201200738 六、發明說明： 【發明所屬之技術領域】 本發明係關於具備有具有從內 形狀之扇翼的電動送風機及搭載其 【先前技術】 習知的電動送風機，雖例如东 顯示’但一般係由：護罩、及被配 、及被複數配置於彼等之間的葉片 護罩側比輪轂側更大地傾斜，藉由 及真空壓力。 特別是於專利文獻1中，記載 罩與後面護罩（輪轂），藉由鉚合 附近的扇翼之曲率半徑時，藉由使 側更大地傾斜，於內周側中，前面 ，在外周側中，對於後面護罩略微 轉風扇。 另外，類似習知之電動送風機 如揭示於以下的專利文獻2。於習 跨輪轂與護罩的外周部間之複數片 央部形成風扇吸入口，使前述各葉 結合部的位置比輪轂側結合部位置 量之離心風扇的葉輪，其特徵爲： 中之輪轂側葉片出口角度和護罩側 緣至外緣之間被扭轉的 之電動吸塵器。 r以下的專利文獻1也有 置於其對向位置的主板 所構成，前述葉片係使 使高速旋轉來獲得風量 :扇翼爲被夾於前面護 而被固定，比較吸入口 前面護罩側比後面護罩 護罩側朝旋轉方向傾斜 垂直之電動送風機的旋 的習知風扇之構造，例 知的風扇中，爲具有橫 的葉片，且於護罩的中 片的後緣部中之護罩側 在反旋轉方向偏離特定 使前述各葉片的後緣部 葉片出口角度相等。 -5- 201200738 [先前技術文獻] [專利文獻] [專利文獻1 ]專利第2 7 5 7 5 0 1號公報（日本專利特開 平3 - 1 5 1 5 9 8號公報） [專利文獻2 ]專利第2 7 3 0 3 9 6號公報（日本專利特開 平4- 1 20753號公報） 【發明內容】 [發明所欲解決之課題] 於習知的電動送風機（專利文獻1)中，對於入口的 氣流，並無進行詳細的葉片角度分布的調整，葉輪內部的 流動容易產生剝離和逆流，成爲能量損失（效率降低）的 原因。特別是於電動送風機的吸入口，以旋轉之送風機和 導引吸入氣流之入口環來進行葉片吸入口和動葉輪出口之 壓力差所產生的洩漏氣流的抑制。因此，於吸入口，在旋 轉體和靜止體的連結部產生段差，考慮此段差氣流和洩漏 氣流，爲了調整與葉片入口角度的匹配及葉片的負載分布 ，需要瞭解葉片內部的現象，將全體做成最佳。即在有入 口洩漏當中，需要與洩漏匹配來調整葉片角度分布，使葉 片的負載分布成爲最佳，來抑制剝離和逆流，以謀求高效 率。另外，對於入口的氣流，並無進行詳細的風扇葉片角 度分布的調整，在吸入口附近，葉輪的葉片之傾斜不與空 氣的流入方向一致，空氣碰觸扇翼的側面，衝擊損失有變 大之虞。 -6 - 201200738 另外，於前述電動送風機（專利文獻1)中，從軸方 向來看的情形，前述葉片對於前述主板的傾斜大，在藉由 板金的組裝過程中，由於壓縮等，葉片或鉚合容易崩潰， 存在組裝上的課題。 另外，於習知的電動送風機（專利文獻1)中，在內 周側（流入側），儘管前面護罩側朝旋轉方向傾斜，但外 周側（流出側）對於後面護罩爲略微垂直，於外周側（流 出側），從前面護罩至後面護罩，空氣的流動變得不均勻 ’即從前面護罩至後面護罩，壓力分布或速度分布變得不 均勻，有能量損失變大之虞。 另外’於習知的風扇（專利文獻2)中，爲了使從風 扇流出的氣流有效率地減速，形成設置於風扇下游之靜止 翼（例如’擴散翼）之情形，將葉片的後緣部中之護罩側 結合部的位置比輪轂側結合部位置於反旋轉方向偏離特定 量之離心風扇的葉輪中，並不謀求與靜止翼之氣流的匹配 ’靜止翼的翼間內容易產生氣流的剝離和逆流，成爲能量 損失（效率降低）的原因。 因此’本發明目的在於··使旋轉軸方向各剖面中之葉 片的形狀適當化，可以抑制葉片間流路之氣流的剝離或逆 流’或者可以降低在葉片出口之氣流的平均流速，或者可 以抑制從葉片出口之護罩至輪轂之流速分布變得不均句， 藉此’提供高效率的電動送風機及搭載其之電動吸塵器。 另外’本發明目的在於提供：於輪轂和護罩鉚合安裝 葉片時’可以抑制葉片壓縮之電動送風機及搭載其之電動 201200738 吸塵器。 [解決課題之手段] 本發明之特徵爲：各葉片，係從半徑方向內緣至半徑 方向外緣，以旋轉軸方向爲基準，從朝旋轉方向側扭轉的 狀態被朝反旋轉軸方向側扭轉，之後，再度被朝旋轉方向 側扭轉。 或者，本發明之特徵爲：各葉片，其從與輪轂的連接 部朝與護罩的連接部之旋轉軸方向的形成方向，於葉片的 半徑方向外緣部，係與旋轉軸方向略微一致，或以旋轉軸 方向爲基準，朝旋轉方向側傾斜，進而各葉片，爲具有： 其旋轉軸方向的形成方向，於葉片的半徑方向中間部，以 旋轉軸方向爲基準，朝旋轉方向側傾斜的部分及對於旋轉 軸方向朝反旋轉方向側傾斜的部分。 或者，本發明之特徵爲：從旋轉軸方向來看的情形， 葉片與輪轂的連接部中之輪轂側弧形線與葉片之和護罩的 連接部中之護罩側弧形線，於從半徑方向內緣至半徑方向 外緣，至少在2處交叉。 或者，本發明之特徵爲：如將對於連結葉片的任意位 置與旋轉軸的軸心之直線的正交線，與從旋轉軸方向來看 ，和彎曲的葉片之外面的接線所形成的角度定義爲葉片角 度時，葉片的輪轂側之葉片角度，特別是於半徑方向外緣 部中，比葉片的護罩側之葉片角度還小。 201200738 [發明效果] 如依據本發明，各葉片，從半徑方向內緣至半徑方向 外緣，以旋轉軸方向爲基準，從朝旋轉方向側扭轉的狀態 被朝反旋轉軸方向側扭轉，之後，再度被朝旋轉方向側扭 轉’藉此，旋轉軸方向各剖面中之葉片的形狀被適當化， 可以抑制葉片間流路之氣流的剝離或逆流。另外，可以降 低在葉片出口之氣流的平均流速。另外，可以抑制從葉片 出口之護罩至輪轂之流速分布變得不均勻。藉此，可以提 升電動送風機之效率，也可以提升電動送風機及搭載其之 電動吸塵器之吸入功率。 如依據本發明，各葉片，其從與輪轂的連接部朝與護 罩的連接部之旋轉軸方向的形成方向，於葉片的半徑方向 外緣部，係與旋轉軸方向略微一致，或以旋轉軸方向爲基 準，朝旋轉方向側傾斜，進而各葉片，爲具有：其旋轉軸 方向的形成方向，於葉片的半徑方向中間部，以旋轉軸方 向爲基準，朝旋轉方向側傾斜的部分及對於旋轉軸方向朝 反旋轉方向側傾斜的部分，藉此，旋轉軸方向各剖面中之 葉片的形狀被適當化，可以抑制葉片間流路之氣流的剝離 或逆流。另外，可以降低在葉片出口之氣流的平均流速。 另外，可以抑制從葉片出口之護罩至輪轂之流速分布變得 不均勻。藉此，可以提升電動送風機之效率，也可以提升 電動送風機及搭載其之電動吸塵器之吸入功率。 如依據本發明，從旋轉軸方向來看的情形，葉片與輪 轂的連接部中之輪轂側弧形線與葉片之和護罩的連接部中 -9 - 201200738 之護罩側弧形線，於從半徑方向內緣至半徑方向外緣，至 少在2處交叉，藉此，在將葉片鉚合安裝於輪轂與護罩時 ，藉由以此交叉部分來鉚合，可以抑制葉片壓縮。進而， 旋轉軸方向各剖面中之葉片的形狀被適當化，可以抑制葉 片間流路之氣流的剝離或逆流。另外，可以降低在葉片出 口之氣流的平均流速。另外，可以抑制從葉片出口之護罩 至輪轂之流速分布變得不均勻。藉此，可以提升電動送風 機之效率，也可以提升電動送風機及搭載其之電動吸塵器 之吸入功率。 如依據本發明，如將對於連結葉片的任意位置與旋轉 軸的軸心之直線的正交線，與從旋轉軸方向來看，和彎曲 的葉片之外面的接線所形成的角度定義爲葉片角度時，葉 片的輪轂側之葉片角度，特別是於半徑方向外緣部中，比 葉片的護罩側之葉片角度還小，藉此，旋轉軸方向各剖面 中之葉片的形狀被適當化，可以抑制葉片間流路之氣流的 剝離或逆流。另外，可以降低在葉片出口之氣流的平均流 速。另外’可以抑制從葉片出口之護罩至輪轂之流速分布 變得不均勻。藉此，可以提升電動送風機之效率，也可以 提升電動送風機及搭載其之電動吸塵器之吸入功率。 【實施方式】 本發明爲一種電動送風機，係具備：圓環狀護罩、及 面對護罩配置的輪轂、及於圓周方向被複數配置於護罩與 輪轂之間的葉片、及轉動護罩與輪轂及葉片之電動部之電 -10- 201200738 動送風機’其特徵爲：各葉片’係以平板來形成，各葉片 ’係從半徑方向內緣朝半徑方向外緣，以旋轉軸方向爲基 準’從朝旋轉方向側扭轉的狀態被至反旋轉軸方向側扭轉 ，之後，再度被朝旋轉方向側扭轉。 本發明爲一種電動送風機’係具備：圓環狀護罩、及 面對護罩配置的輪轂、及於圓周方向被複數配置於護罩與 輪轂之間的葉片、及轉動護罩與輪轂及葉片之電動部之電 動送風機’其特徵爲：各葉片，係以平板來形成，各葉片 ’其從與輪轂的連接部朝與護罩的連接部之旋轉軸方向的 形成方向，於葉片的半徑方向外緣部，係與旋轉軸方向略 微一致，或以旋轉軸方向爲基準，朝旋轉方向側傾斜，各 葉片’爲具有：其旋轉軸方向的形成方向，於葉片的半徑 方向中間部’以旋轉軸方向爲基準，朝旋轉方向側傾斜的 部分及對於旋轉軸方向朝反旋轉方向側傾斜的部分。 本發明爲一種電動送風機，係具備：圓環狀護罩、及 面對護罩配置的輪轂、及於圓周方向被複數配置於護罩與 輪轂之間的葉片、及轉動護罩與輪轂及葉片之電動部之電 動送風機’其特徵爲：各葉片，係以平板來形成，從旋轉 軸方向來看的情形，葉片與輪轂的連接部中之輪轂側弧形 線與葉片之和護罩的連接部中之護罩側弧形線，於從半徑 方向內緣至半徑方向外緣，至少在2處交叉。 本發明爲一種電動送風機，係具備：圓環狀護罩、及 面對護罩配置的輪轂、及於圓周方向被複數配置於護罩與 輪轂之間的葉片、及轉動護罩與輪轂及葉片之電動部之電 -11 - 201200738 動送風機’其特徵爲：各葉片，係以平板來形成，如將對 於連結葉片的任意位置與旋轉軸的軸心之直線的正交線， 與從旋轉軸方向來看，和彎曲的葉片之外面的接線所形成 的角度定義爲葉片角度時，葉片的輪轂側之葉片角度，於 半徑方向內緣部及半徑方向外緣部中，比葉片的護罩側之 葉片角度還小。 如依據本發明，旋轉軸方向各剖面中之葉片的形狀被 適當化，可以抑制葉片間流路之氣流的剝離或逆流。另外 ，可以降低在葉片出口之氣流的平均流速。另外，可以抑 制從葉片出口之護罩至輪轂之流速分布變得不均勻。藉此 ，可以提升電動送風機之效率，也可以提升電動送風機及 搭載其之電動吸塵器之吸入功率。另外，如依據本發明， 藉由使入口洩漏和葉片角度分布匹配，得以抑制葉輪內部 的氣流中之剝離現象和逆流現象，可以謀求高效率。 另外，在將葉片鉚合安裝於輪轂與護罩時，藉由以此 交叉部分來鉚合，可以抑制葉片壓縮。另外，如依據本發 明，藉由使鉚合位置適當化，可以提高組裝精度。 另外，如依據本發明，在葉片的內緣部，可以使葉片 傾斜來和空氣的流入方向一致，得以抑制空氣碰觸葉片的 側面，使得衝擊損失減少。另外，如依據本發明，可以謀 求和設置於此旋轉的葉片的下游之靜止的葉片的氣流之匹 配，可以降低旋轉之葉片的內部的損失及靜止的葉片的內 部之刹離損失’可使能量損失減少。 以下，依據圖面來詳細說明本發明的實施例1、實施 -12- 201200738 例2。 [實施例1] 以下，利用圖面說明本發明之一實施例。 首先’利用第1圖說明電動吸塵器整體。從模型地表 示於第1圖之電動吸塵器本體100之上所見到的橫剖面圖中 ，說明電動吸塵器本體100的構造。如將裝著電動吸塵器 本體100的軟管接頭101側當成電動吸塵器本體100的前側 時’於電動吸塵器本體100，於其前端具備可以裝卸自如 之軟管接頭101。於電動吸塵器本體100的前側具備有保持 紙袋103用之集塵室102，於電動吸麈器本體100的後側具 備收納電動送風機106用之電動機室105，於集塵室102和 電動機室105之間，具備抑制集塵室1〇2內的塵埃流入電動 機室105用之過濾器部1〇4。集塵室1〇2和電動機室105係透 過過濾器部104連通。於集塵室1〇2具備可以裝卸自如之紙 袋1 〇 3。紙袋1 0 3的開口和軟管接頭1 〇 1連通。塵埃一堆積 於紙袋1 〇3內時，紙袋1 03膨脹，對於紙袋1 〇3的開口，位 於相反側之底部會抵接過濾器部1 0 4。於電動機室1 0 5具備 產生吸引力之電動送風機106。於電動送風機106的前側之 兩端和電動機室1 05的前側的內壁面之間，具備抑制電動 送風機106的振動傳達至電動吸塵器本體100用之防振橡膠 1 〇7 (防振構件）。防振構件也可以彈簧來代替橡膠。電 動送風機106係於其前端具備吸入空氣用之送風機入口 108 ’於後側側方具備將空氣排出用之送風機出口 1 09。且送 •13- 201200738 風機入口 108對於過濾器部104爲開口。於電動機室i〇5的 側方具備捲繞收納電源線用之電源線捲軸1 1 〇。於電動送 風機1 06的後側兩側方具備車輪。另外，雖未圖示出，於 軟管接頭101連接有軟管，於軟管連接有接受電動吸塵器 本體100的ΟΝ/OFF等之操作用的操作管，於操作管連接有 可以伸縮自如的延長管，於延長管連接有吸入件。軟管接 頭1 〇 1存在側（上游側）爲電動吸塵器本體1 〇 〇的前側，相 反側爲電動吸塵器本體1〇〇的後側。軟管接頭101、軟管、 操作管、延長管，並非必要的構成，形成於操作管之操作 部或吸入件也可以直接形成於電動送風機106。從上來看 電動吸塵器本體100，正交於電動吸塵器本體100的前後方 向的方向，爲電動吸塵器本體100的左右方向。所謂側方 係指比電動吸塵器本體1 0 0的左右方向的中心更偏向左側 或右側之側。電動送風機1 06可以被載置爲送風機入口 1 08 朝電動吸塵器本體1 00的前側之橫方向（橫向放置），也 可以被載置爲送風機入口 108朝電動吸塵器本體100的上側 之縱方向（縱向放置）。 接著，說明電動吸塵器本體100內的氣流。從軟管接 頭101流入的空氣，進入集塵室102。於第1圖中，作爲集 塵手段雖表示了紙袋1 0 3，但不管紙袋的材質。另外，在 旋風方式的情形，代替紙袋1 03，被收容於旋風室（旋風 式集塵箱）。利用紙袋103，大部分的塵埃被去除的空氣 ，進而通過過濾器部104，於此處，細微的塵埃也被去除 。之後，氣流流入電動機室105。電動送風機1〇6係透過防 -14- 201200738 振橡膠i〇7而被懸掛於電動機室1〇5，從送風機入口 1〇8流 入的二氣藉由電動送風機106被昇壓後，從送風機出口 1〇9 被排出。 接著’利用第2圖說明電動送風機1〇6。電動送風機 106係由：吸入空氣用之送風機2〇1 (風扇部）與驅動送風 機201用之電動機2〇2(驅動部）所構成。 電動機202係於由機威203及後端蓋2〇4所形成的電動 機外殼支擦有旋轉軸205’於旋轉軸205安裝有轉子206。 於轉子206的外周配置有固定部之定子2〇7。對於旋轉部的 轉子206之電氣的供給’係藉由碳刷208及與其接觸之整流 器209所傳達。 送風機201之構造爲：被直結於旋轉軸205之葉輪21〇 、及被設置於葉輪210的外周側之擴散翼211、及對於擴散 翼211夾住隔間板212而被配置於對面之返回導引213係被 收容於風扇殻214內。於葉輪210形成有複數個葉片（動翼 )。擴散翼211和旋轉軸205並無連結，所以並不旋轉。於 擴散翼211也形成有複數個葉片（靜止翼）。葉輪210於圓 環狀的中心部2 1 5中，係和風扇殻2 1 4側所具備的密封材 216槪略接觸，具有防止空氣洩漏的構造。 通過相當於第1圖的送風機入口 108之電動送風機入口 217的空氣，暫且通過中心部215附近後，被以葉輪210昇 壓及增速。之後，通過擴散翼211，氣流略180度轉向，流 入返回導引2 1 3，於此過程中，氣流被減速，減速部分導 致壓力上升。通過返回導引213的氣流，流入電動機的機 -15- 201200738 殻203內，冷卻轉子206、定子207、碳刷208、整流器209 等後被排氣。旋轉軸205的軸方向和電動吸塵器本體1〇〇的 前後方向略微一致。以旋轉軸205爲基準，和軸方向正交 的方向爲半徑方向。 本發明作爲對象的吸塵器用電動送風機的葉輪外徑， 大約在Φ 60mm〜φ 1 2 0mm的範圍，葉片出口高度大約在6 〜12mm的範圍，葉片的厚度大約爲〇.5~1.5mm的範圍，葉 片數量大約爲6〜9片的範圍，輸入大約爲500W〜1 500W的 範圍，最高旋轉數大約每分鐘3 5,000〜50,000轉的範圍。 接著，利用第3圖說明本實施例之電動送風機的中心 部3 00附近的構造。第3圖係將第2圖的中心部2 1 5附近予以 放大之圖。相當於第2圖的密封材216之密封材302，係介 由被安裝於相當於第2圖的風扇殼214之風扇殻3 09的密封 材固定構件301而被固定。對於此密封材302，葉輪中心部 315有侵入，構成密封機構。此密封機構位於此位置雖然 重要，但並不限定爲此種方式。葉片306對於軸方向前側 的護罩壁304及軸方向後側的輪轂壁305，爲藉由鉚合317 而被固定。但是，葉片3 06也可以藉由熔接等鉚合以外的 手段來固定。葉片3 06係由以厚度略微均勻的鋁爲主成分 的材料所構成的平板來構成。此處，略微均勻係包含加工 時的變形或熱變形所導致的厚薄、表面的凹凸所導致的厚 薄。護罩係由以厚度略微均勻的鋁爲主成分的材料所構成 的平板來構成，具有圓環形狀。即護罩係於中心具有圓形 狀的開口。護罩的葉片3 06側壁面爲護罩壁3 04。如第3圖 -16- 201200738 所示般’護罩的外緣（半徑方向的最外周）爲朝向半徑方 向’護罩的內緣（半徑方向的最內周）朝向軸方向。如第 3圖所示般，於護罩的內緣附近，逐漸地從半徑方向轉爲 朝向軸方向。輪轂也由以厚度略微均勻的鋁爲主成分的材 料所構成的平板來構成，具有圓形狀或圓環形狀。輪轂的 葉片306側壁面爲輪轂壁305。如第3圖所示般，輪轂的外 緣及內緣都朝向半徑方向。因此，護罩的外緣和輪轂的外 緣略微平行且分開。葉片3 06、護罩、輪轂也可以是包含 鋁之合金或鋁以外的金屬（例如鐵、不銹鋼、鈦）、陶瓷 。鉚合一般爲沿著葉片3 06的護罩壁3 04側端面及輪轂壁 3 0 5側端面的兩端面準備複數個，此處只著眼於護罩壁3 04 側且最內徑側（內緣側）者予以圖示出。鉚合3 1 7以和葉 片3 06構成爲一體形爲佳。例如，在從平板衝壓出葉片306 時，鉚合3 1 7部分也一同地衝壓的話，可以將鉚合3 1 7和葉 片306構成爲一體形。或者，在從平板切削出葉片306時， 鉚合3 1 7部分也一同地切削出來的話，可以將鉚合3 1 7和葉 片3 06構成爲一體形。葉片3 06的護罩壁304側端面係具有 沿著護罩壁3 04的形狀，葉片3 06的輪轂壁3 05側端面係具 有沿著輪轂壁3 05的形狀。將葉片3 06的護罩壁3 04側端面 的線稱爲護罩側弧形線，將葉片3 06的輪轂壁3 05側端面的 線稱爲輪轂側弧形線。然後，藉由護罩和輪轂及圓周方向 的複數個配置之葉片3 06構成葉輪3 03 »輪轂被固定於相當 於第2圖的旋轉軸2 05之旋轉軸3 08，其結果爲，葉輪3 03被 固定於旋轉軸308。藉此，伴隨旋轉軸3 08的旋轉，葉輪 -17- 201200738 303也隨之旋轉。葉片306的內緣突出於前側’形成葉片前 緣3 0 7。於葉片前緣3 0 7和旋轉軸3 0 8之間具有空間’形成 流路。風扇殼3 09的內周的靜止部前端3 1 4的位置和葉片 306的葉片前緣307之位置並不一致’靜止部前端314比葉 片前緣3 07更位於前側，具有軸方向段差316。即固定部和 旋轉部之間，在軸方向具有段差。風扇殼3 09的內周的靜 止部前端314的位置和護罩的葉輪中心部31 5的位置並不一 致，靜止部前端3 1 4比葉輪中心部3 1 5更位於內周側’具有 徑向段差3 1 0。即固定部和旋轉部之間’於徑向也具有段 差。粗箭頭爲表示氣流的方向3 1 3。空氣進入中心部2 1 5的 入口，流入形成在圓周方向二片鄰接之葉片3 06之間的空 間（流路）。基於徑向段差310的存在’氣流產生洩漏。 接著，利用第4圖說明葉輪400的形狀。第4 ( a )圖係 從軸方向前側來看葉輪400的正面圖。第4 ( b )圖係從和 葉輪4 0 0的旋轉軸垂直側來看之側面圖。如第4 ( a )圖所 示般，相當於第3圖的葉片306之葉片401，係於外周方向 等間隔地設置有8片，具有隨著從葉輪中心部404朝徑向外 側，旋轉方向及反旋轉方向，且再一次扭轉爲旋轉方向之 形狀。另外，如第4 ( b )圖所示般，設匱於葉片40 1的前 面之護罩壁402的最大徑，係比設置於葉片4〇1的後面之輪 轂壁403的最大徑還大。即護罩的外周係比輪轂的外周還 大。因此，護罩的外緣係位於比輪轂的外緣更外周側。另 外，護罩壁402與葉片401之相接外緣，爲同一直徑，輪轂 壁403與葉片401之相接外緣，也爲同一直徑。因此，葉片 -18- 201200738 40 1的護罩側外緣比輪轂側外緣更大。 接著，利用第1 3圖說明葉輪400和擴散翼2 1 1的形狀。 擴散翼2 1 1係以覆蓋葉輪400的外周側之方式所形成。靜止 體之擴散翼211的內緣，位於對於旋轉體之葉輪400的外緣 ，留有葉輪400可以旋轉之程度的間隙的位置。擴散翼2 1 1 係於圓周方向複數片（例如13片）的葉片（靜止翼）406 被夾於前面側的圓環狀構件與底面側的圓環狀構件之間所 形成。擴散翼2 1 1的葉片406，厚度並非均勻，係以樹脂材 料所構成。另外，相對於葉輪400的葉片401被扭轉而具有 3維形狀，擴散翼211的葉片406並不被扭轉，只有傾斜或 彎曲而已，具有2維形狀。擴散翼21 1的葉片406的片數係 比葉輪400的葉片401的片數還多。葉輪400的葉片401從內 緣至外緣，對於以旋轉軸的軸心爲中心的半徑方向，係朝 向和旋轉方向405相反側的反旋轉方向傾斜或彎曲。相對 於此，擴散翼21 1的葉片406係從內緣至外緣，對於以旋轉 軸的軸心爲中心的半徑方向，爲朝葉輪4〇〇的旋轉方向4〇5 傾斜或彎曲，因此，從軸方向來看之情形的葉輪4〇〇之葉 片401的傾斜、彎曲方向，和擴散翼211的葉片406的傾斜 、彎曲方向爲相反，且葉輪400的葉片401的外緣（出口） 的軸方向的形成方向，係和擴散翼2 1 1的葉片4 0 6的內緣（ 入口.）的軸方向的形成方向略微一致。例如’擴散翼211 的葉片406的軸方向的形成方向，在和軸方向略微一致的 情形，葉輪400的葉片401的外緣的軸方向的形成方向’也 和軸方向略微一致或於旋轉方向只少許傾斜爲佳。藉此’ -19- 201200738 從葉輪4 0 0所流出的氣流’可以紊亂少且平滑地流入擴散 翼 2 1 1。 接著，利用第5圖進一步說明葉片500的形狀。第5圖 係從軸方向前側來看1片的葉片5 0 0的正面圖。以旋轉軸方 向爲基準之絕對座標空間來看時，從葉片500的輪轂壁至 護罩壁之旋轉軸方向的形成方向，係於包含內緣部的入口 附近5 0 3朝旋轉方向5 0 5傾斜，隨著朝向葉片的外緣，對於 旋轉方向的傾斜變小’與旋轉軸方向略微一致，成爲略2 維形狀506。進而’從葉片5 00的輪轂壁至護罩壁的旋轉方 向的形成方向，一朝向葉片的外緣時，比起旋轉軸方向更 朝反旋轉方向傾斜，迎向往反旋轉方向的最大傾斜後，進 而接近外緣部時，朝反旋轉方向的傾斜變小，在出口附近 504與旋轉軸方向略微一致，成爲略2維形狀507。從葉片 500的輪轂壁至護罩壁的旋轉軸方向的形成方向，進而在 外緣部中，再度於旋轉方向只少許（數度程度）傾斜。即 從軸方向來看時，葉片5〇〇從內緣至外緣，從往旋轉方向 扭轉的狀態往反旋轉方向扭轉，之後，再度往旋轉方向扭 轉。然後，從軸方向來看時，葉片5〇〇從內緣至外緣，具 有2個略2維形狀5 06、5 07，且具有於其前後，傾斜方向改 變的形狀。此處所謂略2維形狀，係指位於包含旋轉軸方 向的面內，具體而言，係指葉片5 00之與護罩壁的連接部 和葉片500之與輪轂壁的連接部，係存在於旋轉軸方向上 。入口附近50 3的入口端，在半徑方向成爲內緣，在圓周 方向成爲前緣（旋轉方向505的最前端）。出口附近504的 -20- 201200738 出口端’在半徑方向成爲外緣’在圓周方向成爲後綠（旋 轉方向505的最後端）。即在入口附近5〇3和出口附近5〇4 中，雖朝旋轉方向傾斜’但在內緣和外緣之間，具有2點 的略2維形狀，在略2維形狀的前後，傾斜方向改變。另外 ，葉片5 0 0爲將平板彎曲加工所形成者，其板厚，在中間 部並不特別厚’略微均勻。葉片5 0 0之中間部的輪轂側5 〇 2 端面至護罩側5 0 1端面的傾斜，也可以是直線，也可以彎 曲（翻轉亦可）。從葉片500的輪轂壁至護罩壁的旋轉軸 方向的形成方向，在外緣部中，可以和旋轉軸方向略微一 致。內緣部中之葉片5 00的旋轉軸方向的形成方向，和對 於葉片500之空氣的入射角度有關。外緣部中之葉片500的 旋轉軸方向的形成方向，係和對於擴散翼211之空氣的入 射角度的匹配有關。因此，外緣部中之葉片500的旋轉軸 方向的形成方向，以和擴散翼211的葉片406的旋轉方向的 形成方向略微一致爲佳。 從以輪轂側502的形狀（輪轂側弧形線）爲基準之相 對座標空間來看時，於半徑方向中間部中之內緣側’對於 輪轂側502的形狀，護罩側501的形狀（護罩側弧形線）朝 旋轉方向彎曲，於半徑方向中間部之中的外緣側中’對於 輪轂側502的形狀，護罩側501的形狀朝反旋轉方向彎曲’ 在出口附逅504中，對於輪轂側502的形狀，護罩側501的 形狀朝旋轉方向少許飛出。即在半徑方向中間部中2夕f @ 側中，比內緣側，葉片500之與護罩壁的連接部對於與輪 轂壁的連接部之位置，係位於反旋轉方向側’進而在外緣 -21 - 201200738 部中，比起比外緣部位於內周側之外緣側，葉片5 00之與 護罩壁的連接部對於與輪轂壁的連接部之位置，更位於旋 轉方向側》此結果，從葉片500的內緣至外緣，輪轂側502 的形狀（輪轂側弧形線）與護罩側501的形狀（護罩側弧 形線）係於2處交叉》 接著’利用第6圖說明葉片60 1的具體之形狀。第6圖 係從軸方向前側來看葉輪600之正面圖，複數片設置的葉 片601只以1片做代表表示。另外，第6圖之R1〜7係指和以 旋轉軸爲中心之中心部爲同心圓之圓形，將該各圓與護罩 側602的形狀及輪轂側603的形狀交叉的各點與中心軸所形 成的角度當成傾斜角Θ。傾斜角Θ也可以稱爲葉輪600對於 軸方向之朝圓周方向的傾斜角。傾斜角Θ係將護罩側形狀 朝旋轉方向側傾斜的情形當成正的，朝反旋轉方向傾斜的 情形當成負的。