1352777 九、發明說明 【發明所屬之技術領域】 本發明是關於風力發電裝置的傾角驅動裝置以及風力 發電裝置。 【先前技術】 使用於風力發電裝置的風車係有：風車旋轉翼的傾角 φ 爲固定的風車、以及傾角可變的風車。 上述用來改變風車旋轉翼的傾角的機構，例如：可將 油壓缸的壓缸桿的直線移動轉變成風車旋轉翼的軸線外圍 的旋轉之機構（例如：請參考專利文獻1 )。 除了上述專利文獻1所記載的機構之外，尙有一種傾 角可變機構’是利用耳軸構造將油壓缸可朝單一軸的外圍 旋轉地支承在轉子頭，並且將壓缸桿的端部可朝單一軸的 外圍旋轉地支承在風車旋轉翼。 # 根據這種傾角可變機構，油壓缸以及壓缸桿是在對於 風車旋轉翼的軸線呈垂直的平面内，以耳軸構造爲中心被 保持成能夠轉動’也就是，可做單軸的擺動運動。壓缸桿 的端部是被支承於遠離風車旋轉翼的軸線的位置，因此， 可將壓缸桿的直線移動轉變成風車旋轉翼的軸線外圍的旋 轉。 〔專利文獻1〕曰本特開平5-149237號公報 【發明內容】 -4- 1352777 然而，在這種可做單軸擺動運動的傾角驅動機構中， 因爲風力發電設備趨於大型化等等的理由，導致油壓缸以 及壓缸桿的行程變長的情況下，耳軸構造與油壓缸之間的 * 安裝部的構造很容易變形，因而加諸在與耳軸構造的旋轉 軸線正交的軸線外圍的負荷會有過大的虞慮。 此外，導因於作用在大型化的風車旋轉翼的力量，會 有引起風車旋轉翼的根部、轉子頭本身發生變形的可能性 • ，從而作用在與耳軸構造的旋轉軸線正交的軸線外圍的負 荷會有變得過大的虞慮。 如果這種負荷變得太大的話，油壓缸的油封會磨損， 加諸在耳軸構造的結構負擔也會變大，傾角驅動機構的長 期可靠性會有變差的可能性。 除了上述的各點之外，在傾角驅動機構中，爲了防止 油壓缸的油封的磨損等，必須嚴格地要求風車旋轉翼之相 對於旋轉面的平行度，在進行傾角驅動機構的組裝作業時 # 要特別地注意這一點。 有人曾經提出一種機構用來抑制上述問題，是在對風 車旋轉翼的軸線呈垂直的平面内以耳軸構造爲中心來保持 成可轉動，並且在與風車旋轉翼的軸線呈平行的平面内， 也是以追加的耳軸構造爲中心來保持成可轉動，換言之， 係製作成可做雙軸擺動運動的機構。 這麼做的話，用來支承油壓缸的構造會變得很複雜， 所以轉子頭會變得大型化，而且亦有增加成本之虞慮。 本發明是有鑒於上述的課題，其目的是在於提供：只 -5- 1352777 要簡單且低廉的構造，即可防止傾角驅動裝置的可靠性受 損的風力發電裝置的傾角驅動裝置以及風力發電裝置。 爲了達成上述目的，本發明係提供以下的手段。 ' 本發明的第1態樣的風力發電裝置的傾角驅動裝置， 係具備： 對於轉子頭在軸線外圍轉動驅動風車旋轉翼以改變該 風車旋轉翼的傾角的壓缸、可轉動地支承從前述壓缸起與 φ 前述風車旋轉翼的軸線略呈平行地延伸的耳軸的壓缸軸承 ;而在前述壓缸軸承之用來支承前述耳軸的支承部，則是 具備了用來彈性地支承前述耳軸的彈性支承構件。 根據本態樣’壓缸是被壓缸軸承可轉動地支承於與風 車旋轉翼的軸線略呈平行地延伸的耳軸。換言之，壓缸是 可轉動地被支承於與風車旋轉翼的軸線略呈平行的轉動軸 線的外圍。藉此，從壓缸進行伸縮的壓缸桿的端部是被支 承在遠離風車旋轉翼的軸線的位置，因此，壓缸桿的直線 # 移動（壓缸桿的伸縮）將被轉變成風車旋轉翼的軸線外圍 的旋轉’因而可改變風車旋轉翼的傾角，也就是，可以調 整其傾角。 此處’因爲在壓缸軸承之用以支承耳軸的支承部，具 備了可將耳軸予以彈性支承的彈性支承構件，因此，例如 :當風車旋轉翼受到風力時，因轉子頭與風車旋轉翼的安 裝部發生的變形所產生之作用在壓缸（也就是作用在耳軸 )之與耳軸的軸線交叉方向上的力量’將會因爲彈性構件 的變形而被吸收掉。 -6- 1352777 是以，作用於使壓缸撓曲的方向上的力量，將會被彈 性構件所吸收，因此可防止壓缸的油封部等的迅速磨損， 亦可防止傾角驅動裝置的可靠性受損。 ' 而且，只是在壓缸軸承之用來支承耳軸的支承部，具 備了可將耳軸予以彈性支承的彈性支承構件而已，因此與 使用了兩組耳軸的機構比較起來，可使構造簡化以及小型 化，因而可降低製造成本β φ 在上述態樣中，前述彈性支承構件亦可採用：使用了 防震橡膠的結構。 這麼做的話，因轉子頭與風車旋轉翼的安裝部所發生 的變形，而作用在壓缸（也就是，作用在耳軸上）之與耳 軸的軸線交叉方向上的力量將會因爲防震橡膠的變形而被 吸收掉。因此，可防止壓缸的油封部等的迅速磨損，亦可 防止傾角驅動裝置的可靠性受損。 在上述結構中，前述防震橡膠的橡膠面亦可製作成： • 傾斜成朝外側擴徑。 因爲轉子頭與風車旋轉翼的安裝部所發生的變形，耳 軸將會以耳軸的軸線中心變成傾斜的方式來進行移動，因 此，耳軸的外側端將會做最大幅地移動。換言之，耳軸的 移動，是從内側朝外側逐漸地變大。因此，從耳軸作用到 防震橡膠的橡膠面的力量，是較之與耳軸的軸線正交的方 向更朝内側傾斜。 因爲防震橡膠的橡膠面，是傾斜成朝外側擴徑，所以 可有效地支承從耳軸作用到防震橡膠的橡膠面之朝内側傾 1352777 斜的力量。此外，朝向沿著防震橡膠的橡膠面的方向之分 力變小，因此可讓作用到防震橡膠上的剪力變小，進而可 提昇防震橡膠的耐久力。 此外，防震橡膠的橡膠面的傾斜角的大小，最好是選 定爲：與作用在壓缸的各種荷重所產生的對於耳軸的合力 的作用方向大致正交的大小。這種合力的作用方向會隨著 荷重狀態的變化而改變，所以既可採用被假想的合力的作 φ 用方向的中間値，亦可採用被假想爲最高頻率的作用方向 〇 在上述態樣中，前述耳軸的外側端部最好是利用止推 構件來抑制其往外側移動。 壓缸是會隨著轉子頭的旋轉而在轉子頭的軸線中心外 圍進行公轉，因此，在進行這一圈旋轉的期間，壓缸也會 在其本身的軸線外圍進行一次旋轉。因此，如果耳軸與壓 缸軸承之間具有間隙的話，壓缸（耳軸）會讓間隙產生週 Φ 期性的移動，所以耳軸與壓缸軸承就會產生週期性的碰撞 〇 起因於這種耳軸與壓缸軸承的週期性的碰撞，將會產 生噪音，而且該碰撞力量作用到彈性構件身上。 這種現象在耳軸的軸線方向上係更爲顯著，因爲耳軸 的軸線方向上的間隙係較之與被緊密地支承於支承部的軸 線方向交叉的方向上的間隙更大。 根據本態樣，耳軸的外側端部係利用止推構件來抑制 其往外側移動，所以即使在耳軸（壓缸）與壓缸軸承之間 -8- 1352777 具有間隙’亦可抑制耳軸（壓缸）相對於壓缸軸承朝往壓 缸軸承的軸線方向移動。因此，能夠抑制因轉子頭的旋轉 所產生的耳軸與壓缸軸承的週期性的碰撞，所以既可抑制 ' 噪音的產生’又可提高彈性構件的耐久性。 本發明的第2態樣的風力發電裝置，係設置了 ：用來 承受風力的複數個風車旋轉翼；用來將該風車旋轉翼可轉 動地支承於前述風車旋轉翼的軸線外圍，並且被前述風車 ^ 旋轉翼所旋轉驅動的轉子頭；申請專利範圍第1項至第4 項的任何一項所述的傾角驅動裝置；利用前述轉子頭的旋 轉來進行發電的發電設備。 根據本態樣’藉由採用上述第1態樣的傾角驅動裝置 ，可防止傾角驅動裝置的可靠性受損，所以能夠防止作爲 風力發電裝置的可靠性受損。 根據本發明，因爲是在壓缸軸承之用來支承耳軸的支 承部，具備有可彈性支承耳軸的彈性支承構件，所以作用 • 在使壓缸產生撓曲的方向上的力量，係可被該彈性構件所 吸收。藉此，可以防止傾角驅動裝置的可靠性受損。 此外，因爲只是在壓缸軸承之用來支承耳軸的支承部 ，具備了可彈性支承耳軸的彈性支承構件而已，因此，與 具備兩組耳軸的傾角驅動裝置比較起來，可使構造更爲簡 化以及小型化，可降低製造成本。 【實施方式】 〔發明之最佳實施方式〕 -9- 1352777 茲佐以圖式來說明本發明的實施方式如下。 〔第1實施方式〕 茲佐以第1圖至第5圖來説明本發明的第1實施方式 的風力發電裝置。 第1圖是顯示本實施方式的風力發電裝置1的整體槪 略結構的側面圖。 φ 風力發電裝置1是如第1圖所示般地，是用來進行風 力發電。在風力發電裝置1上是設置了：豎立設置在基礎 B上的支柱2、設置在支柱2的上端的機艙3、設在機艙3 之可在略呈水平的軸線外圍旋轉的轉子頭4、用來包覆轉 子頭4的頭部封包件5、呈放射狀地安裝在轉子頭4的旋 轉軸線外圍的複數片的風車旋轉翼6、利用轉子頭4的旋 轉來進行發電的發電設備7。 支柱2是如第1圖所示般地，採用從基礎B往上方（ φ 第1圖的上方）延伸的柱狀結構，例如：採用將複數個單 元在上下方向上連結在一起的結構。 在支柱2的最上部設置了機艙3。如果支柱2是由複 數個單元所構成的話，機艙3就是設置在被設在最上部的 單元上。 機艙3是如第1圖所示般地’將轉子頭4支承成可旋 轉，並且在内部收納著利用轉子頭4的旋轉來進行發電的 發電設備7。 在轉子頭4上，在其旋轉軸線外圍呈放射狀地安裝著 -10- 1352777 複數片的風車旋轉翼6，而轉子頭4的周圍則是被頭部封 包件5所包覆著。 如此一來，如果風從轉子頭4的旋轉軸線方向吹抵達 ' 風車旋轉翼6的話，就會在風車旋轉翼6產生令轉子頭4 在旋轉軸線外圍旋轉的力量，轉子頭4就會被旋轉驅動。 此外，本實施方式雖然是以應用在設置了 3片風車旋 轉翼6的例子來做説明，但是，風車旋轉翼6的數目並不 φ 限定爲3片，亦可應用在 2片或者較3片更多片的情況 ，並未特別加以限定。 第2圖是用來說明一個傾角驅動裝置11以及風車旋 轉翼6的位置關係的示意圖。第3圖是將第2圖的局部剖 開的V視圖。第4圖是將第3圖的W部予以擴大顯示的 擴大側面圖。 在轉子頭4上，設置有可令風車旋轉翼6在風車旋轉 翼6的軸線中心C1外圍旋轉，從而改變風車旋轉翼6的 φ 傾角的傾角驅動裝置11，而且該傾角驅動裝置Π是以一 對一的關係對應於各風車旋轉翼6。 在傾角驅動裝置11係設置了 ：壓缸12、從壓缸12進 行伸縮的壓缸桿13、配置在轉子頭4與壓缸12之間的壓 缸軸承14、配置在風車旋轉翼6與壓缸桿13之間的壓缸 桿軸承15。 壓缸12是在内部配置了壓缸桿13的圓筒狀的構件， 藉由對其内部供給例如：油等的經過加壓的流體，而可將 壓缸桿13沿著壓缸12的軸線推出去或者抽拉進來。 -11 - 1352777 在壓缸12上設置有—對耳軸丨6，耳軸丨6是從壓缸 12圓筒面沿著風車旋轉翼6的軸線方向，也就是沿著z 軸線方向延伸的圓筒狀的構件。 • 壓缸12係與壓缸桿13 —起被配置成：在與風車旋轉 翼6的端面17略呈平行的平面，也就是，與χ_γ平面略 呈平行地延伸。 壓缸桿13是形成圓柱狀的構件，係與壓缸12的軸線 φ 略呈同—軸地配置’且被配置成可沿著該軸線進行直線移 動。 在壓缸桿13的前端係配置了壓缸桿軸承15。在端面 1 7則是與其軸線中心C丨隔著間隔而豎立設置著支柱1 8。 壓缸桿軸承15係可轉動地安裝在支柱18，用來吸收ζ軸 線外圍的轉動。 此外，壓缸桿軸承15係採用球面軸承的結構，亦可 採用可吸收圖中的X軸線、以及、γ軸線外圍的轉動的結 鲁 構。 壓缸軸承14係用來支承壓缸12的一對耳軸16的軸 承’將耳軸16支承成可在沿著風車旋轉翼6的軸線也就 是Ζ軸線延伸的內軸線L1外圍進行轉動。 如第4圖所示’壓缸軸承14係具備有：被固定在轉 子頭4上的托架19、被配置成包圍在耳軸16的外周面之 可轉動地支承該耳軸16的軸套20、被配置成包圍在軸套 2〇的外周面的防震橡膠（彈性支承構件）21、被配置在耳 軸16的外側端部的止推軸套（止推構件）23、設在止推 -12- 1352777 軸套23的外側之用來限制該止推軸套23的移動之蓋構件 24 〇 軸套20以及軸套支承構件21是構成本發明之用來支 承耳軸的支承部。 在托架19設有一個貫通孔25，用來讓耳軸16置入。 在貫通孔25的内周部’固定安裝著中空圓筒形狀的防震 橡膠21。在防震橡膠21的内側，固定安裝著具有凸緣部 的中空圓筒形狀的軸套20。 軸套20是銅合金製的，如第5圖所示，在其外周面 是略呈等間隔地在開設許多貫穿在厚度方向上的孔，且在 孔中埋入石墨26。 軸套20是用來置入耳軸16以將其支承成可以轉動。 此時’石墨26是可在軸套20與耳軸16之間，發揮作爲 潤滑劑的作用，所以可讓耳軸1 6平順地擺動。 防震橡膠21是在厚度方向的中間位置設置了橡膠層 27，隔著軸套20而將耳軸16予以彈性支承。 蓋構件24是被固定安裝在托架19上，用來覆蓋貫通 孔25的外側端。 止推軸套23則是被配置在耳軸16的外側端與蓋構件 24之間。 止推軸套23是被蓋構件24朝往耳軸16側推擠，具 有可抑制耳軸16之朝向內軸線L1的方向移動的功能。 至於發電設備7’係可舉出例如第1圖所示的這種設 置了 ：被傳遞來自轉子頭4的旋轉驅動力因而進行發電的 -13- 1352777 發電機、將發電機所發電的電力轉變成預定的電壓的變壓 器。 其次，槪略地說明由上述的結構所組成的風力發電裝 ' 置1的發電方法。 