201105858 六、發明說明： 【發明所屬之技術領域】 本發明係關於風力發電裝置及其組裳方 ^ 、 尤其係關於 風力發電裝置之主軸與發電機轉子的結合結構。 【先如技術】 風力發電裝置之設計中’主軸與發電機轉子之έ…士構 之最適化為重要之設計項目之_。主轴與發電機轉=有 必要以必要之強度結合。另一方面，如發電機引起短路 時，在主軸與發電機轉子間產生過多轉矩之情形下，較好 的是連結成使之亦可作相對運動。 作為主軸與發電機轉子之結合結構，公知之結構之一種 為’將發電機轉子之轉子板連結於筒狀之套筒，而將該套 筒藉由收縮安裝（收縮碟）緊固連結之方法。該結構容易調 節主軸與發電機轉子之結合強度，且由於藉由一般可取得 之收縮安裝可將發電機轉子連結於主轴，因此較好的是亦 可降低成本。 用套筒與收縮安裝將主軸與發電機轉子結合之結構，例 =係記载於國際公開冊彻簡/111425 αι(專利文㈣ —。專利文獻1揭示了藉由收縮碟（相當於本申㈣之收縮 安：)將接合有發電機轉子之轉子轴承(相當於本申請案之 套同)緊固於主軸之結合結構。該結合結構中，收縮碟係 位於發电機與轴承之間，而於該位置將轉子轴承緊固於主 轴。該收縮碟係由固定碟與可動碟構成，而該固定碟與可 動碟係藉由螺拴連結。螺栓係平行於主軸之中心抽而搞 142403.doc 201105858 入。:螺检被擰緊時，可動碟會壓抵於固定碟而使收縮碟 之内控縮小，而將轉子軸承緊固於主轴。 如此之結合結構之其—胡 、 為，支撐主軸之軸承與發電 曰’隔增大。如上所述，專利文獻(之結合結構中由 於收縮碟位於發電機與軸承之間，且螺栓於平行於絲之 方向***，因此有必要於發電機與轴承之間確保用以緊固 螺栓之作業空間。由此將增大發電機與轴承之間隔。若發 電機與轴承之間隔增大，將增大主軸之弯曲度而使振” X障形由於會增大機械負荷而成為不利因素。發電機 與軸承之間隔增大亦會導致主轴之長度增大之問題。主轴 之長度增大時，將增加主軸之成本。 發電機與轴承之間隔增大的問題，尤其對於直接驅動式 風力發電裝置尤為嚴重。未使用增速機之直接驅動式風力 i置’有必要增大定子極數及轉子極數，因此發電機 之重1有增大之傾向。該情形下若袖承與發電機之距離辦 大，則主轴之弯曲度將更加增大，因而會成為振動增大^ 原因。 [專利文獻1]國際公開冊wo 2007/1 11425 A1 【發明内容】 因此’本發明之目的在於提供—種可縮短支撐主抽之轴 承與發電機之間隔的主軸與發電機轉子的結合結構。 本發明之其-觀點之風力發電裝置，係具備·支撐風車 轉子之主轴，可旋轉地支擇主軸之主軸承；具備發電機轉 子與定子之發電機；與發電機轉子結合且***主軸之套 142403.doc 201105858 二人及油壓收縮安裝’其設於套筒之外側，且將套筒緊固 結合於主軸。油壓收縮安裝係構造成藉由動作流體之供給 使内徑縮小而將套筒緊固於主轴。 —油壓收縮安裝係可設於各個位置。較好的是，油壓收縮 女裝係設於發電機之内部空間。 例如（子具備.定子磁極，其排列配置於主軸之周方 向’及第1及第2定子板’其支撐上述定子磁極，且排列於 主軸之軸方向，且，第！ ^子板與主軸藉由第^發電機轴承 可相對旋轉，而第2定子板與主轴藉由第2發電機軸承可相 對旋轉，X，在發電機轉子具備排列配置於主轴之周方向 的轉子磁極、及設於第j定子板與第2定子板之間用以支撐 轉子磁極之轉子支樓構件的情形下，油壓收縮安裝亦可設 於轉子支撐構件與第1定子板之間。 匕τ較好的是，於第1定子板上，於對應油壓收縮安 ^ 1置°又有開口，其係用以將動作流體供給於油壓收縮 女裝。e亥情形’較好的是，緊固油壓收縮安裝之順序包 括·於第1定子板上所設之開口***臨時保護筒，以使油 壓收縮女裝之孔位於臨時保護筒之内部的步驟，·於臨時保 遵筒之内部將油壓配管連接於孔的步驟；及經由油壓配管 將動作流體供給於油壓收縮安裝，而以油壓收縮安裝將套 筒緊固於主軸的步驟。 又，亦可於套筒之抵接油壓收縮安裝的部分設有縫隙。 取代之，亦可將套筒於抵接油壓收縮安裝之位置予以分 割。具體之為’較好的《，套筒具備排列配置於主軸之軸 142403.doc 201105858 :向的第!及第2套筒構件，且，於 複數之第L其排列設於主軸之周方== =!Γ於第2套筒構件之端設有複數之第2突出部， 八排列…軸之周方向且突出 =突出部分別***於複數之第2突出部中=之= 5設Γ收縮安裝係以抵接於第1突出部及第2突出部之 轉=:另—觀點之風力發電裝置，係具備:支撐風車 Π 旋轉地支撐主軸之主軸承;具備發電機轉 子，、疋子之發電機；與發電機轉子結合且插 ===與主軸之間之油㈣安裝。油壓收縮安 與主轴2根據動作流體之供給使外徑增大而將套筒 :::發電裝置中’定子具備：相對主轴於周方向排列 之第^子2麵’·及支料子磁極且排列於主軸之財向 軸承可相對第1定子板ί主轴藉由第1發電機 Μ # 2疋子板與主轴藉由第2發電機軸承可 之半'，方。該情形’較好的是，油塵收縮安裝係設於主轴 向上不與第1及第2發電機軸承相對之位置。 及又’較好的是構造成，使套筒之設置第1及第2發電機軸 :之位置與抵接於油厂堅收縮安裝之位置之間的部分吸從由 ;油壓收縮安裝之緊固而產生之變形。 根據本發明’可提供一種能縮短發電機與軸承之間隔之 主轴與發電機轉子的結合結構。 142403.doc 201105858 【實施方式】 (第1實施形態） 圖1係本發明之第丨實施形態之風力發電裝置丨之構成的 概略概念圖。本實施形態之風力發電裝置丨具備：塔2、機 搶台板3、主軸4、軸承5、6 '軸承台7、8、及發電機9。 機艙台板3係以可偏航旋轉而載置於塔2之上端。主軸*係 藉由2個軸承5、6而被可旋轉地支撐，軸承5、6藉由軸承 台7、8而固定於機艙台板3。主軸4之一端接合有風車轉子 (未圖示）’而另一端連結有發電機9之轉子。本實施形態之 風力發電裝置It ’主軸4係共用於風車轉子與發電機轉 子，且本實施形態之風力發電裝置丨係作為所謂直接驅動 式風力發電裝置而構成。 圖2A係詳細顯示發電機9附近之風力發電裝置丨之結構， 尤其係發電機9之結構、發電機9與主軸4之結合結構的剖 面圖。 發电機9具備發電機轉子丨丨與定子12。發電機轉子η具 備場磁鐵13(轉子磁極）、支撐場磁鐵13之後板14 '及支撐 後板14之轉子板15、16。定子12具備定子卷線（定子磁 極）17及支樓疋子卷線17之定子板18、19。定子12係藉 由未圖示之支撐機構而連結固定於機艙台板3。 於軸承6朝主軸4之固定上使用了軸承固定構件2〇a、 20b。詳細之為’於主軸4***有軸承固定環2〇a、2〇b，軸 承6係夾於軸承固定環2〇a、20b而固定於主軸4。 另一方面，於發電機轉子11朝主轴4之固定上使用了套 142403.doc 201105858 筒2 1與油壓收縮安裝25。詳細之為，發電機轉子11之轉子 板15、16係藉由螺栓而固定於設於套筒21上的凸緣2ia、 21b。再者，套筒21係藉由油壓收縮安裝25而緊固固定於 主軸4 ^圖2B係顯示油壓收縮安裝25之結構之例的到面 圖。油壓收縮安裝25 ,如圖2B所示，具備固定環％、可動 環27、支撐環28、及環形螺母29。可動環27上設有緊固孔 30a與解除孔3〇b。若於緊固孔3〇a供給動作流體（典型之為 動作油）’則可動環27向箭頭A之方向移動而抵壓於固定環 26藉此，固定環26之内徑（即油壓收縮安裝25之内徑）縮 小’套筒21緊固於主軸4。藉由結合於發電機轉子^之套 筒21緊固於主軸4，而使得發電機轉子11固定於主軸4。如 後述，為將套筒2丨緊固於主軸4，使用油壓收縮安裝U於 本實施形態中係為重要β另一方面，若於解除孔3〇b供給 動作机肢，則可動環27向箭頭B之方向移動而解除緊固。 再次參照圖2A，另，使用端板22係用以防止套筒21向軸 方向（與主軸4之中心線平行之方向。以下亦相同）變位。詳 、屈之為為板22係跨套筒21之端與主軸4之端而安裝，套 筒21係夾於軸承固定環2〇b與端板22。藉此抑制套筒2〗向 軸方向移動。 又，定子12之定子板18、19上設有發電機軸承23、24， 而主軸4及套筒21經由發電機軸承23、24支撐定子板丨8 ' 19。藉由發電機軸承23、24，主軸4及套筒η可相對於定 子板18、19旋轉。該結構對於分散發電機9之重量所致之 機械負荷較為有效。 142403.doc 201105858 另，圖2A中，作為支撐場磁鐵13及後板14之支撐構件使 了轉子板15 16，然而支禮·場磁鐵13及後板14之結構可 予以各種更改。例如，如圖3A所示，作為支撐場磁鐵13及 後板14之支撐構件，亦可使用丨片之轉子板l5A、與接合於 後板14與轉子板15A之補強肋31、32。又，如圖3β所示， 亦可使用圓錐狀之轉子板15B。再者，如圖3C所示，亦可 使用轉子板15C、與—端接合於後板14，@另—端接合於 轉子板15C之兩方的補強臂15〇。 本實施形態之風力發電裝置1之結構的優點為，藉由用 油S收縮安裝25固定套筒21，可縮短軸承6與發電機9之間 的距離。使用藉由動作流體而動作之油壓收縮安裝25之情 2 ’（異於使用螺拴之收縮安裝）無必要於軸承6與油壓收縮 安^ 25之間設置用以實施緊固油壓收縮安裝25之作業的作 業空間。如此可縮短軸承6與發電機9之間的距離。如上 述、’轴承6與發電機9之間之距離的縮短可有效於機械負荷 之減乂與主軸長度之縮短。此時，作為油壓收縮安裝25， 右使用接$動作流體之孔係以將動作流體供給於主抽4之 半位方向而構成者，更有利於軸承6與發電機9之間之距離 的縮短化。 2處’圖2A之結構中’油壓收縮安裝25係位於轴承轉 ，電機9之間’然而油壓收縮安裝25亦可設於發電機9之内 字’由C收縮安裝25設於發電機9之内部係由於具有可 更加縮短轴承6與發電機9之間之距離的優點。〃 例如，如圖4所示，亦可將油壓收縮安裝25設於軸承6之 142403.doc 201105858 側之定子板18與轉子板15之間。又，如圖5所示，又可將 油壓收縮安裝25設於轉子板15與16之間。再者，如圖6所 示，還可將油壓收縮安裝25設於轉子板16與定子板N之 間。 由縮短轴承6與發電機9之間之距離的觀點，如圖7所 示，還可將油壓收縮安裝25設於發電機9與主軸4之端之間 的位置。 又，如圖8A、圖8B所示，複數之油壓收縮安裝可使用 於將套筒21緊固於主軸4。圖以中，油壓收縮安裝2认係 設於發電機9與主軸4之端之間的位置，而油壓收縮安裝 25B係设於發電機9與軸承6之間的位置。另一方面，圖 中，2個油壓收縮安裝25人、25B皆係設於發電機9之内 部。具體之為，油壓收縮安裝25A係設於定子板19與轉子 板16之間，而油壓收縮安裝25B係設於定子板“與轉子板 16之間。 在油壓收縮安裝25係設於發電機9内部之情形下，有必 要進行於油壓收縮安裝25供給作業流體等，用以緊固法壓 收縮安裝25的作業。