葉片6 0 1於和中心部直徑相同直徑R 1 (內 緣部）中，葉片601的護罩側602的形狀和輪轂側603的形 狀相比，朝旋轉方向604只傾斜Θ1，於朝向葉片的外緣之 R2中’朝旋轉方向傾斜的量，成爲Θ2，進而，於朝向葉片 的外緣之R3 (內緣側略2維形狀部）中，護罩側602的形狀 和輪轂側603的形狀交叉，呈略2維形狀。另外，於本發明 中 ’ Θ1 爲 11°，02 爲 9°，Θ1>Θ2>Θ3 (Θ3 = 0)。即葉片 601 於 內緣部中’爲朝旋轉方向之最大傾斜。但具有最大傾斜的 部分’不在內緣部’也可以在比內緣部少許位於外緣側之 部分。另外’從R3進一步朝向葉片的外緣之R4中，葉片 6 0 1的護罩側6 0 2之形狀，和輪轂側6 〇 3的形狀相比，於反 -22- 201200738 旋轉方向傾斜Θ4，朝向葉片的外緣之R5 (朝反旋轉方向的 最大傾斜部）中，朝反旋轉方向傾斜的量，成爲Θ5，進一 步朝向葉片的外緣之R6 (外緣側略2維形狀部）中，護罩 側602的形狀和輪轂側603的形狀再度交叉，成爲略2維形 狀。另外，在本發明中，Θ4爲-3。，Θ5爲-4。，Θ4>Θ5>Θ6( Θ6 = 0 )。另外，從r5稍微至內緣側形成最大傾斜部。另外 ’從R6進一步朝葉片的外緣之R7 (外緣部）中，葉片601 的護罩側602之形狀和輪轂側603的形狀相比，朝旋轉方向 傾斜Θ7。另外，在本發明中，Θ7爲0.5°。即從R1至R2中， 護罩側602的形狀和輪轂側603的形狀相比，朝旋轉方向傾 斜，在R3中，成爲略2維形狀，隨著從R3至R4、R5，朝反 旋轉方向傾斜，於R6中，再度成爲略2維形狀，在外緣中 ，再度朝旋轉方向傾斜。即從葉片的內緣至外緣，將通過 旋轉軸上的圓賦予順序時，與該各圓之傾斜角Θ，係成爲 Θ1>Θ2>Θ7>Θ3 = Θ6>Θ4>Θ5之順序。在同心圓上之對於輪轂的 各葉片的護罩形成方向的最大傾斜角’以5°〜15°爲佳。 2個略2維形狀中之內緣側的略2維形狀’係比半徑方 向中間點更位於內緣側。在比內緣側的略2維形狀更內緣 側中，葉片601朝旋轉方向傾斜’在比內緣側的略2維形狀 更外緣側中，葉片6 0 1雖朝反旋轉方向傾斜’但對於旋轉 方向的最大傾科角的絕對値（例如’ θ 1 = 1 1 ° ) ’係比朝反 旋轉方向的最大傾斜角的絕對値（例如θ 5 = _ 4 ° )還大。2個 略2維形狀中之外緣側的略2維形狀’係位於外緣部附近（ 從外緣部起數m m程度內緣側）° -23- 201200738 接著，利用第7圖說明關於本發明之葉片的葉片角度 分布。第7圖中，劃出對於連結葉片的任意位置與中心軸 (旋轉軸3 08的軸心）之直線的正交線，將該正交線與葉 片的外面之接線所形成的角度當作葉片安裝角度或葉片角 度「β」。橫軸爲直徑。如第7圖所示般，於半徑最少的內 緣中，護罩葉片角度被設定爲比輪轂葉片角度還大。更具 體而言，對於葉片護罩直徑爲D，護罩內徑爲0.387D，輪 轂內徑爲0.3 5 7D之情形，護罩葉片角度被設定爲約25度， 輪轂葉片角度設定爲約22度。即在內緣中，對於輪轂側， 護罩側的葉片角度稍微大，護罩內徑比輪轂內徑大。而且 ’半徑最大的外緣中，護罩葉片角度被設定爲比輪轂葉片 角度還大’葉片的外緣之護罩側外徑，被設定爲比外緣的 輪轂側還大。更具體而言，再將葉片外緣之護罩直徑當成 D的情形’後緣的輪轂側直徑爲0.996D的情形，護罩葉片 安裝角度設定爲約35度，輪轂葉片安裝角度設定爲約20度 〇 進而’接續輪轂壁之葉片的葉片角度分布，係如第7 圖的實線曲線所示般，隨著從輪轂面的內緣朝向外緣而增 加，內緣側的輪轂側之回折點7 0 2到來。然後，葉片角度 隨著朝向外緣緩緩角少，到達外緣側的輪轂側之回折點 7〇2。然後’一過此外緣側的輪轂側之回折點7〇2，葉片角 度隨著朝向外緣再度減少。即接續輪轂之葉片的角度分布 ’設定爲隨著朝向外緣，具有2個的輪轂側之回折點702。 另外’依據入口條件，也可能成爲一個回折點。 -24- 201200738 進而護罩側的葉片角度分布，係如第7圖之虛線曲線 所示般，隨著從護罩內緣朝向外緣’在內緣之後，無角度 增加’內緣側之護罩側的回折點7 〇丨到來。然後，葉片角 度隨者朝向外緣而增加，到達外緣側之護罩側的回折點 7 〇 1。然後，一過此外緣側的護罩側之回折點7 〇 ! ’隨著朝 向外緣，緩慢地到達外緣的葉片角度。即接續輪轂之葉片 的角度分布’被設定爲隨著朝向外緣，具有2個之護罩側 的回折點7 0 1。 進而’護罩側的葉片角度分布之虛線曲線和輪轂側之 葉片角度分布的實線曲線，在比半徑方向的略中央更外緣 側交叉。從交叉點7〇3起之內緣側中，護罩的葉片角度比 輪轂的葉片角度小，從交叉點起之外緣側中，護罩的葉片 角度比輪轂的葉片角度大。另外，葉片角度分布的最大角 度，輪轂的葉片角度以護罩的葉片角度還大。另外，護罩 和輪轂的回折點，比交叉點7〇3位於更內緣側。交叉點703 可以比略中央位置更內緣側，也可以更外緣側。交叉點 7 0 3的位置，例如和流速或流入葉輪3 0 3之入射角有關。 接著，第8圖係表示成爲上述之本實施例之送風機和 比較例之型態的設計點風量之效率的比較。第8圖係固定 擴散翼’將葉片的軸動力設爲一定的狀態’比較以比較例 和本實施例只變更葉.輪之數値解析結果。如第8圖所示般 ，如依據成爲上述之本實施例之送風機’和比較例相比， 得知葉輪的效率雖然是不多，但有增加。另外，擴散翼效 率，本實施例和比較例比較’得知效率提升。進而’於包 -25- 201200738 含葉輪和擴散翼之送風機效率，本實施例和比較例相比， 得知效率獲得提升。如依據成爲本實施例之送風機，和比 較例相比，比起葉輪的效率提升，擴散翼效率提升大，擴 散翼效率提升有助於送風機效率提升。 此處’第14圖係表示本實施例之葉片和比較例之葉片 的形狀圖。表示從軸方向前側所見到之單單複數片葉片》 第14(a)圖係表示本實施例的葉片，第14(b)圖係表示 本實施例之葉片。比較例爲將葉片的後緣部中之護罩側結 合部的位置比輪轂側結合部的位置設爲反旋轉方向，使葉 片的後緣部中之輪轂側葉片出口角度和護罩側葉片出口角 度成爲相等之型態。即指從葉片的內緣至外緣，具有1個 略2維形狀的葉片。比較例之內緣部朝旋轉方向的傾斜角 和本實施例之內緣部朝旋轉方向的傾斜角一致，比較例之 1個略2維形狀的位置（從軸心起之半徑位置）與本實施例 之2個略2維形狀中之內緣側的略2維形狀的位置一致。空 氣調和機和電動吸塵器之電動送風機，其尺寸或旋轉數、 擴散翼之有無等雖不同，但比較例，例如爲將專利文獻2 之空氣調和機的離心風扇適用於作爲本實施例的對象之電 動吸塵器的電動送風機之例子。 關於成爲上述之本實施例的電動送風機，爲了調查設 計點風量的葉輪效率改善效果，於第9圖表示葉輪出口（ 出後緣部處）中之風速的軸方向分布的比較（數値解析結 果）。第9圖的縱軸係表示葉輪出口速度，橫軸係表示從 輪轂側至護罩側之軸方向位置。另外，於橫軸的最大位置 -26- 201200738 表示葉輪出口之平均速度。於葉輪中，葉輪出口速度愈小 ，葉輪內的壓力上升愈大，效率好。另外，於電動吸塵器 之電動送風機中，在葉輪出口有擴散翼存在，從與擴散翼 之氣流的匹配而言，葉輪出口速度的分布很重要。由第9 圖，本實施例和比較例相比，得知平均速度降低。另外， 如比較軸方向的速度一樣性時，本實施例和比較例相比， 護罩側和輪轂側之速度差也小。從上述，葉輪內部的速度 分布獲得改善，可見到效率的提升。於本實施例中，葉輪 出口速度從輪轂側至軸方向中央部，於減少後再增加，從 軸方向中央部至護罩側，也減少後再增加。進而，葉輪出 口速度’比起輪轂端及護罩端，軸方向中央部比較小。本 實施例和比較例相比，特別是從輪轂側起軸方向中央部的 葉輪出口速度小。 進而’第15圖係表示葉片之軸方向各剖面中之內部氣 流的比較（數値解析結果）。第1 5圖係只表示全周存在8 片之葉片401中之2片葉片4〇1。顏色愈淡，數値愈高，速 度愈大。第15圖所示之速度分布，並非以靜止體之電動送 風機106或擴散翼21 1爲基準之絕對座標的速度分布，而是 以旋轉體之葉輪爲基準之相對座標的速度分布。因此，第 15圖中，速度小的部分（顏色濃的部分），對於擴散翼 211其速度大’第15圖中，速度大的部分（顏色淡的部分 )’對於擴散翼21 1其速度小。第i5(a)(b)(c)圖係表示本實 施例之速度分布’第15(d)(e)(f)係表示比較例的速度分布 。另外’第15(a)(d)係表示軸方向之輪轂側剖面（與輪轂 .27- 201200738 壁之連接部）的速度分布，第15(c) (f)係表示軸方向之護 罩側剖面（與護罩壁的連接部）之速度分布，第15(b)(e) 係表示軸方向之中央剖面（輪轂壁和護罩壁之間的中央） 〇 一比較護罩剖面時，本實施例之速度分布（第1 5 (c)圖 )和比較例之速度分布（第15(f)圖）並無大的差異。此可 認爲兩者，護罩側5 0 1的形狀之角度分布都被適當化的關 係。即使比較中央剖面，本實施例的速度分布（第1 5(b)圖 )和比較例的速度分布（第15(e)圖）也無大的差異。此可 認爲兩者，軸方向中央之形狀的角度分布都被適當化的關 係。相對於此，一比較輪轂剖面時，本實施例之速度分布 (第1.5(a)圖）對於比較例的速度分布（第15(d)圖），特 別於葉片的後緣部之反旋轉方向側可見到濃的部分，即低 速度區域小（第15圖中之A部）。此如第7圖所示般，使輪 轂後緣部之葉片角度變小的結果，輪轂後緣部之形狀成爲 沿著氣流的形狀，可以降低低速度區域。然後，如第9圖 所說明般，本實施例和比較例相比，特別是在輪轂側之低 速度區域降低的結果，可以降低輪轂側之速度，平均速度 也可以降低。 進而，關於成爲上述之本實施例之電動送風機，爲了 調查設計點風量的擴散翼效率改善之效果，於第10圖表示 擴散翼之軸方向中央剖面中之內部氣流的比較（數値解析 結果）。第10圖係於全周存在13片的擴散翼中，只表示2 個葉片1001。顏色愈淡，數値愈高，速度愈大。即擴散翼 -28- 201200738 內部的氣流中，從淡的顏色至濃的顏色一樣地變化時，在 擴散翼內部有效率地減速，壓力上升。依據第10圖，比較 例在擴散翼出口部1004中，存在高速區域1002與低速區域 1 003 ’得知從葉輪出來之氣流並不—樣地減速。即得知在 擴散翼出口部1 〇〇4產生剝離，損失變大。另一方面，在實 施例中’在擴散翼出口部1 004並不存在高速區域或低速區 域’得知一樣地減速。即實施例在擴散翼內部的壓力上升 ’和比較例相比，獲得提升，能量損失降低，效率獲得提 升。另外’本實施例之擴散翼的輪轂側剖面及護罩側剖面 之速度分布，和比較例之擴散翼的輪轂側剖面及護罩側剖 面的速度分布並無大的差異。 依據以上，本實施例藉由將葉片的護罩側501的形狀 、軸方向中央部之形狀、輪轂側502之形狀之各各予以適 當化，即將軸方向各剖面之內緣部至外緣部之形狀予以適 當化，可以降低葉輪出口之平均速度，不單可以提升葉輪 之效率，特別是可以提升在擴散翼之效率。特別是使輪轂 側5 02之後緣部的角度分布變小的結果，從旋轉軸方向來 看之情形，葉片的護罩側5 0 1之形狀和輪轂側5 02之形狀不 單在內緣側，在外緣部附近也交叉。 以下，說明本發明之電動送風機的製造方法。 利用第1 1圖說明鉚合。於相.當於第3圖之葉片3 06的葉 片1 1 04的護罩側之上端部（軸方向前側）和輪轂側之下端 部（軸方向後側）之各部設置有複數個鉚合用突起1 1 05 ( 鉚釘）。如前述般，鉚合用突起1 105以和葉片1 1〇4形成爲 -29- 201200738 —體爲佳。爲了和葉片的鉚合用突起1105之位置及數目一 致，於護罩壁1 103和輪轂壁1 101設置複數個鉚合用孔1 102 。因此，護罩壁1 103之複數個鉚合用孔1 102間的相對位置 ，爲沿著葉片1 104的上端部之形狀的位置，輪轂壁1 101之 複數個鉚合用孔1 102間的相對位置，爲沿著葉片1 104之下 端部的形狀之位置。鉚合用孔1 1 〇2爲貫穿孔。例如在全部 爲略2維的情形，護罩壁1 1 03的複數個鉚合用孔1 1 02間的 相對位置和輪轂壁Η 〇 1之複數個鉚合用孔1 1 02間的相對位 置幾乎相同，在本踅施例中，於葉片的內緣側中，葉片 11 04的葉片11 04的上端部係比下端部更倒向旋轉方向405 前側，因此，護罩壁1 103之複數個鉚合用孔1 102間之相對 位置，和輪轂801之複數個鉚合用孔1 102間之相對位置相 比，成爲朝旋轉方向405前側膨脹之位置。第1 1圖中，護 罩、輪轂側都具有3個鉚合構造。葉片1 1 04之上端部的鉚 合用突起1105之各各的位置，係對應葉片1104之下端部之 鉚合用突起1 105之各各的位置。將葉片1 104之鉚合用突起 1 105插入護罩壁1 103和輪轂壁1 101之鉚合用孔1 102，藉由 從外側予以鉚合，葉片1 1 04與護罩壁1 103及輪轂壁1 101被 組裝成一體。另外，第1 1圖所示之葉片形狀，爲葉片外徑 D2: 89mm，葉片寬b2: 6.8mm，b2/D2 =約0.08之扁平的葉 片形狀。此處，所謂鉚合係指：於鉚合用孔1 1 02插入鉚合 用突起1 1 05，貫穿鉚合用孔1 1 02，將飛出相反側之鉚合用 突起1105的前端使用專用工具或專用設備予以壓潰之行爲 。於輪轂壁1101的鉚合用孔1102插入葉片11 04之鉚合用突 -30- 201200738 起1 105予以鉚合，將葉片1 104固定於輪轂壁1 101後，於護 罩壁1103的鉚合用孔1102插入葉片1104的鉚合用突起1105 予以鉚合亦可，反之亦可。另外，於輪轂壁1101的鉚合用 孔1 102及護罩壁1 103的鉚合用孔1 102插入葉片1 104的鉚合 用突起1 105後，予以鉚合亦可。 和比較例相比，於本實施例中，於葉片1 200之特別是 內緣側中，藉由使葉片1 200朝旋轉方向前側傾斜，要保持 葉片1 200和護罩壁3 04之間以及葉片1 200與輪轂壁3 05之間 的氣密變得困難。因此，以將葉片1 200和護罩壁3 04的鉚 合部（連接部）及葉片1 200和輪轂壁3 05之鉚合部（連接 部）用電著塗裝或接著劑予以覆蓋爲佳。特別是比對於比 較例所使用的電著塗裝或接著劑，以黏性低者爲佳。藉此 ，可以防止於葉片1 200和護罩壁3 04之鉚合部（連接部） 及葉片12 00與輪轂壁305之鉚合部（連接部）產生間隙， 抑制空氣氣流的紊亂，能夠抑制效率之降低。 [實施例2 ] 和實施例1基本的構造相同，對於相同要素賦予相同 符號，省略其說明。 於藉由前述說明之鉚合的製造方法中，葉片朝旋轉方 向傾斜的情形，基於護罩與輪轂之旋轉方向的位置的不同 ，鉚合時，葉片容易滑動於旋轉方向，有組裝精度降低的 課題。 相對於此，如第1 2圖所示般，於實施例2中，如前述 -31 · 201200738 所述般，對於輪轂之各葉片的護罩形成方向，在葉片的內 緣中，朝旋轉方向傾斜，隨著朝葉片的內緣和外緣之間， 朝反旋轉方向傾斜，與輪轂側成爲略2維形狀，之後，進 而成爲反旋轉方向，從葉片的外緣在內側再度成爲略2維 形狀，在葉片的外緣再度朝旋轉方向傾斜，從葉片的內緣 至外緣，具有2點之略2維形狀的葉片。因此，如第12圖所 示般，於2點之略2維形狀，將鉚合用突起1 2 05使用於護罩 側1 201與輪轂側1 202，可以防止鉚合時之葉片的滑動，可 以將護罩側1201和輪轂側1 202之距離b控制在特定的尺寸 來製造。另外，在2點之略2維形狀的內緣側及外緣側中， 由於葉片的傾斜方向改變，也有抵消鉚合時之應力的效果 。另外，爲了獲得效果，可以略2維形狀地設置鉚合用突 起。 和比較例相比，於本實施例中，葉片1 200之特別內緣 側中，藉由使葉片1 200朝旋轉方向前側傾斜，要保持葉片 1 200和護罩壁304之間及葉片1 200與輪轂壁3 05之間的氣密 變得困難》因此，以將葉片1 200和護罩壁3 04的鉚合部（ 連接部）及葉片1 200和輪轂壁3 0 5之鉚合部（連接部）用 電著塗裝或接著劑予以覆蓋爲佳。特別是比對於比較例所 使用的電著塗裝或接著劑，以黏性低者爲佳。藉此，可以 防止於葉片1200和護罩壁304之鉚合部（連接部）及葉片 1 200與輪轂壁3 05之鉚合部（連接部）產生間隙，抑制空 氣氣流的紊亂，能夠抑制效率之降低。 •32- 201200738 【圖式簡單說明】 第1圖係吸塵器本體之模型橫剖面圖。 第2圖係吸塵器用電動送風機的剖面圖。 第3圖係葉輪中心部附近的構成圖。 第4圖係葉輪的形狀圖。 第5圖細葉片的形狀圖。 第6圖細葉片的詳細形狀圖。 第7圖係表示葉片的護罩及主板接觸面之葉片安裝角 度分布圖。 第8圖係實施例和比較例之效率的比較圖。 第9圖係實施例和比較例之葉輪出口速度的軸方向分 布之比較圖。 第1 〇圖係實施例和比較例之擴散翼內部的軸方向高度 中央剖面之速度分布的比較圖。 第1 1圖係表示鉚合的位置圖。 第12圖係表示鉚合的突起圖。 第1 3圖係葉輪及擴散翼之形狀圖。 第1 4圖係本實施例和比較例之葉片的形狀圖。 第1 5圖係實施例和比較例之葉輪內部之軸方向高度各 剖面的速度分布的比較圖。 【主要元件符號說明】 100 :電動吸塵器本體 1 〇 1 :軟管接頭 -33- 201200738 102 :集塵室 1 0 3 :紙袋 104 :過濾器部 105 :電動機室 106 :電動送風機 1 〇 7 :防振橡膠 108 :送風機入口 109 :送風機出口 1 1 0 :電源線捲軸 1 1 1 :車輪 201 :送風機 202 :電動機 203 :機殼 2 04 :後端蓋 2 0 5、3 0 8 :旋轉軸 2 0 6 :轉子 207 :定子 2 0 8 :碳刷 2 0 9 :整流器 210、 303、 400、 600 ：葉輪 21 1 :擴散翼 2 1 2 :隔間板 213 :返回導引 214、3 09 :風扇殻 -34- 201200738 2 1 5、3 0 0 :中心部 2 1 6、3 0 2 :密封材 217:電動送風機入口 3 0 1 :密封材固定構件 304 ' 402 、 1103：護罩壁 305、 403、 1101：輪轂壁 306、 401 ' 601、1104、1200:葉片 3 0 7 :葉片前緣 3 1 0 :徑向段差 3 1 3 :空氣氣流的方向 3 1 4 :靜止部前端 3 15、404 :葉輪中心部 3 1 6 :軸方向段差 3 1 7 :鉚合 405、 505、 604、 1203 ：旋轉方向 501、 602、 1201:護罩側 502、 603、 1202 ：輪轂側 5 03 :入口附近 5 0 4 :出口附近 5 0 6、5 0 7 :略2維形狀 701 :護罩側之回折點 702 :輪轂側之回折點 7 0 3 :交叉點 1〇〇1 :葉片 -35- 201200738 1002:商速區域 1 0 0 3 :低速區域 1 004 :擴散翼出口部 1 102 :鉚合用孔 1105、1205:鉚合用突起 -36201200738 VI. [Technical Field] The present invention relates to an electric blower provided with a fan blade having an inner shape and a conventional electric blower equipped with the prior art, although for example, the east display 'but generally The shroud, and the blade shroud side disposed between them are more inclined than the hub side by the vacuum pressure. In particular, in Patent Document 1, the cover and the rear shroud (hub) are formed by riveting the radius of curvature of the adjacent blade, and the side is more inclined, on the inner peripheral side, the front side, and the outer peripheral side. Medium, slightly turning the fan for the rear cover. Further, a conventional electric blower is disclosed in Patent Document 2 below. The impeller of the centrifugal fan is formed by a plurality of central portions between the outer hub portion and the outer peripheral portion of the shroud and the shroud, and the centrifugal fan of the position of the joint portion of each of the blades is more than the position of the hub side joint portion. An electric vacuum cleaner that is twisted between the blade exit angle and the side edge of the shroud to the outer edge. r Patent Document 1 below is also constituted by a main plate placed at its opposite position, and the blade is rotated at a high speed to obtain an air volume: the blade is fixed by being clamped to the front cover, and the front cover side of the suction port is compared with the rear side. A structure of a conventional fan in which the shroud guard side is inclined in a direction perpendicular to the direction of rotation of the electric blower, and the fan is a blade having a horizontal blade and a shroud side in the rear edge portion of the middle piece of the shroud Deviation in the reverse rotation direction makes the blade exit angles of the trailing edge portions of the aforementioned blades equal. [Patent Document 1] [Patent Document 1] Patent No. 2 7 5 7 5 0 1 (Japanese Patent Laid-Open No. Hei 3 - 1 5 1 5 9 8) [Patent Document 2] [Problem to be Solved by the Invention] In a conventional electric blower (Patent Document 1), an inlet is known. The flow of the air does not have a detailed adjustment of the blade angle distribution, and the flow inside the impeller tends to cause peeling and backflow, which is a cause of energy loss (efficiency). In particular, at the suction port of the electric blower, the swirling air blower and the inlet ring for guiding the suction airflow are used to suppress the leakage airflow caused by the pressure difference between the vane suction port and the impeller exit. Therefore, at the suction port, a step is generated at the joint between the rotating body and the stationary body. Considering the stepped airflow and the leakage airflow, in order to adjust the matching with the blade inlet angle and the load distribution of the blade, it is necessary to understand the phenomenon inside the blade, and Into the best. That is, in the case of an inlet leak, it is necessary to match the leak to adjust