在風力發電裝置1中，當風從轉子頭4的旋轉軸線方 向吹抵達風車旋轉翼6時，風力將會被轉變成令轉子頭4 在旋轉軸線外圍旋轉的動力。 φ 這種轉子頭4的旋轉將被傳遞到發電設備7，在發電 設備7中進行發電，而該發電的電力是配合電力供給對象 的需求，例如是頻率爲5 0Hz或60Hz的交流電。 此處，至少在進行發電的期間內，想要讓風力有效率 地作用在風車旋轉翼6，可適度地令機臆3在水平面上進 行轉動，以使轉子頭4朝向上風方向。 其次，說明如何利用傾角驅動裝置1 1來控制風車旋 轉翼6的傾角。 # 如第2圖所示，傾角驅動裝置11係藉由將壓缸桿13 從壓缸12伸出來或拉進去，而可令風車旋轉翼6在軸線 中心C1的外圍轉動，從而改變其傾角。 例如··當壓缸桿13從壓缸12伸長的時候，因爲壓缸 桿13的端部是被固定在遠離風車旋轉翼6的軸線中心C1 的位置，因此’會對於風車旋轉翼6作用了令其在軸線外 圍進行旋轉的力量。 風車旋轉翼6在軸線中心ci外圍進行旋轉的話，係 如第2圖中的二點鏈線（假想線）所示般地，壓缸桿13 -14- 1352777 的前端位置會在端面17内進行移動，所以壓缸12以及壓 缸桿13會藉由壓缸軸承14而在內軸線li的外圍進行轉 動。也就是說，耳軸10會相對於軸套2〇進行轉動。 • 同時’在壓缸桿軸承15，壓缸桿13與風車旋轉翼6 係在與Z軸略呈平行的軸線外圍進行相對的轉動。 另外’當壓缸桿13被拉進壓缸12內的時候，也是與 上述情況同樣地’風車旋轉翼6會在軸線外圍進行轉動， φ 壓缸12以及壓缸桿13會藉由壓缸軸承14而在內軸線L1 的外圍進行轉動。 其次’說明要如何來吸收在本實施方式的特徵也就是 在傾角驅動裝置11中的風車旋轉翼6的根部與轉子頭4 之間的相對的變形。 例如：當風力很強而加諸在風車旋轉翼6的負荷變高 的時候’將會如第3圖中的二點鏈線（假想線）所示般地 ，在風車旋轉翼6的根部、轉子頭4等處將會產生變形。 • 這個時候，風車旋轉翼6的端面17將會產生朝向Y軸的 外圍旋轉的變形。 於是，壓缸12以及壓缸桿13 (也就是耳軸16)將會 以其軸線與內軸線L 1的交點（也就是假想的中心點C2 ) 作爲中心，朝向Y軸的外圍也就是朝向與內軸線L1交叉 的方向進行擺動。 這種擺動，是壓缸桿13的軸線與支柱18的軸線交叉 的點C3在中心點C2的外圍進行移動的範圍再±〇· 1度以 内的微小擺動。 -15- 1352777 這種耳軸16的移動將會因爲防震橡膠21的橡膠層27 受到壓縮而被吸收。亦即，耳軸16之想要產生移動的力 量將會被橡膠層27的彈性變形所吸收。 ' 是以，當風車旋轉翼6受到風力，因轉子頭4與風車 旋轉翼6的安裝部所產生的變形而作用在壓缸12以及壓 缸桿13身上的力量，將會被防震橡膠21的橡膠層27所 吸收，因此可防止壓缸12的油封部等的迅速磨損，從而 φ 可以防止傾角驅動裝置11的可靠性受損。 而且’只是在壓缸軸承14上，具備了可將耳軸16予 以彈性支承的防震橡膠21而已，因此與使用了兩組耳軸 的傾角驅動裝置比較之下，可使構造更簡化以及更小型化 ，製造成本更低廉。 又，當轉子頭4進行旋轉的話，壓缸12將會在轉子 頭4的軸線中心的外圍進行公轉。在其進行一圈公轉的期 間，壓缸12也會在本身的軸線中心的外圍旋轉—圈。 # 因此，如果在耳軸16或壓缸12與軸套20之間具有 間隙的話，耳軸1 6或壓缸1 2將會使得這個間隙產生週期 性的移動’所以耳軸16或壓缸12將會與軸套20產生週 期性的碰撞》 由於這種週期性的碰撞將會產生噪音，而且也會將碰 撞力量作用在耳軸16或壓缸12與軸套20之間。 這種現象在於沿著內軸線L1的方向上係更爲顯著， 因爲沿著內軸線L 1的方向上的間隙係較之與被軸套2 〇所 緊密支承的內軸線L1交叉的方向上的間隙更大。 -16- 1352777 根據本實施方式，耳軸16的外側端部是利用止推軸 套23來抑制其朝往外側的移動，因此，即使在耳軸i6( 壓缸1 2 )與壓缸軸承1 4之間具有間隙的時候，亦可抑制 ' 耳軸16(壓缸12)相對於壓缸軸承14朝往內軸線L1方 向的移動。 因此，可抑制隨著轉子頭4的旋轉所產生的耳軸16( 壓缸12)與壓缸軸承14的週期性的碰撞，所以既可抑制 φ 噪音的產生’又可提昇防震橡膠21的耐久性。 藉此，又可進一步地謀求緩和在組裝本實施方式的傾 角驅動裝置Π時之對於組裝公差（精度）上的要求。 此外，例如：當耳軸16(壓缸12)與壓缸軸承14之 間的間隙很小所以對於噪音等的影響很小的情況下，亦可 省略止推軸套23。 〔第2實施方式〕 φ 其次，佐以第6圖以及第7圖來説明本發明的第2實 施方式的風力發電裝置1。 本實施方式中的防震橡膠21的結構係與第一實施方 式的結構不同，因此，此處主要將針對這個差異的部分來 做説明’對於與前述第一實施方式相同的部分則省略其重 複的説明。 再者’與第一實施方式相同的構件都標示同一元件符 號。 本實施方式中，防震橡膠21的橡膠層27是做成：朝 -17- 1352777 向外側擴徑的圓錐台形狀》因此，橡膠層27的内周面（ 橡膠面）3 0是傾斜成朝外側擴徑。 在托架19上係設置了用來置入耳軸16的凹部28。止 推軸套23是安裝在凹部28的外側内周面。 耳軸16的外側端係做成：可構成球面的—部分之凸 彎曲形狀。止推軸套23的内面係做成：可與耳軸16的外 側端大致全面地接觸的凹彎曲形狀。藉此，即使耳軸16 以中心點C2作爲中心來進行擺動時，止推軸套23也不會 只是單邊地支承耳軸16的外側端，而是可略全面性地予 以支承，因此可穩定耳軸16的移動且加以抑制。 此外’止推軸套23係只要與耳軸16的外側端部的至 少一部分接觸即可，所以其内面形狀只要做成適當的形狀 即可。 這種結構的風力發電裝置1的發電方法、對於風車旋 轉翼6的傾角的控制以及要如何來吸收傾角驅動裝置i】 中的風車旋轉翼6的根部與轉子頭4之間的相對變形的方 法’都是與第1實施方式相同’所以此處就省略重複的説 明。 因爲在傾角驅動裝置11中的風車旋轉翼6的根部與 轉子頭4之間的相對變形的緣故，耳軸16將會以壓缸12 的軸線與內軸線L 1交叉的中心點C 2作爲中心，進行傾斜 地移動。 因此’耳軸16的外側端將會做最大的移動。換言之 ’耳軸1 6的移動，是由内側往外側逐漸變大。 -18- 1352777 所以從耳軸16作用到防震橡膠21的橡膠面30的力 量，是較之與內軸線L1正交的方向更往内側（壓缸12側 )傾斜。 因爲橡膠層27的内周面30是傾斜成往外側擴徑，所 以從耳軸16作用到橡膠層27的内周面30之朝向内側傾 斜的力量將會受到有効率的支承。 此外，朝向沿著橡膠層27的内周面30方向的分力變 小之故，可讓作用在防震橡膠21身上的剪力變小，從而 可提昇防震橡膠的耐久力。 再者，橡膠層27的内周面30的傾斜角的大小最好是 選定爲：對於因作用在壓缸的各種荷重所導致的耳軸16 上的合力的作用方向略呈正交的大小。 茲利用第7圖來説明對於這種角度的思考方法之一例 〇 中心點P是當耳軸16的荷重（力量）朝往軸套20( 防震橡膠21)作用時的假想的中心點。耳軸16將會因轉 子頭4與風車旋轉翼6的安裝部所產生的變形，而在γ軸 外圍，亦即，以中心點C2作爲中心而在Y軸外圍沿著軌 跡R進行旋轉。 當進行調整風車旋轉翼6的傾角時，轉子頭4與風車 旋轉翼6的安裝部將會產生變形。這種情況下，壓缸桿軸 承15的中心點S將會有：因壓缸12的推拉所產生的力量 FCy;以及因上述變形而欲使壓缸12以及壓缸桿13發生 撓曲的力量FM，作用於該處。 -19- 1352777 此時，耳軸16作用到防震橡膠21的力量Fg將會是 :因爲力量Fey致使耳軸16作用到防震橡膠21的力量 F1與因爲力量FM致使耳軸16作用到防震橡膠21的力量 F2相加起來的合力。 力量Fey是由兩個地方的耳軸16來承受，所以單— 個耳軸16作用到防震橡膠21的力量fi將變成FCy/2。 另外，如果中心點C2與中心點p之間的距離爲η，中心 Φ 點C2與中心點S之間的距離爲l的話，因爲力量fm致 使耳軸16作用到防震橡膠的力量Ρ2將變成FM( L/2H ) 。力里F2的作用方向將因爲耳軸16的傾斜而變成朝向内 側。 因此’力量Fg就變成FCy/2+FM(L/2H)。 力量Fg的作用方向係如第7圖所示般地，係較之與 內軸線L1正交的方向更往内側傾斜。 因此’橡膠層27的内周面30最好是傾斜成：朝向與 Φ 這個力量Fg的作用方向略正交的方向延伸。 此外，這種力量Fg的作用方向係當荷重狀態變化時 就會改變’因此，係可採用被推定的力量Fg的作用方向 的中間値’或者亦可採用被推定爲最高頻率的作用方向。 再者，内周面30亦可傾斜成：在軌跡R與内周面30 的交點之中，朝向與軌跡R正交的方向延伸。 此外’本發明並不限定於上述各實施方式，只要在不 脫離本發明的要旨的範圍内，當然都可以適度地改變。 -20- 1352777 【圖式簡單說明】 第1圖是顯示本發明的第1實施方式的風力發電裝置 的整體槪略結構的側面圖。 第2圖是用來說明第1圖的—個傾角驅動裝置以及風 車旋轉翼的位置關係的示意圖。 第3圖是將第2圖的局部剖開後的v視圖。 第4圖是將第3圖的W部擴大顯示的擴大側面圖。 弟5圖是顯不第4圖的軸套的結構的立體圖。 第6圖是將本發明的第2實施方式的風力發電裝置之 與第4圖相同部分予以局部剖開的擴大側面圖。 第7圖是用來說明第6圖的壓缸軸承上承受到因風車 旋轉翼等的變形而被加諸的力量的關係之示意圖。 【主要元件符號說明】 1 :風力發電裝置 4 :轉子頭 6 :風車旋轉翼 7 :發電設備 1 1 :傾角驅動裝置 12 :壓缸 1 3 :壓缸桿 14 :壓缸軸承 1 5 :壓缸桿軸承 1 6 :耳軸 -21 -1352777 IX. Description of the Invention [Technical Field] The present invention relates to a tilt driving device and a wind power generating device for a wind power generator. [Prior Art] A windmill used in a wind power generator includes a windmill in which the inclination angle φ of the wind turbine rotor is fixed, and a windmill in which the inclination angle is variable. The above-described mechanism for changing the inclination angle of the wind turbine rotor blade is, for example, a mechanism for converting the linear movement of the cylinder rod of the hydraulic cylinder into a rotation around the axis of the wind turbine rotor blade (for example, refer to Patent Document 1). In addition to the mechanism described in the above Patent Document 1, there is a tilt angle variable mechanism that uses a trunnion structure to rotatably support a hydraulic cylinder to a rotor head toward a periphery of a single shaft, and to end the end of the cylinder rod The wind turbine rotor can be rotatably supported on the periphery of a single shaft. # According to the variable angle mechanism, the hydraulic cylinder and the cylinder rod are held in a plane perpendicular to the axis of the rotor of the windmill, and are held to be rotatable about the trunnion structure. That is, the