JP3706396B2 - Windmill wing - Google Patents

Windmill wing Download PDF

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Publication number
JP3706396B2
JP3706396B2 JP09958694A JP9958694A JP3706396B2 JP 3706396 B2 JP3706396 B2 JP 3706396B2 JP 09958694 A JP09958694 A JP 09958694A JP 9958694 A JP9958694 A JP 9958694A JP 3706396 B2 JP3706396 B2 JP 3706396B2
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Japan
Prior art keywords
blade
bearing
wind turbine
rotor head
connecting shaft
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.)
Expired - Lifetime
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JP09958694A
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Japanese (ja)
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JPH07310645A (en
Inventor
修一 鳥羽
雄二 松浪
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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Priority to JP09958694A priority Critical patent/JP3706396B2/en
Publication of JPH07310645A publication Critical patent/JPH07310645A/en
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    • 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

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Description

【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。
【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。
【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。
【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、上記ロータヘッドと上記旋回輪軸受の外輪とをボルトにより結合すると共に、上記旋回輪軸受の内輪と上記翼部の連結軸及び駆動部と結合された上記ロータヘッド側のプレートとをボルトにより結合した構成を特徴とする。
【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、上記ロータヘッドと上記旋回輪軸受の外輪とをボルトにより結合すると共に、上記旋回輪軸受の内輪と上記翼部の連結軸及び駆動部と結合された上記ロータヘッド側のプレートとをボルトにより結合す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。
【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。
【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。
【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。
【図面の簡単な説明】
【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。
【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。
【符号の説明】
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[0001]
[Industrial application fields]
The present invention relates to a wind turbine blade in a wind turbine applied to wind power generation or the like.
[0002]
[Prior art]
FIG. 2 is an explanatory diagram of wind turbine blades in a conventional wind turbine used for wind power generation and the like. In the figure, in a conventional wind turbine blade, a blade portion 3f and a rotor head 3 are connected by a deep groove type ball bearing 3a, a connecting shaft 3b, a blade guide 3c, and the like, and a rolling radial thrust bearing mechanism and a blade by the ball bearing 3a. The connecting shaft 3b is supported by a sliding radial bearing 3d mechanism by the guide 3c. Normally, the connecting shaft 3b of the wind turbine blade has a ball bearing 3a load in the thrust direction due to the centrifugal force generated by the rotation of the rotor head 3, aerodynamic force acting on the blade portion 3f (including fluctuation components due to changes in wind speed and wind direction), and blades. The load in the radial direction of the sliding radial bearing 3d due to the weight of the portion 3f, the aerodynamic force (including fluctuation components due to changes in the wind speed and the wind direction) acting on the blade portion 3f, the bending moment due to the blade's own weight, and the like act.
[0003]
[Problems to be solved by the invention]
As described above, in the conventional wind turbine blade, the deep groove type two-point support ball bearing 3a that supports the load on the connecting shaft 3b in the radial direction, and the sliding radial bearing 3d between the blade guide 3c and the connecting shaft 3b. The structure is supported at two locations, and the structure of the connecting portion between the wing portion 3f and the rotor head 3 becomes complicated and the weight increases. Further, since the sliding radial bearing 3d portion by the blade guide 3c has a large friction coefficient, a large burden is imposed on the linkage mechanism 3e necessary for rotating the blade portion 3f to change the pitch.
[0004]
[Means for Solving the Problems]
A wind turbine blade according to the present invention aims to solve the above-mentioned problem, and in a wind turbine blade rotating a blade portion with a variable pitch supported by a rotor head, a slewing ring bearing capable of simultaneously supporting a radial load and a thrust load. The rotor that supports the wing portion via the bolt and connects the rotor head and the outer ring of the slewing ring bearing with bolts, and is connected to the inner ring of the slewing ring bearing, the connecting shaft of the wing part, and the drive unit. It is characterized by a structure in which the head side plate is coupled with a bolt .
[0005]
[Action]
In other words, in the wind turbine blade according to the present invention, the blade portion in the wind turbine blade that rotates the blade portion with the rotor head being supported by the rotor head is supported via the swivel ring bearing capable of supporting the radial load and the thrust load at the same time. The rotor head and the outer ring of the slewing ring bearing are coupled by a bolt, and the inner ring of the slewing ring bearing and the plate on the rotor head side coupled to the connecting shaft and the drive unit of the wing part are coupled by a bolt. It has become so that to bond, it is possible to omit the wing guide in a conventional wind turbine blade by supporting the wings through the simultaneously supportable slewing ring bearing a radial load and thrust load. Accordingly, since the sliding bearing by the blade guide is also eliminated, the friction coefficient when the pitch is changed by rotating the blade portion is reduced.
[0006]
【Example】
FIG. 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 a wind turbine used for wind power generation or the like, and supports a radial load and a thrust load at the same time instead of the deep groove type ball bearing in the conventional wind turbine blade. The four-point support type slewing ring bearing 1 that can be used and the sliding radial bearing by the blade guide are also abolished, and the weight is reduced and the friction coefficient when the pitch is changed by rotating the blade portion 6 is reduced. The burden of the linkage mechanism necessary for changing the pitch is reduced, and the size can be reduced. That is, as shown in the figure, the rotor head 3 and the outer ring 11 of the four-point support type slewing ring bearing 1 are coupled by bolts, and the inner ring 12 of the slewing ring bearing 1 and the connecting shaft 2 of the blade 6 and the rotor head 3 side. The plate 5 is connected with bolts. The plate 5 on the rotor head 3 side is coupled to the drive unit 4, and the rotational driving 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 changed smoothly. It has become. This slewing ring bearing 1 has sufficient strength against the weight of the blade 6 and the centrifugal force and moment generated by the rotation of the rotor head 3. The slewing ring bearing 1 uses a ball shape so that a sufficiently smooth slewing can be performed even if the lubricating grease leaks out and an anti-seizure effect can be obtained, but a roller type may also be used. Further, the ball in the slewing ring bearing 1 is in contact with the groove-shaped ball guides engraved on the outer ring 11 and the inner ring 12 at four points of the arcs 11a, 11b, 12a and 12b, and the load applied to the inner ring 12 Is supporting. The four-point support is possible in this way because the turning speed when the pitch is changed by rotating the wings 6 is slow, so there is no need to consider friction or the like compared to a bearing for a high-speed rotating shaft or the like. Because.
[0007]
In conventional wind turbine blades, the connecting shaft is supported at two locations: a deep groove type two-point support ball bearing that supports the load in the radial direction, and a sliding radial bearing between the blade guide and the connecting shaft. The structure of the connecting portion between the wing portion and the rotor head becomes complicated and the weight increases. Furthermore, since the sliding radial bearing portion by the blade guide has a large coefficient of friction, a large burden is imposed on the linkage mechanism necessary to change the pitch by rotating the blade portion. However, in this wind turbine blade, the rotor head 3 and the blade portion 6 are used. A four-point support type slewing ring bearing 1 capable of supporting a radial load and a thrust direction load at the same time at a connecting part with the connecting shaft 2 is used. The connecting shaft 2 and the driving portion 4 having a pitch of the blade portion 6 are integrated, and the outer ring 11 and the rotor head 3 of the swivel ring bearing 1 are integrated to freely rotate the blade portion 6 while the rotor head 3 is rotating. The pitch of the portion 6 can be changed, and by using the slewing ring bearing 1 that can simultaneously support a radial load and a thrust load, the connecting shaft 2 and the rotor head of the wing portion 6 can be used. 3 and the structure of the connecting portion becomes easy can be omitted wing guide in a conventional wind turbine blade in a weight amount corresponding to the omitted wing guide can be reduced. Further, since the rotation when changing the pitch of the blade portion 6 is only the rolling of the balls in the slewing ring bearing 1, the friction coefficient is smaller than that in the case of the combined use with the conventional sliding radial bearing. The load on the mechanism is small. Further, in the wind turbine blade, for example, a blade guide having a weight of about 400 kg can be omitted, and the strength is increased by using the slewing ring bearing 1, so that the ball bearing of about 30 kg is replaced with the slewing ring bearing 1 of about 150 kg. The weight of about 280kg per connection part is reduced. Since the normal windmill has three wings 6, the weight of the whole is reduced by about 840 kg. In addition, the friction coefficient in the sliding radial bearing between the connecting shaft and the shaft guide in the conventional wind turbine blade is about 0.1, but in the structure of the ball-shaped slewing ring bearing 1 alone, the friction coefficient is about 0.01. The load on the drive unit 4 and its linkage mechanism that change the pitch by rotating the wing unit 6 is significantly reduced.
[0008]
【The invention's effect】
The wind turbine blade according to the present invention is configured as described above, and since the blade guide in the conventional wind turbine blade can be omitted, the structure at the connecting portion between the blade portion and the rotor head is simplified and the weight is reduced. To do. Further, since the friction coefficient when changing the pitch by rotating the wing portion is reduced, the burden on the drive unit and the linkage mechanism for changing the pitch of the wing portion is reduced.
[Brief description of the drawings]
FIG. 1A is a sectional view of a connecting shaft in a wind turbine blade according to an embodiment of the present invention, and FIG.
2A is a cross-sectional view of a rotor head in a conventional wind turbine, and FIG. 2B is a cross-sectional view of a connecting shaft thereof.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 slewing ring bearing 2 connecting shaft 3 of wing | blade part 3 rotor head 4 drive part 5 drive side plate 6 wing part

