JP2007255569A - Tapered roller bearing, spacer, and spindle supporting structure of wind power generator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a tapered roller bearing capable of smoothly rolling rollers and having reduced the possibility of damage to a spacer. <P>SOLUTION: This tapered roller bearing comprises an outer ring, an inner ring, a plurality of tapered rollers 24a, 24b so disposed between the outer ring and the inner ring as to be arranged continuously with each other in the circumferential direction, and a spacer retainer having a plurality of resin spacers 11 which are arranged between the adjacent tapered rollers 24a, 24b and in which the intervals of the surfaces thereof in contact with the tapered rollers 24a, 24b adjacent to each other on a roller pitch circle diameter are gradually increased from the small diameter side end faces to the large diameter side end faces of the tapered rollers 24a, 24b. Inner diameter side guide surfaces 16a, 16b and outer diameter side guide surfaces 17a, 17b guiding the adjacent tapered rollers 24a, 24b are formed on the inner diameter side and the outer diameter side of both side-faces 12a, 12b of the spacer 11 more than the roller pitch circle diameter. The inner diameter side guide surfaces 16a, 16b or the outer diameter side guide surfaces 17a, 17b are brought into contact with the tapered rollers 24a, 24b on two lines. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a tapered roller bearing, a spacer, and a main shaft support structure for a wind power generator, and more particularly to a large tapered roller bearing, a spacer included therein, and a main shaft support structure for a large wind power generator.

  The roller bearing is generally composed of an outer ring, an inner ring, a plurality of rollers disposed between the outer ring and the inner ring, and a cage that holds the plurality of rollers. There are various types of cages for holding rollers, such as press cages, shaving cages, welded cages, and pin type 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 is divided, production and assembly are facilitated.

Here, in a ball bearing, a technique related to a split type spacer type cage in which the cage is divided is described in Japanese Utility Model Laid-Open No. 5-92537 (Patent Document 1).
Japanese Utility Model Publication No. 5-92537 (paragraph number 0007, FIG. 1)

  The spacers shown in Patent Document 1 are independent of each other and are not connected in the circumferential direction. Therefore, when the spacer is a raceway guide, the spacer is easily moved between the outer ring and the inner ring. In the direction, the position becomes unstable.

  Specifically, for example, when the roller bearing having the above-described configuration is used in a lateral orientation, when the spacer is in the top position, the spacer moves downward and the inner ring positioned at the lower portion. The inner ring is guided by the inner ring in contact with the outer diameter surface of the inner ring. On the other hand, when the spacer is at the ground position, the spacer moves downward and comes into contact with the inner diameter surface of the outer ring located at the lower portion to become an outer ring guide guided by the outer ring.

  In this way, if the spacer easily moves in the radial direction and becomes an inner ring guide or an outer ring guide depending on the position in the roller bearing, the radial position of the spacer becomes unstable, and the outer ring or inner ring becomes unstable. There is a risk that abnormal noise may be generated when the contact is made or the spacer is damaged.

  Here, if the spacer is a roller guide, it is possible to reduce the generation of noise due to contact with the outer ring and the inner ring and damage to the spacer.

  However, even when the spacer is a roller guide, if the corner of the spacer's guide surface comes into contact with the adjacent roller, the corner of the guide surface will be damaged or friction with the corner will occur. There is a risk that torque will increase or heat will be generated.

  This will be described with reference to FIG. FIG. 7 is an enlarged cross-sectional view when a pocket peripheral portion of the cage that holds the rollers is cut along a plane orthogonal to the axial direction. Referring to FIG. 7, guide surfaces 104 for guiding the rollers 102 are provided on the side wall surfaces on both sides of the pocket 103 of the cage 101. The guide surface 104 has an arcuate cross section, and the center of curvature is the same as the center of curvature Q1 of the roller 102. That is, the arc of the roller 102 and the arc of the guide surface 104 are formed concentrically. Further, the curvature radius T2 of the guide surface 104 is configured to be slightly larger than the curvature radius T1 of the roller 102.

