JP2008064244A - Spindle supporting structure for wind power generator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a spindle supporting structure for a wind power generator adopting a tapered roller bearing having further increased load capacity and capable of supporting load by the whole bearing. <P>SOLUTION: The wind power generator 11 is provided with blades 15 for receiving wind, a spindle 16 having one end fixed to the blades 15 and rotated together with the blades 15 and the tapered roller bearing 31 for rotatably supporting the spindle 16. In particular, the tapered roller bearing 31 is provided with an inner ring and outer ring with rolling surfaces and a plurality of tapered rollers with rolling surfaces contacting with a raceway surface. The bearing is a full complement roller bearing wherein the adjacent tapered rollers are positioned to contact with each other. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

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

  A conventional wind power generator is described in, for example, Japanese Patent Application Laid-Open No. 2005-207517 (Patent Document 1). The wind power generator described in the publication is rotated by a support base, a nacelle for storing main components arranged on the support base in a horizontally swingable manner via a swivel bearing, and a bearing fixed to the bearing housing. A main shaft freely supported, a blade on one end side of the main shaft, and a speed increaser and a generator on the other end side of the main shaft are provided.

In the wind power generator configured as described above, the main shaft rotates along with the blades that rotate by receiving wind, the rotation of the main shaft is increased by the speed increaser, and the electric power is converted by the generator. The main shaft of the wind power generator receives a radial load and a moment load caused by the weight of the blade in addition to an axial load caused by the blade receiving wind. For this reason, a self-aligning roller bearing or a tapered roller bearing that can be used in an environment in which a radial load, an axial load, and a moment load are simultaneously applied is used as a bearing that supports the main shaft.
JP 2005-207517 A

  In recent years, efforts have been made to improve power generation efficiency, such as increasing the size of blades and installing wind power generators in windier locations, and as a result, the load applied to the bearing that supports the main shaft is also increased. It is getting bigger. Therefore, further improvement in load capacity is required for a spindle support bearing that requires a long life and high reliability.

  In addition, since a load that is biased in a predetermined direction acts on the main shaft of the wind power generator, an area in which the load is applied (hereinafter referred to as “load area”) and a load are not applied in the circumferential direction. It is divided into areas (hereinafter referred to as “non-load areas”). Therefore, the bearing that supports the main shaft supports the load only with the rollers located in the load region. Therefore, the load that can be actually supported by the bearing used in such an environment is only a part of the load that can be supported by the entire bearing.

  Accordingly, an object of the present invention is to provide a main shaft support structure for a wind power generator that employs a tapered roller bearing that further increases the load capacity and that can support the load with the entire bearing. is there.

  A main shaft support structure for a wind power generator according to the present invention includes a blade for receiving wind, a main shaft whose one end is fixed to the blade and rotates together with the blade, and a tapered roller bearing that rotatably supports the main shaft. This is a spindle support structure. When paying attention to the tapered roller bearing, it includes an inner ring and an outer ring having raceway surfaces, and a plurality of tapered rollers having rolling surfaces in contact with the raceway surfaces. The tapered roller bearing is a full-roller type bearing that is disposed at a position where adjacent tapered rollers can contact each other.

  By adopting a full roller type tapered roller bearing as a bearing that supports the main shaft of the wind power generator as in the above configuration, the number of tapered rollers that can be accommodated compared to a tapered roller bearing of the same size having a cage Can be increased. As a result, the load capacity of the entire bearing increases.

  Preferably, the angle θ (contact angle) formed by the bearing rotation center line of the tapered roller bearing and the raceway surface of the outer ring satisfies θ ≧ 40 °. Bearings that support the main shaft of the wind power generator are loaded with not only radial loads but also thrust loads and moment loads.To properly support these loads, the contact angle θ should be within the above range. It is desirable to do.

  Preferably, when the roller diameter at an arbitrary position of the rolling surface of the tapered roller is D, and the distance between the raceway surfaces of the inner ring and the outer ring at the measurement position of the tapered roller is d, the rolling surface of each of the tapered rollers. Satisfies D> d at at least one point.

