JPH07310645A - Windmill blade - Google Patents
Windmill bladeInfo
- Publication number
- JPH07310645A JPH07310645A JP6099586A JP9958694A JPH07310645A JP H07310645 A JPH07310645 A JP H07310645A JP 6099586 A JP6099586 A JP 6099586A JP 9958694 A JP9958694 A JP 9958694A JP H07310645 A JPH07310645 A JP H07310645A
- Authority
- JP
- Japan
- Prior art keywords
- blade
- rotor head
- bearing
- load
- wind turbine
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/70—Wind energy
- Y02E10/72—Wind turbines with rotation axis in wind direction
Landscapes
- Wind Motors (AREA)
Abstract
Description
【0001】[0001]
【産業上の利用分野】本発明は、風力発電などに適用さ
れる風車における風車翼に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a wind turbine blade in a wind turbine applied to wind power generation and the like.
【0002】[0002]
【従来の技術】図2は風力発電などに使用されている従
来の風車における風車翼の説明図である。図において、
従来の風車翼においては翼部3fとロータヘッド3とが
深溝型の玉軸受3a、連結軸3b、翼ガイド3cなどに
より連結されており、玉軸受3aによる転がりラジアル
スラスト軸受機構及び翼ガイド3cによる滑りラジアル
軸受3d機構により連結軸3bを支えている。通常、風
車翼の連結軸3bにはロータヘッド3の回転により生ず
る遠心力による玉軸受3aスラスト方向の荷重、翼部3
fに作用する空気力(風速及び風向の変化による変動成
分を含む)および翼部3f自重による滑りラジアル軸受
3dラジアル方向の荷重、翼部3fに作用する空気力
(風速及び風向の変化による変動成分を含む)および翼
自重による曲げモーメントなどが作用する。2. Description of the Related Art FIG. 2 is an explanatory view of a wind turbine blade in a conventional wind turbine used for wind power generation and the like. In the figure,
In the conventional wind turbine blade, the blade portion 3f and the rotor head 3 are connected by the deep groove type ball bearing 3a, the connecting shaft 3b, the blade guide 3c, etc., and by the rolling radial thrust bearing mechanism and the blade guide 3c by the ball bearing 3a. The sliding radial bearing 3d mechanism supports the connecting shaft 3b. Usually, the load in the thrust direction of the ball bearing 3a due to the centrifugal force generated by the rotation of the rotor head 3 is applied to the connecting shaft 3b of the wind turbine blade, and the blade portion 3
Aerodynamic force acting on f (including fluctuation component due to changes in wind speed and wind direction), sliding radial bearing 3d due to blade 3f own weight, radial load, aerodynamic force acting on blade part 3f (variation component due to changes in wind speed and wind direction) (Including) and bending moment due to the blade's own weight.
【0003】[0003]
【発明が解決しようとする課題】上記のように、従来の
風車翼においては連結軸3bをラジアル方向の荷重を支
える深溝型2点支持式の玉軸受3aと、翼ガイド3cと
連結軸3bとの間の滑りラジアル軸受3dとの2ヶ所で
支える構造になっており、翼部3fとロータヘッド3と
の連結部における構造が複雑になって重量も増加する。
さらに、翼ガイド3cによる滑りラジアル軸受3d部は
摩擦係数が大きいため、翼部3fを回転させてピッチを
変えるのに必要なリンケージ機構3eに大きな負担が掛
かる。As described above, in the conventional wind turbine blade, the deep groove type two-point support type ball bearing 3a for supporting the connecting shaft 3b in the radial direction, the blade guide 3c and the connecting shaft 3b. It has a structure to be supported at two places by the sliding radial bearing 3d between them, and the structure at the connecting portion between the blade portion 3f and the rotor head 3 becomes complicated and the weight also increases.
Further, since the sliding radial bearing 3d portion by the blade guide 3c has a large friction coefficient, a heavy load is imposed on the linkage mechanism 3e required to rotate the blade portion 3f to change the pitch.