the blade angle distribution, so that the load distribution of the blade is optimized to suppress peeling and backflow for high efficiency. In addition, for the airflow at the inlet, the detailed fan blade angle distribution is not adjusted. In the vicinity of the suction port, the inclination of the blade of the impeller does not coincide with the inflow direction of the air, and the air touches the side of the fan, and the impact loss becomes larger. After that. -6 - 201200738 In addition, in the case of the above-described electric blower (Patent Document 1), the blade is inclined to the main plate as viewed from the axial direction, and the blade or the riveting is performed by compression or the like during assembly of the sheet metal. It is easy to collapse, and there are problems in assembly. Further, in the conventional electric blower (Patent Document 1), on the inner peripheral side (inflow side), although the front shroud side is inclined in the rotational direction, the outer peripheral side (outflow side) is slightly perpendicular to the rear shroud, On the outer peripheral side (outflow side), the flow of air becomes uneven from the front shroud to the rear shroud, that is, from the front shroud to the rear shroud, the pressure distribution or the velocity distribution becomes uneven, and the energy loss becomes large. Hey. Further, in the conventional fan (Patent Document 2), in order to efficiently decelerate the airflow flowing out of the fan, a stationary blade (for example, a "diffuser wing" provided downstream of the fan is formed, and the trailing edge portion of the blade is placed. The position of the shroud-side joint portion is located in the impeller of the centrifugal fan that is offset from the hub-side joint portion by a certain amount in the reverse rotation direction, and does not seek to match the airflow of the stationary wing. And countercurrent, which is the cause of energy loss (low efficiency). Therefore, the object of the present invention is to make it possible to appropriately shape the shape of the blade in each cross section in the direction of the rotation axis, thereby suppressing the peeling or backflow of the airflow between the blades, or reducing the average flow velocity of the airflow at the blade outlet, or suppressing The flow velocity distribution from the shroud of the blade outlet to the hub becomes uneven, thereby providing a highly efficient electric blower and an electric vacuum cleaner equipped therewith. Further, an object of the present invention is to provide an electric blower capable of suppressing blade compression and an electric 201200738 vacuum cleaner equipped with the same when the hub and the shroud are riveted and mounted. [Means for Solving the Problem] The present invention is characterized in that each blade is twisted from the inner edge in the radial direction to the outer edge in the radial direction, and is twisted toward the opposite side in the direction of the rotation direction with respect to the direction of the rotation axis. After that, it is again twisted toward the rotation direction side. Alternatively, the present invention is characterized in that each of the vanes has a direction slightly perpendicular to the direction of the rotation axis of the blade in the direction of the direction of the rotation axis of the connection portion with the shroud in the direction of the rotation axis of the blade. Or, the blade is inclined toward the rotation direction side, and each blade has a direction in which the rotation axis direction is formed, and is inclined toward the rotation direction side with respect to the rotation axis direction in the middle portion in the radial direction of the blade. Part and a portion inclined to the side of the rotation axis toward the reverse rotation direction. Alternatively, the present invention is characterized in that, viewed from the direction of the rotation axis, the arc-shaped line on the side of the hub-side curved line in the joint portion between the blade and the hub and the shield-side shield portion of the blade and the shroud The inner edge in the radial direction to the outer edge in the radial direction intersect at least at two places. Alternatively, the present invention is characterized in that an angle of an orthogonal line which is a straight line connecting an arbitrary position of the connecting blade with the axis of the rotating shaft, and an angle formed by the wiring from the direction of the rotating shaft and the outer surface of the curved blade are defined. In the case of the blade angle, the blade angle of the hub side of the blade, particularly in the radially outer edge portion, is smaller than the blade angle of the shroud side of the blade. 201200738 [Effect of the Invention] According to the present invention, each blade is twisted from the inner edge in the radial direction to the outer edge in the radial direction on the side opposite to the rotation direction with respect to the rotation axis direction. Further, it is twisted toward the rotation direction side. Thereby, the shape of the blade in each cross section in the direction of the rotation axis is made appropriate, and peeling or backflow of the airflow in the flow path between the blades can be suppressed. In addition, the average flow rate of the gas stream at the vane outlet can be reduced. In addition, it is possible to suppress the flow velocity distribution from the shroud of the blade outlet to the hub from becoming uneven. Thereby, the efficiency of the electric blower can be improved, and the suction power of the electric blower and the electric vacuum cleaner equipped therewith can be improved. According to the present invention, each of the blades is formed in a direction from a direction in which the connecting portion with the hub is formed in a direction of a rotation axis of the connecting portion with the shroud, and is slightly aligned with the direction of the rotating shaft in the outer peripheral portion of the blade in the radial direction, or is rotated. The axial direction is a reference, and is inclined toward the rotation direction side, and each of the blades has a direction in which the rotation axis direction is formed, and a portion inclined to the rotation direction side with respect to the rotation axis direction in the middle portion in the radial direction of the blade The portion in which the direction of the rotation axis is inclined toward the counter-rotation direction side allows the shape of the blade in each cross section in the direction of the rotation axis to be appropriate, and the peeling or backflow of the airflow in the flow path between the blades can be suppressed. In addition, the average flow rate of the gas stream at the vane outlet can be reduced. In addition, it is possible to suppress the flow velocity distribution from the shroud of the blade outlet to the hub from becoming uneven. Thereby, the efficiency of the electric blower can be improved, and the suction power of the electric blower and the electric vacuum cleaner equipped therewith can be improved. According to the present invention, as seen from the direction of the rotation axis, the arc-shaped line on the side of the hub-side curved line in the joint portion between the blade and the hub and the shroud-side shield of the blade and the shroud is in the shield-side curved line of -9 - 201200738 The inner edge from the radial direction to the outer edge in the radial direction intersect at least at two points, whereby when the blade is caulked and mounted to the hub and the shroud, the blade is compressed by the intersection portion, thereby suppressing the blade compression. Further, the shape of the blade in each cross section in the direction of the rotation axis is made appropriate, and the peeling or backflow of the airflow in the flow path between the blades can be suppressed. In addition, the average flow rate of the airflow at the blade outlet can be reduced. In addition, it is possible to suppress the flow velocity distribution from the shroud of the blade outlet to the hub from becoming uneven. Thereby, the efficiency of the electric blower can be improved, and the suction power of the electric blower and the electric vacuum cleaner equipped therewith can be improved. According to the present invention, the angle formed by the line connecting the arbitrary position of the connecting blade with the axis of the rotating shaft, and the line connecting the outer surface of the curved blade as viewed from the direction of the rotating shaft is defined as the blade angle. When the blade angle of the hub side of the blade, particularly in the outer edge portion in the radial direction, is smaller than the blade angle of the shroud side of the blade, whereby the shape of the blade in each cross section in the direction of the rotating shaft is optimized, and The stripping or countercurrent of the air flow in the flow path between the blades is suppressed. In addition, the average flow rate of the airflow at the blade outlet can be reduced. In addition, it is possible to suppress the flow velocity distribution from the shroud of the blade outlet to the hub from becoming uneven. Thereby, the efficiency of the electric blower can be improved, and the suction power of the electric blower and the electric vacuum cleaner equipped therewith can be improved. [Embodiment] The present invention relates to an electric blower, comprising: an annular shroud; a hub disposed facing the shroud; and a vane disposed between the shroud and the hub in a circumferential direction, and a rotating shroud Electricity from the electric parts of the hub and the blade -10- 201200738 The moving fan is characterized in that each blade is formed by a flat plate, and each blade is oriented from the inner edge in the radial direction toward the outer edge in the radial direction, based on the direction of the rotation axis. 