1373541 六、發明說明： 【發明所屬技術甸域】 發明領域 本發明係有關於一種滾筒式洗衣乾燥機^ 【先前技術:j 發明背景 習知之滾筒式洗衣乾燥機係揭示如日本專利第 4044602號。第15圖係顯示習知之滾筒式洗衣乾燥機之全體 構造之概略圖，第16圖係顯示由軸連結支持構件連結於該 滾筒式洗衣乾燥機之旋轉滾筒之旋轉轴，藉由軸承支持構 件支持於水槽並且連結於馬達之構造部之部分截面圖。 滾琦式洗衣乾燥機具有：水槽1〇2、旋轉滾筒1〇3、馬 達104、轴承支持構件1U、及循環送風路徑1〇9。其中水 槽102係由未圖示之懸吊裝置而彈性支持於洗衣機本體1〇1 内。旋轉滾筒103為帶底圓筒形，由開口之正面側朝向底部 之背面側設置於水槽1〇2内，而旋轉軸1〇5之方向為水平、 或由水平方向向下傾斜。馬達1〇4係用以驅動旋轉滾筒 103 °轴承支持構件hi係在水槽1〇2之背面上支持旋轉軸 105之轴承106、及馬達1〇4。又，軸承支持構件ιη係金屬 製’具體而言係鋁製。循環送風路徑109係由送風扇107銜 接到旋轉滾筒103之路徑。而且，水槽1〇2内之空氣藉由送 風扇107通過循環送風路徑1〇9排出後，會反覆進行除濕、 加熱，並且由送風口 1〇8送風至水槽丨〇2内。如此，旋轉滚 筒103内之衣物等可乾燥。 3 如第_所^麻支持構細具有軸套部llla及座 盤lllb。軸套部llla支持轴承驗座盤叫係於 之基部周圍外伸至包含送風吻之開D部之周邊區域。 又，座盤11 lb係由背面側連接固定於水槽1〇2之背部開口 1〇2a進1^ ’座盤lllb係將馬達104之定子104a固定於背 面。座盤111b於周方向之-部份具有賴送風鳴而露出 於背部之崎則lle。⑽部1Ue係作成残礙循環送風 路徑109之送風侧1〇9自背部的連接。 *第顯示安裝於f知之滾筒式洗衣乾燥機之旋轉 滚筒底。卩之網狀套及軸連結支持構件之安裝狀態的半部截 面圖。第18A圖係顯補滾筒式洗衣乾燥機之轴承支持構件 之截面圖帛18B®係顯示該滾筒式洗衣乾燥機之軸承支持 構件之正面圖’第18C圖係顯示該滾筒式洗衣乾燥機之轴承 支持構件之背面圖。 切除部111c係如第18B圖、第18C圖所示之朝周方向彎 曲之大略矩形之透孔。在包含切除部丨丨卜之外周圍之座盤 111b之全周中，具有安裝孔md，且安裝於水槽1〇2之背 部。座盤111b、水槽1〇2之背部開口 1〇2a、及旋轉軸1〇5之 基部周圍相互間係由密封構件115所密封。 轴連結支持構件112由背面側緊靠旋轉滾筒103之底部 開口 103a。其中’軸連結支持構件112係與受軸承1〇6支持 之旋轉轴105之一端部連結。而且由外周面側將旋轉滾筒 103與軸連結支持構件112螺固於旋轉滾筒1〇3之本體部、底 部嵌合筒壁l〇3b之周方向之複數處而成一體化。其中，旋 1373541 轉轴105係作成於其一端部設置凸緣部1〇5a等且螺固於位 於軸連結支持構件112之中央之軸連結部112a。 進而’轴連結支持構件112係具有放射狀腕1121)、及環 狀密封壁112(^放射狀腕1121)係由軸連結部丨丨乃呈放射狀 延伸。環狀密封壁112c係連結放射狀腕1121)之途中，且連 接嵌合於旋轉滾筒103之底部開口 1〇3a。 放射狀腕112b之各端部係螺固於旋轉滾筒1〇3之本體 部、底部嵌合筒壁103b。環狀密封壁112c與旋轉滾筒103之 底部開口 103a之間係經由密封構件丨13而密封。環狀密封壁 112c與比水槽102之背部壁之送風口 1〇8靠近外周側區域之 部分的環狀部分之間，係經由機械軸封丨14限制由徑方向内 側往外側之通風。機械軸封114係軸連結支持構件ιΐ2與水 。 槽1〇2之環狀凹凸面相嵌而形成之徑方向之曲徑間隙。 -如第16圖、第17圖所示，由内側覆蓋底部開口職之 樹脂製網狀套Π6緊靠、固定於旋轉滾筒1〇3之底部内。網 • 狀套m係與旋轉滾筒ι〇3一起旋轉，並且使來自送風口· - 之送風分散通過。其結果是’可均—地送風至旋轉滾筒ι〇3 θ之廣大區域，可提高乾燥效率，不會乾燥不均。網狀套 116係圓龍。職套116係存留巾切麵邊部、及連結 中央部與周邊部之放射狀補強區域，在朝周方向排列之每 一區段領域U6a形成多數網孔116b。旋轉滾筒1〇3之底部開 口 l〇3a也形成為對應於區段領域116a之位置、及形狀。而 且底部開口 103a係與對應於轴連結支持構件112而開口之 形狀的輪廓部連接。 5 1373541 然而，上述之滾筒式洗衣機構之旋轉滾筒l〇3係橫向設 置或由水平傾斜設置。因此，當旋轉滾筒1〇3橫向設置時， 洗濯物會滯留於旋轉滾筒103之周方向的最下部。又，當旋 轉滾筒103由水平傾斜設置時，洗濯物會滞留於旋轉滾筒 103之轴方向的最下部。進而’洗濯物也會因為使用者而偏 離旋轉軸105之軸線方向投入。因此’旋轉滾筒丨〇3之旋轉 負荷容易產生偏差，成為晃動的原因。在此，旋轉滾筒1〇3 之旋轉支持係在水槽102之背面中以轴支持連結於旋轉滚 筒103之底部之旋轉轴1〇5之懸臂支持。因此，旋轉滚筒1〇3 之晃動產生大約以該軸承為中心之所謂進動運動。 旋轉滾筒103之進動運動傳達至旋轉轴1〇5，位於水槽 102之背面上之軸承支持構件Ui經由軸承1〇6而承受。此時 之承受負荷係將轴套部111 a隨著旋轉軸丨〇5而欲跟著旋轉 滾筒103之偏轉的情況作用為座盤1111}之旋轉軸1〇5之偏轉 側被推入水槽102之背面之力。接著，該力會藉由偏轉之旋 轉而反覆及於座盤111b之全周。如此之承受負荷被認為在 連結了朝周方向排列於旋轉滾筒103之端部之軸連結支持 構件112中也是大致相同的。 對此，日本專利第4044602號所揭示之習知旋轉滾筒 1〇3的支持構造係可相當耐受如此之晃動時之負荷並可抑 制於不妨礙實用之晃動範圍、振動範圍、噪音範圍。 了疋近年來’更為要求提高洗衣乾燥之處理能力。脫 水步驟中，以往為1200rPm左右之旋轉數期望增強3成如 16〇〇rpm左右之高速化。本發明人為了對應於如此之高速化 6 1373541 而以現行之滾筒式洗衣乾燥機進行種種實驗時了解到目 前之旋轉滾筒H)3之支持構造中，用以抑制旋轉滾筒ι〇3因 向逮化運轉之晃動所需要的支持強度不足。而且晃動度、 振動、噪音遠遠超過容許範圍，並且壽命提早降低。又 因此，本發明人著眼於如上述之現行之支持構造中的 軸承支持構件1U、軸連結支持構件112之形狀與負荷之作 動的關係1㈣滾筒1G3在晃動時，旋轉㈣5對轴承支 ，構件111、軸連結支持構件112之最A傾斜角檢定為最大 變形量（第1檢定）。而且檢定了最大變形量時之細承支持構 件111、軸連結支持構件112之應力値的分布（第2檢定）。 第19 A圖係習知之滾筒式洗衣乾燥機之軸承支持構件 在160〇rpm之高速旋轉條件下之應力分布圖第ΐ9β圖係解 析模型圖。第2 G A圖係習知之滾筒式洗衣乾燥機之轴連結支 持構件在l_rpm之高速旋轉條件下之正面側的應力分布 圖’第2GB圖係、該滾筒式洗衣乾燥機之轴連結支持構件在 1600rpm之高速旋轉條件下之背面側的應力分布圖。又第 20C圖係顯示該滚筒式洗衣乾燥機之軸連結支持構件在 1600rpm之兩速旋轉條件下，旋轉軸對於軸連結支持構件之 變形量、傾斜角之測^結果圖，第2GD圖絲析模型圖。第 1檢定係軸承支持構件111使用如第19B圖所示之解析模 型，轴連結支持構件Π2使用如第20D圖所示之解析模型來 進行數値計算。又’第2檢定係勘測第1檢定時之軸承支持 構件1U、軸連結支持構件112之應力分布。第19A圖係顯示 轴承支持構件111之應力分布，並認為最大應力部為切除部 7 1373541 lllc之座盤lllb周方向之兩側廣大區域及對轴承支持構件 111之中心點呈點對稱擴展之部分。 第20a圖、第20B圖係軸連結支持構件112之正背面的 應力分布圖。最大應力在背面側係集中於各放射狀腕112b 之端部’在正面側係集中於位於環狀密封壁112£；部之3支徑 方向肋部112e之對應於切除部lllc之兩側的位置、及對軸 承支持構件111之中心點呈點對稱之位置。程度比最大應力 略低之高應力被認為在正面側係集中於軸連結部112a之周 邊肋部112f、放射狀腕112b之中央縱肋部112d。第20C圖係 顯示旋轉軸105對轴連結支持構件112之變形量、傾斜角之 測定結果。 以上之檢定結果可了解到，不論是否設置放射狀、環 狀之補強肋部、沿著輪廓或不沿著輪廓之箱型補強肋部’ 旋轉軸105對轴承支持構件111、軸連結支持構件112帶來部 分超過強度之最大應力的課題。 C發明内容】 發明概要 本發明之洗衣乾燥機包含：水槽，係受彈性支持於洗 衣機本體内者；旋轉滚筒，係帶底圓筒形，且由開口之正 面側朝向為底部之背面側設置於前述水槽内，而旋轉轴之 方向為水平或由水平方向向下傾斜者；軸連結支持構件’ 係將前述旋轉轴連結於前述旋轉滾筒之底部者；軸承支持 構件，係安裝於前述水槽之背部且經由軸承支持前述旋轉 軸者；馬達，係在前述軸承支持構件上連結於前述旋轉轴 8 而驅動前述旋轉滾筒者，·及循環送風路徑，係藉由送風扇 而將前述水槽内之空氣排出，且將前述空氣除濕後進行加 熱’並且使前述空氣通過送風口而送風至前述水槽内者， 其中，前述滾筒式洗衣乾燥機之特徵在於前述軸連結支持 構件具有：軸連結部，係中央與前述旋轉轴連結者；複數 放射狀腕，係由前述軸連結部呈放射狀延伸且安裝於前述 旋轉滾筒之底部周壁者；及環狀密封壁，係連結複數之前 述放射狀腕之途中，並且連接嵌合於前述旋轉滾筒之底部 開口者，又，前述軸連結支持構件在前述放射狀腕之基部 間有-體成形之立體增強架橋，該立體增強架橋係由前述 軸連結部之湖面前端呈傘狀擴展延伸到水槽側之開放端 緣，並且呈蹼狀銜接前述放射狀腕之基部間。 如此構成之滾筒式洗衣乾燥機之抽連結支持構件係其 t連結部成躲受旋轉滾筒晃動時產生之旋轉軸之傾斜負 荷之中〜卜傾斜負荷由放射狀腕之基部經過途中之環狀 之密封周輯構成之連結部，而傳達到往旋轉滾筒之安裝 各放射狀腕在負荷造成之應力容易集中之基部間，介 由立體增強架橋而由轴連結部之側周面前端側銜接到水槽 彳兩放端’不需要特別增加重量。而且軸連結部之側周 面之間係構成朝水槽側開放之箱型的增強形態，並可提高 •彎曲強度、及對旋雜之傾斜方向_方向機所造叙 °進而箱型之增強形態為朝水槽側之開放形 藉此亦可發揮彈性變形特性，使旋轉軸之傾斜在放射 狀之基。ρ中減輕而大應力不會發生到往旋轉滾筒之安裝 部 圖式簡單說明 第1圖係顯示本發明之實施形態中， 財袖連結支持構件 連結於本發明之實施形態之旋轉滾筒之 ° 構件支持之構造部喊面圖。 轉料由抽承支持 第2Α圖係顯示該滾筒式洗衣乾燥棬 k ± 义灰轉滾筒與旋轉 軸之軸連結支持構件所構成之連結構造部 D| <哉面圖。 第2B圖係銜接第2A圖之下方之圖。 第3圖係顯示本發明之實施形態之滚筒式洗衣乾燥機 中’旋轉滾筒支持於水槽内，並將馬逹安裝於水槽背部， 且與旋轉轴連結之主要部之背面圖。 ^圖倾滾筒式洗衣乾燥機之主要部之水槽的正面 側半部拆下後所看到之分解立體圖。 ^圖—侧看安裝於該滾筒式洗衣乾燥機之水 槽之”，且支__之料，並且安^達之定子之 軸承支持構件之立體圖。 第6圖係由背面侧看第5圖之軸承支持構件之立體圖。 圖係由正面側看本發明之實施形態之滾筒式洗衣 乾燥機之旋轉滾筒的部分橫截面圖。 第7B圖係第7A圖之B_B線橫截面圖。 背邻本發明之實㈣態之料式洗衣乾燥機之 側由正面侧看安裝於旋轉滾筒之料連結支持構件 及配置有網狀套之水槽之背部侧半部之幾乎半部之立體 圖。 10 1373541 面側看該滾筒式洗衣乾燥機 之網狀套之 第9圖係由正 半部之立體圖。 網狀套之 半部由背面側看該滾筒式洗衣乾燥機之 第11圖係由正& 持構件之半部之立體^看該滾筒式洗衣乾燥機之軸連結支 第12圖係由背；y 持構件之半部之”該滾料洗衣㈣機之軸連結支 '體圖。 弟13 A圖係顯 —r承支持構件 件在該㈣錢衣㈣機之_結支持構 笛14AH1二逮旋轉條件下之變形量、最大應力之圖。 係邊滚筒式洗衣乾燥機之軸連結支持構件在 1600rPm之高錢轉條件下之正面側之應力分布圖。 第14Β圖係該滚筒式洗衣乾燥機之抽連結支持構件在 160〇rpm之高速_條件下之背面側之應力分布圖。 第14C圖係顯示該滾筒式洗衣乾燥機之袖連結支持構 件在1600rpm之高速旋轉條件下之變形量、最大應力之圖。 第15圖係顯示習知之滾筒式洗衣乾燥機之全體構造之 概略圖。 第16圖係顯示由軸連結支持構件連結於該滾筒式洗衣 乾燥機之旋轉滚筒之旋轉軸，藉由軸承支持構件支持於水 槽並且連結於馬達之構造部之部分截面圖。 第17圖孫顯示5亥滾筒式洗衣乾燥機中，安裝於旋轉滚 11 1373541 筒底部之網狀套及_結支持構件之安裝狀態之半部截面 圖〇 第腸圖係顯示該滾筒式洗衣乾燥機之轴承支持構件 之截面圖。 第18B圖係顯示該滚筒式洗衣乾燥機之轴承支持構件 之正面圖。 第18C圖係顯示該滾筒式洗衣乾燥機之轴承支持 之背面圖。 第19A圖係該滾筒式洗衣乾燥機之轴承支持構件在 160〇rpm之高速旋轉條件下之應力分布圖。 第19B圖係解析模型圖。 第20A圖係習知之滾筒式洗衣乾燥機之轴連結支持構 件在獅啊之高速旋轉條件下之正面側之應力分布圖。 第·圖係該滾筒式洗衣乾燥機之轴連結支持構件在 16〇〇rpm之高速旋轉條件下之背面侧之應力分布圖。 第脱圖係該滾筒式洗衣乾燥機之轴連結支持構件在 刪—之高速旋轉條件下對於轴連結支持構件之旋轉軸 之變形量、傾斜角之測定結果之圖。 第20D圖係解析模型圖。 t實施方式3 較佳實施例之詳細說明 以下’參照圖式說明本發明之實施形態之滚筒式洗 乾燥機。 第1圖係顯示本發明之實施形態之滾筒式洗衣乾燥機 12 中，由軸連結支持構件連結於旋轉滾筒之旋轉軸由輛承支 持構件支持之構造部喊面圖β第2，係、顯示該滾筒式洗 衣乾燥機之旋轉滚筒與旋轉軸之軸連結支持構件所構成之 連結構造部之截面圖。第2Β圖係連結第2Α圖之下方之圖。 X ’第3圖係顯示本發明之實施形態之滾筒式洗衣乾燥機 中’旋轉m持於水槽内，並將馬達安裝於水槽背部， 且與旋轉軸連結之主要部之背面圖。第4圖係該 乾燥機之主要部之水槽之正面側半部拆下後所看到之^ 立體圖。 如第1圖〜第4圖所*，本發明之實施形態之滚筒式洗衣 乾燥機⑽具有：水槽i、旋轉滾筒3、馬達4、轴承支持構 件6、循環送風路徑、軸連結支持構件8、及網狀套9。 /、中水槽1係藉由未圖示之懸吊裝置機構受彈性支持 於洗衣機本體内。旋轉滾筒3係帶底圓筒形，且由開口之正 面侧朝向為底部之背面舰置於前述水槽内，而旋轉轴之 方向水平或由水平方向向下傾斜者。亦即，本發明之實施 形感中，所謂正面側係旋轉滾筒3開口之側，背面側係正面 側之相反側。馬達4用以驅動旋轉滾筒3。轴承支持構件咚 裴於水槽1之背部，將旋轉軸2之軸承5、及馬達4支持於水 槽1之背面上》而且馬達4在軸承支持構件6上連結於旋轉軸 $循％送風路徑係藉由未圖示之送風扇，將水槽丨内之空 氣排出且進行除濕後，予以加熱，並通過送風口 7送風至 欠槽1内之路徑。旋轉滾筒3内之衣物補㈣環送風路 13 1373541 徑排出水槽1内之空氣’反覆送風而乾燥。金屬製之轴連 結支持構件8係將旋轉軸2連結並支持於旋轉滾筒3之底 部。树知製之網狀套9係覆盍旋轉滾筒3之底部開口 3a。 如第1圖、第4圖所示，軸承支持構件6具有軸套部以與 座盤6b，並經由轴承5支持旋轉軸2 ^在此軸套部6a係支持 軸承5 »座盤6b係於軸套部6a之基部周圍外伸至送風口 7之 開口部之周邊區域，且藉由螺栓U由背面側連接 '固定於 水槽1之背部開口 la。而且座盤6b係藉由螺栓丨2而固定馬達 4之疋子4a。座盤6b係於周方向之—部份具有避開送風口 7 露出於背部之切除部6c。這是因為切除部6(：係作成不妨礙 循環送風路徑之送風側自背部連接之故。 又，座盤6b在該外周全區域中，藉由螺栓丨丨而安裝於 水槽1之背部。座盤6b、水槽1之背部開口 la、旋轉軸2之基 部周圍的相互間係藉由密封構件13而密封。軸套部63之轉 子4b係將内周側轉子4bl及外周側轉子4b2構成為一體。而 且轉子4b藉由螺栓20螺固於旋轉軸2之外端2b。如此，轉子 4b藉由2個轉子4bl、轉子4b2電磁結合於丨個定子4a，體積 不會過大且旋轉滾筒3可以高轉矩進行旋轉驅動β在此，内 周側轉子4M係配置於定子4a之内周，外周側轉子4b2係配 置於定子4a之外周》 軸連結支持構件8由外面側緊靠於旋轉滾筒3之底部開 口 3a。在此，軸連結支持構件8與以受轴承5支持之旋轉軸2 之一端部連結。而且在周方向之複數處由外面側藉由螺栓 Μ而螺固於旋轉滾筒3之本體部、底部嵌合筒壁孙，使底部 14 開口 3a與細連結支持 部設置凸緣部2a，且體化°轉_作成於-端 旋細與軸連結支持構件8::軸連結咖 1為:錢卿陶 ==_開二=::: 射狀辦強2。卩&之周方向兩側設置大約朝向徑方向之放 射狀增= °R1。妓對於最高最大應力集中於赠部&之 兩側之廣大區域的對策。 ,、.·.不正面側看安裝於本發明之實施形態之 滾筒式，衣乾燥機之水槽之背部，並且支持旋轉軸之轴 承安裝馬達之定子之轴承支持構件之立體圖第6圖係 由背面侧看第5圖之軸承支持構件之立體圖。 滾筒式洗衣乾燥機100係如上所述，旋轉滚筒3基本上 係以現行之支持構造被支持於彈性支持之水槽卜且以現行 之驅動構造受驅動。軸承支持構件6具有：支持軸承5之轴 套部6a、及座盤6b。 座盤6b具有切除部6c，且承襲現行之基本形態，不會 妨礙到與循％、送風路;^之連接。可是於切除部&之周.方向 兩側設有放射狀增強部2!，該放射狀增強部21係如第3圖〜 第6圖所示之大略朝向徑方向且大略^字型肋部。因此旋 轉滾筒3在晃動時’可在周方向之局部分擔且承受作用於切 除部6c之座盤6b周方向兩側運作之徑方向之高歪曲負荷。 而且可分散、減少在切除部&之廣大區域發生之最大應 15 力，並可抑制旋轉軸2之傾斜或座盤6b之變形。 此意味著設置放射狀增強部21造成增強所需要之部分 體積增加可與在只有小應力作動之部分的部分體積減少相 抵。這可說是利用應力分布之不同之體積移動增強之軸承 支持構件6的增強方法。 在此，所謂放射狀增強部21 ’對於與一般之放射狀補 強肋部22等重疊的情況，係意指其延長、增厚、增加高度 等之至少1種之增強構造，也有將該等構造複合。第5圖、 第6圖中，係將一般之放射狀補強肋部22、環狀補強肋部 23、沿著輪廓之輪廓部補強肋部24、包圍座盤6b外周之安 裝孔30、31之箱型補強肋部28等作複合設計，並加大比該 等構件還厚之厚度，作成放射狀增強部21。 根據如此之改良’轴承支持構件6中，係在旋轉滾筒3 晃動時之負荷造成切除部6c之兩側之過度最大應力作用之 處設置放射狀增強部21。放射狀增強部21藉由高彎曲強度 而可在周方向局部分擔且承受高負荷。因此在旋轉滾筒3晃 動時’可分散與降低在切除部6c兩側之廣大區域所產生之 最大應力，亦可抑制旋轉轴2之傾斜或座盤讣的變形。由於 改善旋轉滾筒3之晃動度、振動、噪音，因此可進而對應高 速旋轉、高負荷運轉，而可得到充分壽命。該增強所^ 之部分體積增加可與在只則、應力作動之部分的部分體積 減少相抵4此，可防止體積鶴之料支持構件之增強 而重量化，相較於習知設計，可抑制針料速化程度:體 積增加。 又 16 1373541 又’放射狀増強部21係設置成由轴套部6a延伸到座盤 6b之外周附近。藉此，放射狀增強部21由軸套部6a延伸到 外周側，在與旋轉軸2之搖動所造成座盤6b變形之方向一致 之徑方向，增強其變形基部到變形終端。因此可在周方向 上分擔且承受旋轉軸2往切除部6c側之傾斜、及旋轉轴2之 傾斜造成座盤6b往徑方向之歪曲負荷。而且由軸套部6a到 外周之座盤6b之大應力的分散、降低作用可及於座盤讣之 外周部。其結果’可更確實地抑制旋轉轴2往切除部6c側之 傾斜、旋轉轴2之傾斜造成座盤6b之變形。 進而’座盤6b也具有連接放射狀增強部21間而延伸之 架橋增強部25。架橋增強部25係呈朝軸套部6a為凸之略圓 弧狀，且連接成為V字型肋部之放射狀增強部21之間，使之 呈大略A字型肋部。而且，架橋增強部25構成由切除部6c 之軸套部6a側到軸套部6a之三角形之箱型增強部26。又， 隨著箱型構造的增強，也增加該區域之強度。 又’架橋增強部25可提高對於旋轉軸2往切除部6c側之 傾斜及旋轉轴2之傾斜所造成座盤6b之徑方向的彎曲之強 度，並且分散往A型肋部及該等包圍之非肋部狀之平面區域 之應力。其結果可更為降低最大應力値，並更為抑制旋轉 軸2往切除部6c側之傾斜、座盤汕之變形。 架橋增強部25進而沿著切除部6c之軸套部如側輪廓而 形成朝軸套部6a側凸出之屈曲形狀。因此，藉由切除部& 之軸套部6a侧輪廓及朝架橋增強部25之轴套部如側突出之 譬曲形狀，加大切除部6c之切除面積，使送風口 7之開口加 17 大該部分。其結果是可增加送風空氣量，而不會增加送風 負荷’並提高乾燥速度。而且由於對於徑方向之立體化， 可提高在座盤6b之轴套部6a侧之切除部6c周圍之放射狀增 強部21間之徑方向的耐歪曲剛性。 如第4圖所示，切除部6c之兩側的放射狀增強部21係當 旋轉軸2往切除部6c側傾斜變形時，可對將座盤6b推壓至水 槽1背面所及之徑方向之歪曲負荷，防止座盤6b之變形。旋 轉軸2朝與切除部6c相反之相反侧傾斜變形時，切除部以之 兩側之放射狀增強部21以座盤6 b之外周部為支點之槓桿作 用，產生往水槽1背部之推壓力。該推壓力造成旋轉軸2往 切除部6c側之傾斜、及座盤6b之徑方向之歪曲負荷藉由如 第5圖所示之放射狀均衡增強部27之高歪曲強度，而在周方 向局部分担且承受。