JP2007162750A - Rolling bearing and spindle supporting structure of wind power generator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rolling bearing which allows an easy assembly of a spacer. <P>SOLUTION: A roll bearing is equipped with a plurality of rollers, double-row raceway rings arranged so as to face end surfaces respectively and an inner ring spacer 16 arranged between the double-row raceway rings. A fitting face of the inner ring spacer 16 is provided with tapered guide faces 23a, 23b toward the sides of width faces 22a, 22b. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a rolling bearing and a main shaft support structure for a wind power generator.

  A rolling bearing used for a main shaft of a wind power generator needs to receive a radial load against the weight of the blade, a thrust load against a wind force, and a moment load. Therefore, a large double-row tapered roller bearing that can receive a large radial load, thrust load, and moment load with a single rolling bearing is applied to the main shaft of the wind power generator. FIG. 7 is an example of a cross-sectional view of the double row tapered roller bearing 101. Referring to FIG. 7, double row tapered roller bearing 101 includes outer ring 102, double row inner rings 103a and 103b arranged so that small end faces 110a and 110b face each other, and outer ring 102 and double row inner rings 103a and 103b. Between the plurality of tapered rollers 104a and 104b, the pin type cages 105a and 105b holding the plurality of tapered rollers 104a and 104b, and the inner ring 103a and the inner ring 103b arranged in double rows, respectively. And an inner ring spacer 106.

  The double row tapered roller bearing 101 is fixed to a housing (not shown) located on the outer diameter side of the outer ring 102 and supports a rotating shaft 112 located on the inner diameter side of the inner rings 103a and 103b.

  The pin type cages 105a and 105b hold one ends of the pins 107a and 107b penetrating the tapered rollers 104a and 104b and a plurality of pins 107a and 107b protruding to the large end face side of the tapered rollers 104a and 104b. Large-diameter side plates 108a and 108b extending annularly, and small-diameter side plates 109a and 109b extending annularly while holding the other ends of the plurality of pins 107a and 107b projecting to the small end surfaces of the tapered rollers 104a and 104b. .

  The inner ring spacer 106 is disposed such that the width surfaces 111a and 111b on both sides thereof are in contact with the small end surfaces 110a and 110b of the inner rings 103a and 103b. The double row tapered rollers 104a and 104b and the pin type cages 105a and 105b are secured to each other by the inner ring spacer 106 and do not interfere with each other.

A double row tapered roller bearing including such an inner ring spacer 106 is disclosed in Japanese Patent Application Laid-Open No. 2003-49843 (Patent Document 1), and wind power generation using the double row tapered roller bearing as a main shaft support bearing is disclosed. A wind turbine for use is disclosed in Japanese Patent Laid-Open No. 2005-105917 (Patent Document 2).
Japanese Patent Laying-Open No. 2003-49843 (paragraph number 0009, FIG. 1) Japanese Patent Laying-Open No. 2005-105917 (paragraph numbers 0020 to 0039, FIG. 2)

  Here, a method for assembling the double row tapered roller bearing 101 will be briefly described. First, an inner ring assembly in which one inner ring 103a, tapered roller 104a, and pin type cage 105a are combined is attached to the rotating shaft 112. Next, the inner ring spacer 106 is assembled by fitting an opening provided in the inner ring spacer 106 into the rotating shaft 112. Thereafter, an inner ring assembly in which the outer ring 102 and the other inner ring 103b, the tapered roller 104b, and the pin type cage 105b are combined is assembled to assemble a double row tapered roller bearing.

  Here, when the opening hole of the inner ring spacer 106 is cylindrical, that is, when the inner diameter dimension of the opening hole is the same in the axial direction, the inner ring spacer 106 cannot be easily incorporated into the rotating shaft 112. .

  In particular, in a double-row tapered roller bearing that supports the main shaft of a wind power generator, the inner ring spacer 106 that is provided also has an inner diameter of about 2 m and is extremely large. Then, when the inner ring spacer 106 having a thickness of about 20 mm is incorporated, the inner ring spacer 106 is deformed or bent. As a result, installation becomes difficult and workability deteriorates. The same applies when the interference of the opening holes is small.