進行該作業時一旦有異物侵入發電機 9之内部，將有因該異物而使發電機9產生損傷之虞。 較好的是，如圖9所示，使用臨時保護筒4〇，以避兔異 物之侵入所致之發電機9之損傷。於定子板18之油壓從縮 安裝25之孔之附近的位置設開口丨8a，而將臨時保護筒刊 ***於該開口 l8a。臨時保護筒4〇藉由以使油壓收縮安裝 25之孔位於其内部而設置，且於臨時保護筒4〇之内部進行 142403.doc 201105858 用以緊固油壓收縮安裝25之作業，可防止異物之侵入。 更具體之為，本實施形態中，作為臨時保護筒4〇使用保 護官41與撓性管42。作為一例，按以下之順序進行緊固油 壓收縮安裝25之作業。首先，於撓性管42之一端連接於保 護官41之端的狀態下，將保護管41***於定子板a之開口 18a而予以固定。此時，撓性管42之另一端一方面環繞油 壓收縮安裝25之孔並連接於該孔的附近。其次，於保護管 41、撓性管42中插通油壓配管43，且將該油壓配管43連接 於孔。其後，經由油壓配管43將動作流體（典型之為動作 油液）供給於孔而緊固油壓收縮安裝25。之後，於封孔後 撤去保護管41、撓性管42、及油壓配管43。最後，將蓋蓋 上開口 18a，完成作業。 另，圖9中，使用了圖3A之結構之發電機轉子u，然而 當業者應當瞭解，發電機轉子丨丨可使用各種結構。 本實施形態之結構令，發電機轉子u朝主軸4之結合係 藉由將發電機轉子u之轉子板15、16結合於套筒21後，將 套筒21***主軸4而進行。此時，由於發電機轉子u與套 筒21具有相當之重量，因此在進行將套筒21***主軸4之 作業時，較好的是增大主軸4與套筒21之間的間隙。例 如，若主軸4與套筒21之間的間隙為〇 5 mm以上，則容易 將套筒21***主轴4。 為能夠增大主軸4與套筒21之間隙，較好的是，以套筒 21之與油壓收縮安裝25抵接之部分的剛性低於其他部分之 方式構成套筒21。為此’較好的是’於套筒21之與油壓收 142403.doc 201105858 縮安裝25抵接之部分形成縫隙。 例如，如圖10A所示，在套筒21之端部緊固著油壓收縮 安裝25之情形下，較好的是，如圖1〇B所示，於套筒纟丨之 端部設置複數之縫隙21c。此處之圖10A、圖1〇B中，符號 21(1表示抵接油壓收縮安裝25之部分。圖10A之構成中，縫 隙2 1 c係以長條形狀形成於主軸4之軸方向，且係排列配置 於主轴4之周方向。 又，如圖11A所示，在套筒21之中間緊固著油壓收缩安 裝25之情形下，較好的是，如圖11B所示，於套筒21之中 間設置複數之縫隙21c。圖11B之構成中，縫隙2u係以長 條形狀形成於主軸4之軸方向，且係排列配置於主軸4之周 方向。 割 %丨不，秸田於興…，土队项文衣u抵接之位置 套筒21 ,亦可降低與油壓收縮安裝25抵接之部分的 性。圖HC係顯示分割結構之套⑽之結構之例的侧 圖。圖UC所圖示之套筒21之構成係具備於主軸4之軸方 排列的2個套筒構件51、52。套筒構件51之端設有複故 突出部53,其係排列設於主軸4之周方向，而^於主勒 向，套筒構件52之端設有複數之突出部54， :設於周方向’而突出於軸方向。套筒構件Hi係藉E 突出部53、54㈣合。即，套筒構件^各突; =筒構件52之突出部54中的2個之間。 緊固於突出部53,合之部分。如此之結構亦;: 之與㈣I缩安裝25抵接之部分的剛性。 142403.doc 201105858 (第2實施形態） 圖12係顯示本發明之第2實施形態之風力發電裝置1之結 構的刳面圖，尤其係顯示發電機轉子丨丨與主軸4之結合結 構的剖面圖。第2實施形態中，筒狀之油壓收縮安裝25(：係 设於主軸4與套筒21之間。且油壓收縮安裝25C係以接受動 作流體（典型之為動作油）之供給而增大其外徑之方式形 成。當油壓收縮安裝25C之外徑增大時，作用於主軸4與油 壓收縮女裝2 5 C之間之摩擦力、及作用於油壓收縮安裝 25C與套筒21之間之摩擦力將增大，藉此，可將主軸4與套 筒21結合。如圖12所示之將油壓收縮安裝25(：設於主軸$與 套筒21之間的結構，由於在發電機9與軸承6之間亦無必要 設作業空間，故可縮短發電機9與軸承6之間的距離。 將油壓收縮安裝25C設於主軸4與套筒21之間之結構之其 一的問題為，當油壓收縮安裝25C之外徑增大時，有過剩 之機械負荷作用於發電機軸承23、24之可能性。為避免該 問題’較好的是，將油壓收縮安裝25C設於主軸4之半徑方 向之不與發電機軸承23 ' 24相對的位置。藉此可減少油壓 收縮安裝25C之外徑增大時直接作用於發電機軸承23、24 的應力。 另’較好的是係構造成藉由套筒21之設置發電機軸承 23、24之位置與抵接於油壓收縮安裝25C之位置之間的部 分，來吸收因油壓收縮安裝25C之緊固而產生的變形。例 如，一實施形態中，如圖12所示，套筒21係構造成套筒21 之設置發電機轴承23、24之部分之剖面B、c的套筒21的 142403.doc -14· 201105858 厚度薄於套筒21之抵接於油壓收縮安裝25C之部分之到 t的套筒21的厚度。如此之結構中’剖面A抑制油壓收縮 女裝25C之外徑增大所致之套筒21的變形且增大摩擦力， ❿剖面B、C容許套筒21之變形，藉此可抑制作用於發電 機軸承23、24之機械負荷。 电 又’如圖13所示’亦可於套筒21之抵接於油壓收縮安裝 25C之部分與發電機軸承23、24之間的位置設置凹口 η、 56。藉由於凹口 55、56容許套筒21之變形，可抑制作用於 發電機軸承23、24之機械負荷。 、 【圖式簡單說明】 圖1係本發明之一實施形態之風力發電裝置之構成的概 略概念圖； 圖2A係顯示第丨實施形態之風力發電裝置之構成的钊面 圖； 圖28係顯示油壓收縮安裝之結構之例的剖面圖； 圖3A係顯示支撐場磁鐵及後板之構成之例的刳面圖； 圖3B係顯示支撐場磁鐵及後板之構成之另一例的剑面 圖； 圖3C係顯示支撐場磁鐵及後板之構成之再另一例的到面 圖， 圖4係顯示第丨實施形態之發電機與套筒之結合結構之例 的剖面圖； 圖5係顯示第1實施形態之發電機與套筒之結合結構之另 一例的剖面圖； 142403.doc •15- 201105858 圖6係顯示第1實施形態之發 另一例的剖面圖； 電機與套筒之結合結構之再 合結構之又 圖7係顯示第丨實施形態之發電機與套筒之結 一例的剖面圖； 電機與套筒之結合結構之 圖8 A係顯示第1實施形態之發 又一例的剖面圖； 機與套筒之結合結構之 圖8B係顯示第1實施形態之發電 又一例的剖面圖； 裝 又 圖9係顯示用以防止異物侵入發電 之緊固方法的概念圖； 圖1 〇 A係顯示第1實施形態之發電機 一例的剖面圖； 機内部之油壓收縮安 與套筒之結合結構之 圖1 〇 B係顯示第i實施形態之套筒之結構之例的概觀圖； 圖UA係顯示第】實施形態之發電機與套筒之結合結構之 又一例的剖面圖； 圖仙係顯示^實施形態之套筒之結構之另—例的概觀 圖； 圖11C係顯示第丨實施形態之套筒之結構之另一例的側視 圖； 圖12係顯示本發明之第2實施形態之發電機與套筒之結 合結構的例的剖面圖；及 圖丨3係顯示第2實施形態之發電機與套筒之結合結構之 另一例的剖面圖。 【主要元件符號說明】 142403.doc -16 * 201105858 1 風力發電裝置 2 塔 3 機艙台板 4 主軸 5 車由承 6 車由承 7 車由承台 8 軸承台 9 發電機 11 發電機轉子 12 定子 13 場磁鐵 14 後板 15 轉子板 15A 轉子板 15B 轉子板 15C 轉子板 15D 補強臂 16 轉子板 17 定子卷線 18 定子板 18a 開口 19 定子板 20a 軸承固定環 142403.doc -17 軸承固定環 套筒 凸緣 凸緣 縫隙 端板 發電機軸承 發電機軸承 油壓收縮安裝 油壓收縮安裝 油壓收縮安裝 油壓收縮安裝 固定環 可動環 支撐環 環形螺母 緊固子L 解除孔 補強肋 補強肋 臨時保護筒 保護管 撓性管 油壓配管 -18- 201105858 51 套筒構件 52 套筒構件 53 突出部 54 突出部 55 凹口 56 凹口 142403.doc -19·201105858 VI. Description of the Invention: [Technical Field] The present invention relates to a wind power generator and a group thereof, and more particularly to a combined structure of a main shaft of a wind power generator and a generator rotor. [Before technology] In the design of wind power generation equipment, the optimization of the main shaft and the generator rotor is an important design project. Spindle and generator rotation = it is necessary to combine the necessary strength. On the other hand, if the generator causes a short circuit, in the case where excessive torque is generated between the main shaft and the generator rotor, it is preferable to connect so that it can also perform relative motion. As a combination of a main shaft and a generator rotor, one of the known structures is a method of connecting a rotor plate of a generator rotor to a cylindrical sleeve and fastening the sleeve by shrinking mounting (shrinking disc) . This structure easily adjusts the bonding strength between the main shaft and the generator rotor, and since the generator rotor can be coupled to the main shaft by a generally achievable shrink mounting, it is preferable