201139843 六、發明說明： 【發明所屬之技術領域】 本發明係關於直接驅動型風力發電裝置及適於其之轴承 構造，尤其是關於直接驅動型風力發電裝置之主轴及發電 機之支持構造。 【先前技術】 風力發電裝置之一眾所周知之形式為直接驅動型風力發 電裝置。在齒輪型風力發電裝置中，使用增速機增大旋轉 數而將風車轉子之旋轉傳達至發電機，相對於此，在直接 ^動里風力發电裝置中’則是將風車轉子與發電機係藉由 主軸予以直接連結。 在直接驅動型風力發電裝置中，由於使用同步發電機， 使得發電機大型化，且由於發電機與主轴直接連結，因此 在支持主軸與發電機之構造之設計上亦必須有特別之顧 慮。通常會設置以2個軸承可旋轉地支持主轴、且用於防 广电機之定子外殼旋轉之構造體。以下將用於防止發電 狀定子外殼旋轉之構造體稱為扭力支持件。伴隨著主轴 之方疋轉，會於主轴之周向對發電機之定子外殼施加扭力。 力支持件之作用為即使受到如此之扭力施加，亦可支持 定子f殼而使定子外殼不會旋轉。此外，亦有於主軸與定 子外从之間，附加設置丨個或2個發電機軸承，藉由該發電 機軸承支持定子外殼之情況。以2個軸承可旋轉地支持主 抽且以扭力支持件支持定子外殼之構造，揭示於例如歐 洲專利申請案EP1 WOMB工號公報（專利文獻υ、歐洲專利 I48092.doc 201139843 文獻2)及對應日本申請案 文獻3)、以及國際公開 申請案EP2014917A1號公報（專利 之特開2009-19625號公報（專利 \^〇2007/111425號（專利文獻4)。 此處’作為支持風力發電機之主軸之軸承，通常使用具 有調心性之軸承（容許軸撓曲或傾斜之軸承）。這是由於在 直接驅動型風力發電裝置中主軸會產生撓曲，Μ為基於 需要吸收該撓曲之技術思想而考量者。又例如 ΕΡ1327073Β 1中揭示使支持主軸之軸承容許主軸之撓曲 (flexing)(例如該案之請求項丨）。又，國際公開 W〇2〇G7/m425號中揭示有靠近轉子頭之軸承係採用環狀 滾子軸承（toroidal roller bearing)，且靠近發電機之軸承係 採用圓柱滾子軸承（spherical roller bearing)，藉此補償主 軸之對心失準（misalignment)及傾斜（tihing) 〇 然而，根據本申請案發明者之研究，不認為以具有調心 性之2個軸承支持主軸、且以扭力支持件支持定子外殼之 構造適合用於固定維持定子與轉子之間隙。圖8係說明其 理由之圖。以下探討如圖8所示之、藉由第丨軸承1〇1、第2 軸承102支持主軸103，且藉由扭力支持件1〇4支持於主軸 103之周向作用於發電機105之定子外殼1〇6之扭力的構 造。此處，1】係轉子頭側之載荷點與第1軸承1〇1之間之距 離，丨2係弟1軸承101與第2軸承102之間之距離，13係第2軸 承102到扭力支持件104對定子外殼ι〇6作用力之點為止之 距離。又，R〗、R2為第1軸承1 〇 1、第2軸承1 〇2所作用之支 點反力’ R3係使扭力支持件1〇4作用於定子外殼1〇6之支點 148092.doc 201139843 反力。 支撐主軸103之2個軸承（第！軸承1〇1、第2軸承ι〇2)若皆 為具有調心性之軸承，則在各自之位置上會產生撓曲角 γ!、γ2。且，由於撓曲角γζ、與風力發電裝置在佈局上必 然存在之距離丨3，即使扭力未作用於扭力支持件1〇4，亦 會產生支點反力r3。此處，支點反力R3之大小為扭力支持 件104之彈簧常數與變形量δ之積。 该支點反力R3由於會使發動機1〇5之定子與轉子之間的 間隙產生不平衡故而不佳。尤其是使用永久磁石同步發電 機（PMSG)作為發電機105之情況時，間隙不平衡之問題越 顯嚴重。詳細而言，在場磁鐵之磁性吸引力或各種之電力 所作用之永久磁石同步發電機（PMSG)中，必須確實維持 定子與轉子之間之間隙，且必須縮小各種振動模式之位 移。然而，由於支點反力R3，定子外殼1〇6僅會位移發電 機軸承之内部間隙之量，又，定子外殼1〇6自身亦稍有變 形。由於内部間隙量之位移與變形，導致定子與轉子間之 間隙產生不平衡，且除了因旋轉所引起之磁性振動以外， 亦產生撓曲所引起之模式振動。由於撓曲模式振動之產生 會使風力發電裝置之振動增大，故而不佳。又，由於若產 生撓曲模式振動，則疲勞載荷亦增加，故必須高度設計構 造構件（例如，主軸103、扭力支持件1〇4、定子外殼1〇6等） 之強度’而亦會產生重量增大之問題。 [先前技術文獻] [專利文獻] 148092.doc 201139843 [專利文獻1]歐洲專利申請案EP1327073B1號公報 [專利文獻2]歐洲專利申請案EP20U917A1號公報 [專利文獻3]曰本特開2009-09625號公報 [專利文獻4]國際公開W02007/111425號公報 【發明内容】 [發明所欲解決之問題] 因此，本發明之目的在於提供一種在直接驅動型風力發 電裝置中，用於防止發電機之定子與轉子間之間隙不平衡 的技術。 [解決問題之技術手段] 在本發明之一觀點中，直接驅動型風力發電裝置具備： 主軸，其一端連結於風車轉子之轉子頭；發電機，其包含 定子、支持定子之定子外殼、及連結於主軸之另一端之轉 子；第1及第2軸承，其位於轉子頭與發電機之間，並可旋 轉地支持主軸；及扭力支持件，其支持定子外殼。第i軸 承為具有調心性之軸承，而位於較第丨軸承更靠近發電機 之位置之第2軸承為無調心性之轴承。作為第2軸承可使 用雙列圓錐滾子軸承。又，作為^軸承，可使用例如圓 錐滾子軸承、圓柱滾子軸承、或自動調心軸承。 在一實施形態中，第2軸承具備：第丨及第2内輪；第丨及 第2外輪’·設置於第〗内輪與第丨外輪之間的第〗轉動體；設 置於第2内輪與第2外輪之間之第2轉動體；及賦能構件°。 第2外輪與第2内輪之間之間隔為可變，且賦能構件係以使 第2外輪之内周面接近第2内輪之外周面的方式賦能第2外 I48092.doc 201139843 輪。 收容並支持第2轴承之=為’第2軸f可相對於 較佳為使用線接觸或點接觸結合。該情況軸下承:與可42外輪 轴承箱與第2外輪之間插入圓柱滾子。 於例如 第2轴承較佳為進—步具備第3 、 設置於第3内輪與第3外輪之間之第3轉動體。*、及 汾較佳的是定子外殼在對向於收容並支持第2轴承之轴承 =之對向面上具有凹面，純佳為軸承箱之端部位於與對 。面相同之面上’或轴承箱之—部分位於凹部之内部。 从又’扭力支持件具備連結於收容並支持第2轴承之轴承 相^力支持構件之情況時’扭力支持構件較佳為將軸承 相與定子外殼於主軸之半徑方向加以連結。 定子外殼可具備對向於軸承箱之中心部襯板、及連結於 中心部之外緣部之外周部襯板。該情況下，中心部襯板之 構成可為使其中心'部形成為較外緣部下凹，藉此對定子外 α提供凹部’且外周部襯板之構成可為形成從作為扭力支 持件發揮功能之凹部之外緣向主軸之半徑方向内側突出的 犬出部。该情況下，使軸承箱之一部分收容於凹部，且使 犬出部敗入於軸承箱上所設之槽，藉此連結定子外殼與軸 承箱。 在本發明之另一觀點中’軸承構造具備第1及第2内輪； 第1及第2外輪；設置於第1内輪與第2外輪之間之第1轉動 體’。又置於第2内輪與第2外輪之間之第2轉動體；及賦能 148092.doc 201139843 隔為可變，且賦能構件 輪之外肖㈣方式賦能 構件。第2外輪與第2内輪之間之間 係以使第2外輪之内周面接近第2内 第2外輪。 根據本發明，可防止直接驅動型風力發電裂置之發 之定子與轉子之間之間隙不平衡。 ％ 【實施方式】 〜观、刀^電裝置1 構造的立體圖。本實施形態之風力發電裝^係作為 驅動型風力發電裝置而構成，具有如下所述之構成。風力 電裝置!具備塔架2與機艘台座3。機搶台座3可 地配置於塔架2之上端。於機艙台座3上，設置第丨袖承：5 與^軸承箱6，且藉由分別設置於該第】轴承箱$與第冰 承相6之内部之第！轴承8及第2轴承％參照圖^，而可 地支持主轴4。主㈣之—端連接於風車轉子之轉子頭（未 圖不），另一端連接於發電機7。發電機7進而藉由扭 持件20而連結於第2軸承箱6。 圖2係從上方觀察本實施形態之風力發電裝置1之剖面 2 °發電機7具備定子11與轉子⑴定子η係藉由定； 破13予以立拉。s + 卜 磁趨^ 轉子12具備對向於定子11之場 人支持場磁鐵14之轉子片15。轉子片15 2主-之端部之軸套16，藉此將轉子12連結於主轴/ :，在本實施形態中’轴套16連結於主轴4之端部，但 16可與主軸4連接形成，或亦可一體形成。 於轴套16上設置有發電機轴承17、18，且藉由該等之發 I48092.doc 201139843 電機軸承17、18而支持定子外殼13 ^藉由設置於主軸斗之 心電機軸承17、18支持定子外殼！ 3，可有效固定保持定子 11與轉子12之間之間隙。 扭力支持件20連結定子外殼13與第2軸軸承箱6。在本實 施形態中’扭力支持件2G具備銷21、轴套22及橡夥觀套 23。軸套22固定於定子外殼丨3，橡膠襯套以插入至軸套22 之内部。再者’於橡膠襯套23中插入銷21，而將銷21固定 於第2轴承箱6 ° #由如此之構造之扭力支持件2G，以於主 軸4之周向作用之扭力支持於於定子外殼13。 如上所述’在以具有調心性之2個軸承支持主軸，並以 扭力支持件支持定子外殼之構造中，會有發電機之定子與 轉子之間之間隙產生不平衡的問題。為解決該問題，在本 :施形態之風力發電裝置中，採用無調心性之軸承，即不 合才主軸4傾斜之軸承’作為靠近發電機7側之軸承之第2 轴承9 3彳面，使用具有調心性之轴承作為第1轴承 8°更具體而言’使用例如圓錐滾子軸承roller beaHng)'圓“子或自動調心軸承’作為第_承 另方面，使用例如複列圓錐滚子轴承（d〇uble taper roller bearing) ’ 作為第 2軸承9。 圖3係顯示第2軸承9之構造之一 m^ 丨U面圖。第2軸承9 八備内輪25、外輪26 '及設置於^r蓉 又置於4 4之間之圓錐滾子27、 28。圖3中雖各圓示—個圓錐滾子27 Η ., 28 ’但必須睁解方| 數個圓錐滾子27係於主軸4之月。“ ㈣解複 王釉4之周向亚列配置成一且 數個圓錐滾子2 8係於主軸4之周向並列配 配置成—列。内輪 148092.doc 201139843 25安裝於主軸4上，外輪26安裝於第2軸承箱6。於内輪25 上’以在第2軸承9之中心部成為凹狀的方式形成錐形，再 者，於外輪26上，以在第2軸承9之令心部成為凸狀的方式 形成錐形。圓錐滾子27、28係以其半徑向第2軸承9之中心 逐漸縮小的方式配置。藉由如此之構造，第2軸承9以不容 許傾斜而可旋轉的方式保持主軸4。 使用無調心性之軸承作為第2轴承9，藉此於風力發電裝 置1動作時，使主軸4之較第2軸承9更靠近發電機7之側之 部分、軸套16、轉子12及定子外殼13機械性一體化，從而 抑制該等構件之間產生相對位移（displacement)。即’主軸 4之較第2軸承9更靠近發電機7之側之部分、軸套16、轉子 12、及定子夕卜殼U之構件之間的相對位置關係之變動獲得 抑制，而使該等構件整體形同一個單元(unh)般運動。此 可有效使定子Η與轉子12之間之間隙保持固定，並防止間 隙不平衡。 在使=無調心性之軸承作為第2抽承9之本實施形態中， 為更確實保持間隙，較佳減少第2轴承9之端隙，，即較佳 t採用減少第2軸承9之轉動體（滾珠、或滾子）與内輪25及 =輪26間之間隙之軸承構造^圖从係顯示以減少間隙的方 工構成之第2轴承9A，及保持其之㈣由承箱μ之構 之圖。 第2軸承箱6A具備 狀構件38、壓板39、 件38及壓板39係藉由 第1裱狀構件36、中間構件37、第2環 及螺栓40。中間構件37、第2環狀構 螺栓40予以固定於第1環狀構件36。 148092.doc 201139843 第2軸承9A具備第1内輪3la、第2内輪31b、墊片32、第1 外輪33a、第2外輪33b、彈簧35、及圓錐滾子34a、34b。 第1内輪31a、第2内輪3 lb及墊片32插入至主軸4，並藉由 螺母4a予以固定於主軸4。墊片32具有將第1内輪與第2 内輪3〗b保持在期望之距離之功能β第】外輪33a係被第^環 狀構件36及t間構件37夾住並保持。第2外輪331)係被壓抵 於第2環狀構件38之内周面並保持。此處，第2外輪可 於主軸4之軸向滑動。 圓錐滾子34a插入於第！内輪31a與第i外輪33a之間，而 圓錐滾子34b插入於第2内輪31b與第2外輪33b之間。此 處，在圖4A中個圖示一個圓錐滾子34a、3仆，但必須瞭解 複數個圓錐滾子34a係於主軸4之周向並列配置成—列，'且 複數個圓錐滾子34b係於主軸4之周向並列配置成一列。 此處，第1内輪3 la係在相對於主軸4之軸向傾斜、且於 半徑方向外側並朝向發電機7之方向對圓錐滾子34a作用载 荷。又，第2内輪31b係在相對於主軸4之軸向傾斜、且於 =徑方向外側並朝向轉子頭之方向對圓錐滾子34b作用载 何。