single shaft can be made. Swing motion. The end of the cylinder rod is held at a position away from the axis of the rotor of the windmill, so that the linear movement of the cylinder rod can be converted into the rotation of the periphery of the axis of the wind turbine rotor. [Patent Document 1] Japanese Unexamined Patent Application Publication No. Hei No. Hei No. Hei. For the reason that the stroke of the hydraulic cylinder and the cylinder rod becomes long, the structure of the mounting portion between the trunnion structure and the hydraulic cylinder is easily deformed, and thus is applied orthogonally to the rotation axis of the trunnion structure. The load on the periphery of the axis will be too much of a concern. In addition, due to the force acting on the large-sized wind turbine rotor, there is a possibility that the root of the wind turbine rotor and the rotor head itself may be deformed, so as to act on the periphery of the axis orthogonal to the rotation axis of the trunnion structure. The load will become too big a concern. If such a load becomes too large, the oil seal of the hydraulic cylinder will wear, the structural load imposed on the trunnion structure will also increase, and the long-term reliability of the tilt drive mechanism may be deteriorated. In addition to the above-described points, in the tilt drive mechanism, in order to prevent wear of the oil seal of the hydraulic cylinder, it is necessary to strictly require the parallelism of the wind turbine rotor with respect to the rotary surface, and when assembling the tilt drive mechanism # Be especially careful about this. It has been proposed that a mechanism for suppressing the above problem is to maintain a rotatable centering on the trunnion structure in a plane perpendicular to the axis of the windmill rotor, and in a plane parallel to the axis of the windmill rotor, It is also kept rotatable centering on the additional trunnion structure, in other words, it is made into a mechanism capable of biaxial oscillating motion. In doing so, the structure for supporting the hydraulic cylinder becomes complicated, so that the rotor head becomes large, and there is also a concern of increasing the cost. The present invention has been made in view of the above problems, and an object of the present invention is to provide a tilt driving device and a wind power generating device for a wind power generator that can prevent the reliability of the tilt driving device from being impaired by a simple and inexpensive structure of only -5 to 1352777. . In order to achieve the above object, the present invention provides the following means. A tilt driving device for a wind power generator according to a first aspect of the present invention includes: a cylinder that rotationally drives a wind turbine rotor on a periphery of a shaft to change an inclination of the wind turbine rotor, and rotatably supports the pressure from the pressure a cylinder bearing of a trunnion that extends slightly parallel to the axis of the windmill rotor; and a support portion of the cylinder bearing for supporting the trunnion is provided to elastically support the aforementioned An elastic support member of the trunnion. According to this aspect, the cylinder is rotatably supported by the cylinder bearing on the trunnion extending slightly parallel to the axis of the rotor of the wind turbine. In other words, the cylinder is rotatably supported on the periphery of the rotation axis which is slightly parallel to the axis of the wind turbine rotor. Thereby, the end portion of the cylinder rod that is expanded and contracted from the cylinder is supported at a position away from the axis of the wind turbine rotor blade, and therefore, the straight line # movement of the cylinder rod (the expansion and contraction of the cylinder rod) is converted into a windmill rotation. The rotation of the periphery of the wing's axis can thus change the inclination of the windmill's rotor, that is, its inclination can be adjusted. Here, 'the support portion for supporting the trunnion of the cylinder bearing is provided with an elastic support member that can elastically support the trunnion. Therefore, for example, when the wind turbine rotor is subjected to wind, the rotor head and the windmill rotate. The force generated by the deformation of the wing mounting portion acting on the cylinder (i.e., acting on the trunnion) in the direction intersecting the axis of the trunnion will be absorbed by the deformation of the elastic member. -6- 1352777 Therefore, the force acting in the direction in which the cylinder is deflected will be absorbed by the elastic member, thereby preventing rapid wear of the oil seal portion of the cylinder, and also preventing the reliability of the tilt driving device. Damaged. Moreover, only the support portion for supporting the trunnion of the cylinder bearing is provided with an elastic support member capable of elastically supporting the trunnion, so that the structure can be simplified as compared with a mechanism using two sets of trunnions. And miniaturization, the manufacturing cost β φ can be reduced. In the above aspect, the elastic supporting member can also adopt a structure in which an anti-vibration rubber is used. In doing so, due to the deformation of the rotor head and the mounting portion of the wind turbine rotor, the