to reduce the cost. The structure in which the main shaft and the generator rotor are combined by a sleeve and a shrinking installation is described in the International Publication No. 111425 α (Patent Document (4) - Patent Document 1 discloses a shrinking disc (equivalent to this application) (4) Shrinkage safety:) The joint structure of the rotor bearing (corresponding to the application of the present application) to which the generator rotor is coupled is fastened to the main shaft. In the combined structure, the shrinking disc is located between the generator and the bearing. In this position, the rotor bearing is fastened to the main shaft. The shrinking disc is composed of a fixed disc and a movable disc, and the fixed disc and the movable disc are connected by a screw. The bolt is drawn parallel to the center of the main shaft to engage 142403. Doc 201105858 In.: When the screw inspection is tightened, the movable disc will be pressed against the fixed disc to reduce the internal control of the shrink disc, and the rotor bearing is fastened to the main shaft. The combination of the structure is Hu, for, supporting the main shaft The bearing and the power generation are increased. As mentioned above, in the combined structure, since the shrinking disc is located between the generator and the bearing, and the bolt is inserted parallel to the direction of the wire, it is necessary for the generator and the bearing. Ensure the working space for fastening the bolts. This will increase the distance between the generator and the bearing. If the distance between the generator and the bearing increases, the bending of the main shaft will increase and the vibration will increase. The mechanical load becomes a disadvantage. The increase of the distance between the generator and the bearing also causes the length of the main shaft to increase. When the length of the main shaft increases, the cost of the main shaft increases. The problem that the distance between the generator and the bearing increases, In particular, direct-drive wind power generation devices are particularly serious. Direct-drive wind turbines that do not use a speed increaser are required to increase the number of stator poles and the number of rotor poles, so the weight of the generator 1 tends to increase. If the distance between the sleeve and the generator is large, the degree of curvature of the main shaft will increase more, and the vibration will increase. [Patent Document 1] International Publication WO 2007/1 11425 A1 [Invention] The object of the present invention is to provide a combination structure of a main shaft and a generator rotor which can shorten the distance between the bearing and the generator supporting the main pumping. A main shaft that supports the windmill rotor, rotatably supports the main bearing of the main shaft; a generator with a rotor and a stator of the generator; a sleeve that is coupled with the rotor of the generator and inserted into the main shaft 142403.doc 201105858 Two people and a hydraulic shrink installation ' The sleeve is fastened to the outer side of the sleeve, and the sleeve is fastened to the main shaft. The hydraulic contraction mounting system is configured to tighten the inner diameter by the supply of the working fluid to fasten the sleeve to the main shaft. It is preferably located at each position. Preferably, the oil-shrinkable women's clothing is installed in the internal space of the generator. For example, (the stator magnet pole is arranged in the circumferential direction of the main shaft and the first and second stator plates are arranged). The stator poles are supported and arranged in the axial direction of the main shaft, and the first sub-plate and the main shaft are relatively rotatable by the second generator bearing, and the second stator plate and the main shaft are relatively rotatable by the second generator bearing Rotation, X, in the case where the generator rotor has a rotor magnetic pole arranged in the circumferential direction of the main shaft, and a rotor branch member provided between the jth stator plate and the second stator plate for supporting the rotor magnetic pole, Pressure may also be mounted contraction between the rotor support member is provided with a first stator plate. Preferably, the 匕τ is on the first stator plate, and has an opening at the corresponding oil pressure contraction, which is used to supply the working fluid to the oil pressure contraction. In the case of e-hai, it is preferable that the order of tightening the hydraulic pressure