【0004】[0004]
【課題を解決するための手段】本発明に係る風車翼は上
記課題の解決を目的にしており、ロータヘッドにより翼
部をピッチが可変に支持して回転させる風車翼におい
て、ラジアル荷重とスラスト荷重とを同時に支持可能な
旋回輪軸受を介して上記翼部を支持した構成を特徴とす
る。SUMMARY OF THE INVENTION A wind turbine blade according to the present invention is intended to solve the above-mentioned problems, and in a wind turbine blade in which a rotor head supports a blade portion with a variable pitch and rotates, a radial load and a thrust load are applied. And the wing portion are supported via a slewing ring bearing capable of simultaneously supporting and.
【0005】[0005]
【作用】即ち、本発明に係る風車翼においては、ロータ
ヘッドにより翼部をピッチが可変に支持して回転させる
風車翼における翼部がラジアル荷重とスラスト荷重とを
同時に支持可能な旋回輪軸受を介して支持されるように
なっており、ラジアル荷重とスラスト荷重とを同時に支
持可能な旋回輪軸受を介して翼部を支持することにより
従来の風車翼における翼ガイドを省略することができ
る。従って、翼ガイドによる滑り軸受も廃されることに
より翼部を回転させてピッチを変える際の摩擦係数が小
さくなる。That is, in the wind turbine blade according to the present invention, the blade portion of the wind turbine blade that rotates the blade portion by the rotor head while supporting the blade portion with a variable pitch provides the slewing ring bearing capable of simultaneously supporting the radial load and the thrust load. By supporting the blade portion via the slewing ring bearing capable of simultaneously supporting the radial load and the thrust load, the blade guide in the conventional wind turbine blade can be omitted. Therefore, since the slide bearing by the blade guide is also abolished, the friction coefficient when rotating the blade portion and changing the pitch becomes small.
【0006】[0006]
【実施例】図1は本発明の一実施例に係る風車翼の説明
図である。図において、本実施例に係る風車翼は風力発
電などに使用される風車におけるもので、従来の風車翼
における深溝型の玉軸受に代えてラジアル方向の荷重と
スラスト方向の荷重とを同時に支えることができる4点
支持式の旋回輪軸受1を用い、併せて翼ガイドによる滑
りラジアル軸受を廃しており、重量が軽減されるととも
に翼部6を回転させてピッチを変える際の摩擦係数が小
さくなり、ピッチを変えるのに必要なリンケージ機構部
の負担が軽くなり、小型化が可能になっている。即ち、
図に示すようにロータヘッド3と4点支持式の旋回輪軸
受1の外輪11とをボルトにより結合し、旋回輪軸受1
の内輪12と翼部6の連結軸2及びロータヘッド3側の
プレート5とをボルトにより結合している。ロータヘッ
ド3側のプレート5は駆動部4と結合されており、駆動
部4で発生する回転駆動力が連結軸2、翼部6へ伝達さ
れて翼部6のピッチ変更がスムーズに行われる構造にな
っている。この旋回輪軸受1は翼部6の重量及びロータ
ヘッド3の回転により発生する遠心力やモーメントなど
に対して十分な強度を有する。旋回輪軸受1は潤滑用の
グリースが漏れ出た場合でも十分に滑めらかな旋回が可
能で焼付き防止効果が得られるように玉型を用いている
が、コロ型でもよい。また、旋回輪軸受1内の玉は外輪
11と内輪12に刻設されている溝状の玉ガイドと円弧
11a,11b,12a,12bの4ヶ所でほぼ線接触
をして内輪12に掛かる荷重を支えている。このように
4点支持が可能になるのは、翼部6を回転させてピッチ
を変える際の旋回速度が遅いので、高速回転軸用などの
軸受と比較して摩擦等を考慮する必要が無いからであ
る。1 is an explanatory view of a wind turbine blade according to an embodiment of the present invention. In the figure, the wind turbine blade according to the present embodiment is for a wind turbine used for wind power generation, etc., and is capable of simultaneously supporting a radial load and a thrust load in place of a deep groove type ball bearing in a conventional wind turbine blade. The four-point support type slewing ring bearing 1 that can be used is also used, and the sliding radial bearing by the blade guide is also eliminated, so that the weight is reduced and the friction coefficient when rotating the blade portion 6 to change the pitch becomes small. , The load on the linkage mechanism required to change the pitch is lightened, and the size can be reduced. That is,
As shown in the figure, the rotor head 3 and the outer ring 11 of the slewing ring bearing 1 of the four-point support type are connected by bolts to form a slewing ring bearing 1