force acting on the cylinder (that is, acting on the trunnion) in the direction intersecting the axis of the trunnion will be due to the anti-vibration rubber. The deformation is absorbed. Therefore, it is possible to prevent rapid wear of the oil seal portion or the like of the pressure cylinder, and it is also possible to prevent the reliability of the inclination driving device from being impaired. In the above configuration, the rubber surface of the anti-vibration rubber may be formed as follows: • Tilt to expand outward toward the outside. Because of the deformation of the rotor head and the mounting portion of the windmill rotor, the trunnion will move in such a way that the center of the axis of the trunnion becomes inclined, so that the outer end of the trunnion will move to the maximum extent. In other words, the movement of the trunnion gradually increases from the inside toward the outside. Therefore, the force acting from the trunnion to the rubber surface of the anti-vibration rubber is inclined more toward the inner side than the direction orthogonal to the axis of the trunnion. Since the rubber surface of the anti-vibration rubber is inclined to expand outward toward the outside, it is possible to effectively support the strength of the inclined surface of the rubber surface which is applied from the trunnion to the anti-vibration rubber to the inner side by 1352777. Further, since the component force in the direction along the rubber surface of the anti-vibration rubber becomes small, the shearing force acting on the anti-vibration rubber can be made small, and the durability of the anti-vibration rubber can be improved. Further, the magnitude of the inclination angle of the rubber surface of the anti-vibration rubber is preferably selected to be substantially orthogonal to the direction of action of the resultant force against the trunn by the various loads acting on the cylinder. The direction of action of this resultant force changes with the change of the load state, so that the imaginary resultant force can be used as the middle 値 of the direction of the φ, or the action direction of the imaginary maximum frequency can be used in the above-mentioned aspect. Preferably, the outer end portion of the trunnion is restrained from moving outward by a thrust member. The cylinder revolves around the center of the axis of the rotor head as the rotor head rotates. Therefore, during this rotation, the cylinder also rotates once around its own axis. Therefore, if there is a gap between the trunnion and the cylinder bearing, the cylinder (trunnion) will cause the clearance to produce a circumferential Φ movement, so the trunnion and the cylinder bearing will have a periodic collision. The periodic collision of the trunnion with the cylinder bearing will generate noise, and the collision force acts on the elastic member. This phenomenon is more remarkable in the axial direction of the trunnion because the gap in the axial direction of the trunnion is larger than the gap in the direction intersecting the direction of the axis closely supported by the support portion. According to this aspect, the outer end portion of the trunnion is restrained from moving to the outside by the thrust member, so that the trunnion can be suppressed even if there is a gap between the trunnion (cylinder) and the cylinder bearing -8 - 1352777 ( The pressure cylinder is moved relative to the cylinder bearing toward the axis of the cylinder bearing. Therefore, it is possible to suppress the periodic collision between the trunnion and the cylinder bearing due to the rotation of the rotor head, so that the generation of "noise" can be suppressed and the durability of the elastic member can be improved. A wind turbine generator according to a second aspect of the present invention includes: a plurality of wind turbine rotors for receiving wind power; and the wind turbine rotor is rotatably supported on a periphery of an axis of the wind turbine rotor, and is The wind turbine is a rotor head that is rotatably driven by a rotary wing, and the tilting drive device according to any one of the above claims, wherein the power generating device that generates power by the rotation of the rotor head is used. According to this aspect, the inclination driving device according to the first aspect described above can prevent the reliability of the inclination driving device from being impaired, so that the reliability of the wind power generating device can be prevented from being impaired. According to the present invention, since the bearing portion for supporting the trunnion of the cylinder bearing is provided with the elastic supporting member for elastically supporting the trunnion, the force in the direction in which the cylinder is deflected can be Absorbed by the elastic member. Thereby, the reliability of the tilt driving device can be prevented from being impaired. Further, since only the support portion for supporting the trunnion of the cylinder bearing is provided with the elastic support member capable of elastically supporting the trunnion, the structure can be made more in comparison with the inclination driving device having the two sets of trunnions. To simplify and miniaturize, manufacturing costs can be reduced. [Embodiment] [Best Embodiment of the Invention] -9- 1352777 The embodiment of