contraction includes: inserting a temporary protective cylinder into the opening provided in the first stator plate, so that the hole of the oil pressure shrinking female is located inside the temporary protective cylinder a step of connecting the hydraulic piping to the hole in the interior of the temporary compliance cylinder; and supplying the operating fluid to the hydraulic pressure shrinking installation via the hydraulic piping, and fastening the sleeve to the main shaft by hydraulic shrinkage mounting . Further, a slit may be provided in a portion where the sleeve is abutted against the hydraulic pressure shrinkage. Instead, the sleeve can be split at a location that is resistant to hydraulic shrinkage. Specifically, the sleeve is provided with a shaft 142403.doc 201105858 that is arranged in the main shaft and a second sleeve member, and is arranged in the circumference of the main shaft in the plural L. = =! The second sleeve member is provided with a plurality of second projections at the end of the second sleeve member, and the eight arrays are circumferentially oriented and protruded = the projections are respectively inserted into the plurality of second projections == 5 The installation is abutment between the first protruding portion and the second protruding portion. The wind power generating device of the other aspect includes a main bearing that supports the windmill and supports the main shaft in a rotating manner, and includes a generator rotor and a tweezers. Generator; combined with the generator rotor and inserted === oil between the main shaft (four) installation. The hydraulic contraction and the main shaft 2 increase the outer diameter according to the supply of the operating fluid, and the sleeve::: the stator of the power generating device includes: the second sub-surface of the main axis arranged in the circumferential direction and the magnetic pole of the branch The fiscal bearing arranged on the main shaft can be opposite to the first stator plate. The main shaft is made of the first generator Μ #2 疋子板 and the main shaft by the second generator bearing. In this case, it is preferable that the oil-and-dust shrinkage mounting is provided at a position where the main shaft does not face the first and second generator bearings. And 'better' is constructed such that the position of the first and second generator shafts of the sleeve is set to be close to the position of the oil plant that is retracted and installed; Solid deformation. According to the present invention, a coupling structure of a main shaft and a generator rotor which can shorten the distance between the generator and the bearing can be provided. [Embodiment] (First Embodiment) Fig. 1 is a schematic conceptual view showing a configuration of a wind turbine generator according to a third embodiment of the present invention. The wind power generator 本 of the present embodiment includes a tower 2, a platen 3, a main shaft 4, bearings 5, 6', bearing blocks 7, 8 and a generator 9. The nacelle platen 3 is placed at the upper end of the tower 2 in a yawable rotation. The main shaft* is rotatably supported by the two bearings 5, 6, and the bearings 5, 6 are fixed to the nacelle platen 3 by the bearing blocks 7, 8. A rotor (not shown) is coupled to one end of the main shaft 4, and a rotor of the generator 9 is coupled to the other end. The wind power generator It'' spindle 4 of the present embodiment is commonly used for a wind turbine rotor and a generator rotor, and the wind power generator of the present embodiment is configured as a so-called direct drive type wind power generator. Fig. 2A is a cross-sectional view showing in detail the structure of the wind power generator 丨 in the vicinity of the generator 9, particularly the structure of the generator 9, and the combination of the generator 9 and the main shaft 4. The generator 9 is provided with a generator rotor and a stator 12. The generator rotor η has a field magnet 13 (rotor pole), a field plate 13 behind the field magnet 13 and rotor plates 15, 16 supporting the rear plate 14. The stator 12 is provided with stator winding wires (stator magnetic poles) 17 and stator plates 18 and 19 of the branch tweezers winding wires 17. The stator 12 is coupled and fixed to the nacelle platen 3 by a support mechanism (not shown). Bearing fixing members 2a, 20b are used for fixing the bearing 6 toward the main shaft 4. Specifically, the bearing retaining rings 2a and 2b are inserted into the main shaft 4, and the bearing 6 is fixed to the main shaft 4 by being clamped to the bearing