'The state twisted from the side toward the rotation direction is twisted to the side of the reverse rotation axis direction, and then twisted again toward the rotation direction side. The present invention provides an electric blower that includes an annular shroud, a hub that faces the shroud, and a plurality of blades that are disposed between the shroud and the hub in the circumferential direction, and the rotating shroud and the hub and the vane. The electric blower of the electric part is characterized in that each of the blades is formed by a flat plate, and each of the blades is formed in a radial direction of the blade from a connection portion with the hub to a direction of a rotation axis of the connection portion with the shroud. The outer edge portion slightly coincides with the direction of the rotation axis, or is inclined toward the rotation direction side with respect to the rotation axis direction, and each of the blades 'has a direction in which the rotation axis direction is formed, and rotates in the middle portion of the blade in the radial direction. The axial direction is a reference, and a portion that is inclined toward the rotation direction side and a portion that is inclined toward the reverse rotation direction side with respect to the rotation axis direction. The present invention relates to an electric blower comprising: an annular shroud; and a hub disposed facing the shroud; and a vane disposed between the shroud and the hub in a circumferential direction, and a rotating shroud and the hub and the vane The electric blower of the electric part is characterized in that each blade is formed by a flat plate, and the connection between the arc-shaped line on the hub side and the blade and the shield in the connection portion between the blade and the hub is viewed from the direction of the rotation axis. The side curved line of the shroud in the part intersects at least at two points from the inner edge in the radial direction to the outer edge in the radial direction. The present invention relates to an electric blower comprising: an annular shroud; and a hub disposed facing the shroud; and a vane disposed between the shroud and the hub in a circumferential direction, and a rotating shroud and the hub and the vane Electric Part -11 - 201200738 Dynamically-driven fan' is characterized in that each blade is formed by a flat plate, such as an orthogonal line to a straight line connecting an arbitrary position of the blade to the axis of the rotating shaft, and a rotating shaft In the direction, the angle formed by the wiring outside the curved blade is defined as the blade angle, the blade angle of the hub side of the blade, in the radially inner edge portion and the radial outer edge portion, than the blade side of the blade The blade angle is still small. According to the present invention, the shape of the blades in the respective cross sections in the direction of the rotation axis is appropriately adjusted, and the peeling or backflow of the airflow in the flow path between the blades can be suppressed. In addition, the average flow rate of the gas stream at the vane outlet can be reduced. In addition, it is possible to suppress the flow velocity distribution from the shroud of the blade outlet to the hub from becoming uneven. Thereby, the efficiency of the electric blower can be improved, and the suction power of the electric blower and the electric vacuum cleaner equipped therewith can be improved. Further, according to the present invention, by matching the inlet leakage and the blade angular distribution, it is possible to suppress the peeling phenomenon and the backflow phenomenon in the airflow inside the impeller, and it is possible to achieve high efficiency. Further, when the blade is caulked and attached to the hub and the shroud, the blade is compressed by the intersection portion, whereby the blade compression can be suppressed. Further, according to the present invention, the assembly accuracy can be improved by optimizing the riveting position. Further, according to the present invention, at the inner edge portion of the blade, the blade can be inclined to coincide with the inflow direction of the air, so that the air can be prevented from hitting the side surface of the blade, so that the impact loss is reduced. Further, according to the present invention, it is possible to match the airflow of the stationary blades provided downstream of the rotating blades, and it is possible to reduce the internal loss of the rotating blades and the internal braking loss of the stationary blades. The loss is reduced. Hereinafter, Example 1 of the present invention and Example 2 of the implementation -12-201200738 will be described in detail based on the drawings. [Embodiment 1] Hereinafter, an embodiment of the present invention will be described using the drawings. First, the entire vacuum cleaner will be described using Fig. 1 . The structure of the vacuum cleaner body 100 will be described in a cross-sectional view seen from the model shown above on the vacuum cleaner body 100 of Fig. 1. When the side of the hose connector 101 in which the vacuum cleaner body 100 is attached is the front side of the vacuum cleaner body 100, the vacuum cleaner body 100 is provided with a detachable hose connector 101 at its tip end. A dust collecting chamber 102 for holding the paper bag 103 is provided on the front side of the vacuum cleaner main body 100, and a motor chamber 105 for accommodating the electric blower 106 is provided on the rear side of the electric vacuum cleaner main body 100, and is disposed in the dust collecting chamber 102 and the motor chamber 105. The filter unit 1〇4 for suppressing the flow of dust in the dust collecting chamber 1〇2 into the motor chamber 105 is provided. The dust collecting chamber 1〇2 and the motor chamber 105 communicate with each other through the filter unit 104. In the dust collection chamber 1〇2, there is a paper bag 1 〇 3 that can be detachably attached. The opening of the paper bag 1 0 3 is connected to the hose connector 1 〇 1 . When the dust accumulates in the paper bag 1 〇3, the paper bag 101 expands, and the opening of the paper bag 1 〇3 abuts against the filter portion 104 at the bottom of the opposite side. An electric blower 106 that generates an attraction force is provided in the motor chamber 105. Between the both ends of the front side of the electric blower 106 and the inner wall surface of the front side of the motor chamber 105, vibration-proof rubber 1 〇 7 (anti-vibration member) for preventing the vibration of the electric blower 106 from being transmitted to the vacuum cleaner main body 100 is provided. The anti-vibration member can also be replaced by a spring instead of rubber. The electric blower 106 is provided with a blower inlet 108' for sucking air at its front end and a blower outlet 119 for discharging air to the rear side. And the •13-201200738 fan inlet 108 is open to the filter unit 104. A power cord reel 1 1 卷绕 for winding and accommodating the power cord is provided on the side of the motor chamber i〇5. Wheels are provided on both sides of the rear side of the electric blower 106. Further, although not shown, a hose is connected to the hose joint 101, and an operation tube for accepting operation such as ΟΝ/OFF of the vacuum cleaner body 100 is connected to the hose, and the operation tube is connected to an extension that can be stretched and contracted. The tube is connected to the extension tube with an inhalation member. The hose connector 1 〇 1 is located on the front side (upstream side) of the front side of the vacuum cleaner body 1 〇 , and the opposite side is the rear side of the vacuum cleaner body 1 。. The hose joint 101, the hose, the operation tube, and the extension tube are not essential, and the operation portion or the suction member formed in the operation tube may be directly formed in the electric blower 106. From the top, the vacuum cleaner body 100 is orthogonal to the front-rear direction of the vacuum cleaner body 100, and is the left-right direction of the vacuum cleaner body 100. The side means the side which is more to the left side or the right side than the center of the left and right direction of the vacuum cleaner main body 100. The electric blower 106 may be placed in the lateral direction (horizontal direction) of the blower inlet 108 toward the front side of the vacuum cleaner body 100, or may be placed as the blower inlet 108 in the longitudinal direction of the upper side of the vacuum cleaner body 100 (longitudinal direction) Place). Next, the air flow in the vacuum cleaner body 100 will be described. The air flowing in from the hose connector 101 enters the dust collecting chamber 102. In Fig. 1, the paper bag 1 0 3 is shown as a dust collecting means, regardless of the material of the paper bag. Further, in the case of the cyclone method, instead of the paper bag 103, it is housed in a cyclone chamber (cyclone dust box). With the paper bag 103, most of the dust-removed air passes through the filter portion 104 where fine dust is also removed. Thereafter, the airflow flows into the motor chamber 105. The electric blower 1〇6 is suspended in the motor room 1〇5 through the anti--14-201200738 vibrating rubber i〇7, and the two air flowing in from the blower inlet 1〇8 is boosted by the electric blower 106, and then exits from the blower. 1〇9 is discharged. Next, the electric blower 1〇6 will be described using Fig. 2 . The electric blower 106 is composed of a blower 2〇1 (fan portion) for sucking air and a motor 2〇2 (drive unit) for driving the blower 201. The motor 202 is attached to the motor casing formed by the machine 203 and the rear end cover 2〇4 with a rotating shaft 205' to which the rotor 206 is attached to the rotating shaft 205. A stator 2〇7 having a fixed portion is disposed on the outer circumference of the rotor 206. The electrical supply to the rotor 206 of the rotating portion is conveyed by the carbon brush 208 and the rectifier 209 in contact therewith. The blower 201 has a structure in which an impeller 21A that is directly coupled to the rotating shaft 205, a diffusing vane 211 that is provided on the outer peripheral side of the impeller 210, and a return guide that is disposed on the opposite side with respect to the diffuser vane 211 sandwiching the partition plate 212. The guide 213 is housed in the fan case 214. A plurality of blades (moving blades) are formed on the impeller 210. Since the diffusion wing 211 and the rotating shaft 205 are not connected, they do not rotate. A plurality of blades (static blades) are also formed on the diffusion wings 211. The impeller 210 is slightly in contact with the seal member 216 provided on the side of the fan casing 2 1 4 in the central portion 2 15 of the circular ring shape, and has a structure for preventing air leakage. The air corresponding to the electric blower inlet 217 of the blower inlet 108 of Fig. 1 is temporarily passed through the vicinity of the center portion 215, and is then pressurized and increased by the impeller 210. Thereafter, the airflow is slightly rotated by 180 degrees by the diffusion wing 211, and flows into the return guide 2 1 3, in which the airflow is decelerated, and the decelerating portion causes the pressure to rise. The airflow returning to the guide 213 flows into the casing 203 of the motor -15-201200738, and the rotor 206, the stator 207, the carbon brush 208, the rectifier 209, and the like are cooled and exhausted. The axial direction of the rotary shaft 205 slightly coincides with the front-rear direction of the vacuum cleaner body 1A. The direction orthogonal to the axial direction is the radial direction based on the rotation axis 205. The outer diameter of the impeller of the electric blower for vacuum cleaner of the present invention is approximately in the range of Φ 60 mm to φ 1 2 0 mm, and the blade outlet height is approximately in the range of 6 to 12 mm, and the thickness of the blade is approximately 