因此，即使係在與切除部6(；相反之相 反側，亦可分散、降低與切除部6c側相同程度之最大應力。 在此，放射狀均衡增強部27係由切除部6c之兩側的放射狀 增強部21、及與旋轉軸2之轴線周圍對稱且大略呈倒v型肋 部所構成。又，放射狀均衡增強部27與放射狀增強部幻皆 作成以旋轉軸2之軸線為中心之大略X型肋部。 結果，切除部6c之兩侧的放射狀增強部21之座盤牝的 增強在呈點對稱之座盤6b之位置帶來高負荷，但藉由放射 狀均衡增強部27在周方向局部分擔且承受。因此，可達到 在點對稱位置之最大應力往周方向的分散與降低。而且， 可達到以座盤6b之軸套部6a為邊境之切除部&側及與切除 部6c相反之相反側之最大應力往周方向的分散、降低以及 18 1373541 應力値之均衡、降低。其結果，可充分防止旋轉軸2之傾斜 變形、座盤6b之變形。 如第6圖所示’切除部6(：係具有朝座盤汕之外周開放之 大略呈C型之輪廓。在座盤牝之切除部&為透孔之現行形態 下之座盤6b外周側的連絡部也切除，藉此，可與為了增強 而作為體積增加之部分的體積相抵。如此之體積減少可因 應於分布應力値之小，藉由座盤讣之厚度的減少、 一般之 放射狀補強肋部22、環狀補強肋部23、沿著輪廓之輪廓部 補強肋部24、箱型補強肋部28等之厚度、高度的減少、刪 除來進行。 又，放射狀增強部21之端部位於設置於切除部&之開 放知。卩區域6cl中之開放端之安裝孔、及相對於鄰接於 周方向之切除部6C為相反側之安裝孔31b之間。藉此，在安 裝孔31a、安裝孔31b之間，可藉由徑方向之大的耐歪曲強 度達到應力之分散、降低n裝孔31a、安裝孔灿部 之強度不足可藉由緊固於水槽】背部、及由兩側緊固座盤 外周來彌補。進而補強切除部&之開放端部區域。又， 開放端部區域6cl作為增強部33,增強部33係設有連結放射 狀增強部21且厚度Μ增加之增厚增強部32、及比魏部 分之輪腐部補強肋部24更為增厚之輪廓增強部此至少一 種。因此，可更為分散 '降低放射狀增強部η與開放 區域6C1之應力’並可防止開放端部區域6ei之變形、損傷。 又’切除部6c兩側之增強部33與放射狀補強肋部 合。藉此’放射狀增強部21、與其_之放射狀補強肋部 19 、增強部33構成三角形之箱型增強部。藉由箱型構造， 可在切除部6c之周方向兩側增加增強度’提高座盤沾之徑 方向之歪曲強度，可分散與降低應力。 又，由於轴連結支 持構件8在旋轉滾筒3之晃動時受到高負荷 ，因此轴連結支 持構件8如第1圖、第2八圖、第4圖所示，於中央具有與旋轉 軸2連結之軸連結部8ae進而軸連結支持構件8具有：由軸 連結部8a呈放射狀延伸且安裝於旋轉滾筒3之底部周壁之 複數放射狀腕8b '及連結放射狀腕仙之途中且連接嵌合於 方疋轉滾筒3之底部開〇3a之環狀密封壁8c。而且放射狀腕 扑之各端部藉由螺栓14而螺固於旋轉滾筒3之本體部、底部 嵌合筒壁3b。 再者，與強度無關，但是如第2A圖所示，網狀套9與軸 連結支持構件8由背面側緊靠且螺固於旋轉滾筒3底部開 口。如此，由於網狀套9挾持在旋轉滾筒3底部、及軸連結 支持構件8之間，因此不需要網狀套9單獨之安裝構造。又， 周狀套1、要僅通風區域位於旋轉滾筒3之底部即可。其結 果由於樹脂製之網狀套9佔金屬製之旋轉滾筒3之底部的 =二變>，因此旋轉滾筒3底部之金屬面露出比例提高，也 提问旋轉滚筒3底部之質感，並且樹脂製之網狀套9也變得 難以受損。 。第7A圖係由正面側看本發明之實施形態之滾筒式洗衣 乾燥機之旋轉滾筒之部分橫截面圖，第7B圖係第7A圖么 B-B線撗戴面圖。 用狀套9與旋轉滚筒3一起旋轉’並且使來自送風口了么 20 适風分散通過，將送風平均地導入旋轉滾筒3 域，提1^乾燥效率，^^會㈣不均。網狀套9之大區 的通風區域成複數排列於旋轉滾筒3之周方向，並^有網眼 風區域通過作成對應於網眼之大小及㈣個通 底部開口 3a而露出於正面側即可。如此，：。3之 旋轉滚筒3之周方向上排列，不論在哪個旋轉位置=在 自送風口 7之送風均等地導入旋轉滾筒3内且避免乾燥來 均。而且排列在旋轉滾筒3之周方向之各通風域周圍^藉: 金屬製之旋轉滾筒3底部㈣，被包圍裝饰成圍框的狀^。 具體而言，網狀套9係如第4圖所示之圓盤體，用:在 麵轉滾筒3底部之旋轉轴2之轴線周圍均等地作動。在中央 部9a、周邊部％、連接中央部9a與周邊部％之放射狀補強 區域9c除外之領域，在每個在旋轉滾筒3之周方向排列之通 風區域之區段領域9d，形成多數個具有網眼之網孔。亦即， 網狀套9係區段型。對應於此，旋轉滾筒3之底部開口七也 形成為對應於區段領域9d之位置及形狀。如第2B圖所示， 底部開口 3a與區段領域9d嵌合，並且在旋轉滾筒3底部之正 面側，區段領域9d與旋轉滾筒3底部之正面係在同一面。藉 此，合成樹脂製之網狀套9係只有成為通風區域之區段領域 9d在不鏽鋼等金屬製之第7A圖、第7B圖之底部開口 3a與金 屬底部為同一面。如第2B圖、第7A圖所示，可得到一配置 在網狀套9之旋轉滾筒3之周方向上之複數、具體而言為6個 區段領域9d之周圍連續而成之金屬面所裝飾且具有高級感 的外觀。 21 立又，如第2A圖、第2B圖所示，設置於網狀套9之周邊 部9b之背面側之凹陷環狀凹部％之底部、與設置於轴連結 支持構件8之環狀密㈣8e之正面側之凸部環狀凸條崎 接，形成外周部環狀密封區域41。而且，外周部環狀密封 區域41、旋轉滾筒3底部、旋轉軸2之凸緣2a挾著軸連結支 持構立件8之轴連結部8a且藉由螺栓15螺固。藉此，旋轉滚筒 3底部之中央開口 3C周圍壓接於設置在網狀套9之周邊料 ^正面側之凸部環狀&贿，並設有内周部環狀密封區域 不係在網狀套9之挾持構造中必要之内外周的密封可 不使用特別的密封構件即可完成。又， =:=環_與比她之背二= 制由旋轉穿^P#由曲_隙4 5而限 轉袞商3之傻方向内 _環狀凹凸面相㈣^通風在此，曲住間 第8圖係於本發明夕盘 :部正，正，安：二: :又置 之半部之立體圖。第看該滾筒式洗衣乾燥機之網狀套 機之網狀套之半^ ㈣面側細㈣式洗衣乾燥 卞〇丨 體圖。 進而，如第10圖所 邊部外、補強區域以輪概套9於中央部之内周9A、周 補強肋部％。再者1㈣及非料部之背面，形成有 強域9c之輪廓部或非輪心*域9。之補強肋部9h亦可僅在補 邪部之任一者。網狀套9係在露出於 22 旋轉滾筒3内之通風區域中， 轉滾筒3 ’與以保護，並且銲 區域，面剛性高。 承受洗濯物之負荷，覆蓋於旋 由補強肋部9h由周圍支持通風 刘乐固所示 係朝網狀套9側折曲，J袞筒3底部之區段型之底部開口 而且折曲壁如嵌合於網^朝背面側之環狀折曲壁如。 Q , 畎套9之區段領域9d之周圍的凹部 轉滚筒3底部藉由折曲壁如而提高歪曲剛性， 狀套9之保護性能。又，藉由折曲壁3al嵌合 於凹部9g内而不露出， 也不會使洗濯物損傷。又^^之切斷緣不超出外部， 態之外觀佳的賴。 此之構造形料具有邊緣形 如第2Α圖所示’旋轉滾筒3底部中央之軸連結支持 8與旋轉軸3之螺栓固定部係利用多數大的螺栓15以達到堅 強的固結，但是利用螺絲44由正面側將緊靠之金屬蓋 固於軸連結部8a’且覆蓋隱藏多數之螺栓15。再者，軸連 結f持構件8係將設置於放射狀祕之突起8g嵌合於_ 滾筒3底部之擋止孔3d而擋止。又，網狀套9係藉由網狀套9 與輛連結支持構件8之軸連結部仏之間的凹凸形狀 卡合部51而擋止。 备 第11圖係由正面側看本發明之實施型態之滾筒式先矿 乾燥機之軸連結支持構件之半部之立體圖，第12圖^由$ 面側看該滾筒式洗衣乾燥機之轴連結支持構件之半部之立 體圖。 本發明之實施形態中，如第11圖所示，軸連結支持構 23 1373541 件8係在放射狀腕8b基部間’有一體成形並用以增強之立體 增強架橋8e ’該立體增強架橋仏由轴連結部如之側周面前 端呈傘狀擴展延伸到水槽1側之開放端緣，並且呈蹼狀銜接 隣接之放射狀腕8b之基部間。因此，旋轉轴2之傾斜變形時 之高負荷在旋轉軸2之連結部周圍可平均的分散、吸收。而 且集中於旋轉轴2之最大應力大多數會減少，僅於轴連結支 持構件8產生小應力。 具體而言’軸連結支持構件8之軸連結部8a成為承受旋 轉滾筒3晃動時產生之旋轉軸2之傾斜負荷的中心部。而 且，旋轉轴2之傾斜負荷係由放射狀腕8b之基部經由環狀密 封壁8c之連結部而傳達到旋轉滾筒3之安裝部。立體增強架 橋8e不會特別增加軸連結支持構件8的重量，且為在與軸連 結部8a之側周面之間朝水槽1側開放之箱型。而且，軸連結 支持構件8係提高歪曲強度、及對於旋轉軸2之傾斜方向朝 周方向移動所造成之扭曲的強度。又，轴連結支持構件8係 在放射狀腕8b之基部減旋轉轴2之傾斜，而可不產生大應 力到旋轉滾筒3之女裝部。其結果，可降低旋轉滾筒3之晃 動、振動、噪音，提高軸連結支持構件8之耐久性。 又，放射狀腕8b係作成朝背面側開放之截面u字狀。立 體增強架橋8e係在轴連結部8a及放射狀腕8b間，以放射狀 腕8b之對向面為侧邊，以連接側邊之開放端緣為底邊之形 狀。立體增強架橋8e係形成以軸連結部8&之側周部之正面 側為頂點之大略三角錐形之箱型凹部，藉此歪曲、扭曲強 度之増大與彈性變形特性之平衡適當。 24 又，第2B圖所示，立體增強架橋8e係沿著旋轉滾筒3 之中心侧流動之彎曲或屈曲、傾斜之形狀，可使箭頭所示 之來自水槽1之送風口 7之送風遇到網狀套9之區段領域如 後擴散，並且分散透過。亦即，往立體增強架橋8e之開放 端緣之擴展形狀係彎曲形狀、屈曲形狀、傾斜形狀之任一 者皆可。 藉此，送風容易往旋轉滾筒3之中心側。因此相較於如 驾知叙夕半送風到旋轉滚筒3之周邊區域而中央部不足的 凊況’可提高乾燥效率。對此，立體增強架橋&往水槽^則 開放之端緣形狀宜對應於送風口 7之旋轉中心側之口緣形 狀。如第5圖、第6圖所示，立體增強架橋以為大略對應於 切除部6c之架橋增強部25之屈曲形狀且往旋轉中心側擴張 之形狀。亦即，立體增強架橋8e之開放端緣、及送風口 7之 旋轉軸2侧之内周緣可朝旋轉轴2側凸出彎曲。 進而，立體增強架橋仏之彎曲或屈曲、傾斜方向宜大 略對應於送風口 7之旋轉中心側之口緣位置。因此，立體掸 強架橋8e之傾斜角對應於旋轉軸2之軸線大約宜為45。左 右。可是，並不限於該傾斜角，通過送風口 7之吹入方向' 送風口 7之導風方向、來自與其連接之循環送風路徑的送風 路徑方向也包含在内，只要適當決定旋轉滾筒3内之導風方 向即可。任一者皆宜為環狀密封壁8c之内周與送風口7之軸 連結部8a之相反側之内周的形狀在旋轉軸2之方向上大略 一致，且送風口 7之旋轉軸3側之内周緣與立體增強架橋心 之開放端緣在旋轉軸2之方向一致。藉此，放射狀腕扑晝分 25 輪連結部8a與環狀密封壁8(；之間而形成之區段型通風領域 句態及大小可對應於送風σ7之通風領域，具有不損及由 送風口 7往水槽1内之送風的優點。 立進而，如第12圖所示，立體增強架橋8e在其與軸連結 —P8a之外面之間係呈朝背面側開放之立體形狀。如第7圖所 八銜接於立體增強架橋8e之各放射狀腕8b為截面u字型之 形狀，且與網狀套9之放射狀補強_之背面相對向而可支 持。又，如第2圖所示，在放射狀腕处之長度方向之途中， 形成由u字型底部立起且銜接兩側壁間之架橋壁放射狀 腕朴被賦予往其長財向2端連接之㈣構造，提高扭曲強 度、歪曲強度。 其次’就與以馳刪聊時之高負荷條 =之實施《之軸承支持構件6、_結支持構件8之= ^中所說明之方法相同之方法進行之第卜第2檢定^ 機之L Λ 施型態之㈣式洗衣乾释 機之軸承支持構件在1600rpm之高逮旋轉條 無 布圖，第圖係顯示同滾筒式洗衣乾燥機 應力分 件在160Grpm之高速旋轉條件下之變形量 結支持構 又，第MA圖係本發明之實施型態之 應力者， 連結支持構件在_卿之高速旋轉條4燥機之轴 力分布圖，第14Β圖係同滾筒式洗衣 ：正面側之應 件在_啊之高速旋轉條件下之背面側之連結支持構 14C圖係顯示同滾筒式洗衣乾燥機之轴連:二布圖，第 寻構件在 26 1373541 1600rpm之高速旋轉條件下之變形量、最大應力者。 第1檢定係使用與背景技術相同之解析模型。亦即，軸 承支持構件6使用第19B圖所示之解析模型’轴連結支持構 件8使用第20C圖所示之解析模型。又，第2檢定係勘測第j 檢定時之轴承支持構件6、轴連結支持構件8之應力分布。 軸承支持構件6之第1、第2檢定結果如第13B圖所示， 相對於習知之變形量〇 24。、最大應力6lMPa(重量3.6kg)， 變形量為0.09。、最大應力為33MPa(重量4.4kg)。第13A圖係 顯示變形量為〇.〇9。、最大應力33MPa時之應力分布部。最 大應力部係分散且集中於由放射狀增強部21之軸套部6&沿 著切除部6c之轴套部6a側之架橋增強部25、在切除部&之 相反側隣接於放射狀增強部21之放射狀補強肋部22之基部 側、鄰接於切除部6c之相反側之放射狀補強肋部22之基部 側一部份、挾著軸套部6 a而對軸承支持構件6之中心點呈點 對稱之放射狀補強肋部22、放射狀均衡增強部27之基部側 或靠近基部之根部《其他領域被認為在部分之應力降低極 多。又’本發明之實施形態之轴承支持構件6的重量相對於 習知之重量3.6乂§為4_41<^，大約增加不到14°/。之重量。可 是，以最大應力來看，本發明之實施形態之軸承支持構件6 相較於習知之6lMPa，大約減半為33MPa，可以了解到可不 增加相當多的重量來對應。 軸連結支持構件8之第1、第2檢定結果係如第14C圖所示， 相對於習知之變形量為0.15。、最大應力為5〇MPa(重量 3.5kg) ’變形量為〇 〇9。、最大應力為25MPa(重量3 9kg)。第 27 1373541 14A圖、第14B圖係個別顯示變形量為〇.〇9°、最大應力為 25MPa時在正背面之應力分布部。其結果認為最大應力集 中於旋轉轴2，除此之外之部分的應力係輕微的。本發明之 實施形態之軸連結支持構件8相對於習知之重量3.5kg，為 3.9kg ’增加約超過10%之重量。又，如第14C圖所示，在本 發明之實施形態中，相對於習知之5〇MPa，最大應力減半 為25MPa。此種情況下也可不增加大的重量而對應。 C囷式簡單說明3 第1圖係顯示本發明之實施形態中，由軸連結支持構件 連結於本發明之實施形態之旋轉滾筒之旋轉軸由軸承支持 構件支持之構造部的截面圖。 第2A圖係顯示同滾筒式洗衣乾燥機之旋轉滾筒與旋轉 轴之軸連結支持構件所構成之連結構造部之截面圖。' 第2B圖係連結第2A圖之下方之圖。 部BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a drum type laundry dryer. [Prior Art: J BACKGROUND OF THE INVENTION A conventional drum type laundry dryer is disclosed in Japanese Patent No. 4044602. Fig. 15 is a schematic view showing the entire structure of a conventional drum type washing and drying machine, and Fig. 16 is a view showing a rotary shaft coupled to a rotary drum of the drum type washing and drying machine by a shaft coupling support member, supported by a bearing support member. A partial cross-sectional view of the structure of the motor connected to the water tank. The Rolling-type laundry dryer has a water tank 1〇2, a rotary drum 1〇3, a motor 104, a bearing support member 1U, and a circulating air supply path 1〇9. The water tank 102 is elastically supported in the washing machine body 1〇1 by a suspension device (not shown). The rotary drum 103 has a bottomed cylindrical shape, and is disposed in the water tank 1〇2 from the front side of the opening toward the back side of the bottom, and the direction of the rotating shaft 1〇5 is horizontal or inclined downward from the horizontal direction. The motor 1〇4 is used to drive the rotary drum 103. The bearing support member hi is a bearing 106 that supports the rotary shaft 105 and the motor 1〇4 on the back surface of the water tank 1〇2. Further, the bearing support member ιη is made of metal, specifically, made of aluminum. The circulating air supply path 109 is a path in which the blower fan 107 is coupled to the rotary drum 103. Further, the air in the water tank 1〇2 is discharged by the delivery fan 107 through the circulating air supply path 1〇9, and then dehumidified and heated, and air is blown into the water tank 2 by the air supply port 1〇8. Thus, the clothes and the like in the rotary drum 103 can be dried. 3 If the first support structure has a sleeve portion 111a and a seat 111b. The sleeve portion 111a supports the bearing inspection plate so as to extend around the base portion to the peripheral portion of the open D portion containing the air blowing kiss. Further, the seat 11 lb is connected to the back opening of the water tank 1〇2 by the back side. 1〇2a is inserted into the seat 111b to fix the stator 104a of the motor 104 to the back. The portion of the seat disk 111b in the circumferential direction has a wind blow and is exposed on the back. (10) The 1Ue system is configured to be connected to the back side of the air supply side 1〇9 of the circulating air supply path 109. * The first display is installed on the bottom of the rotating drum of the drum dryer. A half cross-sectional view of the mounting state of the mesh sleeve and the shaft coupling support member. Figure 18A is a cross-sectional view of the bearing support member of the retort-type drum dryer. 