  As in the above configuration, by reducing the distance d between the raceway surfaces from the roller diameter D at any position in the circumferential direction of the tapered roller bearing (hereinafter, this relationship is referred to as “negative gap”), all the tapered rollers are provided. A load is applied to the inner and outer rings. Thereby, the main shaft support structure of a wind power generator with a long life and high reliability can be obtained. Furthermore, since the distance between the raceway surfaces is set as a negative gap, it is possible to prevent the tapered rollers from slipping and the like, so that it is possible to prevent rotation failure due to interference between adjacent tapered rollers.

As one embodiment, crowning is formed on the rolling surface of the tapered roller, the roller diameter at the top of the crowning of the tapered roller is D ₁ , and the distance between the raceway surfaces at the position corresponding to the top of the crowning of the tapered roller is d. When _1, in all of the tapered _rollers, satisfy D 1> _{d 1.}

  As another embodiment, D> d is satisfied in the entire rolling surface of all the tapered rollers.

When using tapered rollers with a crowning formed on the rolling surface, since all the tapered rollers support the load only at the top of the crowning at a light load, D ₁ > d ₁ is satisfied. On the other hand, since the tapered roller is elastically deformed under heavy load and supports the load on the entire rolling surface, D> d is established over the entire rolling surface of all the tapered rollers.

  According to the present invention, the use of the full roller type tapered roller bearing as the bearing for supporting the main shaft of the wind power generator increases the load capacity as compared with a tapered roller bearing of the same size having a cage. In addition, since the load can be supported by all the rollers at all times by setting the distance between the raceway surfaces to be a negative gap, a long-life and highly reliable main shaft support structure for a wind power generator can be obtained.

  With reference to FIGS. 1-7, the wind generator 11, the tapered roller bearing 31, and the method of incorporating the tapered roller bearing 31 which employ | adopted the main shaft support structure which concerns on one Embodiment of this invention are demonstrated in the main shaft 16. FIG. 1 and 2 are diagrams showing the internal structure of the wind power generator 11, FIGS. 3 and 4 are diagrams showing a tapered roller bearing 31 that supports the main shaft 16 of the wind power generator 11, and FIGS. 5 to 7 are cones. FIG. 3 is a view showing a method for incorporating the roller bearing 31 into the main shaft 16.

  First, referring to FIGS. 1 and 2, the wind power generator 11 includes a support 12, a swivel bearing 13, a nacelle 14, a blade 15, a main shaft 16, a speed increaser 17, and a generator 18. And a bearing housing 19, a tapered roller bearing 31 as a spindle support bearing, a turning motor 20, and a speed reducer 21.

  The nacelle 14 is installed on the support 12 via a swivel bearing 13 and can be swiveled horizontally by a turning motor 20 and a speed reducer 21. Moreover, it functions as a housing that accommodates the main shaft 16, the speed increaser 17, the power generator 19, the tapered roller bearing 31, the turning motor 20, the speed reducer 21, and the like, which are main components of the wind power generator 11.

  The blade 15 is fixed to one end of the main shaft 16 and receives wind to rotate. One end of the main shaft 16 is connected to the blade 15 and the other end is connected to the speed increaser 17, and the rotation of the blade 15 is transmitted to the generator 18 via the speed increaser 17. Further, it is rotatably supported by a tapered roller bearing 31 incorporated in the bearing housing 19.

  A large axial load is applied to the tapered roller bearing 31 by wind force received by the blade 15, and a large radial load and a large moment load are applied by the weight of the blade 15 and the like. Therefore, as main shaft support bearings used in such an environment, as shown in FIG. 3, an inner ring 32 including left and right inner ring members 32a and 32b, an outer ring 33, a plurality of tapered rollers 34, and an inner ring spacer. A tapered roller bearing 31 having 35 is employed.

  The inner ring member 32a has a raceway surface 36a on the outer diameter surface, a small collar 37a on one end of the raceway surface 36a, a large collar 38a on the other end, and a plurality of axially extending end faces on the large collar 38a side. Bolt holes 39a. The inner ring member 32b has the same configuration. The inner ring members 32a and 32b constitute the inner ring 32 by arranging the small collars 37a and 37b facing each other with the inner ring spacer 35 interposed therebetween. The outer ring 33 has double-row raceway surfaces 33a and 33b corresponding to the raceway surfaces 36a and 36b of the inner ring members 32a and 32b, and a plurality of through holes 33c penetrating in the axial direction.