the present invention will be described below with reference to the drawings. [First Embodiment] A wind power generator according to a first embodiment of the present invention will be described with reference to Figs. 1 to 5 . Fig. 1 is a side view showing the overall schematic configuration of the wind turbine generator 1 of the present embodiment. The φ wind turbine generator 1 is used for wind power generation as shown in Fig. 1. The wind power generator 1 is provided with a strut 2 erected on the foundation B, a nacelle 3 provided at the upper end of the strut 2, and a rotor head 4 provided in the nacelle 3 which is rotatable about a slightly horizontal axis. The head pack 5 of the rotor head 4 is covered, and a plurality of wind turbine rotor blades 6 radially attached to the periphery of the rotation axis of the rotor head 4 and a power generating device 7 for generating electric power by the rotation of the rotor head 4 are provided. As shown in Fig. 1, the pillar 2 has a columnar structure extending upward from the base B (the upper side of Fig. 1), and for example, a structure in which a plurality of units are connected in the vertical direction. A nacelle 3 is provided at the uppermost portion of the strut 2. If the strut 2 is composed of a plurality of units, the nacelle 3 is disposed on the unit disposed at the uppermost portion. The nacelle 3 supports the rotor head 4 so as to be rotatable as shown in Fig. 1, and houses therein a power generating device 7 that generates electric power by the rotation of the rotor head 4. On the rotor head 4, a plurality of wind turbine rotating blades 6 of -10- 1352777 are radially mounted on the periphery of the rotation axis thereof, and the periphery of the rotor head 4 is covered by the head sealing member 5. In this way, if the wind blows from the direction of the rotation axis of the rotor head 4 to the 'windmill rotor blade 6, the wind turbine rotor 6 generates a force for rotating the rotor head 4 around the rotation axis, and the rotor head 4 is rotated. drive. Further, although the present embodiment has been described as being applied to the case where three wind turbine rotor blades 6 are provided, the number of wind turbine rotor blades 6 is not limited to three, and may be applied to two or three. The situation of more films is not particularly limited. Fig. 2 is a schematic view for explaining the positional relationship between a tilt driving device 11 and a windmill rotating blade 6. Fig. 3 is a V-sectional view partially broken away from Fig. 2. Fig. 4 is an enlarged side elevational view showing the W portion of Fig. 3 enlarged. On the rotor head 4, a tilt driving device 11 for rotating the wind turbine rotor 6 around the axis center C1 of the windmill rotor 6 to change the φ tilt angle of the wind turbine rotor 6 is provided, and the tilt driving device is The relationship of one to one corresponds to each of the wind turbine rotor blades 6. The tilt driving device 11 is provided with a cylinder 12, a cylinder rod 13 that expands and contracts from the cylinder 12, a cylinder bearing 14 disposed between the rotor head 4 and the cylinder 12, and a rotor rotating shaft 6 and pressure. Cylinder rod bearing 15 between the cylinder rods 13. The cylinder 12 is a cylindrical member in which the cylinder rod 13 is disposed, and the cylinder rod 13 can be placed along the axis of the cylinder 12 by supplying a pressurized fluid such as oil to the inside thereof. Push it out or pull it in. -11 - 1352777 The cylinder 12 is provided with a pair of trunnion 丨 6 which is a circle extending from the cylindrical surface of the cylinder 12 along the axis of the wind turbine rotor 6, that is, a circle extending along the z-axis. A tubular member. • The cylinder 12 is arranged, together with the cylinder rod 13, to be arranged in a plane substantially parallel to the end face 17 of the wind turbine rotor 6, i.e., extending parallel to the χ_γ plane. The cylinder rod 13 is a member which is formed in a cylindrical shape and is disposed so as to be axially aligned with the axis φ of the cylinder 12 and is arranged to be linearly movable along the axis. A cylinder rod bearing 15 is disposed at the front end of the cylinder rod 13. At the end face 17, the strut 18 is erected at intervals from the center of the axis C. A cylinder rod bearing 15 is rotatably mounted to the strut 18 for absorbing the rotation of the periphery of the crucible shaft. Further, the cylinder rod bearing 15 is constructed by a spherical bearing, and can also adopt a structure in which the X-axis in the absorption view and the rotation of the periphery of the γ-axis are used. The cylinder bearing 14 is a bearing for supporting a pair of trunnions 16 of the cylinder 12, and supports the trunnion 16 so as to be rotatable about the periphery of the inner axis L1 extending along the axis of the wind turbine rotor 6 and the crucible axis. As shown in Fig. 4, the "cylinder bearing 14" is provided with a bracket 19 fixed to the rotor head 4, and a sleeve rotatably supporting the trunnion 16 so as to surround the outer peripheral surface of the trunnion 16 20. An anti-vibration rubber (elastic support member) 21 that is disposed to surround the outer peripheral surface of the boss 2〇, a thrust bushing (thrust member) 23 disposed at an outer end portion of the trunnion 16 , and