帛18B® shows the front view of the bearing support member of the drum-type washer dryer. Figure 18C shows the bearing of the drum-type washer dryer. Support the back view of the component. The cut-out portion 111c is a substantially rectangular through hole that is curved in the circumferential direction as shown in Figs. 18B and 18C. The entire circumference of the seat disk 111b surrounding the cutout portion has a mounting hole md and is attached to the back portion of the water tank 1〇2. The seat disk 111b, the back opening 1〇2a of the water tank 1〇2, and the periphery of the base of the rotating shaft 1〇5 are sealed by the sealing member 115. The shaft coupling support member 112 abuts against the bottom opening 103a of the rotary drum 103 from the back side. The 'shaft coupling support member 112 is coupled to one end of the rotating shaft 105 supported by the bearing 1〇6. Further, the rotary drum 103 and the shaft coupling support member 112 are screwed to the outer peripheral portion of the rotary drum 1〇3 and the peripheral portion of the bottom fitting tubular wall 10b3 by the outer peripheral surface side, and are integrated. Here, the rotary shaft 1373541 is formed of a shaft connecting portion 112a which is provided with a flange portion 1〇5a or the like at one end thereof and which is screwed to the center of the shaft coupling support member 112. Further, the 'shaft coupling support member 112 has a radial wrist 1121) and the annular seal wall 112 (the radial wrist 1121) extends radially from the shaft coupling portion. The annular seal wall 112c is in the middle of connecting the radial wrists 1121), and is coupled to the bottom opening 1〇3a of the rotary drum 103. Each end portion of the radial wrist 112b is screwed to the body portion of the rotary drum 1〇3 and the bottom fitting cylinder wall 103b. The annular seal wall 112c and the bottom opening 103a of the rotary drum 103 are sealed via a sealing member 13 to be sealed. The annular seal wall 112c and the annular portion of the portion closer to the outer peripheral side region than the air supply port 1〇8 of the back wall of the water tank 102 restrict ventilation from the radially inner side to the outer side via the mechanical shaft seal 14. The mechanical shaft seal 114 is a shaft that supports the support member ι 2 and water. The annular concave-convex surface of the groove 1〇2 is embedded to form a labyrinth gap in the radial direction. - As shown in Figs. 16 and 17, the resin-made mesh ferrule 6 covering the bottom opening from the inside is abutted and fixed in the bottom of the rotary drum 1〇3. The net cover m is rotated together with the rotary drum ι〇3, and the air supply from the air supply port is dispersed. As a result, the air can be uniformly supplied to the wide area of the rotating drum ι 3 θ, and the drying efficiency can be improved without uneven drying. Mesh sleeve 116 is a round dragon. The cover 116 is a slit portion of the cut towel, and a radial reinforcing region connecting the center portion and the peripheral portion, and a plurality of meshes 116b are formed in each of the segment regions U6a arranged in the circumferential direction. The bottom opening l〇3a of the rotary drum 1〇3 is also formed to correspond to the position and shape of the segment area 116a. Further, the bottom opening 103a is connected to a contour portion having a shape corresponding to the opening of the shaft coupling support member 112. 5 1373541 However, the rotary drum 103 of the above-described drum type laundry mechanism is disposed laterally or horizontally. Therefore, when the rotary drum 1〇3 is disposed laterally, the laundry is retained in the lowermost portion of the circumferential direction of the rotary drum 103. Further, when the rotary drum 103 is disposed to be horizontally inclined, the laundry is retained in the lowermost portion of the rotary drum 103 in the axial direction. Further, the laundry is also placed in the axial direction of the rotating shaft 105 by the user. Therefore, the rotational load of the rotary drum 丨〇3 is likely to vary, which causes sway. Here, the rotation support of the rotary drum 1〇3 is supported by the cantilever of the rotary shaft 1〇5 which is coupled to the bottom of the rotary drum 103 by the shaft in the back surface of the water tank 102. Therefore, the sway of the rotating drum 1〇3 produces a so-called precessional motion centered on the bearing. The precessional movement of the rotary drum 103 is transmitted to the rotary shaft 1〇5, and the bearing support member Ui located on the back surface of the water tank 102 is received via the bearing 1〇6. At this time, the load is applied to the side of the rotating shaft 1〇5 of the seat plate 1111 by the deflection of the rotating shaft 103 with the rotation of the rotating shaft 丨〇5. The force on the back. Then, the force is repeated over the entire circumference of the seat pan 111b by the rotation of the deflection. The load is considered to be substantially the same in the shaft coupling support member 112 that is connected to the end portion of the rotary drum 103 in the circumferential direction. In this regard, the support structure of the conventional rotary drum 1〇3 disclosed in Japanese Patent No. 4,046,602 can withstand the load at the time of such swaying and can be suppressed from obstructing the practical sway range, vibration range, and noise range. In recent years, it has been more demanding to improve the processing capacity of laundry drying. In the dehydration step, the number of rotations of about 1200 rPm is expected to increase by about 3 to about 16 rpm. In order to cope with such a high-speed development of 6 1373541, the present inventors have learned from the current drum type washing and drying machine that the current rotating drum H) 3 is supported in the support structure for suppressing the rotating drum ι〇3 The support strength required for the shaking of the operation is insufficient. Moreover, the sway, vibration, and noise far exceed the allowable range, and the life is lowered early. Further, the inventors of the present invention have focused on the relationship between the shape of the bearing support member 1U and the shaft coupling support member 112 in the conventional support structure described above and the load operation. (4) When the drum 1G3 is swaying, the (four) five pairs of bearing branches, the member 111 The most A tilt angle of the shaft coupling support member 112 is determined as the maximum amount of deformation (first test). Further, the distribution of the stress 値 of the fine support member 111 and the shaft coupling support member 112 at the time of the maximum deformation amount was examined (second test). Fig. 19A is a diagram of a stress distribution diagram of a conventional roller-type washer-dryer bearing support member at a high speed rotation of 160 rpm. The second GA diagram is a stress distribution diagram of the front side of the shaft joint support member of the conventional drum type laundry dryer under the high-speed rotation condition of l_rpm, the second GB diagram, the shaft connection support member of the drum type laundry dryer is at 1600 rpm. The stress distribution diagram on the back side under high-speed rotation conditions. FIG. 20C is a view showing the measurement result of the deformation amount and the inclination angle of the rotating shaft with respect to the shaft connecting support member under the condition of two-speed rotation of the drum type laundry dryer under the condition of two-speed rotation at 1600 rpm, and the second GD image analysis Model diagram. The first verification bearing support member 111 uses an analytical model as shown in Fig. 19B, and the shaft coupling support member Π 2 performs the numerical calculation using an analytical model as shown in Fig. 20D. Further, the second test is to survey the stress distribution of the bearing support member 1U and the shaft connection support member 112 at the first inspection timing. Fig. 19A shows the stress distribution of the bearing support member 111, and it is considered that the maximum stress portion is a large portion on both sides in the circumferential direction of the seat disk 111b of the cut portion 7 1373541 lllc and a portion which is point-symmetrically extended to the center point of the bearing support member 111 . Fig. 20a and Fig. 20B are diagrams showing the stress distribution on the front and back sides of the shaft coupling support member 112. The maximum stress is concentrated on the back side of the end portion of each of the radial arms 112b. The front side is concentrated on the annular sealing wall 112. The three-diameter rib 112e of the portion corresponds to the two sides of the cut-away portion 111c. The position and the position of the center point of the bearing support member 111 are point-symmetric. The high stress which is slightly lower than the maximum stress is considered to be concentrated on the front side of the peripheral rib 112f of the shaft coupling portion 112a and the central longitudinal rib 112d of the radial wrist 112b. Fig. 20C shows the results of measurement of the amount of deformation and the inclination angle of the shaft connecting support member 112 by the rotating shaft 105. As can be seen from the