  With such a configuration, for example, when the roller 102 starts to roll from the above-described top position or ground position, the roller 102 has a boundary portion between the guide surface 104 and the inner diameter surface 106a or the outer diameter surface 106b. Will come into contact with the corners 105a and 105b. If it does so, there exists a possibility that the corner | angular parts 105a and 105b may be damaged, or the corner | angular parts 105a and 105b may cause the increase in torque and heat_generation | fever by friction with 102.

  Here, as shown in FIG. 8, the curvature radius T4 of the guide surface 114 provided on the side wall surface of the pocket 113 of the cage 111 is made larger than the curvature radius T3 of the roller 112, and the arc of the guide surface 114 is formed. Even if the curvature center Q3 is set to a position different from the curvature center Q2 of the roller 112 on the PCD (Pitch Circle Diameter) 116, which is the position where the roller behavior is most stable, At the time of guidance, the corners 115a, 115b and 112 are brought into contact. Therefore, the corners 115a and 115b may be damaged, or the torque may increase due to friction with the corners 115a and 115b, or the heat generation may occur.

  An object of the present invention is to provide a tapered roller bearing capable of smoothly rolling a roller and reducing the risk of damage to a spacer.

  Another object of the present invention is to provide a spacer that can smoothly roll a roller and that is less likely to be damaged.

  Still another object of the present invention is to provide a main shaft support structure for a wind power generator that achieves a long service life.

  A tapered roller bearing according to the present invention is arranged between an outer ring, an inner ring, a plurality of tapered rollers arranged in a circumferential direction between the outer ring and the inner ring, and adjacent tapered rollers, and has a roller pitch circle diameter. Including a plurality of spacers in which the interval between the surfaces contacting the adjacent tapered rollers gradually increases from the small-diameter side end surface of the tapered roller toward the large-diameter side end surface, and the plurality of spacers are provided separately from each other And a spacer type retainer. Of the side surfaces on both sides of the spacer, an inner diameter side guide surface and an outer diameter side guide surface for guiding adjacent tapered rollers are provided on the inner diameter side and the outer diameter side from the roller pitch circle diameter. Here, the two tapered rollers adjacent to the inner diameter side guide surface or the outer diameter side guide surface are in contact with each other by two lines.

  With this configuration, the cage segment becomes a roller guide, and even if the spacer is about to move in the radial direction, the two adjacent tapered rollers and the inner diameter side guide surface, or the two adjacent tapered rollers and the outer diameter The side guide surface comes into contact with the two lines, and the movement of the spacer is restricted. If it does so, the corner | angular part of an inner diameter side and an outer diameter side guide surface and a tapered roller will not contact. That is, in the above-described state, even when the spacer is at the top position or the ground position, the tapered rollers adjacent to the corner portions of the inner diameter side and outer diameter side guide surfaces are in contact with each other at the start of rolling of the tapered rollers. Never do. Therefore, it is possible to prevent the corners of the inner diameter side and outer diameter side guide surfaces from being damaged, and increase in torque or heat generation due to friction between the corners and the tapered rollers. As a result, the tapered roller can be smoothly rolled, and the risk of damage to the spacer can be reduced.

  Here, the two lines are two lines or outer diameter side guide surfaces that form an inner diameter side guide surface among the side surfaces on both sides of the spacer when the spacer is cut along a plane orthogonal to the axial direction. And does not include a corner (edge) that is a portion where the guide surface intersects the outer diameter surface and inner diameter surface of the spacer.