〇. 5~1. In the range of 5 mm, the number of blades is approximately 6 to 9 pieces, the input range is approximately 500 W to 1 500 W, and the maximum number of rotations is approximately 35,000 to 50,000 rpm. Next, the structure in the vicinity of the center portion 300 of the electric blower of the present embodiment will be described with reference to Fig. 3. Fig. 3 is an enlarged view of the vicinity of the center portion 2 1 5 of Fig. 2; The seal member 302 corresponding to the seal member 216 of Fig. 2 is fixed via a seal member fixing member 301 attached to the fan case 309 corresponding to the fan case 214 of Fig. 2 . With respect to this sealing material 302, the impeller center portion 315 is invaded to constitute a sealing mechanism. Although this sealing mechanism is important in this position, it is not limited to this. The vane 306 is fixed by the caulking 317 with respect to the shroud wall 304 on the front side in the axial direction and the hub wall 305 on the rear side in the axial direction. However, the vane 306 may be fixed by means other than riveting such as welding. The blade 306 is composed of a flat plate made of a material having a slightly uniform thickness of aluminum as a main component. Here, the slight uniformity includes the thickness due to deformation or thermal deformation during processing, and the thickness caused by the unevenness of the surface. The shield is composed of a flat plate made of a material having a slightly uniform thickness of aluminum as a main component, and has a ring shape. That is, the shield is attached to the center with a circular opening. The vane surface of the shroud 3 06 is the shroud wall 3 04. As shown in Fig. 3 -16 - 201200738, the outer edge (outermost circumference in the radial direction) of the shield is oriented in the radial direction toward the inner edge (the innermost circumference in the radial direction) of the shield. As shown in Fig. 3, in the vicinity of the inner edge of the shroud, it gradually changes from the radial direction to the axial direction. The hub is also formed of a flat plate made of a material having a slightly uniform thickness of aluminum as a main component, and has a circular shape or a circular ring shape. The side wall surface of the vane 306 of the hub is the hub wall 305. As shown in Figure 3, the outer and inner edges of the hub are oriented in the radial direction. Therefore, the outer edge of the shroud and the outer edge of the hub are slightly parallel and separated. The blade 306, the shroud, and the hub may be made of an alloy other than aluminum or a metal other than aluminum (e.g., iron, stainless steel, titanium) or ceramic. Riveting is generally performed along the side surface of the shroud wall 306 of the blade 306 and the end faces of the end face of the hub wall 305 side. Here, attention is paid only to the side of the shroud wall 306 and the innermost side (inner side) The edge side is shown. It is preferable that the shirring 3 1 7 is formed integrally with the blade 306. For example, when the blade 306 is punched out from the flat plate, the portion of the riveting portion 31 is also punched together, and the riveting portion 31 and the blade piece 306 can be integrally formed. Alternatively, when the blade 306 is cut out from the flat plate, the portion of the riveting portion 31 is also cut together, and the riveting portion 317 and the blade piece 306 may be integrally formed. The side wall surface of the shroud wall 304 of the vane 306 has a shape along the shroud wall 306, and the end surface of the hub wall 305 of the vane 306 has a shape along the hub wall 305. The line of the end face of the shroud wall 306 of the blade 306 is referred to as a shroud-side curved line, and the line of the end face of the hub wall 305 of the blade 306 is referred to as a hub-side curved line. Then, the impeller 3 03 is formed by the shroud and the hub and the plurality of blades 31 in the circumferential direction. The hub is fixed to the rotating shaft 308 corresponding to the rotating shaft 205 of FIG. 2, and as a result, the impeller 3 03 is fixed to the rotating shaft 308. Thereby, the impeller -17-201200738 303 also rotates with the rotation of the rotary shaft 308. The inner edge of the blade 306 protrudes from the front side' to form the leading edge of the blade 307. There is a space ' between the leading edge of the blade 3 0 7 and the axis of rotation 3 0 8 to form a flow path. The position of the stationary portion leading end 3 1 4 of the inner circumference of the fan case 309 and the position of the blade leading edge 307 of the blade 306 do not coincide with each other. The stationary portion leading end 314 is located on the front side more than the blade leading edge 3 07, and has an axial direction step 316. That is, there is a step in the axial direction between the fixed portion and the rotating portion. The position of the stationary portion front end 314 of the inner circumference of the fan case 309 and the position of the impeller center portion 315 of the shroud do not coincide with each other, and the stationary portion front end 3 1 4 is located on the inner peripheral side more than the impeller center portion 3 1 5 The step is 3 1 0. That is, the relationship between the fixed portion and the rotating portion also has a step in the radial direction. The thick arrow indicates the direction of the airflow 3 1 3 . The air enters the entrance of the center portion 2 15 and flows into a space (flow path) formed between the two adjacent blades 3 06 in the circumferential direction. Based on the presence of the radial step difference 310, the airflow creates a leak. Next, the shape of the impeller 400 will be described using FIG. The fourth (a) diagram is a front view of the impeller 400 as seen from the front side in the axial direction. Fig. 4(b) is a side view as seen from the side perpendicular to the rotation axis of the impeller 400. As shown in Fig. 4(a), the blades 401 corresponding to the blades 306 of Fig. 3 are provided at eight equal intervals in the outer circumferential direction, and have a rotation direction from the impeller center portion 404 toward the outer side in the radial direction. And the direction of reverse rotation, and once again twisted into the shape of the direction of rotation. Further, as shown in Fig. 4(b), the maximum diameter of the shroud wall 402 provided on the front surface of the vane 40 1 is larger than the maximum diameter of the hub wall 403 provided behind the vane 4〇1. That is, the outer circumference of the shield is larger than the outer circumference of the hub. Therefore, the outer edge of the shroud is located on the outer peripheral side of the outer edge of the hub. In addition, the outer edge of the shroud wall 402 and the vane 401 are the same diameter, and the hub wall 403 and the outer edge of the vane 401 are also of the same diameter. Therefore, the outer edge of the shroud side of the blade -18-201200738 40 1 is larger than the outer edge of the hub side. Next, the shape of the impeller 400 and the diffusion vane 21 1 will be described using FIG. The diffusion wing 2 1 1 is formed to cover the outer peripheral side of the impeller 400. The inner edge of the diffuser 211 of the stationary body is located at the outer edge of the impeller 400 for the rotating body, leaving a position where the impeller 400 can rotate. A blade (stationary blade) 406 in which a plurality of (for example, 13) blades are formed in the circumferential direction is formed between the annular member on the front side and the annular member on the bottom side. The vanes 406 of the diffuser 2 1 1 are not uniform in thickness and are composed of a resin material. Further, the blade 401 with respect to the impeller 400 is twisted to have a three-dimensional shape, and the blade 406 of the diffuser blade 211 is not twisted, but is inclined or curved, and has a two-dimensional shape. The number of blades 406 of the diffuser wing 21 1 is more than the number of blades 401 of the impeller 400. The blade 401 of the impeller 400 is inclined or curved in the radial direction centering on the axis of the rotating shaft from the inner edge to the outer edge in the radial direction opposite to the side opposite to the rotational direction 405. On the other hand, the blade 406 of the diffuser blade 21 1 is inclined or curved in the radial direction centering on the axis of the rotating shaft from the inner edge to the outer edge in the radial direction about the axis of the rotating shaft 4〇〇. The inclination and bending direction of the blade 401 of the impeller 4 来看 as viewed from the axial direction, and the inclination and bending direction of the blade 406 of the diffusion wing 211 are opposite, and the axis of the outer edge (outlet) of the blade 401 of the impeller 400 The direction of formation of the direction, and the inner edge of the blade 4 0 6 of the diffuser 2 1 1 (inlet. The direction in which the axial direction is formed is slightly uniform. For example, in the case where the axial direction of the blade 406 of the diffusion wing 211 is slightly coincident with the axial direction, the direction of the axial direction of the outer edge of the blade 401 of the impeller 400 is also slightly aligned with the axial direction or only in the rotational direction. A little tilt is better. Thereby, the airflow ‧ from the impeller 400 can be turbulently and smoothly flowed into the diffuser 2 1 1 . Next, the shape of the blade 500 will be further described using FIG. Fig. 5 is a front view of the blade 500 of one piece viewed from the front side in the axial direction. When viewed in the absolute coordinate space based on the direction of the rotation axis, the direction from the hub wall of the blade 500 to the direction of the rotation axis of the shroud wall is in the vicinity of the entrance including the inner edge portion 5 0 3 in the direction of rotation 5 0 5 The inclination is smaller toward the outer edge of the blade, and the inclination in the direction of rotation becomes smaller than the direction of the rotation axis, and becomes a slightly two-dimensional shape 506. Further, the direction from the direction in which the hub wall of the blade 500 is formed to the direction of rotation of the shroud wall is inclined toward the reverse rotation direction as compared with the direction of the rotation axis toward the outer edge of the blade, and is inclined toward the maximum inclination in the reverse rotation direction. Further, when approaching the outer edge portion, the inclination in the reverse rotation direction becomes small, and the vicinity of the outlet 504 slightly coincides with the direction of the rotation axis, and becomes a slightly two-dimensional shape 507. From the hub wall of the blade 500 to the direction in which the shield wall is formed in the direction of the rotation axis, the outer edge portion is again inclined only a little (a few