above verification results, whether the radial or annular reinforcing ribs are provided, the box-shaped reinforcing ribs along the contour or not along the contour, the rotating shaft 105, the bearing support member 111, and the shaft coupling support member 112 are known. A problem that brings some of the maximum stress beyond the strength. C Summary of the Invention Summary of the Invention The laundry dryer of the present invention comprises: a water tank which is elastically supported by the washing machine body; a rotating drum having a bottom cylindrical shape and being disposed from the front side of the opening toward the back side of the bottom In the water tank, the direction of the rotating shaft is horizontal or inclined downward from the horizontal direction; the shaft connecting support member ' connects the rotating shaft to the bottom of the rotating drum; the bearing supporting member is attached to the back of the sink And supporting the rotating shaft via a bearing; the motor is coupled to the rotating shaft 8 by the bearing supporting member to drive the rotating drum, and the circulating air blowing path is configured to discharge the air in the water tank by a blower fan And removing the air, heating, and blowing the air to the water tank through the air blowing port, wherein the drum type laundry dryer is characterized in that the shaft coupling support member has a shaft coupling portion, a center portion and The rotating shaft connector; the plurality of radial wrists extending radially from the shaft coupling portion And the annular sealing wall is connected to a plurality of the radial arms, and is connected to the bottom opening of the rotating drum, and the shaft coupling supporting member is in the radiation a three-dimensionally-reinforced bridge formed by a body-shaped body between the bases of the wrists, wherein the front end of the lake surface of the shaft joint portion extends in an umbrella shape to the open end edge of the water tank side, and is connected to the radial wrist in a braid shape Between the bases. The pumping connection supporting member of the drum-type washer-dryer thus constructed is such that the t-joining portion is subjected to the tilting load of the rotating shaft generated when the rotating drum is shaken, and the tilting load is passed through the ring of the base of the radial wrist. The joint portion formed by the seal is arranged to be connected to the base of each of the radial arms to which the load is applied to the rotating drum, and the front end side of the side peripheral surface of the shaft joint portion is connected to the sink through the three-dimensional reinforcing bridge彳 放 放 ' does not need to add special weight. Further, between the side peripheral surfaces of the shaft coupling portion, a box-shaped reinforced form that is open toward the water tank side is formed, and the bending strength and the inclination direction of the twisting _ the direction of the machine are further improved, and the box type is enhanced. In order to open toward the sink side, the elastic deformation property can also be exerted, so that the rotation axis is inclined on a radial basis. The ρ is reduced and the large stress does not occur in the mounting portion of the rotating drum. The first embodiment shows the embodiment of the present invention. The financial sleeve connecting support member is coupled to the rotating member of the rotating drum according to the embodiment of the present invention. Supported construction department shouting the map. The transfer material is supported by the suction support. The second drawing shows the connection structure of the drum type laundry drying 棬 k ± the yoke rotating drum and the shaft connecting support member of the rotating shaft D| <哉面图. Figure 2B is a diagram below the diagram of Figure 2A. Fig. 3 is a rear view showing the main portion of the drum-type washer-dryer according to the embodiment of the present invention in which the rotary drum is supported in the water tank and the stirrup is attached to the back of the water tank and coupled to the rotating shaft. ^The front side of the sink of the main part of the tilting drum type laundry dryer is an exploded perspective view seen after the side half is removed. ^图—Look at the side of the tank of the drum-type washer dryer, and support the material of the __, and the perspective view of the bearing support member of the stator. Figure 6 shows the back view from the back side. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 7B is a cross-sectional view of the rotary drum of the drum type laundry dryer of the embodiment of the present invention. Fig. 7B is a cross-sectional view taken along line B_B of Fig. 7A. The side of the material-type washing and drying machine of the solid state (fourth) state is a perspective view of the material connecting support member attached to the rotating drum and the almost half of the back side half of the water tank in which the mesh sleeve is disposed, as seen from the front side. 10 1373541 The ninth diagram of the mesh sleeve of the drum type laundry dryer is a perspective view of the positive half. The half of the mesh sleeve is viewed from the back side, and the eleventh figure of the drum type laundry dryer is composed of the positive & The half of the three-dimensional ^ look at the drum-type laundry dryer shaft connection branch Figure 12 is the back; y holding the half of the member of the "rolling laundry (four) machine shaft connection branch body diagram. The 13th A-picture shows the deformation and maximum stress of the supporting member in the (4) Qianyi (4) machine. The stress distribution diagram of the front side of the shaft connecting support member of the side drum type laundry dryer under the high cost of 1600 rPm. Fig. 14 is a graph showing the stress distribution on the back side of the pumping-type supporting member of the drum type laundry dryer at a high speed of 160 rpm. Fig. 14C is a graph showing the amount of deformation and the maximum stress of the sleeve connecting support member of the drum type laundry dryer at a high speed rotation of 1600 rpm. Fig. 15 is a schematic view showing the entire configuration of a conventional drum type laundry dryer. Fig. 16 is a partial cross-sectional view showing a rotating shaft of a rotary drum to which the shaft coupling support member is coupled to the drum type laundry dryer, supported by a bearing support member in the water tank, and coupled to the motor. Figure 17 shows the half-section of the installation of the mesh sleeve and the _junction support member installed in the bottom of the barrel of the rotating roller 11 1373541 in the 5 Hai drum type laundry dryer. The intestine diagram shows the drum type laundry drying. A cross-sectional view of the bearing support member of the machine. Figure 18B is a front elevational view showing the bearing support member of the drum type laundry dryer. Figure 18C is a rear view showing the bearing support of the drum type laundry dryer. Fig. 19A is a graph showing the stress distribution of the bearing supporting member of the drum type laundry dryer under high-speed rotation conditions of 160 rpm. Figure 19B is an analytical model diagram. Fig. 20A is a diagram showing the stress distribution on the front side of the lion's high-speed rotation condition of the shaft-type support member of the conventional drum type laundry dryer. Fig. 1 is a stress distribution diagram of the back side of the shaft-type connecting support member of the drum type laundry dryer under high-speed rotation conditions of 16 rpm. The first drawing is a graph showing the measurement results of the amount of deformation and the inclination angle of the rotating shaft of the shaft coupling supporting member under the high-speed rotation condition of the drum type washing and drying machine. The 20th figure is an analytical model diagram. (Third Embodiment) DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a drum type washing and drying machine according to an embodiment of the present invention will be described with reference to the drawings. In the drum-type washer-dryer 12 according to the embodiment of the present invention, the structure in which the rotation-supporting shaft connected to the rotary drum is supported by the bearing support member by the shaft coupling support member is shown in the second figure. A cross-sectional view of a connection structure portion formed by a support roller of a rotating drum of a drum type washing and drying machine and a shaft of a rotating shaft. The second diagram is a diagram below the second diagram. X Fig. 3 is a rear view showing a main portion of the drum type washing and drying machine according to the embodiment of the present invention in which the rotation m is held in the water tank and the motor is attached to the back of the water tank and connected to the rotating shaft. Fig. 4 is a perspective view of the front side of the water tank of the main part of the dryer, which is seen after