retaining rings 2a and 20b. On the other hand, a sleeve 142403.doc 201105858 is used for fixing the generator rotor 11 toward the main shaft 4, and the cylinder 2 1 and the hydraulic contraction mounting 25 are used. Specifically, the rotor plates 15, 16 of the generator rotor 11 are fixed to the flanges 2ia, 21b provided on the sleeve 21 by bolts. Further, the sleeve 21 is fastened and fixed to the main shaft 4 by the hydraulic contraction mounting 25. Fig. 2B is a plan view showing an example of the structure of the hydraulic contraction mounting 25. The hydraulic contraction mounting 25, as shown in Fig. 2B, includes a fixed ring %, a movable ring 27, a support ring 28, and a ring nut 29. The movable ring 27 is provided with a fastening hole 30a and a release hole 3〇b. When a working fluid (typically a working oil) is supplied to the fastening hole 3〇a, the movable ring 27 moves in the direction of the arrow A to press against the fixing ring 26, whereby the inner diameter of the fixing ring 26 (ie, oil pressure contraction) The inner diameter of the mounting 25 is reduced. The sleeve 21 is fastened to the main shaft 4. The generator rotor 11 is fixed to the main shaft 4 by being fastened to the main shaft 4 by a sleeve 21 coupled to the generator rotor. As will be described later, in order to fasten the sleeve 2丨 to the main shaft 4, the hydraulic pressure shrinkage mounting U is important in the present embodiment. On the other hand, when the operating hole is supplied to the releasing hole 3〇b, the movable ring 27 is actuated. Move in the direction of arrow B to release the fastening. Referring again to Fig. 2A, the end plate 22 is used to prevent the sleeve 21 from being displaced in the axial direction (the direction parallel to the center line of the main shaft 4, the same applies hereinafter). More specifically, the plate 22 is mounted across the end of the sleeve 21 and the end of the main shaft 4, and the sleeve 21 is clamped to the bearing retaining ring 2〇b and the end plate 22. Thereby, the sleeve 2 is restrained from moving in the axial direction. Further, the stator plates 18, 19 of the stator 12 are provided with generator bearings 23, 24, and the main shaft 4 and the sleeve 21 support the stator plates 8' 19 via the generator bearings 23, 24. The main shaft 4 and the sleeve n are rotatable relative to the stator plates 18, 19 by the generator bearings 23, 24. This structure is effective for dispersing the mechanical load due to the weight of the generator 9. 142403.doc 201105858 In addition, in Fig. 2A, as the supporting members for supporting the field magnet 13 and the rear plate 14, the rotor plate 15 is provided. However, the structure of the ballast field magnet 13 and the rear plate 14 can be variously modified. For example, as shown in Fig. 3A, as the supporting members for supporting the field magnet 13 and the rear plate 14, a rotor plate 15A for cymbal and reinforcing ribs 31, 32 joined to the rear plate 14 and the rotor plate 15A may be used. Further, as shown in Fig. 3β, a conical rotor plate 15B may be used. Further, as shown in Fig. 3C, the rotor plate 15C may be used, and the rear end 14 may be joined to the rear plate 14, and the other end may be joined to both of the rotor plates 15C. The structure of the wind turbine generator 1 of the present embodiment has an advantage in that the distance between the bearing 6 and the generator 9 can be shortened by shrinking the mounting sleeve 25 with the oil S. It is not necessary to install between the bearing 6 and the oil pressure shrinkage seal 25 to perform the tightening oil pressure contraction using the hydraulic pressure shrinking installation 25 operated by the action fluid. The workspace for the job of installing 25. This shortens the distance between the bearing 6 and the generator 9. As described above, the shortening of the distance between the bearing 6 and the generator 9 is effective for reducing the mechanical load and shortening the length of the main shaft. At this time, as the hydraulic contraction mounting 25, the hole for the right operating fluid is used to supply the operating fluid to the half direction of the main pumping 4, which is more advantageous for the distance between the bearing 6 and the generator 9. Shorten. 