Claims (1)

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、上記ロータヘッドと上記旋回輪軸受の外輪とをボルトにより結合すると共に、上記旋回輪軸受の内輪と上記翼部の連結軸及び駆動部と結合された上記ロータヘッド側のプレートとをボルトにより結合したことを特徴とする風車翼。In a wind turbine blade that rotates while supporting a blade portion with a variable pitch supported by a rotor head, the blade portion is supported via a swirl ring bearing capable of simultaneously supporting a radial load and a thrust load. A wind turbine characterized in that an outer ring of a bearing is coupled with a bolt, and an inner ring of the slewing ring bearing is coupled with a plate on the rotor head side coupled with a connecting shaft and a drive unit of the wing portion by a bolt. Wings.
JP09958694A 1994-05-13 1994-05-13 Windmill wing Expired - Lifetime JP3706396B2 (en)

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 JPH07310645A (en) 1995-11-28
JP3706396B2 true JP3706396B2 (en) 2005-10-12

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Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4533642B2 (en) * 2004-02-20 2010-09-01 三菱重工業株式会社 Winding wheel bearing structure for windmill
US7927019B2 (en) 2005-05-31 2011-04-19 Mitsubishi Heavy Industries Ltd. Slewing bearing structure
CN101858313B (en) * 2010-06-10 2012-05-30 北京京冶轧机轴承制造有限公司 Wind generating set and variable blade bearing thereof
JP2013076441A (en) * 2011-09-30 2013-04-25 Mitsubishi Heavy Ind Ltd Turning ring bearing structure for wind turbine, and method for replacing turning ring bearing structure for wind turbine

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JPH07310645A (en) 1995-11-28

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