  Preferably, the inner diameter side and outer diameter side guide surfaces have an arc shape in cross section, the radius of curvature of the arc is larger than the radius of curvature of the adjacent tapered rollers, and the center of curvature of the arc is larger than the roller pitch circle diameter. On the inner diameter side or outer diameter side. By configuring in this way, even if the guide surface is a curved surface having an arcuate cross section, the two tapered rollers adjacent to the inner diameter side or outer diameter side guide surface can be brought into contact with each other by two lines. Therefore, the tapered roller can be smoothly rolled, and the risk of damage to the spacer can be reduced.

  More preferably, when the radius of curvature of the arc is R1 and the radius of curvature of the tapered roller is R2, the relationship is 1.02R2 <R1 <1.15R2. By satisfying the dimensional relationship as described above, the spacer can be appropriately guided.

  Further, the inner diameter side and outer diameter side guide surfaces may be flat surfaces. Also by doing this, the two tapered rollers adjacent to the inner diameter side or outer diameter side guide surface can be brought into contact with each other by two lines.

  More preferably, a plane including a contact point at which the adjacent tapered roller contacts the inner or outer guide surface and a central axis of the adjacent tapered roller, and a central axis of the adjacent tapered roller in contact with the roller pitch circle diameter Assuming that the angle between the plane including the angle θ is θ °, the relationship is 40 ° <θ ° <70 °. By comprising in this way, a spacer can be guided appropriately. Specifically, the amount of movement of the spacer in the radial direction can be reduced by making θ ° larger than 40 °. Moreover, the amount of movement of the spacer in the circumferential direction can be reduced by making θ ° smaller than 70 °.

  More preferably, an oil reservoir is provided between the inner diameter side and outer diameter side guide surfaces provided on the same side surface. By comprising in this way, the lubricant hold | maintained at the oil sump can be supplied to a tapered roller, and a tapered roller can be rolled smoothly.

  In another aspect of the present invention, when the spacer is disposed between the adjacent tapered rollers, the distance between the surfaces contacting the adjacent tapered rollers in the roller pitch circle diameter is large from the small diameter side end surface of the tapered rollers. An inner diameter that guides adjacent tapered rollers on the inner diameter side and the outer diameter side of the roller pitch circle diameter, out of the side surfaces on both sides of the spacer, gradually increasing toward the radial end surface. A side guide surface and an outer diameter side guide surface are provided, and the inner diameter side guide surface or the two tapered rollers adjacent to the outer diameter side guide surface are in contact with each other through two lines.

  In such a spacer, the inner diameter side or outer diameter side guide surface and the two tapered rollers adjacent to each other are in contact with each other by two lines, so that the corner portion of the guide surface of the spacer and the tapered roller do not contact each other. . If it does so, a tapered roller can be rolled smoothly and damage to a spacer can be prevented.

  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 tapered roller bearing. The tapered roller bearing includes an outer ring, an inner ring, a plurality of tapered rollers arranged in a circumferential direction between the outer ring and the inner ring, and a tapered roller arranged between adjacent tapered rollers and adjacent in the roller pitch circle diameter. Including a plurality of spacers whose intervals between the surfaces abutting on the tapered rollers gradually increase from the small-diameter side end surface toward the large-diameter side end surface, and the plurality of spacers are provided separately from each other. A mold holder. Of the side surfaces on both sides of the spacer, an inner diameter side guide surface and an outer diameter side guide surface for guiding adjacent tapered rollers are provided on the inner diameter side and the outer diameter side from the roller pitch circle diameter. Here, the two tapered rollers adjacent to the inner diameter side guide surface or the outer diameter side guide surface are in contact with each other by two lines.

  Since the main shaft support structure of such a wind power generator includes a roller bearing that can smoothly roll the tapered roller and has a reduced risk of damage to the spacer, a long life can be realized. .