  Referring to FIG. 4, the tapered roller 34 has a small end surface 34a, a large end surface 34b, and a rolling surface 34c. The small end surface 34a faces the small collars 37a, 37b of the inner ring members 32a, 32b. Arranged between the inner ring 32 and the outer ring 33. Further, a crowning is formed on the rolling surface 34c, and the top thereof is located at the center of the roller length. The “rolling surface” is the length of the portion excluding the chamfered portions at both ends, and is a surface that can come into contact with the raceway surfaces 36a, 36b, 33a, 33b of the inner ring 32 and the outer ring 33 when incorporated in the bearing. Point to.

  The tapered roller bearing 31 having the above-described configuration is a back combination bearing in which the tapered rollers 34 are arranged in a double row in the axial direction and the small end surfaces 34a of the tapered rollers 34 in the left and right rows are butted together. Moreover, in each raceway surface, it is a full roller type bearing arrange | positioned in the position where the adjacent tapered rollers 34 can mutually contact.

  Further, when the roller diameter at an arbitrary position of the rolling surface 34c of the tapered roller 34 is D and the distance between the raceway surfaces of the inner ring 32 and the outer ring 33 at the measurement position of the roller diameter of the tapered roller 34 is d, all the tapered rollers 34 are provided. At least one location on each track surface 34c satisfies D> d. That is, the distance between the raceway surfaces is a negative gap.

Specifically, when the load applied to the tapered roller bearing 31 is small (light load), the raceway surfaces 36a and 33a and the rolling surface 34c are in contact only at the top of the crowning. That is, a negative clearance (D ₁ > d ₁ ) is obtained only at the top of the crowning of all the tapered rollers 34. Incidentally, d ₁ refers to the raceway surface distance between the position corresponding to the top of the crowning.

  On the other hand, when the load applied to the tapered roller bearing 31 is large (at the time of heavy load), the rolling surface 34c of the tapered roller 34 is elastically deformed, and the contact area between the raceway surfaces 36a and 33a and the rolling surface 34c increases. To do. When the entire area of the rolling surface 34c comes into contact with the raceway surfaces 36a and 33a, a negative gap (D> d) is formed in the entire area of the rolling surface 34c of all the tapered rollers 34.

  By using the full roller type tapered roller bearing 31 as in the above configuration, the number of tapered rollers 34 that can be accommodated is increased compared to a tapered roller bearing of the same size including a cage. As a result, the load capacity of the entire bearing can be increased. Further, by setting the distance between the raceway surfaces as a negative gap, a load is applied to all the tapered rollers 34 via the inner and outer rings 32 and 33. As a result, even when used in an environment including a load area and a non-load area, a large load can be supported and the rigidity of the tapered roller bearing 31 is improved.

  Further, since the rotation directions at the contact positions of the adjacent tapered rollers 34 are opposite to each other, in the full roller type tapered roller bearing 31, rotation failure due to interference of the adjacent tapered rollers 34 becomes a problem. However, by making the distance between the raceway surfaces a negative gap, it is possible to prevent the side rollers of the tapered rollers 34 from slipping or the like, so that rotation failure due to interference between adjacent tapered rollers 34 is suppressed. As a result, the rotation and revolution of the tapered roller 34 become smooth.

  By using the tapered roller bearing 31 configured as described above as a bearing for supporting the main shaft 16 of the wind power generator 11, a long-life and highly reliable main shaft support structure of the wind power generator can be obtained.

  In addition, although the tapered roller 34 in the said embodiment showed the example in which the top of crowning is located in the center of the roller length of the tapered roller 34, it is not restricted to this but can be set to arbitrary positions. Moreover, although the example in which the crowning is formed on the rolling surface 34c has been shown, the present invention can also be applied to a tapered roller bearing that employs a tapered roller in which no crowning is formed.

  Moreover, although the tapered roller bearing 31 in the said embodiment showed the example of a double row, it may not be restricted to this, A single row may be sufficient, and even if it is a multi-row bearing with three or more rows of raceway surfaces. Good. Moreover, although the example of the back roller combination was shown for the tapered roller bearing 31, it is not restricted to this, The front combination bearing which faced | matched the large end surfaces 34b of the tapered roller 34 may be sufficient.