degrees) in the direction of rotation. That is, when viewed from the axial direction, the blade 5 turns from the inner edge to the outer edge, and is twisted in the reverse rotation direction from the state of being twisted in the rotational direction, and then twisted again in the rotational direction. Then, when viewed from the axial direction, the blade 5 has two slightly two-dimensional shapes 5 06 and 5 07 from the inner edge to the outer edge, and has a shape in which the oblique direction is changed in front and rear. The term "slightly two-dimensional shape" as used herein refers to a plane located in a direction including a rotation axis, and specifically refers to a connection portion of the blade 500 to the shroud wall and a connection portion of the blade 500 to the hub wall, which is present in In the direction of the rotation axis. The inlet end of the inlet 50 3 has an inner edge in the radial direction and a leading edge in the circumferential direction (the leading end in the rotational direction 505). -20- 201200738 near the exit 504 The exit end 'becomes the outer edge in the radial direction' becomes the rear green in the circumferential direction (the last end of the rotational direction 505). That is, in the vicinity of the entrance 5〇3 and the vicinity of the exit 5〇4, although inclined in the direction of rotation, but between the inner edge and the outer edge, there is a slightly two-dimensional shape of two points, and the direction of inclination is slightly before and after the two-dimensional shape. change. Further, the blade 500 is formed by bending a flat plate, and its thickness is not particularly thicker at the intermediate portion. The inclination of the end face 5 〇 2 of the intermediate portion of the blade 500 to the end face of the cover 50 1 1 may be a straight line or a bend (inverting). The direction from the hub wall of the blade 500 to the direction of the rotation axis of the shroud wall can be slightly aligned with the direction of the rotation axis in the outer edge portion. The direction in which the blade 500 in the inner edge portion is formed in the direction of the rotation axis is related to the angle of incidence of the air to the blade 500. The direction in which the direction of the rotation axis of the blade 500 in the outer edge portion is formed is related to the matching of the angle of incidence of the air of the diffusion fin 211. Therefore, the direction in which the blade 500 in the outer edge portion is formed in the direction of the rotation axis is preferably slightly coincident with the direction in which the blade 406 of the diffusion blade 211 is formed. The shape of the shroud side 501 in the shape of the hub side 502 on the inner edge side in the radial direction intermediate portion when viewed from the opposite coordinate space based on the shape of the hub side 502 (the hub side curved line) The cover side curved line) is curved in the rotation direction, and in the outer edge side among the intermediate portions in the radial direction, 'the shape of the hub side 502, the shape of the shield side 501 is curved in the reverse rotation direction' in the outlet attachment 504, With regard to the shape of the hub side 502, the shape of the shroud side 501 flies out slightly in the direction of rotation. That is, in the middle portion of the intermediate portion in the radial direction, on the side of the inner edge, the position of the connecting portion of the blade 500 with the shroud wall with respect to the connection portion with the hub wall is located on the side opposite to the direction of rotation 'and thus on the outer edge - 21 - 201200738 The part is located on the outer peripheral side of the inner peripheral side than the outer edge portion, and the connection portion of the vane 500 to the shroud wall is located on the side of the rotation direction side with respect to the position of the joint portion with the hub wall. From the inner edge to the outer edge of the blade 500, the shape of the hub side 502 (the curved line on the hub side) and the shape of the shroud side 501 (the curved line on the side of the shroud) are crossed at two places. The specific shape of the blade 60 1 will be described. Fig. 6 is a front view of the impeller 600 as seen from the front side in the axial direction, and the blade 601 provided in the plurality of sheets is represented by only one piece. Further, R1 to 7 in Fig. 6 mean a circle which is concentric with a center portion around the rotation axis, and points and centers at which the respective circles intersect the shape of the shroud side 602 and the shape of the hub side 603. The angle formed by the shaft is taken as a tilt angle Θ. The inclination angle Θ can also be referred to as the inclination angle of the impeller 600 in the circumferential direction with respect to the axial direction. The inclination angle 当 is a case where the shape of the shroud side is inclined toward the side of the rotation direction, and the case where it is inclined in the reverse rotation direction is negative. The blade 601 is of the same diameter R 1 (inner edge portion) as the center portion, and the shape of the shroud side 602 of the blade 601 is inclined only by Θ1 in the direction of rotation 604 as compared with the shape of the hub side 603, toward the blade. The amount of the outer edge R2 that is inclined in the direction of rotation becomes Θ2, and further, the shape of the shroud side 602 and the shape of the hub side 603 in the R3 (the two-dimensional shape portion on the inner edge side) toward the outer edge of the blade. Crossed, slightly 2-dimensional shape. Further, in the present invention, 'Θ1 is 11°, 02 is 9°, Θ1>Θ2> Θ3 (Θ3 = 0). That is, the blade 601 is the largest inclination in the rotational direction in the inner edge portion. However, the portion having the largest inclination "not the inner edge portion" may be located on the outer edge side slightly smaller than the inner edge portion. Further, in the R4 from R3 further toward the outer edge of the blade, the shape of the shroud side 602 of the blade 610 is inclined by Θ4 in the direction of rotation of the reverse-22-201200738 as compared with the shape of the hub side 6 〇3. In the R5 (the largest inclined portion in the reverse rotation direction) toward the outer edge of the blade, the amount inclined in the reverse rotation direction becomes Θ5, and further toward the outer edge of the blade R6 (the outer edge side is slightly two-dimensionally shaped) The shape of the shroud side 602 and the shape of the hub side 603 are again intersected to have a slightly two-dimensional shape. Further, in the present invention, Θ4 is -3. , Θ5 is -4. , Θ 4 > Θ 5 & Θ 6 ( Θ 6 = 0 ). Further, a maximum inclined portion is formed from r5 to the inner edge side. Further, from R6 to R7 (outer edge portion) of the outer edge of the blade, the shape of the shroud side 602 of the vane 601 is inclined by Θ7 in the direction of rotation as compared with the shape of the hub side 603. In addition, in the present invention, Θ7 is 0. 5°. That is, from R1 to R2, the shape of the shroud side 602 is inclined in the direction of rotation as compared with the shape of the hub side 603, and is slightly two-dimensional in R3, and in the reverse rotation direction from R3 to R4, R5. Tilt, in R6, again becomes a slightly two-dimensional shape, and in the outer edge, it is inclined again in the direction of rotation. That is, when the order is given by the circle on the rotating shaft from the inner edge to the outer edge of the blade, the inclination angle 与 with the respective circles becomes the order of Θ1 > Θ 2 > Θ 7 > Θ 3 = Θ 6 > Θ 4 > The maximum inclination angle ′ of the shroud forming direction of each of the blades of the hub on the concentric circle is preferably 5° to 15°. The slightly two-dimensional shape ' on the inner edge side of the two slightly two-dimensional shapes is located on the inner edge side more than the intermediate point in the radial direction. In the outer edge side which is slightly more than the inner edge side, the blade 601 is inclined in the rotational direction. In the outer edge side which is slightly more than the inner edge side, the blade 6 0 1 is inclined in the reverse rotation direction. However, the absolute 値 (for example, ' θ 1 = 1 1 ° ) ' for the maximum inclination angle in the direction of rotation is larger than the absolute 値 (for example, θ 5 = _ 4 ° ) of the maximum inclination angle in the reverse rotation direction. The two-dimensional shape of the outer edge of the two-dimensional shape is located in the vicinity of the outer edge portion (the inner edge side is several mm from the outer edge portion). -23- 201200738 Next, the description will be made with reference to FIG. The blade angle distribution of the blade of the invention. In Fig. 7, an orthogonal line is drawn for a straight line connecting the arbitrary position of the blade to the central axis (the axis of the rotating shaft 308), and the angle formed by the orthogonal line and the outer wiring of the blade is regarded as a blade. Mounting angle or blade angle "β". The horizontal axis is the diameter. As shown in Fig. 7, in the innermost edge of the radius, the shroud blade angle is set to be larger than the hub blade angle. More specifically, the diameter of the blade shroud is D, and the inner diameter of the shroud is 0. 