  An object of the present invention is to provide a rolling bearing that can easily incorporate a spacer.

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

  The rolling bearing according to the present invention includes a plurality of rollers, a double row raceway ring arranged so that the end faces face each other, and a spacer arranged between the double row raceway rings. Here, a tapered guide surface is provided on the fitting surface of the spacer.

  With this configuration, the inner diameter dimension of the width of the opening hole provided in the spacer is made larger than the minimum inner diameter dimension of the spacer, or the outer diameter dimension of the spacer width surface is set to the maximum outer diameter of the spacer. It can be made smaller than the diameter dimension. Then, when the spacer is incorporated into the rotary shaft or the housing, the radial dimension difference in the width surface of the spacer is large, so that the spacer can be easily incorporated using the guide surface. Moreover, since it is a taper-shaped guide surface, a spacer can be smoothly inserted to a fitting surface, and there is little possibility of damaging a rotating shaft, a housing, or a spacer.

  Preferably, the inner diameter of the spacer in the width direction is 0.7 mm or more larger than the minimum inner diameter of the spacer. If the inner diameter dimension of the width surface is too small, it becomes difficult to incorporate using the guide surface when the fitting surface and the outer diameter surface are greatly displaced. Therefore, a minimum difference in the radial dimension can be ensured by increasing the inner diameter dimension by 0.7 mm or more.

  More preferably, the angle of the tapered guide surface with respect to the bearing axis is less than 10 °. If the taper angle with respect to the bearing axis is increased more than necessary, the thickness of the spacer itself becomes thin, and as a result, it becomes difficult to ensure the rigidity of the spacer. By making the taper angle smaller than 10 °, the thickness of the spacer can be ensured and the minimum rigidity necessary for the spacer can be maintained.

  More preferably, the roller is a tapered roller. To receive thrust load, moment load and radial load at the same time, tapered roller bearings are applied. Here, in the rolling bearing configured as described above, if the roller is a tapered roller, the thrust load, moment load, and radial load described above can be simultaneously received, and the spacer can be easily incorporated to improve workability. To do.

  In another aspect of the present invention, the main shaft support structure of the wind power generator includes a blade that receives wind power, one end of which is fixed to the blade, the main shaft that rotates together with the blade, and a fixed member that can rotate the main shaft. And a rolling bearing to support. Here, the rolling bearing includes a plurality of rollers, a double row raceway ring arranged so that the end faces face each other, and a spacer arranged between the double row raceway rings, and a fitting surface of the spacer Is provided with a tapered guide surface.

  By comprising in this way, since the spindle support structure of the wind power generator which has the above-mentioned rolling bearing can incorporate a spacer easily, workability | operativity improves and productivity becomes favorable.

  According to the present invention, since the mating surface of the spacer is provided with the tapered guide surface, the inner diameter of the spacer in the width surface is made larger than the minimum inner diameter of the spacer, The outer diameter dimension in the width surface can be made smaller than the maximum outer diameter dimension of the spacer. Then, when the spacer is incorporated into the rotary shaft or the housing, the radial dimension difference in the width surface of the spacer is large, so that the spacer can be easily incorporated using the guide surface.

  Further, the main shaft support structure of a wind power generator having such a rolling bearing can be easily incorporated with a spacer, and therefore has high productivity.

  Embodiments of the present invention will be described below with reference to the drawings. FIG. 2 is a cross-sectional view showing a double row tapered roller bearing 11 when the rolling bearing according to one embodiment of the present invention is a double row tapered roller bearing. Referring to FIG. 2, double-row tapered roller bearing 11 includes outer ring 12, double-row inner rings 13a and 13b arranged such that small end surfaces 21a and 21b face each other as double-row races, outer ring 12 and inner ring 13a. , 13b, a plurality of tapered rollers 14a, 14b, pin-type cages 15a, 15b for holding the plurality of tapered rollers 14a, 14b, and an inner ring disposed between the inner ring 13a and the inner ring 13b. And a seat 16. The inner ring spacer 16 is disposed such that the width surfaces 22a and 22b on both sides thereof are in contact with the small end surfaces 21a and 21b of the inner rings 13a and 13b.