being removed. The drum type laundry dryer (10) according to the embodiment of the present invention includes a water tank i, a rotary drum 3, a motor 4, a bearing support member 6, a circulating air supply path, and a shaft coupling support member 8, as in the first to fourth figures. And mesh sleeve 9. / The middle sink 1 is elastically supported in the washing machine body by a suspension mechanism (not shown). The rotary drum 3 has a bottomed cylindrical shape, and the rear side of the opening facing the bottom is placed in the aforementioned water tank, and the direction of the rotating shaft is horizontally or inclined downward from the horizontal direction. That is, in the embodiment of the present invention, the front side is the side of the opening of the rotary drum 3, and the back side is the side opposite to the front side. The motor 4 is used to drive the rotary drum 3. The bearing support member is disposed on the back of the water tank 1, and the bearing 5 of the rotating shaft 2 and the motor 4 are supported on the back surface of the water tank 1 and the motor 4 is coupled to the rotating shaft on the bearing support member 6 by the % air supply path. The air in the water tank is discharged by a fan (not shown) and dehumidified, and then heated, and the air is blown through the air blowing port 7 to the path in the under-groove 1. The laundry in the rotary drum 3 is filled with (4) the air supply path 13 1373541 The air in the water discharge tank 1 is discharged to the air and dried. The metal shaft coupling support member 8 connects and supports the rotary shaft 2 to the bottom of the rotary drum 3. The mesh sleeve 9 of the tree is covered by the bottom opening 3a of the rotary drum 3. As shown in FIGS. 1 and 4, the bearing support member 6 has a boss portion to engage with the seat plate 6b and supports the rotary shaft 2 via the bearing 5. The bushing portion 6a supports the bearing 5 » the seat plate 6b is attached to The periphery of the base portion of the boss portion 6a extends to the peripheral portion of the opening portion of the air supply port 7, and is fixed to the back opening 1a of the water tank 1 by the bolt U connected from the back side. Further, the seat pan 6b is fixed to the dice 4a of the motor 4 by the bolt 丨2. The seat pan 6b is in the circumferential direction - a portion having a cutout portion 6c that is exposed to the air outlet 7 and exposed to the back. This is because the cut-out portion 6 is formed so as not to hinder the air-sending side of the circulating air-sending path from being connected to the back. Further, the seat pan 6b is attached to the back of the water tank 1 by bolts in the entire outer peripheral region. The disk 6b, the back opening la of the water tank 1, and the periphery of the base portion of the rotating shaft 2 are sealed by the sealing member 13. The rotor 4b of the boss portion 63 is formed integrally with the inner circumferential side rotor 4b1 and the outer circumferential side rotor 4b2. And the rotor 4b is screwed to the outer end 2b of the rotating shaft 2 by the bolt 20. Thus, the rotor 4b is electromagnetically coupled to the stator 4a by the two rotors 4b1 and 4b2, the volume is not excessively large and the rotating drum 3 can be high. Torque rotation drive β Here, the inner circumference side rotor 4M is disposed on the inner circumference of the stator 4a, and the outer circumference side rotor 4b2 is disposed on the outer circumference of the stator 4a. The shaft connection support member 8 abuts against the rotary drum 3 from the outer side. a bottom opening 3a. Here, the shaft coupling support member 8 is coupled to one end of the rotating shaft 2 supported by the bearing 5. Further, the body is screwed to the body of the rotating drum 3 by bolts on the outer side at a plurality of portions in the circumferential direction. Department, bottom fitting tube wall sun, The bottom portion 14 opening 3a and the thin joint support portion are provided with the flange portion 2a, and the body is turned into a - end screwing and shaft coupling support member 8:: the shaft connection coffee 1 is: Qian Qingtao ==_Open two =::: The shot is strong 2. The radial direction of the radial direction of both sides of the 卩& is increased by ± °R1. 妓 The countermeasure against the widest area where the highest maximum stress is concentrated on both sides of the gift part & The front view of the bearing support member of the stator of the drum type, the clothes dryer of the embodiment of the present invention, and the bearing supporting member of the bearing mounting motor supporting the rotating shaft is not shown on the front side. Looking at the back side, a perspective view of the bearing support member of Fig. 5. The drum type laundry dryer 100 is as described above, and the rotary drum 3 is basically supported by the elastic support sink in the current support structure and is supported by the current drive structure. The bearing support member 6 has a sleeve portion 6a for supporting the bearing 5 and a seat plate 6b. The seat plate 6b has a cutout portion 6c and inherits the current basic form, and does not hinder the passage and the air supply path; Connection. But in the direction of the cutting section & Radial reinforcement portions 2 are provided on both sides, and the radial reinforcement portions 21 are substantially slanted in the radial direction as shown in Figs. 3 to 6 so that the rotary drum 3 is swayable. In the circumferential direction, it is subjected to a high bending load in the radial direction of the circumferential direction of the seat disk 6b of the cutting portion 6c, and can disperse and reduce the maximum force which occurs in a large area of the cutting portion & It is possible to suppress the inclination of the rotating shaft 2 or the deformation of the seat plate 6b. This means that the increase in the volume required to provide the radial reinforcing portion 21 for reinforcement can be offset by the partial volume reduction in the portion where only small stress is actuated. It is an enhancement method of the bearing support member 6 that utilizes a different volumetric movement of the stress distribution. Here, the case where the radial reinforcing portion 21' overlaps with the general radial reinforcing rib 22 or the like means at least one type of reinforcing structure such as elongation, thickening, and height increase, and the like. complex. In Figs. 5 and 6, the general radial reinforcing rib 22, the annular reinforcing rib 23, the reinforcing rib 24 along the contour portion of the contour, and the mounting holes 30, 31 surrounding the outer periphery of the seat 6b are provided. The box-shaped reinforcing ribs 28 and the like are combined and designed to have a thickness thicker than the members to form the radial reinforcing portion 21. According to such a modified 'bearing support member 6, the radial reinforcing portion 21 is provided at a position where the load on the rotating drum 3 is shaken to cause excessive maximum stress on both sides of the cut portion 6c. The radial reinforcing portion 21 can be subjected to a high load in the circumferential direction portion by the high bending strength. Therefore, when the rotary drum 3 is shaken, the maximum stress generated in a wide area on both sides of the cut-away portion 6c can be dispersed and reduced, and the inclination of the rotary shaft 2 or the deformation of the seat cymbal can be suppressed. Since the sloshing degree, vibration, and noise of the rotary drum 3 are improved, it is possible to further support a high-speed rotation and a high-load operation, and a sufficient life can be obtained. The increase in the volume of the reinforcement portion can be offset from the partial volume reduction in the portion where only the stress is actuated, thereby preventing the weight of the support material of the crane material from being enhanced and weighted, and suppressing the needle compared to the conventional design. The rate of materialization: the volume increases. Further, 16 1373541 and the 'radial sturdy portion 21 are provided so as to extend from the boss portion 6a to the outer periphery of the seat pan 6b. Thereby, the radial reinforcing portion 21 extends from the boss portion 6a to the outer peripheral side, and the deformed base portion is reinforced to the deformation end in the radial direction in which the direction in which the seat disk 6b is deformed by the rocking of the rotating shaft 2 is deformed. Therefore, it is possible to share in the circumferential direction and to withstand the inclination of the rotating shaft 2 toward the cut-away portion 6c side and the inclination of the rotating shaft 2 to cause the skewing load of the seat pan 6b in the radial direction. Further, the dispersion and lowering of the large stress from the boss portion 6a to the outer peripheral seat disk 6b can be applied to the outer peripheral portion of the seat pan. As a result, it is possible to more reliably suppress the inclination of the rotary shaft 2 