再者，第1外輪33a係在相對於主軸4之軸向傾斜、且 於2徑方向外側並朝向轉子頭之方向對圓錐滾子“a作用 載荷。又，第2外輪33b係在相對於主軸4之軸向傾斜、且 於半徑方向外側並朝向發電機7之方向對圓錐滾子糾作用 載荷。藉由如此之構造，支持作用於主軸4之軸向載荷以 及輕向載荷F r。 此外，於第2外輪33b與中間構件37之間插人彈簧35,且 148092.doc 201139843 第2外輪33b對主軸4之軸向賦能。由於第2内輪3 lb之外周 面與第2外輪33b之内周面相對於主軸4之轴向傾斜，於是 使得彈簧35以使第2外輪33b之内周面接近第2内輪3 lb之外 周面之的方式賦能第2外輪33b。藉由該彈簧35之作用，使 第2軸承9之端隙、即圓錐滾子34b與第2内輪3ib間之間 隙，及圓錐滾子34b與第2外輪33b間之間隙縮小。如此之 構k可將主軸4之較第2軸承9更靠近發電機7之側之部分、 軸套16、轉子12、及定子外殼13機械性一體化，並有效抑 制》亥等構件之間產生相對位移。這可有效防止定子11與轉 子12之間之間隙不平衡。 如圖4A之軸承構造進一步可有效提高圓錐滾子3“、3仆 間之負載之均-性，並解決第】内輪3u、第2内輪川、與 第1外輪33a、第2外輪33b之間之溫度差之問題。在圖3之 軸承構&中’於主軸4之軸向施加負載時，會對另一方的 圓錐;袞子列（例如、圓錐滾子28列）施加較大負載。這會縮 短第2軸承9之奇命故而不佳。又’當主轴*旋轉時，第2轴 &會上升’且内輪25之溫度上升大於外輪％。若 内輪25之溫度相對高於外輪26之温度，則内輪25之熱膨脹 亦大於外輪26 ’於是使得作用於圓錐滚子27、28之機械負 載增大。這會縮短圓錐滾子27、28之壽命故而不佳。、 从另一方面，根據圖4A之構造，對第2軸承9作用軸向之載 芍 清況犄，s亥載荷Fa會藉由彈簧35之作用而均等地作 用於圓錐滚子34a、34b。因此可防止因對其中一方的圓錐 滚子列施加較大之負載而導致壽命縮短。又，根據圖从之 148092.doc •12· 201139843 構造，即使第1内輪31a、第2内輪31b之溫度上升大於第i 外輪33a、第2外輪33b之溫度上升’第1内輪31a、第2内輪 31b之熱膨脹會被彈簣35吸收。因此，可避免第i内輪 31a、第2内輪31b與第1外輪33a'第2外輪33b之間之溫度 差的問題。 為進一步減少主軸4之位移，如圖4Β所示，可設置3列之 圓錐滾子，。在圖4Β之第2軸承9Β之構造中，附加設置第 3内輪31c及第3外輪33c，且於其間設置圓錐滾子34^。於 第1内輪31 a與第3内輪31c之間設置墊片32a，且於第2内輪 31b與第3内輪31c之間設置墊片32b，藉此使第i内輪3u與 第3内輪31c保持在期望之間隔，且，使第2内輪31b與第3 内輪31.c保持在期望之間隔。又，第}外輪33a與第3外輪 33c係被第1環狀構件36a與中間構件37夾住並保持。此 時，於第1外輪33a與第3外輪33c之間插入墊片36b，使第i 外輪3 3 a與第2外輪3 3 c保持在期望之間隔。 再者，在設置3列轉動體之圖4B之構造中，亦可取代圓 錐滾子34a、34b、34c而改為使用滾珠作為轉動體。使用 滾珠作為轉動體可降低成本故而較佳。 在圖4A、圖4B之構造中，第2外輪33b必須能夠在第之環 狀構件3 8之内周面上於軸向滑動。此時，在將第2環狀構 件38大型化之情況時，可能會有第2環狀構件38之製造誤 差增大，且第2外輪33b難以在第2環狀構件38之内周面滑 動的情況。 為使第2外輪33b可相對於第2環狀構件38移動，第2外輪 148092.doc -13-BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a direct drive type wind power generator and a bearing structure suitable therefor, and more particularly to a support structure for a spindle and a generator of a direct drive type wind power generator. [Prior Art] One of the well-known forms of wind power generation devices is a direct drive type wind power generation device. In a gear-type wind power generator, a speed increaser is used to increase the number of revolutions, and the rotation of the wind turbine rotor is transmitted to the generator. In contrast, in the direct-drive wind power generator, the wind turbine rotor and the generator are It is directly connected by the main shaft. In a direct drive type wind power generator, since a synchronous generator is used, the generator is enlarged, and since the generator is directly coupled to the main shaft, special consideration must be given to the design of the support main shaft and the generator. A structure in which two bearings rotatably support the main shaft and is used to rotate the stator casing of the anti-radiation motor is usually provided. The structure for preventing the rotation of the power generating stator casing is hereinafter referred to as a torsion support. With the rotation of the main shaft, a torque is applied to the stator casing of the generator in the circumferential direction of the main shaft. The force support member functions to support the stator f shell even if subjected to such a torque, so that the stator housing does not rotate. In addition, there are also two or two generator bearings added between the main shaft and the stator, and the stator housing is supported by the generator bearing. The construction of the stator casing is rotatably supported by two bearings and supported by a torsion support member, as disclosed in, for example, European Patent Application No. EP1 WOMB No. (Patent Document No., European Patent No. I48092.doc 201139843 Document 2) and corresponding Japan Application Document 3), and International Publication No. EP2014917A1 (Patent No. 2009-19625 (Patent No. 2007/111425 (Patent Document 4). Here 'as a main shaft supporting a wind power generator) Bearings, usually with self-aligning bearings (bearings that allow the shaft to flex or tilt), this is due to the fact that the main shaft is deflected in a direct-drive wind turbine, which is based on the technical idea of absorbing the deflection. Further, for example, ΕΡ1327073Β1 discloses that the bearing supporting the main shaft allows the flexing of the main shaft (for example, the request item of the case). Further, the international publication W〇2〇G7/m425 discloses that it is close to the rotor head. The bearing system uses a toroidal roller bearing, and the bearing close to the generator uses a spherical roller bearing. Compensating for the misalignment and tilting of the main shaft. However, according to the study by the inventors of the present application, it is not considered that the main shaft is supported by the two bearings having the self-aligning property, and the stator outer casing is supported by the torsion support member. It is suitable for fixing and maintaining the gap between the stator and the rotor. Fig. 8 is a diagram for explaining the reason. The following discussion, as shown in Fig. 8, supports the main shaft 103 by the second bearing 1〇1 and the second bearing 102, and by the torque The support member 1〇4 supports a structure in which the circumferential direction of the main shaft 103 acts on the torsion force of the stator case 1〇6 of the generator 105. Here, 1] is a relationship between the load point on the rotor head side and the first bearing 1〇1. The distance between the 丨2 dynasty 1 bearing 101 and the second bearing 102, and the distance from the 13th second bearing 102 to the point where the torsion support member 104 acts on the stator casing 〇6. Further, R, R2 The fulcrum reaction force 'R3' acting on the first bearing 1 〇1 and the second bearing 1 〇2 causes the torsion support member 1〇4 to act on the fulcrum of the stator casing 1〇6 148092.doc 201139843 reaction force. 