  The double row tapered roller bearing 11 is fixed to a housing (not shown) located on the outer diameter side of the outer ring 12 and supports the rotary shaft 20 located on the inner diameter side of the inner rings 13a and 13b.

  In addition, when pin type cages 15a and 15b are used as cages, a large number of tapered rollers 14a and 14b can be accommodated in the double-row tapered roller bearing 11, which is preferable when receiving a high load.

  The pin-type cages 15a and 15b are annular members that hold one ends of pins 17a and 17b penetrating the tapered rollers 14a and 14b and a plurality of pins 17a and 17b projecting to the small end surfaces of the tapered rollers 14a and 14b. Small-diameter side plates 19a and 19b, and annular large-diameter side plates 18a and 18b that hold the other ends of the plurality of pins 17a and 17b protruding toward the large end surfaces of the tapered rollers 14a and 14b. The small-diameter side plates 19a and 19b are disposed on the small collar side of the inner rings 13a and 13b, and have a smaller diameter than the large-diameter side plates 18a and 18b disposed on the large collar side.

  The small-diameter side plates 19a and 19b and the double-row tapered rollers 14a and 14b constituting the pin-type cages 15a and 15b are secured to each other by the inner ring spacer 16 and do not interfere with each other. The inner ring spacer 16 is required to have a minimum rigidity because pressure is applied from the inner rings 13a and 13b arranged on both sides when the inner ring spacer 16 is assembled.

  Next, the shape of the inner ring spacer 16 and the method for incorporating the inner ring spacer 16 will be described. FIG. 1 is an enlarged cross-sectional view showing a part of the inner ring spacer 16 among the parts indicated by I in FIG. FIG. 3 is a view showing a state in which the inner ring spacer 16 is incorporated into the rotary shaft 20. Referring to FIGS. 1 and 2, the inner ring spacer 16 is provided with an opening 26 for fitting the rotary shaft 20 into the opening. Tapered guide surfaces 23a and 23b are provided on the inner diameter surface of the opening hole 26, that is, the fitting surface that fits with the rotary shaft 20 disposed on the inner diameter side, toward the width surfaces 22a and 22b. By doing so, the inner diameter of the width surfaces 22a and 22b can be made larger than the inner diameter of the smallest inner diameter surface 24 having the smallest diameter among the inner diameter surfaces of the inner ring spacer 16. Further, by making the guide surfaces 23a and 23b tapered, the minimum inner diameter surface 24 and the guide surfaces 23a and 23b are smoothly connected.

  Next, a method of incorporating the inner ring spacer 16 into the rotating shaft 20 will be described with reference to FIG. The inner ring spacer 16 is provided with the opening hole 26 as described above. The inner ring spacer 16 is moved in the direction of arrow C in FIG. 3 and inserted into the opening 26 of the inner ring spacer 16 from the end face 28 side of the rotation shaft 20, so that the inner ring spacer 16 is incorporated into the rotation shaft 20. It is. Here, even if the minimum inner diameter surface 24 of the inner ring spacer 16 and the outer diameter surface 25 of the rotary shaft 20 are inserted at positions shifted by dotted lines in FIG. 3, a guide surface 23 a is provided on the fitting surface. Since the inner diameter dimension of the width surface 22a is large, it can be easily incorporated using the guide surface 23a. In this case, the width surfaces 22a and 22b of the inner ring spacer 16 and the end surface 28 of the rotating shaft 20 do not interfere with each other. Thereafter, when the inner ring spacer 16 is inserted into the rotating shaft 20, the tapered guide surface 23a and the minimum inner diameter surface 24 are smoothly connected to each other, so that the inner ring spacer 16 is smoothly assembled and rotated with the fitting surface of the inner ring spacer 16. The outer diameter surface 25 of the shaft 20 will fit properly.