2 'in the structure of Figure 2A' hydraulic compression installation 25 is located between the bearing and the motor 9 ' however, the oil pressure shrink installation 25 can also be set inside the generator 9 'set by the C shrink installation 25 set to the generator The internals of 9 have the advantage of further shortening the distance between the bearing 6 and the generator 9. For example, as shown in Fig. 4, the hydraulic contraction mounting 25 may be provided between the stator plate 18 and the rotor plate 15 on the side of the bearing 142403.doc 201105858. Further, as shown in Fig. 5, a hydraulic shrinkage mounting 25 may be provided between the rotor plates 15 and 16. Further, as shown in Fig. 6, a hydraulic contraction mounting 25 may be provided between the rotor plate 16 and the stator plate N. From the viewpoint of shortening the distance between the bearing 6 and the generator 9, as shown in Fig. 7, the hydraulic contraction mounting 25 can also be provided at a position between the generator 9 and the end of the main shaft 4. Further, as shown in Figs. 8A and 8B, a plurality of hydraulic contraction mountings can be used to fasten the sleeve 21 to the main shaft 4. In the figure, the hydraulic contraction mounting 2 is provided at a position between the generator 9 and the end of the main shaft 4, and the hydraulic contraction mounting 25B is provided between the generator 9 and the bearing 6. On the other hand, in the figure, two hydraulic pressure shrinking installations of 25 people and 25B are provided inside the generator 9. Specifically, the hydraulic contraction mounting 25A is disposed between the stator plate 19 and the rotor plate 16, and the hydraulic contraction mounting 25B is disposed between the stator plate and the rotor plate 16. The hydraulic pressure shrinking mounting 25 is provided in the system. In the case of the inside of the generator 9, it is necessary to supply a working fluid or the like to the hydraulic pressure shrinking attachment 25 to fasten the work of the normal pressure shrinkage mounting 25. When foreign matter enters the inside of the generator 9, there is a case where the foreign matter enters the inside of the generator 9. The generator 9 is damaged by the foreign matter. Preferably, as shown in Fig. 9, the temporary protective cylinder 4 is used to avoid the damage of the generator 9 caused by the invasion of the foreign body of the rabbit. The oil pressure is provided from the position near the hole of the shrink fitting 25 to open the opening 8a, and the temporary protective cylinder is inserted into the opening l8a. The temporary protective cylinder 4 is located inside the hole by the hydraulic pressure shrinking mounting 25 The 142403.doc 201105858 is installed in the interior of the temporary protective cylinder 4 to tighten the hydraulic pressure shrinking installation 25, and the intrusion of foreign matter can be prevented. More specifically, in the present embodiment, as the temporary protective cylinder 4〇 Use the protection officer 41 and the flexible tube 42 As an example, the operation of tightening the hydraulic pressure shrinkage mounting 25 is performed in the following order. First, in a state where one end of the flexible tube 42 is connected to the end of the protector 41, the protective tube 41 is inserted into the opening 18a of the stator plate a. At this time, the other end of the flexible tube 42 surrounds the hole of the hydraulic pressure shrinking mounting 25 on the one hand and is connected to the vicinity of the hole. Secondly, the hydraulic tube 43 is inserted into the protective tube 41 and the flexible tube 42, The hydraulic piping 43 is connected to the hole. Thereafter, the working fluid (typically, the operating fluid) is supplied to the hole via the hydraulic pipe 43 to tighten the hydraulic contraction mounting 25. Thereafter, the sealing is removed after sealing. The tube 41, the flexible tube 42, and the hydraulic pressure pipe 43. Finally, the cover is closed with the opening 18a to complete the work. In addition, in Fig. 9, the generator rotor u of the structure of Fig. 3A is used, but the practitioner should understand that Various configurations can be used for the generator rotor. The structure of the present embodiment is such that the coupling of the generator rotor u to the main shaft 4 is performed by coupling the rotor plates 15, 16 of the generator rotor u to the sleeve 21, and then the sleeve 21 is inserted into the spindle 4. At this time, due to the hair The rotor u and the sleeve 21 have a considerable weight, so when performing the work of inserting the sleeve 21 into the spindle 4, it is preferable to increase the gap between the spindle 4 and the sleeve 21. For example, if the spindle 4 and the sleeve When the gap between the cylinders 21 is 〇5 mm or more, the sleeve 21 is easily inserted