2 bearings (first! bearing 1〇1, 2nd bearing ι〇2) The self-aligning bearings produce deflection angles γ! and γ2 at their respective positions. Moreover, due to the deflection angle γζ, the distance between the wind turbine and the wind power generator must be 丨3, even if the torque does not act on the torsion support. The workpiece 1〇4 also generates the fulcrum reaction force r3. Here, the magnitude of the fulcrum reaction force R3 is the product of the spring constant of the torsion support member 104 and the deformation amount δ. The fulcrum reaction force R3 causes the engine 1〇5 It is not preferable that the gap between the stator and the rotor is unbalanced. Especially in the case of using a permanent magnet synchronous generator (PMSG) as the generator 105, the problem of gap imbalance is more serious. In detail, in the permanent magnet synchronous generator (PMSG) in which the magnetic attraction of the field magnet or various electric powers acts, it is necessary to surely maintain the gap between the stator and the rotor, and it is necessary to reduce the displacement of various vibration modes. However, due to the fulcrum reaction force R3, the stator casing 1〇6 only displaces the amount of internal clearance of the generator bearing, and the stator casing 1〇6 itself is slightly deformed. Due to the displacement and deformation of the internal gap amount, the gap between the stator and the rotor is unbalanced, and in addition to the magnetic vibration caused by the rotation, the mode vibration caused by the deflection is also generated. Since the vibration of the flexural mode causes the vibration of the wind power generator to increase, it is not preferable. Further, since the fatigue load is also increased when the flexural mode vibration occurs, it is necessary to highly design the strength of the structural member (for example, the main shaft 103, the torsion support member 1〇4, the stator casing 1〇6, etc.) and also generate weight. Increase the problem. [Prior Art Document] [Patent Document] 148092.doc 201139843 [Patent Document 1] European Patent Application No. EP1327073B1 [Patent Document 2] European Patent Application No. EP20U917A1 [Patent Document 3] 曰本特开2009-09625号[Patent Document 4] International Publication No. WO2007/111425 SUMMARY OF INVENTION [Problem to be Solved by the Invention] Therefore, an object of the present invention is to provide a stator for preventing a generator in a direct drive type wind power generator A technique of unbalanced gaps with the rotor. [Means for Solving the Problem] In one aspect of the present invention, a direct drive type wind turbine generator includes: a main shaft having one end coupled to a rotor head of a wind turbine rotor; and a generator including a stator, a stator casing supporting the stator, and a connection a rotor at the other end of the main shaft; first and second bearings located between the rotor head and the generator and rotatably supporting the main shaft; and a torsion support member supporting the stator housing. The i-axis bearing is a self-aligning bearing, and the second bearing located closer to the generator than the second bearing is a non-aligning bearing. As the second bearing, a double row tapered roller bearing can be used. Further, as the bearing, for example, a tapered roller bearing, a cylindrical roller bearing, or a self-aligning bearing can be used. In one embodiment, the second bearing includes: a second and second inner wheel; a second and second outer wheel '· a first rotating body disposed between the inner wheel and the outer wheel; and the second inner wheel and the second inner wheel 2 a second rotating body between the outer wheels; and an energizing member °. The interval between the second outer wheel and the second inner wheel is variable, and the energizing member is configured to energize the second outer surface so that the inner circumferential surface of the second outer wheel approaches the outer circumferential surface of the second inner wheel. The second bearing f is accommodated and supported by the second bearing f. It is preferable to use a line contact or a point contact. In this case, the shaft is placed underneath: a cylindrical roller is inserted between the outer wheel bearing housing and the second outer wheel. For example, the second bearing preferably has a third third rotor that is disposed between the third inner wheel and the third outer wheel. *, and 汾 It is preferable that the stator casing has a concave surface on the opposite surface of the bearing opposite to the bearing and supporting the second bearing, and it is preferable that the end portion of the bearing housing is located and opposed. The face on the same face or the part of the bearing housing is located inside the recess. When the torque supporting member is provided to be coupled to the bearing supporting member for accommodating and supporting the second bearing, the torque supporting member preferably connects the bearing phase and the stator casing in the radial direction of the main shaft. The stator casing may have a center lining facing the bearing housing and a peripheral lining connected to the outer