a thrust stop -12- 1352777 The cover member 24 for restricting the movement of the thrust collar 23 on the outer side of the sleeve 23, the sleeve 20 and the sleeve support member 21 are the support portions for supporting the trunnion of the present invention. A through hole 25 is provided in the bracket 19 for placing the trunnion 16 therein. A hollow cylindrical anti-vibration rubber 21 is fixedly attached to the inner peripheral portion of the through hole 25. Inside the anti-vibration rubber 21, a hollow cylindrical boss 20 having a flange portion is fixedly attached. The bushing 20 is made of a copper alloy. As shown in Fig. 5, a plurality of holes penetrating in the thickness direction are formed at substantially equal intervals on the outer peripheral surface thereof, and graphite 26 is buried in the holes. The sleeve 20 is for insertion into the trunnion 16 to support it for rotation. At this time, the graphite 26 functions as a lubricant between the sleeve 20 and the trunnion 16, so that the trunnion 16 can be smoothly swung. The anti-vibration rubber 21 is provided with a rubber layer 27 at an intermediate position in the thickness direction, and the trunnion 16 is elastically supported via the boss 20. The cover member 24 is fixedly mounted on the bracket 19 to cover the outer end of the through hole 25. The thrust collar 23 is disposed between the outer end of the trunnion 16 and the cover member 24. The thrust collar 23 is pushed by the cover member 24 toward the trunnion 16 side, and has a function of suppressing the movement of the trunnion 16 in the direction of the inner axis L1. As for the power generating apparatus 7', for example, a 133-1352777 generator in which the rotational driving force from the rotor head 4 is transmitted and the power generated by the generator is converted, for example, is shown. A transformer that is a predetermined voltage. Next, a power generation method of the wind power generation device 1 composed of the above-described structure will be briefly described. In the wind power generator 1, when wind is blown from the rotation axis of the rotor head 4 to the wind turbine rotor 6, the wind force is converted into power for rotating the rotor head 4 around the rotation axis. The rotation of the rotor head 4 of this kind is transmitted to the power generating apparatus 7, and power generation is performed in the power generating apparatus 7, and the power generated by the power is matched with the demand of the power supply target, for example, an alternating current having a frequency of 50 Hz or 60 Hz. Here, at least during the period in which power generation is performed, it is desired to cause the wind to efficiently act on the wind turbine rotor blade 6, and the casing 3 can be appropriately rotated on the horizontal surface so that the rotor head 4 faces the windward direction. Next, it is explained how to use the tilt driving device 1 1 to control the inclination of the wind turbine rotor blade 6. # As shown in Fig. 2, the tilt driving device 11 rotates the wind turbine rotor 6 around the center of the axis C1 by extending or pulling the cylinder rod 13 from the cylinder 12, thereby changing its inclination. For example, when the cylinder rod 13 is extended from the cylinder 12, since the end portion of the cylinder rod 13 is fixed at a position away from the center C1 of the axis of the wind turbine rotor blade 6, it acts on the wind turbine rotor blade 6. The force that causes it to rotate around the axis. When the windmill rotor 6 rotates around the center of the axis ci, the front end position of the cylinder rod 13 - 14 - 1352777 is performed in the end face 17 as shown by the two-dot chain line (hypothetical line) in Fig. 2 . Moving, the cylinder 12 and the cylinder rod 13 are rotated by the cylinder bearing 14 at the periphery of the inner shaft li. That is, the trunnion 10 will rotate relative to the sleeve 2〇. • At the same time, in the cylinder rod bearing 15, the cylinder rod 13 and the wind turbine rotor 6 are relatively rotated around the axis parallel to the Z-axis. In addition, when the cylinder rod 13 is pulled into the cylinder 12, as in the above case, the windmill rotor 6 will rotate around the axis, and the φ cylinder 12 and the cylinder rod 13 will be driven by the cylinder bearing. 14 is rotated around the outer axis L1. Next, it is explained how to absorb the relative deformation between the root of the wind turbine rotor 6 and the rotor head 4 in the feature of the present embodiment, that is, in the pitch driving device 11. For example, when the wind is strong and the load applied to the wind turbine rotor 6 becomes high, it will be at the root of the wind turbine rotor wing 6 as shown by the two-point chain line (imaginary line) in Fig. 3 . Deformation will occur at the rotor head 4 and the like. • At this time, the end face 17 of the windmill rotor 6 will produce a deformation that rotates toward the periphery of the Y-axis. Thus, the cylinder 12 and the cylinder rod 13 (i.e., the trunnion 16) will center with the intersection of its axis and the inner axis L1 (i.e., the imaginary center point C2) toward the periphery of the Y-axis, that is, toward the The direction in which the inner axis L1 intersects is swung. This swing is a slight swing within a range in which the point C3 at which the axis of the cylinder rod 13 intersects with the axis of the strut 18 moves outside the center point C2 by ±1·1. -15- 1352777 The movement of the trunnion 16 will be absorbed because the rubber layer 27 of the anti-vibration rubber 21 is compressed. That is, the amount of force of the trunnion 16 intended to cause movement will be absorbed by the elastic deformation of the rubber layer 27. 