  By doing so, the inner ring spacer 16 can be easily incorporated into the rotating shaft 20 without causing the inner ring spacer 16 and the rotating shaft 20 to interfere with each other.

  In this case, tapered guide surfaces 23a and 23b are provided toward the width surfaces 22a and 22b on both sides of the inner ring spacer 16 and may be inserted into the rotary shaft 20 from any direction. If the directionality of the inner ring spacer 16 to be inserted into is determined in advance, a tapered guide surface may be provided toward only one of the width surfaces in accordance with the direction. Further, a chamfered portion 27 may be provided at the corners of the outer diameter surface 29 and the guide surfaces 23a and 23b of the inner ring spacer 16 from the viewpoint of improving the handleability.

  Here, the difference between the inner diameter dimension of the minimum inner diameter surface 24 and the inner diameter dimension of the width surface 22a, which is indicated by a dimension twice the dimension A in FIG. 1, is 0.7 mm or more. If comprised in this way, the difference of the minimum radial direction dimension can be ensured. In this case, if the difference in the radial dimension is made larger than necessary, the thickness of the inner ring spacer 16 becomes thin, and the required rigidity cannot be ensured.

  Further, the minimum inner diameter surface 24 is parallel to the bearing axis, and when the taper angle of the guide surface 23a with respect to the bearing axis is B, the angle B is preferably smaller than 10 °. When the angle is 10 ° or more, the inner diameter dimension of the width surface 22a becomes larger than necessary, and the thickness of the inner ring spacer 16 becomes thin as described above, and the necessary rigidity may not be maintained. In the dimensional relationship of the double row tapered roller bearing 11 described above, the taper angle B is preferably 2 to 3 °.

  Further, in the above-described embodiment, the inner ring spacers disposed between the double rows of inner rings arranged so as to face each other have been described. However, the present invention is not limited to this, and the double rows arranged so as to face each other. The same applies to the outer ring spacer disposed between the outer rings.

  FIG. 4 is a cross-sectional view showing the double row tapered roller bearing in this case. Referring to FIG. 4, double row tapered roller bearing 31 includes double row outer rings 32a and 32b, inner ring 33, and double row outer ring 32a arranged such that end faces 40a and 40b face each other as double row races. , 32b and the inner ring 33 are arranged between the plurality of tapered rollers 34a and 34b, the pin type cages 35a and 35b holding the plurality of tapered rollers 34a and 34b, and the outer rings 32a and 32b. The outer ring spacer 36 is provided. The outer ring spacer 36 is disposed such that the width surfaces 41a and 41b on both sides thereof are in contact with the end surfaces 40a and 40b of the outer rings 32a and 32b.

  The double row tapered roller bearing 31 is fixed to the housing 37 positioned on the outer diameter side of the outer rings 32 a and 32 b and supports the rotating shaft 42 positioned on the inner diameter side of the inner ring 33.

  Here, tapered fitting surfaces 39a and 39b are provided on the fitting surface of the outer ring spacer 36 toward the width surfaces 41a and 41b. As a result, the outer diameter dimension of the width surfaces 41 a and 41 b of the outer ring spacer 36 is smaller than the outer diameter dimension of the largest outer diameter surface 38 having the largest diameter among the outer diameter surfaces of the outer ring spacer 36. Then, even when there is a slight shift when the outer ring spacer 36 is incorporated into the housing 37, it can be incorporated without interfering with the opening hole provided in the housing 37. In this case as well, a tapered guide surface may be provided toward one width surface of the outer ring spacer 36 in consideration of the insertion direction of the outer ring spacer 36 in the same manner as described above.

  5 and 6 show an example of the main shaft support structure of the wind power generator when the double row tapered roller bearing described above is applied as the main shaft support bearing 55. FIG. The casing 53 of the nacelle 52 that supports the main components of the main shaft support structure is installed on the support base 50 via a swivel bearing 51 at a high position so as to be horizontally rotatable. A main shaft 56 that fixes a blade 57 that receives wind power to one end is rotatably supported in a casing 53 of the nacelle 52 via a main shaft support bearing 55 incorporated in a bearing housing 54. Is connected to the speed increaser 58, and the output shaft of the speed increaser 58 is coupled to the rotor shaft of the generator 59. The nacelle 52 is turned at an arbitrary angle by the turning motor 60 via the speed reducer 61.