edge portion of the center portion. In this case, the center lining plate may be configured such that the center portion thereof is formed to be recessed from the outer edge portion, thereby providing a recessed portion to the outer stator α, and the outer peripheral lining may be formed to be formed as a torque support member. A dog-out portion whose outer edge of the concave portion of the function protrudes inward in the radial direction of the main axis. In this case, one of the bearing housings is housed in the recessed portion, and the dog outlet portion is defeated in the groove provided in the bearing housing, thereby coupling the stator housing and the bearing housing. In another aspect of the present invention, the bearing structure includes first and second inner wheels, first and second outer wheels, and a first rotating body disposed between the first inner ring and the second outer wheel. The second rotating body is placed between the second inner wheel and the second outer wheel; and the energizing 148092.doc 201139843 is variable and the energizing member wheel is provided in a mode other than the four-fourth mode. The inner circumferential surface of the second outer wheel is brought close to the second inner second outer wheel between the second outer wheel and the second inner wheel. According to the present invention, it is possible to prevent a gap imbalance between the stator and the rotor of the direct drive type wind power generation. % [Embodiment] A perspective view of the structure of the observation device and the electric device 1. The wind power generation system of the present embodiment is configured as a drive type wind power generator, and has the following configuration. Wind power installation! It has a tower 2 and a pedestal 3. The machine pedestal 3 is configurable at the upper end of the tower 2. On the nacelle pedestal 3, the third sleeves: 5 and the bearing housings 6 are provided, and are respectively disposed in the interior of the first bearing housing $ and the first ice bearing phase 6! The bearing 8 and the second bearing % can support the spindle 4 with reference to Fig. The main (4) end is connected to the rotor head of the windmill rotor (not shown), and the other end is connected to the generator 7. The generator 7 is further coupled to the second bearing housing 6 by the twisting member 20. Fig. 2 is a cross-sectional view of the wind turbine generator 1 of the present embodiment as seen from above. The generator 7 is provided with a stator 11 and a rotor (1), and the stator η is fixed by a break. The s + magnet rotor 12 has a rotor piece 15 that faces the field support field magnet 14 of the stator 11. The boss 16 of the end portion of the rotor piece 15 2 is connected to the main shaft / : in this embodiment, the bushing 16 is coupled to the end of the main shaft 4 in the present embodiment, but 16 can be connected to the main shaft 4 Or may be formed integrally. The generator bearings 17, 18 are disposed on the sleeve 16, and the stator housing 13 is supported by the motor bearings 17, 18 of the I48092.doc 201139843. Supported by the spindle motor bearings 17, 18 provided in the spindle bucket Stator housing! 3. The gap between the stator 11 and the rotor 12 can be effectively fixed. The torsion support 20 connects the stator housing 13 and the second shaft bearing housing 6. In the present embodiment, the torsion support 2G is provided with a pin 21, a boss 22, and a rubber sheath 23. The sleeve 22 is fixed to the stator housing 丨3, and the rubber bushing is inserted into the inside of the sleeve 22. Furthermore, the pin 21 is inserted into the rubber bushing 23, and the pin 21 is fixed to the second bearing housing 6°. The torsion force supporting member 2G is configured to support the circumferential force of the main shaft 4 to support the stator. The outer casing 13. As described above, in the configuration in which the main shaft is supported by two bearings having alignment and the stator housing is supported by the torsion support member, there is a problem that the gap between the stator and the rotor of the generator is unbalanced. In order to solve this problem, in the wind power generator of the present embodiment, a bearing having no self-aligning property, that is, a bearing that does not match the tilt of the main shaft 4 is used as the second bearing 9 3 of the bearing close to the generator 7 side, and is used. A bearing with self-aligning as the first bearing 8° more specifically 'uses, for example, a tapered roller bearing roller beaHng' 'circle' or a self-aligning bearing' as the first aspect, using, for example, a double tapered roller bearing (d〇uble taper roller bearing) ' As the second bearing 9. Fig. 3 is a view showing one of the structures of the second bearing 9 m^ 丨 U. The second bearing 9 is provided with an inner wheel 25 and an outer wheel 26' and is disposed at ^ r Rong is placed between 4 and 4 tapered rollers 27, 28. In Figure 3, although each circle shows a tapered roller 27 Η ., 28 'but must be resolved | Several tapered rollers 27 are attached to the main shaft (4) The circumferential sub-column of the king glaze 4 is arranged in one and a plurality of tapered rollers 28 are arranged side by side in the circumferential direction of the main shaft 4 to be arranged in a row. The inner wheel 148092.doc 201139843 25 is mounted on the main shaft 4, and the