  According to this invention, the cage segment serves as a roller guide, and even if the spacer tries to move in the radial direction, the two adjacent tapered rollers and the inner diameter side guide surface, or the two adjacent tapered rollers and the outer diameter side guide. The surface contacts the two lines, and the movement of the spacer is restricted. If it does so, the corner | angular part of an inner diameter side and an outer diameter side guide surface and a tapered roller will not contact. That is, in the above-described state, even when the spacer is at the top position or the ground position, the tapered rollers adjacent to the corner portions of the inner diameter side and outer diameter side guide surfaces are in contact with each other at the start of rolling of the tapered rollers. Never do. Therefore, it is possible to prevent the corners of the inner diameter side and outer diameter side guide surfaces from being damaged, and increase in torque or heat generation due to friction between the corners and the tapered rollers. As a result, the tapered roller can be smoothly rolled, and the risk of damage to the spacer can be reduced.

  In addition, since the spacer on the inner diameter side or the outer diameter side of the spacer comes into contact with two adjacent tapered rollers through two lines, the corner of the guide surface of the spacer contacts the tapered roller. There is no. If it does so, a tapered roller can be rolled smoothly and damage to a spacer can be prevented.

  In addition, such a main shaft support structure of a wind power generator includes a roller bearing that can smoothly roll a tapered roller and has a reduced risk of damage to the spacer, thereby realizing a long service life. Can do.

  Embodiments of the present invention will be described below with reference to the drawings. FIG. 2 is a perspective view showing the spacer 11 included in the spacer type holder according to the embodiment of the present invention. Referring to FIG. 2, spacer 11 is disposed between adjacent tapered rollers such that outer diameter surface 14a faces the outer ring and inner diameter surface 14b faces the inner ring.

  The small-diameter side end surface 13a and the large-diameter side end surface 13b of the spacer 11 have a small-diameter side protrusion 15a and a large-diameter side that respectively contact the small end surface and large end surface of the tapered roller when arranged between adjacent tapered rollers. A protruding portion 15b is provided. By comprising in this way, the small diameter side protrusion part 15a and the large diameter side protrusion part 15b are made to contact | abut to the small end surface and large end surface of an adjacent tapered roller, and the axial movement of the spacer 11 is controlled. Can do.

  The spacer 11 includes side surfaces 12a and 12b having curved surfaces along the rolling surfaces of the tapered rollers. When arranged between adjacent tapered rollers, the circumferential distance between the side surface 12a and the side surface 12b, which is a surface that contacts the adjacent tapered rollers in the roller pitch circle diameter, is from the small diameter side end surface 13a to the large diameter side end surface. It gradually increases toward 13b. By doing so, when the spacer 11 is disposed between the adjacent tapered rollers, the spacer 11 can be disposed along the rolling surface of the tapered roller. The distance in the length direction can be kept constant.

  Here, an inner diameter side guide surface 16a having a circular cross section is provided on the inner diameter side of the one side surface 12a of the spacer 11 with respect to the PCD. Further, an outer diameter side guide surface 17a having a circular arc cross section is provided on the outer diameter side of the PCD. Similarly, of the other side surface 12b of the spacer 11, an inner diameter side guide surface 16b is provided on the inner diameter side of the PCD, and an outer diameter side guide surface 17b is provided on the outer diameter side. The configuration of the inner diameter side guide surfaces 16a and 16b and the outer diameter side guide surfaces 17a and 17b will be described later.

  FIG. 3 is a cross-sectional view of the tapered roller bearing 21 including the spacer type cage including the spacer 11 shown in FIG. 2 when cut along a plane passing through the center of the spacer 11 and orthogonal to the circumferential direction. is there. FIG. 1 shows a tapered roller 24a included in a tapered roller bearing 21, a tapered roller 24b, and a spacer 11 disposed therebetween, passing through the center of the spacer 11 and perpendicular to the central axis direction of the tapered roller 24a. It is sectional drawing at the time of cut | disconnecting by the plane to do. From the viewpoint of easy understanding, FIG. 1 does not show the small-diameter side protrusion 15a and the large-diameter side protrusion 15b.