'When the wind turbine rotor 6 receives wind, the force acting on the cylinder 12 and the cylinder rod 13 due to the deformation of the rotor head 4 and the mounting portion of the wind turbine rotor 6 will be the anti-vibration rubber 21 Since the rubber layer 27 is absorbed, rapid wear of the oil seal portion or the like of the cylinder 12 can be prevented, and φ can prevent the reliability of the inclination driving device 11 from being impaired. Further, 'only the anti-vibration rubber 21 for elastically supporting the trunnion 16 is provided on the cylinder bearing 14, so that the structure can be simplified and made smaller as compared with the inclination driving device using the two sets of trunnions. It is cheaper to manufacture. Further, when the rotor head 4 is rotated, the cylinder 12 will revolve around the periphery of the center of the axis of the rotor head 4. During its revolution, the cylinder 12 also rotates around the center of its own axis. # Therefore, if there is a gap between the trunnion 16 or the cylinder 12 and the sleeve 20, the trunnion 16 or the cylinder 12 will cause periodic movement of this gap 'so the trunnion 16 or the cylinder 12 A periodic collision will occur with the sleeve 20. This periodic collision will generate noise and will also exert a collision force between the trunnion 16 or the cylinder 12 and the sleeve 20. This phenomenon is more pronounced in the direction along the inner axis L1 because the gap in the direction along the inner axis L 1 is in a direction crossing the inner axis L1 which is tightly supported by the bushing 2 的The gap is larger. -16- 1352777 According to the present embodiment, the outer end portion of the trunnion 16 is restrained from moving outward by the thrust boss 23, and therefore, even in the trunnion i6 (cylinder 12) and the cylinder bearing 1 When there is a gap between the four, the movement of the trunnion 16 (cylinder 12) with respect to the cylinder bearing 14 in the direction of the inner axis L1 can be suppressed. Therefore, the periodic collision of the trunnion 16 (cylinder 12) with the cylinder bearing 14 due to the rotation of the rotor head 4 can be suppressed, so that the generation of φ noise can be suppressed, and the durability of the anti-vibration rubber 21 can be improved. Sex. Thereby, it is possible to further alleviate the requirements for assembly tolerance (accuracy) when assembling the tilt drive device of the present embodiment. Further, for example, when the gap between the trunnion 16 (pressure cylinder 12) and the cylinder bearing 14 is small and the influence on noise or the like is small, the thrust collar 23 may be omitted. [Second Embodiment] φ Next, a wind power generator 1 according to a second embodiment of the present invention will be described with reference to Figs. 6 and 7 . The structure of the anti-vibration rubber 21 in the present embodiment is different from that of the first embodiment. Therefore, the portion for this difference will be mainly explained here. 'The same portions as those of the first embodiment are omitted. Description. Further, the same members as those of the first embodiment are denoted by the same component symbol. In the present embodiment, the rubber layer 27 of the anti-vibration rubber 21 is formed into a truncated cone shape that expands outward toward -17 to 1352777. Therefore, the inner peripheral surface (rubber surface) 30 of the rubber layer 27 is inclined outward. Expand the diameter. A recess 28 for inserting the trunnion 16 is provided on the bracket 19. The thrust collar 23 is attached to the outer inner peripheral surface of the recess 28. The outer end of the trunnion 16 is formed into a convex curved shape which can constitute a spherical surface. The inner surface of the thrust collar 23 is formed in a concavely curved shape that is substantially in full contact with the outer end of the trunnion 16. Thereby, even if the trunnion 16 is swung with the center point C2 as the center, the thrust collar 23 does not support the outer end of the trunnion 16 unilaterally, but can be supported in a slightly comprehensive manner, and thus can be supported. The movement of the trunnion 16 is stabilized and suppressed. Further, the thrust bushing 23 is only required to be in contact with at least a part of the outer end portion of the trunnion 16, and therefore the inner surface shape may be an appropriate shape. The power generation method of the wind turbine generator 1 having such a configuration, the control of the inclination of the wind turbine rotor blade 6, and the method of how to absorb the relative deformation between the root portion of the wind turbine rotor blade 6 and the rotor head 4 in the pitch drive device i] 'Es are the same as in the first embodiment', and thus the overlapping description will be omitted here. Because of the relative deformation between the root of the windmill rotor 6 and the rotor head 4 in the pitch driving device 11, the