outer wheel 26 is attached to the second bearing housing 6. The inner ring 25 is tapered in such a manner that the center portion of the second bearing 9 is concave, and the outer ring 26 is tapered so that the core portion of the second bearing 9 is convex. The tapered rollers 27 and 28 are arranged such that their radii gradually decrease toward the center of the second bearing 9. With such a configuration, the second bearing 9 holds the main shaft 4 so as to be rotatable without being inclined. A non-aligning bearing is used as the second bearing 9, whereby the portion of the main shaft 4 closer to the side of the generator 7, the sleeve 16, the rotor 12, and the stator housing when the wind power generator 1 is operated 13 mechanical integration, thereby inhibiting the relative displacement between the members. That is, the variation of the relative positional relationship between the portion of the main shaft 4 that is closer to the side of the generator 7 than the second bearing 9 to the side of the generator 7, the sleeve 16, the rotor 12, and the member of the stator U is suppressed. The components are integrally shaped to move in the same unit (unh). This effectively keeps the gap between the stator turns and the rotor 12 fixed and prevents the gap from being unbalanced. In the present embodiment in which the bearing having no centering is used as the second pumping member 9, it is preferable to reduce the end gap of the second bearing 9 in order to more reliably maintain the gap, that is, it is preferable to reduce the rotation of the second bearing 9 The bearing structure of the gap between the body (ball or roller) and the inner wheel 25 and the wheel 26 is shown as a second bearing 9A which is formed by a method for reducing the gap, and (4) is constructed by the bearing box μ. Picture. The second bearing housing 6A includes the member 38, the pressure plate 39, the member 38, and the pressure plate 39 by the first jaw member 36, the intermediate member 37, the second ring, and the bolt 40. The intermediate member 37 and the second annular structure bolt 40 are fixed to the first annular member 36. 148092.doc 201139843 The second bearing 9A includes a first inner wheel 31a, a second inner wheel 31b, a spacer 32, a first outer wheel 33a, a second outer wheel 33b, a spring 35, and tapered rollers 34a and 34b. The first inner ring 31a, the second inner wheel 3 lb and the spacer 32 are inserted into the main shaft 4, and are fixed to the main shaft 4 by a nut 4a. The spacer 32 has a function of holding the first inner ring and the second inner wheel 3b at a desired distance. The outer ring 33a is sandwiched and held by the second ring member 36 and the t-member 37. The second outer ring 331) is pressed against the inner circumferential surface of the second annular member 38 and held. Here, the second outer wheel can slide in the axial direction of the main shaft 4. The tapered roller 34a is inserted in the first! The inner ring 31a and the i-th outer wheel 33a are interposed, and the tapered roller 34b is inserted between the second inner wheel 31b and the second outer wheel 33b. Here, one tapered roller 34a, 3 is illustrated in Fig. 4A, but it must be understood that a plurality of tapered rollers 34a are arranged side by side in the circumferential direction of the main shaft 4, and a plurality of tapered rollers 34b are attached. The columns of the main shaft 4 are arranged side by side in a row. Here, the first inner ring 3a is inclined with respect to the axial direction of the main shaft 4, and is biased toward the tapered roller 34a in the radial direction outward toward the generator 7. Further, the second inner ring 31b is inclined with respect to the axial direction of the main shaft 4, and is applied to the tapered roller 34b in the direction of the outer side in the radial direction toward the rotor head. In addition, the first outer ring 33a is inclined with respect to the axial direction of the main shaft 4, and applies a load to the tapered roller "a" toward the rotor head in the outer side in the 2 radial direction. Further, the second outer ring 33b is fixed relative to the main shaft. The axial tilt of 4 is applied to the tapered roller in the radial direction outward and toward the generator 7. With such a configuration, the axial load acting on the main shaft 4 and the light load F r are supported. A spring 35 is inserted between the second outer wheel 33b and the intermediate member 37, and 148092.doc 201139843 the second outer wheel 33b energizes the axial direction of the main shaft 4. The outer circumference of the second inner wheel 3 lb and the outer circumference of the second outer wheel 33b The circumferential surface is inclined with respect to the axial direction of the main shaft 4, so that the spring 35 energizes the second outer ring 33b such that the inner circumferential surface of the second outer ring 33b approaches the outer circumferential surface of the second inner ring 3 lb. The end gap of the second bearing 9, that is, the gap between the tapered roller 34b and the second inner ring 3ib, and the gap between the tapered roller 34b and the second outer ring 33b are reduced. Thus, the k can be compared with the main shaft 4. 