  1, 2 and 3, tapered roller bearing 21 includes an outer ring 22, an inner ring 23, a plurality of tapered rollers 24 a and 24 b disposed between outer ring 22 and inner ring 23, and an adjacent cone. A plurality of spacers 11 disposed between the rollers 24a and 24b are included, and a plurality of spacers 11 are provided separately from each other.

  Here, the radius of curvature R1 of the arc constituting the inner diameter side guide surface 16a of the spacer 11 is configured to be larger than the radius of curvature R2 of the tapered roller 24a in the cross section. Further, the curvature center P is configured to be located on the outer diameter side of the PCD 18. Similarly, the radius of curvature of the arc constituting the inner diameter side guide surface 16b of the spacer 11 is also configured to be larger than the radius of curvature R2 of the tapered roller 24a in the cross section. The center of curvature is also located on the outer diameter side of the PCD 18. Further, the outer diameter side guide surfaces 17a and 17b also have a radius of curvature larger than the radius of curvature R2 of the tapered roller 24a, and the center of curvature is located on the inner diameter side of the PCD 18.

  That is, the cross section of the two inner diameter side guide surfaces 16a and 16b and the two outer diameter side guide surfaces 17a and 17b provided on the side surfaces 12a and 12b on both sides of the spacer 11 is composed of a total of four arcs. ing. Here, from the viewpoint of easy understanding, the radius of curvature of the inner diameter side guide surfaces 16a and 16b and the outer diameter side guide surfaces 17a and 17b is set to the same R1.

  The spacer 11 is restricted from moving toward the outer diameter side of the spacer 11, that is, in the direction of arrow A in FIG. 1, by the inner diameter side guide surfaces 16a and 16b. Further, movement of the spacer 11 toward the inner diameter side, that is, movement in the direction indicated by the arrow B in FIG. 1 is restricted by the outer diameter side guide surfaces 17a and 17b. Thereby, the spacer 11 becomes roller guidance. That is, the spacer 11 is guided by the adjacent tapered rollers 24a and 24b.

  Here, in the spacer 11, the inner side guide surfaces 16a and 16b and the two tapered rollers 24a and 24b adjacent to each other are in contact with each other through two lines. That is, when the spacer 11 moves to the outer diameter side, the two lines indicating the inner diameter side guide surfaces 16a and 16b and the two tapered rollers 24a and 24b come into contact with each other. Then, when the spacer 11 moves to the outer diameter side, the corner portions 19a and 19b, which are the portions where the inner diameter side guide surfaces 16a and 16b intersect the inner diameter surface 14b, and the tapered rollers 24a and 24b are in contact with each other. Absent. Similarly, when the spacer 11 moves to the inner diameter side, the two lines indicating the outer diameter side guide surfaces 17a and 17b and the two tapered rollers 24a and 24b come into contact with each other. Then, when the spacer 11 moves to the inner diameter side, the corner portions 20a and 20b, which are portions where the outer diameter side guide surfaces 17a and 17b intersect the outer diameter surface 14a, and the tapered rollers 24a and 24b come into contact with each other. There is no. That is, when the spacer 11 moves to the inner diameter side or the outer diameter side, the tapered rollers 24a and 24b do not come into contact with the corner portions 19a, 19b, 20a, and 20b.

  Therefore, no load is applied to the corners 19a, 19b, 20a, 20b from the tapered rollers 24a, 24b, and the corners 19a, 19b, 20a, 20b can be prevented from being damaged. Further, it is possible to prevent an increase in torque, heat generation, and the like due to friction between the corner portions 19a, 19b, 20a, and 20b and the tapered rollers 24a and 24b.

  In this case, the relationship between R1 and R2 is preferably 1.02R2 <R1 <1.15R2. By comprising in this way, the spacer 11 can be used as roller guidance appropriately.