into the main shaft 4. In order to increase the gap between the main shaft 4 and the sleeve 21, it is preferable to install the sleeve 21 with the oil pressure contraction. The portion of the abutting portion is lower in rigidity than the other portions to constitute the sleeve 21. For this reason, it is preferable that a gap is formed in the portion of the sleeve 21 which is in contact with the hydraulic pressure 142403.doc 201105858. As shown in FIG. 10A, in the case where the hydraulic contraction mounting 25 is fastened to the end of the sleeve 21, it is preferable to provide a plurality of ends at the end of the sleeve as shown in FIG. The slit 21c. Here, in Fig. 10A and Fig. 1B, reference numeral 21 (1 denotes a portion that abuts against the hydraulic contraction mounting 25. In the configuration of Fig. 10A, the slit 2 1 c is formed in an elongated shape in the axial direction of the main shaft 4, Further, the arrangement is arranged in the circumferential direction of the main shaft 4. Further, as shown in Fig. 11A, in the case where the hydraulic contraction mounting 25 is fastened in the middle of the sleeve 21, preferably, as shown in Fig. 11B, In the middle of the cylinder 21, a plurality of slits 21c are provided. In the configuration of Fig. 11B, the slits 2u are formed in a long shape in the axial direction of the main shaft 4, and are arranged in the circumferential direction of the main shaft 4 in a row. Xing..., the positional sleeve 21 abutted by the soil team item Wenyi u can also reduce the part of the part that abuts against the hydraulic contraction mounting 25. Figure HC shows a side view of an example of the structure of the sleeve (10) of the divided structure. The sleeve 21 shown in Fig. UC is provided with two sleeve members 51 and 52 arranged in the axial direction of the main shaft 4. The end of the sleeve member 51 is provided with a recurring projection 53 which is arranged in the main shaft. 4 in the circumferential direction, and in the main direction, the end of the sleeve member 52 is provided with a plurality of protruding portions 54, which are disposed in the circumferential direction and protrude from the axial direction The sleeve member Hi is joined by the E projections 53, 54. That is, the sleeve members are respectively protruded; = between the two projections 54 of the tubular member 52. The fastening portion 53 is fastened to the joint portion 53. The structure of the wind power generator 1 according to the second embodiment of the present invention is shown in FIG. 12 is a plan view showing the structure of the wind turbine generator 1 according to the second embodiment of the present invention. In particular, a cross-sectional view showing a structure in which the rotor 丨丨 of the generator is coupled to the main shaft 4 is provided. In the second embodiment, the cylindrical hydraulic pressure shrinkage mounting 25 (: is provided between the main shaft 4 and the sleeve 21, and the oil pressure is applied. The shrink-fit mounting 25C is formed in such a manner as to increase the outer diameter of the supply of the operating fluid (typically the operating oil). When the outer diameter of the hydraulic shrink-fitting mounting 25C is increased, the main shaft 4 and the hydraulic contracting wear are applied. The friction between 2 5 C and the friction between the hydraulic shrinkage mounting 25C and the sleeve 21 will increase, whereby the main shaft 4 can be combined with the sleeve 21. As shown in Fig. 12 Oil pressure shrink installation 25 (: a structure provided between the main shaft $ and the sleeve 21 due to the relationship between the generator 9 and the bearing 6 There is no need to provide a working space, so the distance between the generator 9 and the bearing 6 can be shortened. The problem of the hydraulic pressure shrinking mounting 25C being disposed between the main shaft 4 and the sleeve 21 is that when the hydraulic pressure is contracted When the outer diameter of 25C is increased, there is a possibility that an excessive mechanical load acts on the generator bearings 23, 24. To avoid this problem, it is preferable that the hydraulic pressure shrinkage mounting 25C is provided in the radial direction of the main shaft 4 The position opposite to the generator bearing 23' 24, thereby reducing the stress acting directly on the generator bearings 23, 24 when the outer diameter of the hydraulic contraction mounting 25C is increased. Further, it is preferable to construct a portion between the position where the generator bearings 23 and 24 are disposed by