2 bearing 9 is closer to the side of the generator 7, the sleeve 16, the rotor 12, and the stator The shell 13 is mechanically integrated, and effectively suppresses the relative displacement between the members such as Hai. This can effectively prevent the gap between the stator 11 and the rotor 12 from being unbalanced. The bearing structure as shown in Fig. 4A can further effectively improve the tapered roller 3 "There is a problem of the temperature difference between the inner wheel 3u, the second inner wheel, and the first outer wheel 33a and the second outer wheel 33b. When the load is applied to the axial direction of the main shaft 4 in the bearing structure & of Fig. 3, a large load is applied to the other conical; the dice row (for example, the tapered roller 28 column). This will shorten the odds of the second bearing 9 and it is not good. Further, when the spindle * rotates, the second axis & rises and the temperature of the inner wheel 25 rises more than the outer wheel %. If the temperature of the inner wheel 25 is relatively higher than the temperature of the outer wheel 26, the thermal expansion of the inner wheel 25 is also greater than that of the outer wheel 26' such that the mechanical load acting on the tapered rollers 27, 28 is increased. This will shorten the life of the tapered rollers 27, 28, which is not preferable. On the other hand, according to the configuration of Fig. 4A, the second bearing 9 is applied to the axial load 犄, and the s-load Fa is equally applied to the tapered rollers 34a, 34b by the action of the spring 35. Therefore, it is possible to prevent the life from being shortened by applying a large load to one of the tapered roller rows. In addition, the temperature rise of the first inner ring 31a and the second inner wheel 31b is larger than the temperature rise of the i-th outer wheel 33a and the second outer wheel 33b, as shown in Fig. 148092.doc • 12·201139843, the first inner wheel 31a and the second inner wheel. The thermal expansion of 31b is absorbed by the magazine 35. Therefore, the problem of the temperature difference between the i-th inner wheel 31a and the second inner wheel 31b and the first outer wheel 33a' second outer wheel 33b can be avoided. To further reduce the displacement of the spindle 4, as shown in Fig. 4A, three rows of tapered rollers can be provided. In the structure of the second bearing 9A of Fig. 4A, the third inner wheel 31c and the third outer wheel 33c are additionally provided, and a tapered roller 34^ is provided therebetween. A spacer 32a is provided between the first inner ring 31a and the third inner wheel 31c, and a spacer 32b is provided between the second inner wheel 31b and the third inner wheel 31c, whereby the i-th inner wheel 3u and the third inner wheel 31c are held at At a desired interval, the second inner ring 31b and the third inner wheel 31.c are kept at a desired interval. Further, the outer ring 33a and the third outer ring 33c are sandwiched and held by the first annular member 36a and the intermediate member 37. At this time, the spacer 36b is inserted between the first outer ring 33a and the third outer wheel 33c, and the i-th outer wheel 3 3 a and the second outer wheel 3 3 c are held at a desired interval. Further, in the structure of Fig. 4B in which three rows of rotating bodies are provided, the balls may be used instead of the tapered rollers 34a, 34b, and 34c as the rotating body. It is preferable to use the ball as the rotating body to reduce the cost. In the structure of Figs. 4A and 4B, the second outer ring 33b must be slidable in the axial direction on the inner circumferential surface of the first ring-shaped member 38. At this time, when the second annular member 38 is increased in size, the manufacturing error of the second annular member 38 may increase, and the second outer ring 33b may not slide on the inner circumferential surface of the second annular member 38. Case. In order to move the second outer ring 33b relative to the second annular member 38, the second outer wheel 148092.doc -13-
S 201139843 33b與第2環狀構件38之間之接觸較佳為線接觸或點接觸 (非面接觸）。藉此，使作用於第2外輪33b與第2環狀構件％ 之間之摩擦變小，從而第2外輪33b變得容易相對於第2環 狀構件3 8移動。 更具體而言，如圖4C所示，亦可於第2外輪33b與第2環 狀構件38之間插入圓柱滾子51。圖4(：雖僅圖示有丨個圓柱 滾子51，但必須瞭解圖仏係於主軸4之周向並列配置有複 數個圓柱料51。各圓柱滾子51係以使其中心、軸平行於主 軸4之軸向的方式配置。如圖4]〇及圖4E所示，圓柱滾子η 藉由保持器52而被保持於期望之位置。圓柱滾子51盥 環狀構件38為線接觸，又圓柱滾子51與第2外輪33b為線接 觸，藉此使第2外輪33b變得容易相對於第2環狀構件兜移 動。在圖4C〜圖4E中乃使用圓柱滾子，但亦可取代圓柱滾 子而改為使用滾珠。又’如圖4C〜圖4E般於第2外輪3脑 第2環狀構件38之間插入圓柱滚子或滾珠之構造，亦可適 用於圖4B之設置3列轉動體之構造。 較佳為縮短從扭力支持件2〇對定子外殼Η作用力之位置 至第2轴承9為止的主車由4之軸向之距離，以it 一步抑制主 軸4之較第2軸承9更靠近發電機7之側之部分、轴套16、轉 子12、及定子外殼13之間產生相對位移，並進—步降低定 子11與轉子12之間之間隙之不平衡。 因此，如圖5所示’較佳為於定子外殼Η上設置凹部 3a使第2轴承相6之端部位於定子外殼之凹部⑴之 内。卩。又，第2軸承箱6之端部以亦可位於與對向於定子外 148092.doc 201139843 殼13之第2軸承箱6之對向面13b相同的面上。無論是何種 情況皆可縮短從扭力支持件2〇對定子外殼丨3作用力之位置 至第2軸承9為止的主軸4之軸向之距離。 又，圖6係顯示用於縮短從扭力支持件對定子外殼13作 用力之位置至第2軸承9為止之距離之其他構造的圖。在圖 6之構造中，將圓盤狀之扭力支持構件24直接接合於第2軸 承箱6之端部，進而將定子外殼13連結於扭力支持構件24 之外周部。於扭力支持構件24之中心設置有開口，使主軸 4插通於a亥開口。再者，在圖6之構造中，由於第2軸承9與 疋子外殼13之間之距離近，故未設置靠近第2軸承9之側之 發電機轴承1 7。 根據如此之構造，可使從扭力支持構件24對定子外殼13 作用力之位置設於第2軸承箱6之端部。即，扭力支持構件 24係構成為從第2軸承箱6之端部於主軸4之半徑方向延 伸彳之而與疋子外殼13連結。因此’可縮短從扭力支持構 件24對定子外殼13作用力之位置至第2軸承9為止之距離。 此可有效進一步抑制主軸4之較第2軸承9更靠近發電機7之 側之部分、軸套16、轉子12、及定子外殼13之間產生相對 位移。 最理想的是使從扭力支持件2〇對定子外殼13作用力之位 置與第2轴承9之中心一致。圖7A、圖川係顯示可使從扭 力支持件20對定子外殼13作用力之位置與第2轴承9之中心 一致之構造的圖。 在圖7A、圖7B之構造中，於定子外殼！ 3形成凹部，於 148092.doc 201139843 該凹部中’收容第2軸承箱6C之一部分。詳細而言，定子 外殼u之正面襯板由外周部襯板41與巾㈣襯板42構成。 外周部襯板41接合於令心部襯板42之外緣部。中心部襯板 42其中心部分設為較外緣部下凹之形狀。 此外外周襯板4 1之一部分從與中心部襯板42之接合 位置向半徑方向内側突出’且將該突出之部分(突出部叫 嵌入至設置於第2軸承箱6C之槽44，藉此支持定子外殼 13。即，在本實施形態、巾，定子外殼13之外周部概板以 突出部4U作為扭力支持件發揮功能。