The inner ring 12 is connected to the connecting shaft 2 of the blade portion 6 and the plate 5 on the rotor head 3 side by bolts. The plate 5 on the rotor head 3 side is connected to the drive unit 4, and the rotational drive force generated by the drive unit 4 is transmitted to the connecting shaft 2 and the blade unit 6 so that the pitch of the blade unit 6 can be smoothly changed. It has become. The slewing ring bearing 1 has sufficient strength against the weight of the blade portion 6 and the centrifugal force and moment generated by the rotation of the rotor head 3. The slewing ring bearing 1 uses a ball type so that it can swivel sufficiently smoothly even if grease for lubrication leaks out and a seizure prevention effect is obtained, but a roller type may be used. Further, the balls in the slewing ring bearing 1 make almost linear contact with the groove-shaped ball guides engraved in the outer ring 11 and the inner ring 12 at four points of the arcs 11a, 11b, 12a, 12b, and the load applied to the inner ring 12. Is supporting. In this way, four-point support is possible because the swirling speed when rotating the blade 6 to change the pitch is slow, so there is no need to consider friction and the like as compared with bearings for high-speed rotating shafts and the like. Because.
【0007】従来の風車翼においては連結軸をラジアル
方向の荷重を支える深溝型2点支持式の玉軸受と、翼ガ
イドと連結軸との間の滑りラジアル軸受との2ヶ所で支
える構造になっており、翼部とロータヘッドとの連結部
における構造が複雑になって重量も増加する。さらに、
翼ガイドによる滑りラジアル軸受部は摩擦係数が大きい
ため、翼部を回転させてピッチを変えるのに必要なリン
ケージ機構に大きな負担が掛かるが、本風車翼において
はロータヘッド3と翼部6の連結軸2との連結部にラジ
アル方向の荷重とスラスト方向の荷重とを同時に支持す
ることができる4点支持式の旋回輪軸受1を用い、この
旋回輪軸受1の内輪12と翼部6の連結軸2と翼部6ピ
ッチの駆動部4とを一体化し、旋回輪軸受1の外輪11
とロータヘッド3とを一体化してロータヘッド3が回転
中でも自由に翼部6を旋回させて翼部6のピッチを変更
することができる構造をしており、ラジアル方向の荷重
とスラスト方向の荷重とを同時に支えることのできる旋
回輪軸受1を使用することにより翼部6の連結軸2とロ
ータヘッド3との連結部の構造が簡単になって従来の風
車翼における翼ガイドを省略することができ、翼ガイド
を省略した分だけ重量が軽減される。さらに、翼部6の
ピッチを変える際の回転は旋回輪軸受1内の玉の転がり
のみにより、従来の滑りラジアル軸受との併用の場合と
比較すると摩擦係数が小さくなるので、駆動部4におけ
るリンケージ機構の負荷が小さくなっている。また、本
風車翼においては例えば重さ約400kgの翼ガイドを省
略することができ、旋回輪軸受1の使用により強度が増
加するので約30kgの玉軸受から約150kgの旋回輪軸
受1に替わるが、連結部1ヶ所につき約280kgの重量
が軽減する。通常風車は翼部6が3本であるので、全体
で約840kgの重量が軽減される。また、従来の風車翼
における連結軸と軸ガイドとの間の滑りラジアル軸受に
おける摩擦係数は約0.1であるが、玉型の旋回輪軸受
1のみの構造では摩擦係数が約0.01となり、翼部6
を回転させてピッチを変える駆動部4及びそのリンケー
ジ機構の負荷が著しく軽減される。A conventional wind turbine blade has a structure in which a connecting shaft is supported at two places, a deep groove type two-point support type ball bearing for supporting a load in a radial direction and a sliding radial bearing between the blade guide and the connecting shaft. Therefore, the structure of the connecting portion between the blade portion and the rotor head becomes complicated and the weight also increases. further,
Since the sliding radial bearing portion by the blade guide has a large friction coefficient, a heavy load is imposed on the linkage mechanism required to rotate the blade portion and change the pitch. However, in this wind turbine blade, the rotor head 3 and the blade portion 6 are connected. A slewing ring bearing 1 of a four-point support type capable of simultaneously supporting a load in the radial direction and a load in the thrust direction is used in a connecting portion with the shaft 2, and an inner ring 12 of the slewing ring bearing 1 and a wing portion 6 are connected. The shaft 2 and the drive unit 4 having the blade portion 6 pitch are integrated to form an outer ring 11 of the slewing ring bearing 1.