trunnion 16 will center on the center point C 2 at which the axis of the cylinder 12 intersects the inner axis L1. , move it obliquely. Therefore, the outer end of the trunnion 16 will make the greatest movement. In other words, the movement of the trunnion 16 is gradually increased from the inside to the outside. -18- 1352777 Therefore, the force applied from the trunnion 16 to the rubber surface 30 of the anti-vibration rubber 21 is inclined toward the inner side (the side of the pressure cylinder 12) in the direction orthogonal to the inner axis L1. Since the inner peripheral surface 30 of the rubber layer 27 is inclined to expand outward, the force which is inclined from the trunnion 16 to the inner peripheral surface 30 of the rubber layer 27 toward the inner side is efficiently supported. Further, since the component force in the direction along the inner circumferential surface 30 of the rubber layer 27 becomes small, the shearing force acting on the anti-vibration rubber 21 can be made small, and the durability of the anti-vibration rubber can be improved. Further, it is preferable that the inclination angle of the inner peripheral surface 30 of the rubber layer 27 is selected such that the direction of action of the resultant force on the trunnion 16 due to the various loads acting on the cylinder is slightly orthogonal. An example of a method of thinking about such an angle is described with reference to Fig. 7. The center point P is an imaginary center point when the load (force) of the trunnion 16 acts toward the sleeve 20 (anti-vibration rubber 21). The trunnion 16 will be rotated along the track R on the periphery of the y-axis, that is, around the center point C2 and around the periphery of the Y-axis, due to deformation of the rotor head 4 and the mounting portion of the windmill rotor 6. When the inclination of the wind turbine rotor 6 is adjusted, the mounting portion of the rotor head 4 and the wind turbine rotor 6 will be deformed. In this case, the center point S of the cylinder rod bearing 15 will have a force FCy due to the pushing and pulling of the cylinder 12, and the force to deflect the cylinder 12 and the cylinder rod 13 due to the above deformation. FM, acting on it. -19- 1352777 At this time, the force Fg of the trunnion 16 acting on the anti-vibration rubber 21 will be: because the force Fey causes the trunnion 16 to act on the force F1 of the anti-vibration rubber 21 and the force FM causes the trunnion 16 to act on the anti-vibration rubber 21 The force of F2 adds up together. The force Fey is received by the trunnions 16 of the two places, so the force fi of the single trunnion 16 acting on the anti-vibration rubber 21 will become FCy/2. In addition, if the distance between the center point C2 and the center point p is η, and the distance between the center Φ point C2 and the center point S is 1, since the force fm causes the force of the trunnion 16 to act on the anti-vibration rubber Ρ 2 will become FM (L/2H). The direction of action of the force F2 will become inward toward the side due to the inclination of the trunnion 16. Therefore, the force Fg becomes FCy/2+FM (L/2H). The direction of action of the force Fg is inclined more inward than the direction orthogonal to the inner axis L1 as shown in Fig. 7. Therefore, the inner peripheral surface 30 of the rubber layer 27 is preferably inclined so as to extend in a direction slightly orthogonal to the direction of action of the force Fg of Φ. Further, the direction of action of this force Fg changes when the load state changes. Therefore, the intermediate 値 of the direction of action of the estimated force Fg can be used or the direction of action estimated to be the highest frequency can be employed. Further, the inner circumferential surface 30 may be inclined so as to extend in a direction orthogonal to the trajectory R among the intersections of the trajectory R and the inner circumferential surface 30. Further, the present invention is not limited to the above-described embodiments, and may be appropriately changed as long as it does not deviate from the gist of the invention. -20- 1352777 [Brief Description of the Drawings] Fig. 1 is a side view showing the overall schematic configuration of a wind turbine generator according to a first embodiment of the present invention. Fig. 2 is a schematic view for explaining the positional relationship between the inclination driving device and the rotor of the wind turbine of Fig. 1. Fig. 3 is a view showing a part of Fig. 2 taken along the line v. Fig. 4 is an enlarged side view showing an enlarged display of a portion W of Fig. 3. Figure 5 is a perspective view showing the structure of the bushing of Fig. 4. Fig. 6 is an enlarged side elevational view, partially broken away, of the same portion of the wind turbine generator according to the second embodiment of the present invention. Fig. 7 is a schematic view for explaining the relationship between the force applied to the cylinder bearing of Fig. 6 by the deformation of the rotor or the like of the windmill. [Description of main component symbols] 1 : Wind power generation device 4 : Rotor head 6 : Wind turbine rotor blade 7 : Power generation equipment 1 1 : Inclination drive device 12 : Pressure cylinder 1 3 : Cylinder rod 14 : Cylinder bearing 1 5 : Pressure cylinder Rod bearing 1 6 : trunnion - 21