387D, the inner diameter of the hub is 0. In the case of 3 5 7D, the shroud blade angle is set to about 25 degrees and the hub blade angle is set to about 22 degrees. That is, in the inner edge, on the hub side, the blade angle on the shroud side is slightly larger, and the inner diameter of the shroud is larger than the inner diameter of the hub. Further, in the outer edge having the largest radius, the shroud blade angle is set to be larger than the hub blade angle, and the outer shroud outer diameter of the blade is set to be larger than the outer hub side. More specifically, the diameter of the shroud of the outer edge of the blade is taken as D. The diameter of the hub side of the trailing edge is 0. In the case of the 996D, the guard blade mounting angle is set to about 35 degrees, and the hub blade mounting angle is set to about 20 degrees, and thus the blade angle distribution of the blades of the hub wall is as shown by the solid curve in FIG. As the outer edge of the hub surface increases toward the outer edge, the inflection point 7 0 2 on the hub side of the inner edge side comes. Then, the blade angle gradually decreases toward the outer edge and reaches the inflection point 7〇2 on the hub side of the outer edge side. Then, once the inflection point 7〇2 of the hub side on the other side is passed, the blade angle decreases again toward the outer edge. That is, the angular distribution of the blades of the succeeding hub is set to have two inflection points 702 on the hub side toward the outer edge. In addition, depending on the entry conditions, it may also become a turning point. -24- 201200738 Furthermore, the blade angle distribution on the shroud side is as shown by the dashed curve in Fig. 7, with no angle increase from the inner edge of the shroud toward the outer edge 'the inner edge' The turning point 7 on the side of the cover comes. Then, the blade angle increases toward the outer edge, reaching the inflection point 7 〇 1 on the shroud side of the outer edge side. Then, the turning point 7 〇 ! ' on the side of the shroud on the other side is slowly reached the blade angle of the outer edge as it goes toward the outer edge. That is, the angular distribution ' of the blades of the succeeding hub is set to have the two inflection points 7 0 1 on the shroud side toward the outer edge. Further, the solid line curve of the dotted line curve of the blade angle distribution on the shroud side and the blade angle distribution on the hub side intersects on the outer edge side of the slightly more center in the radial direction. In the inner edge side from the intersection point 7〇3, the blade angle of the shroud is smaller than the blade angle of the hub, and from the intersection side, the blade angle of the shroud is larger than the blade angle of the hub. In addition, the maximum angle of the blade angle distribution, the blade angle of the hub is larger with the blade angle of the shield. In addition, the inflection point of the shroud and the hub is located on the more inner side than the intersection point 7〇3. The intersection 703 may be closer to the inner edge side than the center position, or may be the outer edge side. The position of the intersection 7 0 3 is, for example, related to the flow rate or the angle of incidence of the impeller 3 0 3 . Next, Fig. 8 shows a comparison of the efficiency of the design point air volume which is the type of the air blower of the present embodiment described above and the comparative example. Fig. 8 is a diagram showing that the fixed diffusion wing 'sets the axial power of the blade to a certain state'. In the comparative example and the present embodiment, only the leaves are changed. The number of rounds is analyzed. As shown in Fig. 8, the efficiency of the impeller is increased as compared with the comparative example, as compared with the comparative example of the present embodiment which is the above-described embodiment. Further, the diffusion wing efficiency, the comparison between the present example and the comparative example was found to improve the efficiency. Further, in the case of the air blower efficiency of the impeller and the diffuser, the efficiency of the present embodiment and the comparative example was improved. According to the blower which is the embodiment, compared with the comparative example, the efficiency of the diffuser is increased more than the efficiency of the impeller, and the efficiency of the spreader is improved to contribute to the efficiency of the blower. Here, Fig. 14 is a view showing the shape of the blade of the present embodiment and the blade of the comparative example. The single-blade blade is seen from the front side in the axial direction. Fig. 14(a) shows the blade of the present embodiment, and Fig. 14(b) shows the blade of the embodiment. In the comparative example, the position of the shroud-side joint portion in the trailing edge portion of the blade is set to be the reverse rotation direction from the position of the hub-side joint portion, and the hub-side vane outlet angle and the shroud-side vane outlet in the trailing edge portion of the vane are made. The angle becomes equal. That is, it has a blade having a slightly two-dimensional shape from the inner edge to the outer edge of the blade. The inclination angle of the inner edge portion in the rotation direction of the comparative example coincides with the inclination angle of the inner edge portion in the rotation direction of the present embodiment, and the position of the first two-dimensional shape of the comparative example (the radial position from the axial center) and the present In the two slightly two-dimensional shapes of the embodiment, the positions of the slightly two-dimensional shapes on the inner edge side are the same. The air blower of the air conditioner and the electric air blower are different in size, the number of rotations, the presence or absence of the diffusion wing, and the like. For the comparative example, for example, the centrifugal fan of the air conditioner of Patent Document 2 is applied to the object of the present embodiment. An example of an electric blower for an electric vacuum cleaner. In the electric blower of the present embodiment, in order to investigate the impeller efficiency improvement effect of the design point air volume, the comparison of the axial direction distribution of the wind speed in the impeller outlet (at the trailing edge portion) is shown in Fig. 9 ). The vertical axis of Fig. 9 indicates the impeller exit speed, and the horizontal axis indicates the axial position from the hub side to the shroud side. In addition, the maximum position on the horizontal axis -26- 201200738 indicates the average speed of the impeller exit. In the impeller, the smaller the impeller exit velocity, the greater the pressure rise in the impeller and the better the efficiency. Further, in the electric blower of the electric vacuum cleaner, there is a diffuser vane at the impeller exit, and the distribution of the impeller exit speed is important from the matching with the airflow of the diffuser vane. From Fig. 9, it is found that the average speed is lowered as compared with the comparative example. Further, when the speed in the axial direction is the same, the difference in speed between the shroud side and the hub side is smaller than in the comparative example. From the above, the velocity distribution inside the impeller is improved, and the efficiency is improved. In the present embodiment, the impeller exit speed is increased from the hub side to the central portion in the axial direction, and is increased from the center portion in the axial direction to the shroud side. Further, the impeller outlet speed 'is smaller than the hub end and the shroud end in the axial center portion. In the present embodiment, in comparison with the comparative example, the impeller exit speed at the center portion in the axial direction from the hub side is small. Further, Fig. 15 shows a comparison of internal airflow in each cross section of the blade in the axial direction (a numerical analysis result). Fig. 15 shows only two of the blades 401 of the eight blades 401 which are present throughout the circumference. The lighter the color, the higher the number and the faster the speed. The velocity distribution shown in Fig. 15 is not the velocity distribution of the absolute coordinates based on the electric blower 106 or the diffuser 21 1 of the stationary body, but the velocity distribution of the relative coordinates based on the impeller of the rotating body. Therefore, in Fig. 15, the portion having a small speed (the portion having a rich color) has a large speed for the diffusion fin 211. In Fig. 15, the portion having a large speed (the portion having a light color) is small for the diffusion wing 21 1 . The i5(a), (b) and (c) diagrams show the velocity distribution of the present embodiment. 15(d)(e)(f) shows the velocity distribution of the comparative example. In addition, the 15th (a) and (d) show the hub side section in the axial direction (with the hub). 27- 201200738 Speed distribution of the wall connection, 15(c)(f) shows the velocity distribution of the shroud side section (connection to the shroud wall) in the axial direction, section 15(b)(e) Indicates the central section of the axial direction (the center between the hub wall and the shroud wall). When comparing the shroud profiles, the velocity distribution of this example (Fig. 15(c)) and the velocity distribution of the comparative example (p. 15(f) Figure) There is no big difference. It can be considered that the angular distribution of the shape of the shield side 501 is both properly defined. Even when the central cross section is compared, the velocity distribution (Fig. 15(b)) of the present embodiment and the velocity distribution (Fig. 15(e)) of the comparative example are not greatly different. It can be considered that the angular distribution of the shape of the center in the axial direction is properly defined. In contrast, when comparing the hub profile, the velocity distribution of this embodiment (1st. 5(a) Fig.) For the velocity distribution of the comparative example (Fig. 15(d)), a thick portion is visible particularly on the side of the reverse rotation direction of the trailing edge portion of the blade, that is, the low velocity region is small (Fig. 15) Part A). As shown in Fig. 7, as a result of making the blade angle of the rear edge portion of the hub small, the shape of the rear edge portion of the hub becomes a shape along the air flow, and the low speed region can be reduced. Then, as described in Fig. 9, in comparison with the comparative example, particularly in the case where the low speed region on the hub side is lowered, the speed on the hub side can be reduced, and the average speed can be lowered. Further, in the electric blower of the present embodiment described above, in order to investigate the effect of improving the efficiency of the diffusing wing for designing the point air amount, the comparison of the internal airflow in the central cross section of the diffuser in the axial direction is shown in Fig. 10 (the numerical analysis result) . Fig. 10 shows that there are 13 blades in the diffusion wing throughout the circumference, and only two blades 1001 are shown. The lighter the color, the higher the number and the higher the speed. That is, when the airflow inside the diffuser -28-201200738 changes from a light color to a rich color, the inside of the diffuser is efficiently decelerated and the pressure rises. According to Fig. 10, in the comparative example, in the diffusion wing outlet portion 1004, the high-speed region 1002 and the low-speed region 1 003 ' are known to decelerate from the impeller. That is, it is known that peeling occurs at the diffusion wing outlet portion 1 〇〇4, and the loss is increased. On the other hand, in the embodiment, 'there is no high-speed area or low-speed area in the diffusion-wing outlet portion 1 004', and it is known that the speed is decelerated. That is, the pressure rise inside the diffuser in the embodiment was improved as compared with the comparative example, the energy loss was lowered, and the efficiency was improved. Further, the speed distribution of the hub side cross section and the shroud side cross section of the diffusion fin of the present embodiment is not significantly different from the speed distribution of the hub side cross section and the shroud side cross section of the diffusion