small diameter side plate 17b among the portions indicated by II in FIG. Referring to FIG. 2, if the outer diameter of the escape portion 20 provided in the region facing the minimum inner diameter portion of the inner ring spacer 18 is A and the minimum inner diameter of the small-diameter side plate 17b is B, the relationship of B> A is established. . By doing so, it is possible to reliably avoid interference between the inner ring spacer 18 and the small diameter side plates 17a and 17b. Further, when the maximum outer diameter of the inner ring spacer 18 is C, a relationship of C> B is established. By doing so, the rigidity of the inner ring spacer 18 can be maintained.

  Here, the shape of the escape portion 20 may be any shape that can avoid interference between the outer diameter portion 19 of the inner ring spacer 18 and the corner portions K of the small diameter side plates 17a and 17b. Further, a groove-shaped relief portion having a V-shaped cross section may be provided in a region facing the minimum inner diameter of the small-diameter side plates 17a and 17b. By doing so, the outer diameter of the end face of the inner ring spacer 18 becomes the same as the central part and is larger than the outer diameter of the escape part, so the amount of escape of the escape part is minimized and the rigidity of the inner ring spacer is increased. Can be maintained.

  In the previous embodiment, the shape of the relief portion has two slopes in the cross section and has a step shape. However, the shape is not limited to this, and the step shape is not configured. May be.

  FIG. 3 is a schematic view showing an example of an inner ring spacer 55 and small-diameter side plates 17a and 17b according to another embodiment of the present invention. With reference to FIG. 3, one inclined surface is formed from the outer diameter portion 56 toward the left and right end faces of the inner ring spacer 55, and this is defined as a relief portion 57. In this case, since the escape portion 57 has a single slope, the step of forming the escape portion 57 can be facilitated.

  Further, in the previous embodiment, the large thickness is the central portion and has a certain width. However, the present invention is not limited to this, and the large thickness may not have a width.

  FIG. 4 is a schematic view showing an example of an inner ring spacer 60 and small-diameter side plates 17a and 17b according to still another embodiment of the present invention. Referring to FIG. 4, one inclined surface is formed from the substantially central portion of inner ring spacer 60 toward the left and right end surfaces of inner ring spacer 60, and this is defined as escape portion 62. In this case, since there is no width having a thickness at the center, the inner ring spacer 60 having a relatively simple configuration can be obtained.

  In the previous embodiment, the escape portion is provided only in the inner ring spacer. However, the present invention is not limited to this, and the escape portion may be provided in any of the inner ring spacer and the small-diameter side plate.

  FIG. 5 is a schematic view showing an example of an inner ring spacer 65 and small-diameter side plates 68a and 68b according to still another embodiment of the present invention. Referring to FIG. 5, the small-diameter side plates 68a and 68b have a small-diameter side plate so as to ensure a large minimum inner diameter of the minimum inner-diameter portion that is an interference portion by cutting the corner K corresponding to the minimum inner-diameter portion. Cylindrical surfaces 69a and 69b are provided on 68a and 68b. By cutting the corner portion K or the like, the minimum inner diameter is increased, and the shape is changed from a square shape to a cylindrical shape. In this case, the minimum inner diameter can be increased by cutting to an amount that can ensure the rigidity of the small-diameter side plates 68a and 68b.

  Here, for the inner ring spacer 65, a relief portion 67 with a reduced thickness is provided in a region facing the cylindrical surfaces 69a and 69b of the small-diameter side plates 68a and 68b. In this case, since the inner diameter is larger than the minimum inner diameter at the corner portion K, the outer diameter of the escape portion 67 may be larger than the outer diameter of the escape portion provided in FIG.

  Thus, by increasing the minimum inner diameter of the small diameter side plates 68a and 68b, interference between the minimum inner diameter portion and the inner ring spacer 65 may be avoided.

  By doing so, the minimum inner diameter of the small-diameter side plates 68a and 68b can be increased, and the outer diameter of the escape portion 67 can be increased. Accordingly, it is possible to avoid interference between the inner ring spacer 65 and the small diameter side plates 68a and 68b while maintaining the rigidity of the inner ring spacer 65 and the small diameter side plates 68a and 68b well.

  6 and 7 show an example of a main shaft support structure of a wind power generator in which the double row tapered roller bearing described above is applied as the main shaft support bearing 35. FIG. The casing 33 of the nacelle 32 that supports the main components of the spindle support structure is installed on the support base 30 via the swivel bearing 31 at a high position so as to be able to turn horizontally. A main shaft 36 that fixes a blade 37 that receives wind power to one end is rotatably supported in a casing 33 of the nacelle 32 via a main shaft support bearing 35 incorporated in a bearing housing 34. Is connected to the speed increaser 38, and the output shaft of the speed increaser 38 is coupled to the rotor shaft of the generator 39. The nacelle 32 is turned at an arbitrary angle by a turning motor 40 via a speed reducer 41.