When the rear combination includes a rotation center line l ₀ of the bearing, the intersection of the contact line l _1, l ₂ of the left and right rows of the tapered rollers 34 and the inner and outer rings 32, 33 alpha, the distance between the beta (hereinafter ("Distance between action points") becomes longer, so that rigidity is improved.

  Next, a method for incorporating the tapered roller bearing 31 into the main shaft 16 will be described with reference to FIGS. FIGS. 5 and 6 are views showing a state before and after the tapered roller bearing 31 is assembled to the main shaft 16, and FIG. 7 is a flowchart showing the main steps of incorporating one inner ring member 32 b of the tapered roller bearing 31 into the main shaft 16. is there.

  When the tapered roller bearing 31 is incorporated into the main shaft 16 of the large-scale wind power generator 11, the operation is performed by fixing the main shaft 16 vertically on the ground. First, the inner ring member 32a is inserted through the main shaft 16 with the large flange 38a facing downward. Next, the tapered roller 34 is incorporated in the raceway surface 36a of the inner ring member 32a. Here, since the center of gravity G of the tapered roller 34 is positioned radially inward from the outer diameter surface of the large collar 38a, the tapered roller 34 is not caught on the raceway surface 36a and is not caught by the large collar 38a. Absent. Further, the inner ring spacer 35 is inserted through the main shaft 16.

The tapered roller bearing 31 that supports the main shaft 16 of the wind power generator 11 is loaded with a thrust load generated when the blade 15 receives wind and the like, and a radial load and a moment load generated due to the weight of the blade 15 and the like. Therefore, in order to properly support these loads, the rotational center line l ₃ of the tapered roller bearing 31, the raceway surface 33a of the outer diameter surface, i.e. the outer ring 33 of the tapered roller 34 at a position in contact with the raceway surface 33a of the outer ring 33 the angle between the virtual line l ₄ of the theta (hereinafter referred to as "contact angle") is set to θ ≧ 40 °. The contact angle of the conventional general tapered roller bearing is about 10 ° to 35 °.

  Next, referring to FIG. 7, the inner ring member 32b and the outer ring 33 are assembled before being incorporated into the main shaft 16 (S11). Specifically, the inner ring member 32b is placed with the side of the large collar 38a facing downward. Next, the tapered roller 34 is incorporated in the raceway surface 36b of the inner ring member 32b. Next, the outer ring 33 is assembled so that the raceway surface 33b of the outer ring 33 and the rolling surface 34c of the tapered roller 34 are in proper contact.

  Next, the inner ring member 32b and the outer ring 33 are fixedly connected (S12). Specifically, one end of the L-shaped fixing jig 1 and the bolt hole 39 b of the inner ring member 32 b are fixed by the bolt 2, and the other end and the through hole 33 c of the outer ring 33 are fixed by the fixing rod 3. Thereby, since the tapered roller 34 is restrained between the raceway surfaces 36b and 33b, it does not fall off.

  Next, as shown in FIG. 5, the inner ring member 32b and the outer ring 33 that are fixedly connected are lifted (S13), and the raceway surface 33a of the outer ring 33 is directed downward and incorporated into the main shaft 16 (S14). Further, as shown in FIG. 6, it is confirmed that the raceway surface 33a of the outer ring 33 is in proper contact with the tapered roller 34 incorporated in the inner ring member 32a, and the fixing jig 1 is removed.

Finally, the raceway distance d between the inner ring 32 and the outer ring 33 is adjusted (S15). Specifically, the width dimension of the inner ring spacer 35 is adjusted in advance, and the distance between the raceway surfaces is set to a predetermined value by applying a preload between the inner ring members 32a and 32b. More specifically, a negative gap (D ₁ > d ₁ ) is set at the top of the crowning of all the tapered rollers 34.

  Note that the above-described incorporation procedure is an example, and other steps may be further added, or the order of some steps may be changed. Further, as the fixing jig 1, any structure that can fix and connect the inner ring member 32b and the outer ring 33 can be adopted.