The rotor head 3 is integrated with the rotor head 3 so that the blade portion 6 can freely rotate to change the pitch of the blade portion 6 even when the rotor head 3 is rotating, and the load in the radial direction and the load in the thrust direction can be changed. By using the slewing ring bearing 1 capable of supporting both and at the same time, the structure of the connecting portion between the connecting shaft 2 of the blade portion 6 and the rotor head 3 is simplified and the blade guide in the conventional wind turbine blade can be omitted. It is possible, and the weight is reduced by omitting the wing guide. Further, the rotation when changing the pitch of the wing portion 6 is caused only by the rolling of the balls in the slewing ring bearing 1, and the friction coefficient becomes smaller than in the case of using the conventional sliding radial bearing together. The mechanical load is small. Further, in the present wind turbine blade, for example, a blade guide having a weight of about 400 kg can be omitted, and since the strength is increased by using the slewing ring bearing 1, the ball bearing of about 30 kg is replaced with the slewing ring bearing 1 of about 150 kg. The weight is reduced by about 280kg per connecting part. Since a normal wind turbine has three blades 6, a total weight of about 840 kg is reduced. Further, the friction coefficient of the sliding radial bearing between the connecting shaft and the shaft guide in the conventional wind turbine blade is about 0.1, but the friction coefficient is about 0.01 in the structure of only the spherical swivel bearing 1. , Wings 6
The load on the drive unit 4 and its linkage mechanism, which rotate to change the pitch, is significantly reduced.
【0008】[0008]
【発明の効果】本発明に係る風車翼は前記のように構成
されており、従来の風車翼における翼ガイドを省略する
ことができるので、翼部とロータヘッドとの連結部にお
ける構造が簡単になって重量が軽減する。また、翼部を
回転させてピッチを変える際の摩擦係数が小さくなるの
で、翼部のピッチを変える駆動部およびリンケージ機構
に掛かる負担が軽減する。The wind turbine blade according to the present invention is constructed as described above, and since the blade guide in the conventional wind turbine blade can be omitted, the structure of the connecting portion between the blade portion and the rotor head can be simplified. And the weight is reduced. Further, since the friction coefficient when rotating the blade portion to change the pitch is reduced, the load on the drive unit and the linkage mechanism for changing the pitch of the blade portion is reduced.
【図1】図1(a)は本発明の一実施例に係る風車翼に
おける連結軸の断面図、同図(b)はその旋回輪軸受の
断面図である。FIG. 1 (a) is a sectional view of a connecting shaft in a wind turbine blade according to an embodiment of the present invention, and FIG. 1 (b) is a sectional view of a slewing wheel bearing thereof.
【図2】図2(a)は従来の風車におけるロータヘッド
の断面図、同図(b)はその連結軸の断面図である。2A is a sectional view of a rotor head in a conventional wind turbine, and FIG. 2B is a sectional view of a connecting shaft thereof.