詳細而言，於圖7A 所示之第2轴承箱6C ’形成有槽44、與橫跨槽料而貫通於 主軸4之轴向之開口 45。另-方面，於外周部襯板41之突 出部4la形成有開口 41b。在外周部襯板以突出部4u嵌 入至設置於第2轴承箱6C之槽44的狀態下，將銷43插入第2 軸承箱6C之Μ 口 45。銷43係以貫通設置於第2轴承箱冗之 開口 45、與設置於外周部襯板41之突出部“a之開口 4^的 方式插入。藉此將定子外殼13固定於第2轴承箱6c^ 在圖7A、圖7B之構造中’由於外周部襯板“之突出部 41a將第2轴承箱6C之中間部位與定子外殼^連結於主軸4 之半徑方向，因此可縮短從扭力支持件2〇對定子外殼Η作 用力之位置至第2軸承9之中心為止的主軸4之轴向之距 離，而理想的是可使其一致。這可進一步抑制主轴4之較 第2軸承9更靠近發電機7之側之部分、軸套16、轉子、及 定子外殼13之間產生相對位移，並進__步降低定子u與轉 子12間之間隙之不平衡故而較佳。 148092.doc •16- 201139843 【圖式簡單說明】 圖1係顯示本發明之一實施形態之風力發電裝置之構成 的立體圖。 圖2係顯示圖1之風力發電機之構成之剖面圖。 圖3係顯示位於靠近發電機側之第2軸承之構成之一例的 剖面圖。 圖4A係顯示第2軸承之構成之其他例之剖面圖。 圖4B係進一步顯示第2軸承之構成之其他例之剖面圖。 圖4C係進—步顯示第2軸承之構成之其他例之剖面圖。 圖4D係詳細顯示圖4C之第2軸承之構成之剖面圖。 圖4E係詳細顯示圖4C之第2轴承之構成之立體圖。 圖5係顯示圖!之風力發電裝置之構成之放大剖面圖。 圖6係顯示本發明之其他實施形態之風力發電裝置之構 成的立體圖。 圖7A係顯示本發明之—實施形態之風力發電裝置之構成 的立體圖。 圖7B係顯示訊之風力發電裳置之構成之剖面圖。 比圖8係說明在直接驅動型風力發電裝置中，2個軸承兩者 皆具有調心性之情況所產生之問題的圖。 【主要元件符號說明】 1 風力發電裝置 2 塔架 3 機艙台座 主轴 148092.docThe contact between S 201139843 33b and the second annular member 38 is preferably a line contact or a point contact (non-face contact). Thereby, the friction acting between the second outer ring 33b and the second annular member % is reduced, and the second outer ring 33b is easily moved relative to the second ring member 38. More specifically, as shown in Fig. 4C, a cylindrical roller 51 may be inserted between the second outer ring 33b and the second ring member 38. Fig. 4 (: Although only one cylindrical roller 51 is illustrated, it is necessary to understand that the plurality of cylindrical materials 51 are arranged side by side in the circumferential direction of the main shaft 4. The cylindrical rollers 51 are arranged such that their centers and axes are parallel. Arranged in the axial direction of the main shaft 4. As shown in Fig. 4 and Fig. 4E, the cylindrical roller η is held at a desired position by the retainer 52. The cylindrical roller 51 盥 the annular member 38 is in line contact. Further, the cylindrical roller 51 and the second outer ring 33b are in line contact, whereby the second outer ring 33b is easily moved relative to the second annular member pocket. In FIGS. 4C to 4E, a cylindrical roller is used, but The cylindrical roller can be used instead of the cylindrical roller. The structure of inserting a cylindrical roller or a ball between the second annular member 38 of the second outer wheel 3 as shown in FIG. 4C to FIG. 4E can also be applied to FIG. 4B. The structure of the three rows of rotating bodies is provided. It is preferable to shorten the distance from the axial direction of the main vehicle from the position where the torsion supporting member 2 is biased to the stator casing 至 to the second bearing 9, and to suppress the spindle 4 in one step. A relative position is generated between the portion closer to the side of the generator 7 than the second bearing 9, the sleeve 16, the rotor 12, and the stator casing 13. Moving, and stepping down, the imbalance between the gap between the stator 11 and the rotor 12 is reduced. Therefore, as shown in Fig. 5, it is preferable to provide a recess 3a on the stator casing so that the end of the second bearing phase 6 is located in the stator casing. In the recess (1), the end of the second bearing housing 6 may be located on the same surface as the opposing surface 13b of the second bearing housing 6 that faces the outer casing 148092.doc 201139843. In any case, the distance from the axial force of the torsion support member 2 to the position of the stator housing 3 to the axial direction of the main shaft 4 from the second bearing 9 can be shortened. Further, Fig. 6 shows the support for shortening from the torque. A view showing another structure of the distance from the position of the stator casing 13 to the second bearing 9. In the structure of Fig. 6, the disk-shaped torque supporting member 24 is directly joined to the end of the second bearing housing 6. Further, the stator case 13 is coupled to the outer peripheral portion of the torsion support member 24. An opening is provided at the center of the torsion support member 24, and the main shaft 4 is inserted into the a-hai opening. Further, in the structure of Fig. 6, the second The distance between the bearing 9 and the rafter shell 13 is close, so it is not set close. The generator bearing 17 on the side of the bearing 9 is provided in such a position that the position at which the torque supporting member 24 exerts a force on the stator housing 13 can be provided at the end of the second bearing housing 6. That is, the torsion supporting member 24 is The end portion of the second bearing housing 6 is extended from the end portion of the second bearing housing 6 in the radial direction of the main shaft 4, and is coupled to the latch housing 13. Therefore, the position from the torque supporting member 24 to the stator housing 13 can be shortened to the second bearing 9 The distance between the shaft 4, the sleeve 16, the rotor 12, and the stator casing 13 is more effectively suppressed from the portion of the main shaft 4 closer to the side of the generator 7 than the second bearing 9. The position of the torsion support member 2 to the stator housing 13 is the same as the center of the second bearing 9. Fig. 7A and Fig. 7 are views showing a structure in which the position at which the torque member 20 applies a force to the stator case 13 coincides with the center of the second bearing 9. In the configuration of Figures 7A, 7B, in the stator housing! 