  By adopting the above assembling procedure, it is possible to prevent the tapered roller 34 from dropping off when the full roller type tapered roller bearing 31 is incorporated into the main shaft 16. This facilitates the incorporation of the tapered roller bearing 31 into the main shaft 16.

  Further, the present invention can obtain the effect even when applied to other types of bearings, for example, self-aligning roller bearings. However, since the tapered roller bearing can easily adjust the distance between the raceway surfaces as described above, it can be said that the present invention is particularly suitable for the tapered roller bearing.

  Here, the center of gravity of the tapered roller 34 moves radially inward of the tapered roller bearing 31 as the contact angle θ increases. Therefore, the above incorporation method is suitable for a bearing having a large contact angle θ such as a tapered roller bearing 31 that supports the main shaft 16 of the wind power generator 11. As other methods for moving the center of gravity of the tapered roller radially inward, it is conceivable to extremely reduce the roller angle or extremely increase the outer diameter of the large collar. However, these are not suitable for bearings that support the main shaft 16 of the wind power generator 11 because the load capacity decreases and the rotation of the tapered rollers becomes unstable.

  Furthermore, from the viewpoint of versatility, the example in which the bolt holes 39a and 39b are provided in both the inner ring members 32a and 32b has been shown. It is sufficient to provide the bolt hole 39b.

  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 present invention is advantageously used for a main shaft support structure of a wind power generator.

It is a figure which shows the wind generator which employ | adopted the spindle support structure which concerns on one Embodiment of this invention. It is an illustration side view of the wind power generator shown in FIG. It is a figure which shows the tapered roller bearing which supports the main axis | shaft of the wind power generator shown in FIG. It is an enlarged view of the tapered roller shown in FIG. It is a figure which shows the state before incorporating one of the inner ring members of a tapered roller bearing in a main shaft. It is a figure which shows the state after incorporating a tapered roller bearing in a main shaft. It is a flowchart which shows the main method of incorporating one of the inner ring members of a tapered roller bearing into a main shaft.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Fixing jig, 2 volt | bolt, 3 fixing rod, 11 Wind power generator, 12 Support stand, 13 Turning seat bearing, 14 Nacelle, 15 Blade, 16 Spindle, 17 Speed up gear, 18 Generator, 19 Bearing housing, 20 Turning motor , 21 Reducer, 31 Conical roller bearing, 32 Inner ring, 32a, 32b Inner ring member, 33 Outer ring, 33a, 33b Outer ring raceway surface, 33c Through hole, 34 Conical roller, 34a Small end surface, 34b Large end surface, 34c Rolling surface, 35 Inner ring spacer, 36a, 36b Inner ring raceway surface, 37a, 37b Small rod, 38a, 38b Large rod, 39a, 39b Bolt hole.

Claims (5)

A blade that receives the wind,
A main shaft whose one end is fixed to the blade and rotates together with the blade;
A main shaft support structure of a wind power generator comprising a tapered roller bearing that rotatably supports the main shaft,
The tapered roller bearing includes an inner ring and an outer ring having a raceway surface, and a plurality of tapered rollers having a rolling surface in contact with the raceway surface,
A main shaft support structure for a wind power generator, which is a full-roller type bearing in which the adjacent tapered rollers are arranged at positions where they can contact each other. The angle θ formed between the bearing rotation center line of the tapered roller bearing and the raceway surface of the outer ring is:
The main shaft support structure for a wind power generator according to claim 1, wherein θ ≧ 40 ° is satisfied. The roller diameter at an arbitrary position of the rolling surface of the tapered roller is D,
When the distance between the raceway surfaces of the inner ring and the outer ring at the measurement position of the diameter of the tapered roller is d,
The main shaft support structure for a wind power generator according to claim 1 or 2, wherein D> d is satisfied at at least one of the rolling surfaces of each of the tapered rollers. A crowning is formed on the rolling surface of the tapered roller,
The roller diameter at the top of the crown of the tapered roller is D ₁ ,
When the track surface distance between the position corresponding to the top of the crowning of the tapered roller and d _1,
In all of the tapered rollers, D _1> satisfy the d _1, the main shaft support structure of a wind generator according to claim 3.   The main shaft support structure for a wind power generator according to claim 3, wherein D> d is satisfied over the entire rolling surface of all the tapered rollers.

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