  Further, when the spacer 11 moves to the outer diameter side, a contact point where the tapered roller 24a comes into contact with the inner diameter side guide surface 16a is defined as S, and a plane 29a including S and the central axis of the tapered roller 24a, and the PCD 18 If the angle between the contact surface and the plane 29b including the central axis of the tapered roller 24a is θ °, it is preferable that the relationship be 40 ° <θ ° <70 °.

  By doing so, the spacer 11 can be guided appropriately. When the spacer 11 is arranged in the circumferential direction, a guide gap that allows slight movement in the radial direction and the circumferential direction of the spacer 11 is provided. Specifically, θ ° is more than 40 °. By enlarging, the amount of movement of the spacer 11 in the radial direction can be reduced in the guide gap. Further, by making θ ° smaller than 70 °, the amount of movement of the spacer 11 in the circumferential direction can be reduced in the guide gap. Also, the inner diameter side guide surface 16b and the outer diameter side guide surfaces 17a and 17b are preferably configured to have the same relationship.

  Here, between the inner diameter side guide surface 16a and the outer diameter side guide surface 17a provided on the same side surfaces 12a and 12b, between the inner diameter side guide surface 16b and the outer diameter side guide surface 17b, a so-called inner diameter side guide surface 16a and outer diameter are provided. An oil sump 30 is provided at a joint portion between the side guide surface 17a and a joint portion between the inner diameter side guide surface 16b and the outer diameter side guide surface 17b.

  By comprising in this way, a lubricant can be hold | maintained at the oil sump 30 located in the joint part of inner diameter side guide surface 16a, 16b and outer diameter side guide surface 17a, 17b. Then, the lubricant can be supplied from the oil reservoir 30 to two adjacent tapered rollers 24a and 24b, and the tapered rollers 24a and 24b can be smoothly rolled. In addition, since such a joint part does not contact the tapered rollers 24a and 24b and does not require strength, for example, an oil sump 30 recessed in a groove shape in the circumferential direction is provided, and more lubricant is provided. May be held. Further, the oil reservoir 30 may be provided so as to connect the inner diameter side guide surfaces 16a and 16b and the outer diameter side guide surfaces 17a and 17b with a smooth cross-section R shape.

  In the above embodiment, the inner diameter side and outer diameter side guide surfaces are configured such that the cross sections thereof are arcuate, but the present invention is not limited to this, and may be flat. FIG. 4 is a sectional view showing a part of the tapered roller bearing in this case, and corresponds to FIG. Referring to FIG. 4, the inner diameter side and outer diameter side guide surfaces 44 a, 44 b, 45 a, and 45 b provided on the side surfaces on both sides of the spacer 41 are each formed of a flat surface.

  Also with this configuration, the inner diameter side or outer diameter side guide surfaces 44a, 44b, 45a, 45b and the two tapered rollers 42a, 42b adjacent to each other are in contact with two lines. Therefore, the corners 46a, 46b, 47a, 47b on the inner diameter side and the outer diameter side do not come into contact with the tapered rollers 42a, 42b, and the corners 46a, 46b, 47a, 47b can be prevented from being damaged. . Similarly to the above, an oil reservoir 48 may be provided between the inner diameter side and outer diameter side guide surfaces 44a, 44b, 45a, 45b provided on the same side surface. Also in this case, as described above, a contact point where the tapered roller 42a contacts the inner diameter side guide surface 44a is defined as S ′, a plane 49a including S ′ and the central axis of the tapered roller 42a, and the PCD 43, If the angle between the tapered roller 42a and the plane 49b including the central axis is θ ′ °, it is preferable that 40 ° <θ ′ ° <70 °. The other inner diameter side guide surface 44b and the outer diameter side guide surfaces 45a and 45b are preferably configured to have the same relationship.

  In the above embodiment, the inner diameter side and the outer diameter side guide surface provided on the side surface of the spacer are each configured with one radius of curvature and one center of curvature. However, the present invention is not limited to this, and a plurality of arcs may be used. Moreover, you may include a curved surface and a plane.