3, a recess is formed, and one of the second bearing housings 6C is accommodated in the recess 148092.doc 201139843. In detail, the front lining of the stator casing u is composed of a peripheral lining 41 and a lining 42. The outer peripheral liner 41 is joined to the outer edge portion of the core liner 42. The center portion liner 42 has a central portion which is formed in a concave shape from the outer edge portion. Further, a part of the outer circumferential lining 41 protrudes from the joint position with the center lining 42 toward the inner side in the radial direction, and the protruding portion (the protruding portion is inserted into the groove 44 provided in the second bearing housing 6C, thereby supporting In the present embodiment, the outer peripheral portion of the outer casing of the stator casing 13 functions as a torsion support member. In detail, the second bearing housing 6C' shown in Fig. 7A is formed. The groove 44 and the opening 45 that penetrates the axial direction of the main shaft 4 across the groove. On the other hand, the projection 41a of the outer peripheral liner 41 is formed with an opening 41b. The outer peripheral liner is embedded with the projection 4u. In the state of the groove 44 of the second bearing housing 6C, the pin 43 is inserted into the opening 45 of the second bearing housing 6C. The pin 43 is inserted through the opening 45 of the second bearing housing and is provided on the outer peripheral portion. The opening 41 of the projection 41 of the plate 41 is inserted. Thereby, the stator housing 13 is fixed to the second bearing housing 6c. In the configuration of Figs. 7A and 7B, the projection 41a of the outer peripheral lining is The middle portion of the second bearing housing 6C and the stator housing ^ are coupled to the radial direction of the main shaft 4 Therefore, the distance from the axial force of the torsion support member 2 to the stator housing 至 to the axial direction of the second bearing 9 can be shortened, and it is desirable to make them uniform. This can further suppress the spindle 4 Relatively displaced between the portion of the second bearing 9 closer to the side of the generator 7, the sleeve 16, the rotor, and the stator casing 13, and further reducing the imbalance between the stator u and the rotor 12, and thus preferably BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a perspective view showing a configuration of a wind power generator according to an embodiment of the present invention. Fig. 2 is a cross-sectional view showing the configuration of the wind power generator of Fig. 1. 3 is a cross-sectional view showing an example of a configuration of a second bearing located close to the generator side. Fig. 4A is a cross-sectional view showing another example of the configuration of the second bearing. Fig. 4B is a view showing another example of the configuration of the second bearing. Fig. 4C is a cross-sectional view showing another example of the configuration of the second bearing. Fig. 4D is a cross-sectional view showing the structure of the second bearing of Fig. 4C in detail. Fig. 4E shows the second bearing of Fig. 4C in detail. Stereoscopic view Fig. 5 is an enlarged cross-sectional view showing a configuration of a wind power generator of the present invention. Fig. 6 is a perspective view showing a configuration of a wind power generator according to another embodiment of the present invention. Fig. 7A is a view showing a wind power generation according to an embodiment of the present invention. Fig. 7B is a cross-sectional view showing the structure of the wind power generation device. Fig. 8 is a view showing the case where both bearings have the self-aligning property in the direct drive type wind power generator. Diagram of the problem [Explanation of main components] 1 Wind turbine 2 Tower 3 Cabin pedestal 148092.doc
S -17- 201139843 4a 螺母 5 第1軸承箱 6 第2軸承箱 7 發電機 8 第1軸承 9 第2軸承 11 定子 12 轉子 13 定子外殼 13a 凹部 13b 對向面 14 場磁鐵 15 轉子片 16 軸套 17 ' 18 發電機軸承 20 扭力支持件 21 銷 22 軸套 23 橡膠襯套 24 扭力支持構件 25 内輪 26 外輪 27、28 圓錐滾子 31a 有第1内輪 148092.doc -18- 201139843 31b 第2内輪 31c 第3内輪 32、32a、32b ' 36b 墊片 33a 第1外輪 33b 第2外輪 33c 第3外輪 34a、34b、34c 圓錐滾子 35 彈簀 36 ' 36a 第1環狀構件 37 中間構件 38 第2環狀構件 39 壓板 40 螺栓 41 外周部觀板 41a 突出部 41b 開口 42 中心部概板 43 銷 44 槽 45 開口 51 圓柱滾子 52 保持器 101 第1軸承 102 第2軸承 148092.doc - 19- 201139843 103 主轴 104 扭力支持件 105 發電機 106 定子外殼 Fa 車由向載荷 Fr 徑向載荷 Yl ' J2 撓曲角 148092.doc -20-S -17- 201139843 4a Nut 5 1st bearing housing 6 2nd bearing housing 7 Generator 8 1st bearing 9 2nd bearing 11 stator 12 rotor 13 stator housing 13a recess 13b opposite surface 14 field magnet 15 rotor piece 16 bushing 17 ' 18 Generator bearing 20 Torque support 21 Pin 22 Bushing 23 Rubber bushing 24 Torque support member 25 Inner wheel 26 Outer wheel 27, 28 Tapered roller 31a With inner wheel 148092.doc -18- 201139843 31b 2nd inner wheel 31c Third inner wheel 32, 32a, 32b' 36b washer 33a first outer wheel 33b second outer wheel 33c third outer wheel 34a, 34b, 34c tapered roller 35 magazine 36' 36a first annular member 37 intermediate member 38 second ring Member 39 press plate 40 bolt 41 outer peripheral plate 41a projection 41b opening 42 central portion plate 43 pin 44 slot 45 opening 51 cylindrical roller 52 retainer 101 first bearing 102 second bearing 148092.doc - 19- 201139843 103 Spindle 104 Torque Support 105 Generator 106 Stator Housing Fa Vehicle Loaded Fr Radial Load Yl ' J2 Deflection Angle 148092.doc -20-