the sleeve 21 and the position abutting against the oil pressure contraction mounting 25C to absorb the tightness of the installation 25C due to the oil pressure contraction. Solid deformation. For example, in one embodiment, as shown in FIG. 12, the sleeve 21 is configured as a sleeve 21 of the sleeve 21, which is provided with a section B, c of the portion of the generator bearings 23, 24, 142403.doc -14·201105858 Thickness Thinner than the thickness of the sleeve 21 of the sleeve 21 abutting the portion of the oil pressure shrinking mount 25C to t. In such a structure, the profile A suppresses the deformation of the sleeve 21 caused by the increase in the outer diameter of the hydraulic pressure shrinkage women's 25C and increases the frictional force, and the profile B and C allow the deformation of the sleeve 21, thereby suppressing the action. The mechanical load on the generator bearings 23, 24. Further, as shown in Fig. 13, the recesses η, 56 may be provided at positions between the portion of the sleeve 21 that abuts against the hydraulic contraction mounting 25C and the generator bearings 23, 24. By the deformation of the sleeve 21 by the notches 55, 56, the mechanical load acting on the generator bearings 23, 24 can be suppressed. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a schematic conceptual view showing a configuration of a wind power generator according to an embodiment of the present invention; Fig. 2A is a plan view showing a configuration of a wind power generator according to a third embodiment; FIG. 3A is a cross-sectional view showing an example of a structure for supporting a field magnet and a rear plate; FIG. 3B is a plan view showing another example of a structure for supporting a field magnet and a rear plate; Fig. 3C is a cross-sectional view showing still another example of the structure of the support field magnet and the rear plate, and Fig. 4 is a cross-sectional view showing an example of the structure of the combination of the generator and the sleeve of the third embodiment; 1 is a cross-sectional view showing another example of a combination of a generator and a sleeve according to an embodiment; 142403.doc • 15-201105858 FIG. 6 is a cross-sectional view showing another example of the first embodiment; a combination of a motor and a sleeve Fig. 7 is a cross-sectional view showing an example of a junction between a generator and a sleeve according to a second embodiment; Fig. 8A showing a structure in which a motor and a sleeve are coupled; Fig. A is a cross-sectional view showing still another example of the first embodiment. ; machine and sleeve Fig. 8B is a cross-sectional view showing still another example of power generation in the first embodiment; Fig. 9 is a conceptual view showing a fastening method for preventing foreign matter from entering power generation; Fig. 1 shows a first embodiment; FIG. 1 is a schematic view showing an example of a structure of a sleeve of the i-th embodiment; FIG. A cross-sectional view of another example of a combination of a generator and a sleeve; Fig. 1 is a schematic view showing another example of the structure of the sleeve of the embodiment; Fig. 11C is a view showing the structure of the sleeve of the third embodiment; Fig. 12 is a cross-sectional view showing an example of a coupling structure between a generator and a sleeve according to a second embodiment of the present invention; and Fig. 3 is a view showing a combination of a generator and a sleeve according to the second embodiment. A cross-sectional view of another example of the structure. [Description of main component symbols] 142403.doc -16 * 201105858 1 Wind power generator 2 Tower 3 Cabin platen 4 Spindle 5 Car by bearing 6 Car by bearing 7 Car by cap 8 Bearing table 9 Generator 11 Generator rotor 12 Stator 13 field magnet 14 rear plate 15 rotor plate 15A rotor plate 15B rotor plate 15C rotor plate 15D reinforcing arm 16 rotor plate 17 stator winding 18 stator plate 18a opening 19 stator plate 20a bearing retaining ring 142403.doc -17 bearing retaining ring sleeve Flange flange slot end plate generator bearing generator bearing oil pressure shrinkage installation oil pressure shrinkage installation oil pressure shrinkage installation oil pressure shrinkage installation fixed ring movable ring support ring ring nut fastener L release hole reinforcement rib reinforcement rib temporary protection cylinder Protective tube flexible tube hydraulic piping -18- 201105858 51 Sleeve member 52 Sleeve member 53 Projection 54 Projection 55 Notch 56 Notch 142403.doc -19·