  5 and 6 show an example of a main shaft support structure of a wind power generator to which a tapered roller bearing according to an embodiment of the present invention is applied as a main shaft support bearing 75. FIG. The casing 73 of the nacelle 72 that supports the main components of the main shaft support structure is installed on the support base 70 via a swivel bearing 71 at a high position so as to be horizontally rotatable. A main shaft 76 that fixes a blade 77 that receives wind power to one end is rotatably supported in a casing 73 of the nacelle 72 via a main shaft support bearing 75 incorporated in a bearing housing 74. Is connected to a speed increaser 78, and the output shaft of the speed increaser 78 is coupled to the rotor shaft of the generator 79. The nacelle 72 is turned at an arbitrary angle by the turning motor 80 via the speed reducer 81.

  The main shaft support bearing 75 incorporated in the bearing housing 74 is a tapered roller bearing according to an embodiment of the present invention, and includes a plurality of outer ring, inner ring, outer ring and inner ring arranged in a circumferential direction. The interval between the surfaces of the tapered rollers and the adjacent tapered rollers that are in contact with the adjacent tapered rollers in the roller pitch circle diameter gradually increases from the small-diameter side end surface to the large-diameter side end surface. A spacer type retainer including a plurality of spacers, the spacers being provided separately from each other. Of the side surfaces on both sides of the spacer, an inner diameter side guide surface and an outer diameter side guide surface for guiding adjacent tapered rollers are provided on the inner diameter side and the outer diameter side from the roller pitch circle diameter. Here, the inner diameter side guide surface or the outer diameter side guide surface and the tapered roller are in contact with each other by two lines.

  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. Here, when the cage for holding the tapered roller is of a split type and configured as described above, the tapered roller can be smoothly rolled, and damage to the spacer can be prevented. Then, the main shaft support structure of the wind power generator can achieve a long life.

  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 tapered roller bearing according to the present invention can smoothly roll the tapered roller and can prevent the spacer from being damaged. Therefore, the tapered roller bearing is effectively used for a tapered roller bearing that requires a long life. The

  Further, the spacer according to the present invention can smoothly roll the tapered roller and can prevent the spacer from being damaged. Therefore, the spacer included in the tapered roller bearing that requires a long life. It is used effectively.

  Further, the main shaft support structure of a wind power generator according to the present invention is effectively used for the main shaft support structure of a wind power generator that requires a long life.

It is an expanded sectional view of the spacer provided in the tapered roller bearing and arrange | positioned between two adjacent tapered rollers. It is a perspective view of the spacer contained in the tapered roller bearing which concerns on one Embodiment of this invention. It is sectional drawing which shows the tapered roller bearing which concerns on one Embodiment of this invention. It is an expanded sectional view which shows 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. 6 is a schematic side view of the main shaft support structure of the wind power generator shown in FIG. 5. It is an expanded sectional view which shows the pocket periphery of the conventional holder | retainer, and the circular arc of a guide surface is a thing concentric with the circular arc of a roller. It is an expanded sectional view which shows the pocket periphery of the conventional holder | retainer, and the center of curvature of the circular arc which comprises a guide surface exists on PCD.

Explanation of symbols

  11, 41 spacer, 12a, 12b side surface, 13a small diameter side end surface, 13b large diameter side end surface, 14a outer diameter surface, 14b inner diameter surface, 15a small diameter side protruding portion, 15b large diameter side protruding portion, 16a, 16b, 44a, 44b inner diameter side guide surface, 17a, 17b, 45a, 45b outer diameter side guide surface, 18, 43 PCD, 19a, 19b, 20a, 20b, 46a, 46b, 47a, 47b corner, 21 tapered roller bearing, 22 outer ring, 23 Inner ring, 24a, 24b, 42a, 42b Tapered roller, 29a, 29b, 49a, 49b Planar, 30, 48 Oil reservoir, 70 Support base, 71 Swivel seat bearing, 72 Nacelle, 73 Casing, 74 Bearing housing, 75 Main shaft support Bearing, 76 spindle, 77 blade, 78 speed increaser, 79 generator, 80 turning motor, 81 speed reducer.