  The main shaft support bearing 35 incorporated in the bearing housing 34 is a double row tapered roller bearing according to an embodiment of the present invention, and includes an outer ring, left and right inner rings arranged to face the small-diameter side end faces, An inner ring spacer disposed between the inner rings, a plurality of tapered rollers disposed between the outer ring and the left and right inner rings, and left and right cages that maintain the spacing between the plurality of tapered rollers in the left and right rows. . Each of the cages described above includes a pin that passes through each tapered roller, a small-diameter side plate that extends annularly while holding one end of a plurality of pins protruding to the small end surface side of each tapered roller, and a large end surface side of each tapered roller And a large-diameter side plate extending annularly while holding the other ends of the plurality of pins projecting. The inner ring spacer described above has a relief portion with a reduced thickness in a region facing the minimum inner diameter portion of the small diameter side plate.

  By making the main shaft support bearing 35 a double-row tapered roller bearing having such a configuration, the inner ring spacer and the small-diameter side plate do not interfere with each other, and the rigidity of the inner ring spacer is maintained to a certain extent. The angle can be increased and a larger thrust load and moment load can be received. As a result, it is possible to provide a main shaft support structure for a wind power generator that can receive larger thrust loads and moment loads.

  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 main shaft support structure of the double-row tapered roller bearing and the wind power generator according to the present invention has a large contact angle without causing interference between the inner ring spacer and the small-diameter side plate and maintaining good rigidity of the inner ring spacer. Therefore, it can be effectively used particularly for a double-row tapered roller bearing and a main shaft support structure of a wind power generator that receive a large radial load, thrust load and moment load.

It is a figure showing an example of double row tapered roller bearing 11 concerning one embodiment of this invention. It is an enlarged view showing the details of the inner ring spacer 18 and the small diameter side plate 17b according to an embodiment of the present invention. It is the schematic which shows an example of the inner ring spacer 55 and the small diameter side plates 17a and 17b based on other embodiment of this invention. It is the schematic which shows an example of the inner ring spacer 60 and the small diameter side board 17a, 17b based on further another embodiment of this invention. It is the schematic which shows an example of the inner ring | wheel spacer 65 and the small diameter side board 68a, 68b based on other embodiment of this invention. It is a figure which shows an example of the spindle support structure of the wind power generator using the double row tapered roller bearing which concerns on this invention. FIG. 7 is a schematic side view of the main shaft support structure of the wind power generator shown in FIG. 6. It is the schematic at the time of using the self-aligning roller bearing 101 for the main axis | shaft of a wind power generator. It is sectional drawing which shows an example of the conventional double row tapered roller bearing 121. It is sectional drawing which shows the double row tapered roller bearing 121 in the case of the conventional large contact angle.

Explanation of symbols

  11 Double-row tapered roller bearing, 12a, 12b Inner ring, 13a, 13b Tapered roller, 14 Outer ring, 15a, 15b Pin, 16a, 16b Large-diameter side plate, 17a, 17b, 68 Small-diameter side plate, 18, 55, 60, 65 Inner ring spacer, 19, 56 Outer diameter part, 20, 57, 62, 67 Relief part, 30 Support base, 31 Swivel seat bearing, 32 Nacelle, 33 Casing, 34 Bearing housing, 35 Main shaft support bearing, 36 Main shaft, 37 Blade , 38 speed increaser, 39 generator, 40 motor for turning, 41 speed reducer, 69a, 69b cylindrical surface.

Claims (5)

An outer ring, left and right inner rings arranged so that the end surfaces on the small diameter side face each other, an inner ring spacer arranged between the left and right inner rings, and a plurality of tapered rollers arranged between the outer ring and the left and right inner rings, A double row tapered roller bearing comprising left and right cages for holding a plurality of tapered roller intervals in the left and right rows,
Each retainer includes a pin penetrating each tapered roller, a small-diameter side plate extending annularly while holding one end of a plurality of pins protruding to the small end surface side of each tapered roller, and a large end surface side of each tapered roller A large-diameter side plate that holds the other ends of the plurality of protruding pins and extends annularly,
The inner ring spacer is a double-row tapered roller bearing having a relief portion with reduced thickness in a region facing a minimum inner diameter portion of the small-diameter side plate. The double row tapered roller bearing according to claim 1, wherein an outer diameter of the escape portion is smaller than a minimum inner diameter of the small-diameter side plate. The double row tapered roller bearing according to claim 1 or 2, wherein a maximum outer diameter of the inner ring spacer is larger than a minimum inner diameter of the small-diameter side plate. The double-row tapered roller bearing according to claim 1, wherein a minimum inner diameter portion of the small-diameter side plate forms a cylindrical surface. 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 double-row tapered roller bearing that rotatably supports the main shaft,
The double-row tapered roller bearing is disposed between the outer ring, the left and right inner rings arranged so that the end surfaces on the small diameter side face each other, the inner ring spacer disposed between the left and right inner rings, and the outer ring and the left and right inner rings. A plurality of tapered rollers, and left and right cages that maintain the spacing between the plurality of tapered rollers in the left and right rows,
Each retainer includes a pin penetrating each tapered roller, a small-diameter side plate extending annularly while holding one end of a plurality of pins protruding to the small end surface side of each tapered roller, and a large end surface side of each tapered roller A large-diameter side plate that holds the other ends of the plurality of protruding pins and extends annularly,
The inner ring spacer is a main shaft support structure for a wind power generator, and has a relief portion with a reduced thickness in a region facing a minimum inner diameter portion of the small-diameter side plate.

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