toward the cut-away portion 6c side and the inclination of the rotary shaft 2 to cause deformation of the seat pan 6b. Further, the seat pan 6b also has a bridge reinforcing portion 25 that extends between the radial reinforcing portions 21. The bridge reinforcing portion 25 is formed in a slightly circular arc shape convex toward the boss portion 6a, and is connected between the radially reinforcing portions 21 of the V-shaped rib portion so as to have a substantially A-shaped rib portion. Further, the bridge reinforcing portion 25 constitutes a triangular box-shaped reinforcing portion 26 from the boss portion 6a side of the cut portion 6c to the boss portion 6a. Also, as the box structure is enhanced, the strength of the area is also increased. Further, the bridge bridging portion 25 can increase the strength of the bending of the seat disk 6b in the radial direction caused by the inclination of the rotating shaft 2 toward the cutting portion 6c side and the inclination of the rotating shaft 2, and is dispersed to the A-shaped rib portion and the surrounding portions. Stress in a non-ribbed planar area. As a result, the maximum stress 更为 can be further reduced, and the inclination of the rotary shaft 2 toward the cut portion 6c and the deformation of the seat cymbal can be further suppressed. The bridge reinforcing portion 25 further forms a bent shape that protrudes toward the boss portion 6a side along the boss portion of the cut portion 6c such as the side profile. Therefore, by the profile of the side of the sleeve portion 6a of the cutting portion & and the curved shape of the sleeve portion of the bridge reinforcing portion 25 as shown in the side, the cut-out area of the cut-away portion 6c is enlarged, and the opening of the air supply port 7 is added 17 Big part. As a result, the amount of supply air can be increased without increasing the air supply load and increasing the drying speed. Further, since the three-dimensional shape in the radial direction is obtained, the flexural rigidity in the radial direction between the radial reinforcing portions 21 around the cut portion 6c on the boss portion 6a side of the seat pan 6b can be improved. As shown in Fig. 4, the radial reinforcing portions 21 on both sides of the cut-away portion 6c are capable of pressing the seat plate 6b to the radial direction of the back surface of the water tank 1 when the rotating shaft 2 is obliquely deformed toward the cut-away portion 6c side. The load is distorted to prevent deformation of the seat pan 6b. When the rotating shaft 2 is obliquely deformed on the opposite side opposite to the cutting portion 6c, the radially reinforcing portion 21 on both sides of the cutting portion acts as a fulcrum with the outer peripheral portion of the seat plate 6b as a fulcrum, thereby generating a pressing force toward the back of the water tank 1. . The pressing force causes the inclination of the rotating shaft 2 toward the cut-away portion 6c side and the distortion load of the radial direction of the seat plate 6b by the high-bending strength of the radial equalizing reinforcing portion 27 as shown in Fig. 5, and locally in the circumferential direction. Share and bear. Therefore, even on the opposite side to the cut-away portion 6, the maximum stress which is the same as the side of the cut-away portion 6c can be dispersed and reduced. Here, the radial balance-enhancing portion 27 is formed on both sides of the cut-away portion 6c. The radial reinforcing portion 21 and the symmetrical ribs and the substantially inverted v-shaped ribs are formed around the axis of the rotating shaft 2. Further, the radial equalizing reinforcing portion 27 and the radial reinforcing portion are formed with the axis of the rotating shaft 2 as The central portion has a substantially X-shaped rib. As a result, the reinforcement of the seat disk ridge of the radial reinforcing portion 21 on both sides of the cut-away portion 6c brings a high load at the position of the point-symmetric seat disk 6b, but is enhanced by the radial balance. The portion 27 is carried in the circumferential direction portion. Therefore, the dispersion and the reduction of the maximum stress in the point symmetry position in the circumferential direction can be achieved. Further, the cut portion & side of the joint portion 6a of the seat pan 6b can be achieved. And the dispersion and reduction of the maximum stress on the opposite side of the opposite portion of the cut-away portion 6c in the circumferential direction and the balance and the stress 18 of 18 1373541. As a result, the tilting deformation of the rotating shaft 2 and the deformation of the seat plate 6b can be sufficiently prevented. Figure 6 shows the cut The portion 6 (: has a substantially C-shaped outline that is open to the periphery of the seat pan. The joint portion on the outer peripheral side of the seat plate 6b in the current form of the through hole is also cut off. It can be offset with the volume which is the part of the volume increase for reinforcement. Such volume reduction can be made small due to the small distribution stress ,, by the reduction of the thickness of the seat 讣, the general radial reinforcing rib 22, the annular reinforcement The ribs 23 are reduced in thickness and height along the contour portion reinforcing ribs 24 and the box-shaped reinforcing ribs 28, etc. Further, the end portions of the radial reinforcing portions 21 are located at the cutout portions & The opening hole of the open end of the 6 region 6cl and the mounting hole 31b opposite to the cut portion 6C adjacent to the circumferential direction are formed between the mounting hole 31a and the mounting hole 31b. The dispersion of the stress can be achieved by the large bending resistance of the radial direction, and the strength of the n-hole 31a and the canopy of the mounting hole can be reduced by fastening to the sink back and fastening the outer circumference of the seat by both sides. Then strengthen the resection section & Further, the open end region 6cl serves as the reinforcing portion 33, and the reinforcing portion 33 is provided with a thickening reinforcing portion 32 that connects the radial reinforcing portion 21 and has a thickness Μ increased, and a reinforcing rib portion of the wheel rot portion of the Wei portion. 24 at least one of the thickened contour reinforcing portions. Therefore, the stress of the radial reinforcing portion η and the open region 6C1 can be further dispersed 'and the deformation and damage of the open end portion 6ei can be prevented. The reinforcing portion 33 on both sides of the 6c is combined with the radial reinforcing rib. The radial reinforcing portion 21, the radial reinforcing rib 19 and the reinforcing portion 33 constitute a triangular box-shaped reinforcing portion. The reinforcing degree can be increased on both sides of the cut portion 6c in the circumferential direction to increase the bending strength of the diameter of the seat plate, and the stress can be dispersed and reduced. Further, since the shaft coupling support member 8 receives a high load when the rotary drum 3 is shaken, the shaft coupling support member 8 is coupled to the rotary shaft 2 at the center as shown in FIG. 1, FIG. 2, and FIG. The shaft coupling portion 8ae and the shaft coupling support member 8 have a plurality of radial wrists 8b' that are radially extended by the shaft coupling portion 8a and are attached to the bottom peripheral wall of the rotary drum 3, and are connected and fitted to the radial wrist. The annular sealing wall 8c of the opening 3a of the bottom of the rotating drum 3 is opened. Further, each end portion of the radial wrist is screwed to the main body portion of the rotary drum 3 and the bottom fitting tubular wall 3b by bolts 14. Further, irrespective of the strength, as shown in Fig. 2A, the mesh sleeve 9 and the shaft coupling support member 8 are abutted against the back side and screwed to the bottom opening of the rotary drum 3. Thus, since the mesh sleeve 9 is held between the bottom of the rotary drum 3 and the shaft coupling support member 8, the separate mounting structure of the mesh sleeve 9 is not required. Further, the circumferential sleeve 1 is only required to be located at the bottom of the rotary drum 3. As a result, since the resin-made mesh sleeve 9 occupies the second change of the bottom of the metal rotary drum 3, the exposure ratio of the metal surface at the bottom of the rotary drum 3 is increased, and the texture of the bottom of the rotary drum 3 is also questioned, and resin is made. The mesh sleeve 9 also becomes difficult to damage. . Fig. 7A is a partial cross-sectional view showing the rotary drum of the drum type washing and drying machine of the embodiment of the present invention as seen from the front side, and Fig. 7B is a view of the B-B line of the seventh embodiment. The sleeve 9 is rotated together with the rotary drum 3, and the airflow from the air supply port 20 is dispersed, and the air is introduced into the rotating drum 3 in an average