1 旋回輪軸受 2 翼部の連結軸 3 ロータヘッド 4 駆動部 5 駆動側のプレート 6 翼部 1 slewing wheel bearing 2 connecting shaft of blades 3 rotor head 4 drive unit 5 drive side plate 6 blade unit
【手続補正書】[Procedure amendment]
【提出日】平成6年6月13日[Submission date] June 13, 1994
【手続補正1】[Procedure Amendment 1]
【補正対象書類名】図面[Document name to be corrected] Drawing
【補正対象項目名】図1[Name of item to be corrected] Figure 1
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【図1】 [Figure 1]
Claims (1)
に支持して回転させる風車翼において、ラジアル荷重と
スラスト荷重とを同時に支持可能な旋回輪軸受を介して
上記翼部を支持したことを特徴とする風車翼。1. A wind turbine blade, in which a rotor head supports a blade portion with a variable pitch for rotation, wherein the blade portion is supported via a slewing ring bearing capable of simultaneously supporting a radial load and a thrust load. And a windmill wing.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP09958694A JP3706396B2 (en) | 1994-05-13 | 1994-05-13 | Windmill wing |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP09958694A JP3706396B2 (en) | 1994-05-13 | 1994-05-13 | Windmill wing |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH07310645A true JPH07310645A (en) | 1995-11-28 |
JP3706396B2 JP3706396B2 (en) | 2005-10-12 |
Family
ID=14251207
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP09958694A Expired - Lifetime JP3706396B2 (en) | 1994-05-13 | 1994-05-13 | Windmill wing |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP3706396B2 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2005337267A (en) * | 2004-02-20 | 2005-12-08 | Mitsubishi Heavy Ind Ltd | Revolving wheel bearing structure for windmill |
WO2006129351A1 (en) * | 2005-05-31 | 2006-12-07 | Mitsubishi Heavy Industries, Ltd. | Structure of slewing ring bearing |
CN101858313A (en) * | 2010-06-10 | 2010-10-13 | 北京京冶轧机轴承制造有限公司 | Wind generating set and variable blade bearing thereof |
WO2013047617A1 (en) * | 2011-09-30 | 2013-04-04 | 三菱重工業株式会社 | Rotating ring bearing structure for wind wheel and method for replacing rotating ring bearing structure for wind wheel |
-
1994
- 1994-05-13 JP JP09958694A patent/JP3706396B2/en not_active Expired - Lifetime
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2005337267A (en) * | 2004-02-20 | 2005-12-08 | Mitsubishi Heavy Ind Ltd | Revolving wheel bearing structure for windmill |
JP4533642B2 (en) * | 2004-02-20 | 2010-09-01 | 三菱重工業株式会社 | Winding wheel bearing structure for windmill |
WO2006129351A1 (en) * | 2005-05-31 | 2006-12-07 | Mitsubishi Heavy Industries, Ltd. | Structure of slewing ring bearing |
KR101022104B1 (en) * | 2005-05-31 | 2011-03-17 | 미츠비시 쥬고교 가부시키가이샤 | Slewing bearing structure |
US7927019B2 (en) | 2005-05-31 | 2011-04-19 | Mitsubishi Heavy Industries Ltd. | Slewing bearing structure |
EP2532904A2 (en) | 2005-05-31 | 2012-12-12 | Mitsubishi Heavy Industries | Structure of slewing ring bearing |
CN101858313A (en) * | 2010-06-10 | 2010-10-13 | 北京京冶轧机轴承制造有限公司 | Wind generating set and variable blade bearing thereof |
WO2013047617A1 (en) * | 2011-09-30 | 2013-04-04 | 三菱重工業株式会社 | Rotating ring bearing structure for wind wheel and method for replacing rotating ring bearing structure for wind wheel |
Also Published As
Publication number | Publication date |
---|---|
JP3706396B2 (en) | 2005-10-12 |
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