Claims (8)

Outer ring,
Inner ring,
A plurality of tapered rollers arranged in a circumferential direction between the outer ring and the inner ring;
A plurality of tapered rollers arranged between adjacent tapered rollers and having a roller pitch circle diameter in which the interval between the surfaces in contact with the adjacent tapered rollers gradually increases from the small diameter side end surface to the large diameter side end surface of the tapered roller. A tapered roller bearing including a spacer, and a plurality of spacers provided separately from each other.
Of the side surfaces on both sides of the spacer, an inner diameter side guide surface and an outer diameter side guide surface for guiding the adjacent tapered rollers are provided on the inner diameter side and the outer diameter side from the roller pitch circle diameter,
A tapered roller bearing in which two tapered rollers adjacent to the inner diameter side guide surface or the outer diameter side guide surface are in contact with two lines. The inner diameter side and the outer diameter side guide surface has a circular arc cross section,
The radius of curvature of the arc is larger than the radius of curvature of the adjacent tapered rollers,
The tapered roller bearing according to claim 1, wherein the center of curvature of the arc is on the inner diameter side or the outer diameter side with respect to the roller pitch circle diameter. When the radius of curvature of the arc is R1, and the radius of curvature of the tapered roller is R2,
The tapered roller bearing according to claim 2, having a relationship of 1.02R2 <R1 <1.15R2. The tapered roller bearing according to claim 1, wherein the inner diameter side and outer diameter side guide surfaces are flat surfaces. A plane including a contact point at which the adjacent tapered roller contacts the inner diameter side or outer diameter side guide surface and a central axis of the adjacent tapered roller, and a central axis of the adjacent tapered roller in contact with the roller pitch circle diameter If the angle between the plane including the angle is θ °,
The tapered roller bearing according to any one of claims 1 to 4, having a relationship of 40 ° <θ ° <70 °. The tapered roller bearing according to claim 1, wherein an oil reservoir is provided between the inner diameter side and outer diameter side guide surfaces provided on the same side surface. When arranged between the adjacent tapered rollers, the distance between the surfaces of the tapered rollers that contact the adjacent tapered rollers in the circle pitch diameter gradually increases from the small diameter side end surface to the large diameter side end surface of the tapered rollers. A space
Of the side surfaces on both sides of the spacer, on the inner diameter side and the outer diameter side from the roller pitch circle diameter, an inner diameter side guide surface and an outer diameter side guide surface for guiding the adjacent tapered rollers are provided,
A spacer, which is in contact with two tapered rollers adjacent to the inner diameter side guide surface or the outer diameter side guide surface with two lines. A blade that receives wind,
One end of which is fixed to the blade and rotates with the blade;
A main shaft support structure for a wind power generator, which is incorporated in a fixed member and has a tapered roller bearing that rotatably supports the main shaft,
The tapered roller bearing is disposed between an outer ring, an inner ring, a plurality of tapered rollers arranged in a circumferential direction between the outer ring and the inner ring, and the adjacent tapered rollers, and has a roller pitch circle diameter. A plurality of spacers in which the interval between the surfaces contacting the adjacent tapered rollers gradually increases from the small-diameter side end surface of the tapered roller toward the large-diameter side end surface; It is provided with a spacer type retainer provided,
Of the side surfaces on both sides of the spacer, an inner diameter side guide surface and an outer diameter side guide surface for guiding the adjacent tapered rollers are provided on the inner diameter side and the outer diameter side from the roller pitch circle diameter,
A main shaft support structure of a wind power generator, in which the inner tapered surface or the two tapered rollers adjacent to the outer guiding surface are in contact with each other through two lines.

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