manner to improve the drying efficiency, and the (4) unevenness. The ventilation area of the large area of the mesh sleeve 9 is arranged in plural in the circumferential direction of the rotary drum 3, and the mesh air area is exposed on the front side by making the size corresponding to the mesh and the (four) through bottom opening 3a. . in this way,:. The rotary drum 3 is arranged in the circumferential direction of the rotary drum 3, and is introduced into the rotary drum 3 uniformly at any rotational position = air supply from the air supply port 7 to avoid drying. Further, it is arranged around the respective ventilation fields in the circumferential direction of the rotary drum 3, and the bottom portion (four) of the rotary drum 3 made of metal is surrounded by the shape of the frame. Specifically, the mesh sleeve 9 is a disk body as shown in Fig. 4, and is equally moved around the axis of the rotary shaft 2 at the bottom of the surface rotating drum 3. In the field of the central portion 9a, the peripheral portion %, and the radial reinforcing region 9c connecting the central portion 9a and the peripheral portion %, a plurality of segment regions 9d of the ventilation regions arranged in the circumferential direction of the rotary drum 3 are formed. A mesh with a mesh. That is, the mesh sleeve 9 is a segment type. Corresponding to this, the bottom opening 7 of the rotary drum 3 is also formed to correspond to the position and shape of the segment area 9d. As shown in Fig. 2B, the bottom opening 3a is fitted to the segment area 9d, and on the front side of the bottom of the rotary drum 3, the segment area 9d is flush with the front surface of the bottom of the rotary drum 3. Therefore, the mesh case 9 made of synthetic resin has only the segment area which becomes the ventilation area. 9d is the same as the bottom of the metal in the 7A and 7B of the metal such as stainless steel. As shown in FIG. 2B and FIG. 7A, a metal surface which is disposed in the circumferential direction of the rotary drum 3 of the mesh sleeve 9 and, in particular, the continuous circumference of the six segment areas 9d can be obtained. A decorative and high-grade look. 21, and as shown in FIG. 2A and FIG. 2B, the bottom of the recessed annular recessed portion % provided on the back side of the peripheral portion 9b of the mesh sleeve 9 and the annular dense (four) 8e provided on the shaft coupling support member 8. The convex portion annular ridge on the front side is spliced to form an outer peripheral annular seal region 41. Further, the outer peripheral annular seal region 41, the bottom of the rotary drum 3, and the flange 2a of the rotary shaft 2 are coupled to the shaft coupling portion 8a of the support member 8 by a shaft, and are screwed by the bolt 15. Thereby, the central opening 3C at the bottom of the rotary drum 3 is crimped to the convex portion of the front side of the mesh sleeve 9 and is provided with a ring and a bribe, and the inner peripheral annular sealing region is not attached to the net. The sealing of the inner and outer circumference necessary for the holding structure of the sleeve 9 can be accomplished without using a special sealing member. Also, =:= ring _ and her back two = system by rotation wear ^ P# by the song _ gap 4 5 and limited to the idiot 3 in the stupid direction _ ring concave surface (four) ^ ventilation here, sway The eighth figure is attached to the present invention: the front, the positive, the security: two:: a three-dimensional view of the half. First, look at the half of the mesh sleeve of the mesh type of the drum type laundry dryer. (4) Face side fine (four) type laundry drying 卞〇丨 Body diagram. Further, as shown in Fig. 10, the reinforcing region is surrounded by the wheel sleeve 9 at the inner circumference 9A of the center portion, and the circumferential reinforcing portion rib portion %. Further, the back surface of the 1 (four) and the non-material portion is formed with a contour portion of the strong region 9c or a non-circle * field 9. The reinforcing ribs 9h may be used only in any of the remedies. The mesh sleeve 9 is in a ventilated area exposed in the 22 rotating drum 3, and the rotating drum 3' is protected and has a high surface rigidity. The load of the washing material is covered, and the cover is rotated by the reinforcing rib 9h, and the left side of the J-cylinder 3 is bent toward the mesh sleeve 9 by the surrounding support ventilation. The annular bent wall that is fitted to the back side of the net is as follows. Q, the recess around the segment area 9d of the holster 9 The bottom of the rotating drum 3 enhances the rigidity of the ridge by bending the wall, and the protective property of the sleeve 9. Further, the bent wall 3al is fitted into the recessed portion 9g without being exposed, and the laundry is not damaged. Moreover, the cutting edge of ^^ does not exceed the outside, and the appearance of the state is good. The structural shape has an edge shape as shown in Fig. 2'. The shaft fastening support 8 of the center of the bottom of the rotary drum 3 and the bolt fixing portion of the rotary shaft 3 utilize a large majority of bolts 15 for strong consolidation, but with screws 44 is fixed to the shaft coupling portion 8a' by the metal on the front side and covers a plurality of bolts 15 which are hidden. Further, the shaft coupling member 8 is formed by fitting the radial projection 8g to the stopper hole 3d at the bottom of the drum 3. Further, the mesh sleeve 9 is stopped by the concave-convex engagement portion 51 between the mesh sleeve 9 and the shaft coupling portion 连结 of the connection support member 8. 11 is a perspective view of a half of a shaft coupling support member of a drum type prior mine dryer according to an embodiment of the present invention viewed from the front side, and FIG. 12 is an axis of the drum type laundry dryer viewed from the side of the surface. A perspective view of a half of the connecting support member. In the embodiment of the present invention, as shown in Fig. 11, the shaft coupling support member 23 1373541 8 is a three-dimensionally reinforced bridge 8e that is integrally formed and reinforced between the bases of the radial wrists 8b. The front end surface of the joint portion extends in an umbrella shape and extends to the open end edge on the side of the water tank 1, and is connected to the base portion of the adjacent radial wrist 8b in a meandering shape. Therefore, the high load at the time of the oblique deformation of the rotary shaft 2 can be uniformly dispersed and absorbed around the joint portion of the rotary shaft 2. Moreover, the maximum stress concentrated on the rotating shaft 2 is mostly reduced, and only the small stress is generated by the shaft coupling supporting member 8. Specifically, the shaft coupling portion 8a of the shaft coupling support member 8 serves as a center portion that receives the tilting load of the rotary shaft 2 which is generated when the rotary drum 3 is shaken. Further, the tilting load of the rotating shaft 2 is transmitted to the mounting portion of the rotary drum 3 by the base portion of the radial arm 8b via the connecting portion of the annular sealing wall 8c. The three-dimensional reinforcing frame bridge 8e does not particularly increase the weight of the shaft coupling support member 8, and is a box type that is open to the side of the water tank 1 between the side peripheral surface of the shaft coupling portion 8a. Further, the shaft coupling support member 8 is configured to increase the strength of the bending and the strength of the distortion caused by the movement of the tilting direction of the rotating shaft 2 in the circumferential direction. Further, the shaft coupling support member 8 is inclined at the base of the radial wrist 8b by the rotation axis 2, and does not generate a large stress to the women's portion of the rotary drum 3. As a result, the sway, vibration, and noise of the rotary drum 3 can be reduced, and the durability of the shaft coupling support member 8 can be improved. Further, the radial wrist 8b is formed in a U-shaped cross section that is open toward the back side. The vertical reinforcing bridge 8e is formed between the shaft connecting portion 8a and the radial wrist 8b with the side opposite to the radial side of the radial arm 8b and the bottom end of the connecting side as the bottom side. The three-dimensional reinforcing bridge 8e is formed into a box-shaped recess having a substantially triangular pyramid shape with the front side of the side peripheral portion of the shaft coupling portion 8& as a vertex, whereby the balance between the bending strength and the torsional strength and the elastic deformation characteristic are appropriate. Further, as shown in Fig. 2B, the three-dimensional reinforcing bridge 8e is curved or bent or inclined along the center side of the rotary drum 3, so that the air blow from the air supply port 7 of the water tank 1 as indicated by the arrow can be encountered. The segment area of the sleeve 9 