vane of the comparative example. According to the above, in the present embodiment, the shape of the shroud side 501 of the blade, the shape of the central portion in the axial direction, and the shape of the hub side 502 are appropriately adjusted, that is, the inner edge portion to the outer edge portion of each cross section in the axial direction. Appropriate shape can reduce the average speed of the impeller outlet, not only can improve the efficiency of the impeller, especially the efficiency of the diffusion wing. In particular, as a result of reducing the angular distribution of the rear edge portion of the hub side 502, the shape of the shroud side 510 of the blade and the shape of the hub side 502 are not only on the inner edge side as viewed from the direction of the rotation axis. It also crosses near the outer edge. Hereinafter, a method of manufacturing the electric blower of the present invention will be described. The riveting will be described using Fig. 1 . Yu Xiang. A plurality of riveting protrusions 1 1 05 are provided in each of the upper end portion (the axial direction front side) and the lower end portion of the hub side (the rear side in the axial direction) of the blade 1 106 of the blade 3 06 of Fig. 3; (rivets). As described above, the staking protrusions 1105 are preferably formed as -29-201200738 with the blades 1 1 〇4. In order to conform to the position and number of the protrusions 1105 for the riveting of the blade, a plurality of caulking holes 1102 are provided in the shroud wall 1103 and the hub wall 1101. Therefore, the relative positions between the plurality of caulking holes 1102 of the shroud wall 1103 are the positions along the shape of the upper end portion of the blade 1104, and the relative positions of the plurality of caulking holes 1102 of the hub wall 1101. Is the position along the shape of the lower end of the blade 1 104. The caulking hole 1 1 〇 2 is a through hole. For example, in the case where all are slightly two-dimensional, the relative positions between the plurality of caulking holes 1 1 02 of the shroud wall 1 1 03 and the relative positions of the plurality of caulking holes 1 1 02 of the hub wall 〇 1 are almost the same. In the present embodiment, in the inner edge side of the blade, the upper end portion of the blade 104 of the blade 104 is more inclined than the lower end toward the front side in the rotational direction 405, and therefore, the plurality of riveting of the shroud wall 1 103 The relative position between the holes 1102 is a position that expands toward the front side in the rotational direction 405 as compared with the relative position between the plurality of caulking holes 1102 of the hub 801. In Fig. 1, the shroud and the hub side have three riveting structures. The respective positions of the caulking projections 1105 at the upper end portions of the vanes 1 10 04 correspond to the respective positions of the caulking projections 1 105 at the lower end portions of the vanes 1104. The riveting protrusion 1 105 of the blade 1 104 is inserted into the shroud wall 1 103 and the riveting hole 1 102 of the hub wall 1 101, by riveting from the outside, the blade 1 104 and the shroud wall 1 103 and the hub wall 1 101 is assembled into one. In addition, the blade shape shown in Fig. 1 is the blade outer diameter D2: 89 mm, and the blade width b2: 6. 8mm, b2/D2 = about 0. The flat leaf shape of 08. Here, the riveting means that the caulking projection 1 1 05 is inserted into the caulking hole 1 1 02, and the caulking hole 1 1 02 is inserted, and a special tool or a special device is used for the front end of the riveting projection 1105 flying out of the opposite side. The act of crushing. The caulking hole 1102 of the hub wall 1101 is inserted into the riveting projection -30-201200738 of the blade 11 04, and the blade 1104 is fixed to the hub wall 1101, and the caulking hole 1102 of the shroud wall 1103 is inserted. The caulking protrusion 1105 inserted into the blade 1104 may be riveted, or vice versa. Further, the caulking hole 1102 of the hub wall 1101 and the caulking hole 1102 of the shroud wall 1103 are inserted into the caulking protrusion 1105 of the blade 1104, and then riveted. Compared with the comparative example, in the present embodiment, in the particularly inner edge side of the blade 1 200, by tilting the blade 1 200 toward the front side in the rotational direction, it is necessary to maintain between the blade 1 200 and the shield wall 3 04 and Airtightness between the blade 1 200 and the hub wall 305 becomes difficult. Therefore, it is preferable to coat the caulking portion (joining portion) of the blade 1 200 and the shroud wall ZZ and the rivet portion (joining portion) of the blade 1 200 and the hub wall 305 with an electric coating or an adhesive. . In particular, it is preferable that the adhesion is lower than the electrocoating or the adhesive used in the comparative example. Thereby, it is possible to prevent a gap between the blade 1 200 and the staking portion (connection portion) of the shroud wall 404 and the rivet portion (connection portion) of the blade 12 00 and the hub wall 305, thereby suppressing disturbance of the air flow and suppressing Reduced efficiency. [Embodiment 2] The same reference numerals are given to the same elements as in the first embodiment, and the description thereof will be omitted. In the manufacturing method of the riveting described above, when the blade is inclined in the rotational direction, the blade is easily slid in the rotational direction due to the difference in the position of the shield in the rotational direction of the hub, and the assembly accuracy is lowered. Question. On the other hand, as shown in FIG. 2, in the second embodiment, as described in the above -31 to 201200738, the shroud forming direction of each blade of the hub is in the rotational direction of the inner edge of the blade. The inclination is inclined toward the reverse rotation direction toward the opposite side of the blade, and becomes slightly two-dimensional with the hub side, and then becomes the reverse rotation direction, and becomes slightly two-dimensional from the outer edge of the blade. The shape is inclined at the outer edge of the blade again in the direction of rotation, and has a blade having a two-dimensional shape of two points from the inner edge to the outer edge of the blade. Therefore, as shown in Fig. 12, the caulking protrusion 1 2 05 is used for the shroud side 1 201 and the hub side 1 202 at a slightly two-dimensional shape at 2 o'clock, thereby preventing the blade from slipping during the caulking. The distance b between the shroud side 1201 and the hub side 1 202 is controlled to a specific size to be manufactured. Further, in the inner edge side and the outer edge side of the two-dimensional shape of the two points, the inclination direction of the blade is changed, and the effect of the stress at the time of the caulking is also canceled. Further, in order to obtain an effect, the riveting protrusion may be provided in a slightly two-dimensional shape. Compared with the comparative example, in the present embodiment, in the special inner edge side of the blade 1 200, between the blade 1 200 and the shroud wall 304 and the blade 1 200 are maintained by tilting the blade 1 200 toward the front side in the rotational direction. The airtightness with the hub wall 305 becomes difficult. Therefore, the rivet portion (joining portion) of the blade 1 200 and the shroud wall 306 and the rivet portion of the blade 1 200 and the hub wall 305 ( It is preferable that the connecting portion is covered with an electric coating or an adhesive. In particular, it is preferable that the adhesion is lower than the electrocoating or the adhesive used in the comparative example. Thereby, it is possible to prevent a gap between the blade portion 1200 and the caulking portion (joining portion) of the shroud wall 304 and the caulking portion (joining portion) of the blade 1 200 and the hub wall 305, thereby suppressing disturbance of the air flow and suppressing efficiency. Reduced. • 32- 201200738 [Simple description of the drawing] Figure 1 is a cross-sectional view of the model of the vacuum cleaner body. Fig. 2 is a cross-sectional view showing an electric blower for a vacuum cleaner. Fig. 3 is a structural view of the vicinity of the center portion of the impeller. Figure 4 is a diagram of the shape of the impeller. Figure 5 is a diagram of the shape of the thin blade. Figure 6 shows the detailed shape of the blade. Figure 7 is a diagram showing the blade mounting angle distribution of the blade shroud and the main plate contact surface. Fig. 8 is a comparison diagram of the efficiencies of the examples and comparative examples. Fig. 9 is a comparison diagram of the axial direction distribution of the impeller exit speeds of the examples and the comparative examples. Fig. 1 is a comparison diagram of the velocity distribution in the axial direction of the inside of the diffuser of the embodiment and the comparative example. Fig. 1 is a view showing the position of the riveting. Fig. 12 is a view showing a projection of the riveting. Figure 13 is a diagram of the shape of the impeller and the diffuser. Fig. 14 is a view showing the shape of the blades of the present embodiment and the comparative example. Fig. 15 is a comparison diagram of the velocity distributions of the respective sections in the axial direction of the impeller inside the embodiment and the comparative example. [Description of main components] 100: Vacuum cleaner body 1 〇1: Hose connector-33- 201200738 102: Dust chamber 1 0 3 : Paper bag 104: Filter unit 105: Motor room 106: Electric blower 1 〇7: Vibration rubber 108: blower inlet 109: blower outlet 1 1 0 : power cord reel 1 1 1 : wheel 201 : blower 202 : motor 203 : casing 2 04 : rear end cover 2 0 5, 3 0 8 : rotary shaft 2 0 6: rotor 207: stator 2 0 8 : carbon brush 2 0 9 : rectifier 210, 303, 400, 600: impeller 21 1 : diffusion wing 2 1 2: compartment plate 213: return guide 214, 3 09: fan casing -34- 201200738 2 1 5, 3 0 0 : Center part 2 1 6 , 3 0 2 : Sealing material 217: Electric blower inlet 3 0 1 : Sealing material fixing member 304 '402, 1103: Shroud walls 305, 403, 1101: hub wall 306, 401 '601, 1104, 1200: blade 3 0 7 : blade leading edge 3 1 0 : radial step difference 3 1 3 : direction of air flow 3 1 4 : stationary part front end 3 15 , 404 : impeller Center portion 3 1 6 : axis direction step difference 3 1 7 : riveting 405, 505, 604, 1203: rotation directions 501, 602, 1201: shroud sides 502, 603, 1202: Hub side 5 03 : Near the entrance 5 0 4 : Near the exit 5 0 6 , 5 0 7 : Slightly 2 dimensional shape 701 : Back point 702 on the shroud side : Break point on the hub side 7 0 3 : Intersection point 1〇〇1 : Blade-35- 201200738 1002: Commercial speed zone 1 0 0 3 : Low speed zone 1 004 : Diffusion wing exit part 1 102 : Riveting hole 1105, 1205: Riveting protrusion - 36