  The main shaft support bearing 55 incorporated in the bearing housing 54 is a rolling bearing according to an embodiment of the present invention, and includes a plurality of rollers, a double row raceway ring arranged so as to face end faces, and a double row And a spacer disposed between the race rings. Here, a tapered guide surface is provided on the fitting surface of the spacer. When the main shaft support bearing 55 is a double-row tapered roller bearing having such a configuration, the spacer can be easily incorporated into the main shaft 56. Such a main shaft support structure of a wind power generator has good productivity.

  In the above embodiment, the roller provided in the rolling bearing is held by the pin type cage. However, the present invention is not limited to this, and other cages such as a welded cage and a press cage are used. , May be held. Further, the roller is not limited to a tapered roller, and may be another roller such as a cylindrical roller.

  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.

  Since the rolling bearing according to the present invention can easily incorporate a spacer, it is effectively used for a rolling bearing that requires good workability.

  Since the main shaft support structure for a wind power generator according to the present invention has good productivity, it can be effectively used for the main shaft support structure for a large-scale wind power generator.

It is an expanded sectional view expanding and showing a part of inner ring spacer. It is sectional drawing which shows the double row tapered roller bearing which concerns on one Embodiment of this invention. It is a figure showing the state which incorporates an inner ring spacer to a rotating shaft. It is sectional drawing which shows the double row tapered roller bearing which concerns 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. 6 is a schematic side view of the main shaft support structure of the wind power generator shown in FIG. 5. It is sectional drawing which shows an example of the conventional double row tapered roller bearing.

Explanation of symbols

  11, 31 Double row tapered roller bearings, 12, 32a, 32b Outer ring, 13a, 13b, 33 Inner ring, 14a, 14b, 34a, 34b Conical roller, 15a, 15b, 35a, 35b Pin type cage, 16 Inner ring spacer, 17a, 17b Pin, 18a, 18b Large diameter side plate, 19a, 19b Small diameter side plate, 20, 42 Rotating shaft, 21a, 21b Small end surface, 22a, 22b, 41a, 41b Wide surface, 23a, 23b, 39a, 39b Guide surface , 24 Minimum inner surface, 25, 29 Outer surface, 26 Open hole, 27 Chamfered portion, 28, 40a, 40b End surface, 36 Outer ring spacer, 37 Housing, 38 Maximum outer surface, 50 Support base, 51 Swivel seat bearing , 52 nacelle, 53 casing, 54 bearing housing, 55 spindle support bearing, 56 spindle, 57 blade, 58 speed increaser, 9 generator, 60 swing motor, 61 speed reducer.

Claims (5)

With multiple times,
A double-row race ring arranged so that the end faces face each other;
A rolling bearing comprising a spacer disposed between the double row raceways,
A rolling bearing provided with a tapered guide surface on a fitting surface of the spacer. 2. The rolling bearing according to claim 1, wherein an inner diameter dimension of a width surface of the spacer is 0.7 mm or more larger than a minimum inner diameter dimension of the spacer. The rolling bearing according to claim 1, wherein an angle of the tapered guide surface with respect to the bearing axis is smaller than 10 °. The rolling bearing according to claim 1, wherein the roller is a tapered roller. A blade that receives wind,
One end of which is fixed to the blade and rotates with the blade;
A main shaft support structure of a wind power generator, which is incorporated in a fixed member and has a rolling bearing that rotatably supports the main shaft,
The rolling bearing includes a plurality of rollers, a double row raceway ring arranged to face end faces, and a spacer arranged between the double row raceway rings,
A main shaft support structure for a wind power generator, wherein a tapered guide surface is provided on a fitting surface of the spacer.

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