is post-diffused and dispersed. That is, the expanded shape of the open end edge of the three-dimensional reinforcing bridge 8e may be any of a curved shape, a bent shape, and a tilted shape. Thereby, the air supply is easily moved to the center side of the rotary drum 3. Therefore, the drying efficiency can be improved as compared with the case where the center portion of the rotary drum 3 is insufficiently supplied to the peripheral portion of the rotary drum 3. In this regard, the shape of the end edge of the three-dimensional reinforcing bridge & to the sink is preferably corresponding to the shape of the edge of the center of rotation of the air supply port 7. As shown in Fig. 5 and Fig. 6, the three-dimensional reinforcing bridge has a shape that roughly corresponds to the buckling shape of the bridge reinforcing portion 25 of the cut-away portion 6c and expands toward the center of rotation. That is, the open end edge of the three-dimensional reinforcing bridge 8e and the inner peripheral edge of the air supply port 7 on the side of the rotating shaft 2 can be convexly curved toward the side of the rotating shaft 2. Further, the bending or buckling of the three-dimensional reinforcing bridge and the direction of inclination should preferably correspond to the position of the edge of the center of rotation of the air supply port 7. Therefore, the inclination angle of the three-dimensional truss bridge 8e corresponds to the axis of the rotary shaft 2, which is preferably about 45. Left and right. However, it is not limited to the inclination angle, and the direction of the air blowing port 7 in the blowing direction of the air blowing port 7 and the direction of the air blowing path from the circulating air blowing path connected thereto are also included, and the inside of the rotating drum 3 is appropriately determined. The direction of the wind guide can be. In either case, the inner circumference of the annular seal wall 8c and the inner circumference of the side opposite to the shaft coupling portion 8a of the air supply port 7 are substantially identical in the direction of the rotary shaft 2, and the rotary shaft 3 side of the air supply port 7 is provided. The inner periphery and the open end edge of the three-dimensional reinforcing bridge are aligned in the direction of the rotating shaft 2. Thereby, the radial wrist whip splits between the 25-wheel connecting portion 8a and the annular sealing wall 8 (the segmental ventilation field formed by the sentence and the size can correspond to the ventilation field of the air supply σ7, without damaging The air supply port 7 has the advantage of the air supply in the water tank 1. Further, as shown in Fig. 12, the three-dimensional reinforcing bridge 8e has a three-dimensional shape which is open toward the back side between the outer surface of the shaft connection and the P8a. The radial wrists 8b connected to the three-dimensional reinforcing bridge 8e are in the shape of a U-shaped cross section, and are supported by the back side of the radial reinforcing _ of the mesh sleeve 9. Further, as shown in Fig. 2 On the way of the length of the radial wrist, a radial structure of the bridge wall which is raised from the bottom of the u-shaped shape and which is connected between the two side walls is provided with a (four) structure connected to the two ends of the long-term financial direction, thereby improving the twisting strength, Bending the strength. Secondly, the second check is made in the same way as the method described in the "bearing support member 6, _ knot support member 8 = ^". L Λ 轴承 轴承 式 式 式 式 式 式 式 式 式The high-speed 1600 rpm rotating bar has no layout. The figure shows the deformation support structure of the drum-type laundry dryer under the high-speed rotation condition of 160G rpm. The MA picture is the stress of the embodiment of the present invention. The axial force distribution diagram of the connecting support member in the high-speed rotating strip 4 dryer of the _Qing, and the 14th drawing is the same as the drum type washing: the supporting structure of the front side of the supporting member at the back side of the high-speed rotation condition of _ah The 14C system shows the same axis as the drum type washing and drying machine: the second layout, the deformation component and the maximum stress of the first component under the high-speed rotation condition of 26 1373541 1600 rpm. The first verification system uses the same analytical model as the background technology. That is, the bearing support member 6 uses the analytical model shown in Fig. 19B, and the axial connection support member 8 uses the analytical model shown in Fig. 20C. Further, the second test is to survey the bearing support member 6 of the jth check. The stress distribution of the shaft coupling support member 8. The first and second verification results of the bearing support member 6 are as shown in Fig. 13B, with respect to the conventional deformation amount 〇24, the maximum stress 6lMPa (weight 3.6kg), deformation The maximum stress is 33 MPa (weight 4.4 kg). Figure 13A shows the stress distribution at a deformation of 〇.〇9 and a maximum stress of 33 MPa. The maximum stress is dispersed and concentrated by the radial reinforcement. The boss portion 6 of the 21 is disposed along the base portion side of the radial reinforcing rib 22 of the radial reinforcing portion 21 on the opposite side of the cut portion & a portion of the base portion side of the radial reinforcing rib 22 adjacent to the opposite side of the cutout portion 6c, a radial reinforcing rib 22 that is point-symmetric to the center point of the bearing support member 6 next to the boss portion 6a, and radiation The base side of the shape equalizing reinforcement portion 27 or the root portion near the base portion "other fields are considered to have a much reduced stress in part. Further, the weight of the bearing support member 6 of the embodiment of the present invention is 3.6 乂 § § 4_41 <^, approximately less than 14°/. The weight. However, in terms of the maximum stress, the bearing support member 6 of the embodiment of the present invention is approximately halved to 33 MPa as compared with the conventional 6 MPa, and it can be understood that the weight can be increased without increasing the weight. The first and second verification results of the shaft coupling support member 8 are as shown in Fig. 14C, and the amount of deformation with respect to the conventional one is 0.15. The maximum stress is 5 〇 MPa (weight 3.5 kg) ’ deformation amount is 〇 〇 9. The maximum stress is 25 MPa (weight 39 kg). Chapter 27 1373541 14A and 14B show the stress distribution portion on the front and back sides when the deformation amount is 〇.〇9° and the maximum stress is 25 MPa. As a result, it is considered that the maximum stress is concentrated on the rotating shaft 2, and the stress in the other portions is slight. The shaft joint supporting member 8 of the embodiment of the present invention has an increase of more than 10% by weight of 3.9 kg' with respect to a conventional weight of 3.5 kg. Further, as shown in Fig. 14C, in the embodiment of the present invention, the maximum stress is halved to 25 MPa with respect to the conventional 5 MPa. In this case, it is also possible to increase the weight without increasing the weight. C. Brief Description of the Drawings Fig. 1 is a cross-sectional view showing a structural portion in which a rotating shaft of a rotary drum according to an embodiment of the present invention is supported by a bearing supporting member in an embodiment of the present invention. Fig. 2A is a cross-sectional view showing a connection structure portion formed by a shaft connecting support member of a rotary drum and a rotary shaft of a drum type washing and drying machine. 'Fig. 2B is a diagram connecting the lower part of Fig. 2A. unit
第3圖係顯示本發明之實施形態之滚筒式洗衣乾燥機 中，旋轉滾筒支持於水槽内，並將馬達安裝於水槽背 且與旋轉軸連結之主要部之背面圖。 S 之水槽之Fig. 3 is a rear elevational view showing the main portion of the drum type washing and drying machine according to the embodiment of the present invention in which the rotary drum is supported in the water tank and the motor is attached to the water tank back and coupled to the rotating shaft. S sink
第4圖係同滾筒式洗衣乾燥機之拆下主要部 正面側半部來看之分解立體圖。 第5圖係由正面側看安裝於同滚筒式先 槽之背部並且支持旋轉軸之轴承 承支持構件之立體圖 衣乾燥機之水 且安裝馬達<定子之軸 第6圖 第7八 係由背面側看第5圖之輪承支持構件之 圖係由正面側看本發明之嘗偷 筒式洗衣 28 乾燥機之旋轉滾筒之部分橫截面圖。 第7B圖係第7A圖之β·β線橫截面圖。 第8圖倍於本發明之實施变態之滾筒式洗衣 背部正面側* iL面側看安裝於祕滾狀轴連接機之 及配置有網狀套之水槽之背部侧半部之幾乎半部之二 圓。 丰部二，滾筒式洗衣乾燥機-網狀套之 半：::"面側看同滾筒式'洗衣乾燥機之網狀套之 持構=::::看_式—機，結支 技第12圖係由背面側看同滾筒式洗衣乾燥機之軸連結支 持構件之半部之立體圖。 、·· 第13·係顯示同滚筒式洗衣乾燥機之 在1600—之高逮旋轉條件下之應力分布圖. 、 :圖:顯示同滚筒式洗衣乾〜 :=速旋轉條件下吻^ —速支持構件在 第⑽圖係同滾筒式洗衣乾燥機之 1600rpm之高輯轉條件下l丨 :圖:顯㈣滾筒式洗衣乾燥機二連结支持構 件在1600rpm之向速旋轉條件下之 戈心里、最大應力之圖。 29 1373541 第15圖係顯示習知之滾筒式洗衣乾燥機之全體構造之 概略圖。 第16圖係顯示由輛連結支持構件連結於該滾筒式洗衣 乾燥機之旋轉滾筒之旋轉轴，藉由軸承支持構件支持於水 槽並且連結於馬達之構造部之部分截面圖。 第Π圖係顯示安裝於該滾筒式洗衣乾燥機之旋轉滾筒 底部之網狀套及轴連結支持構件之安裝狀態的半部截面 圖0 乐尔翔不同滾筒式洗衣乾燥機之軸承支持構件 之截面圖β 第⑽圖係顯示同滾筒式洗衣乾燥機之軸承支持構件 之正面圖。 第18C圖係顯示同滾筒式洗衣乾燥機之轴承支持 之背面圖。 第詞:系同滚筒式洗衣乾燥機之轴承支持構件在 160〇rpm之商速旋轉條件下之應力分布圖。 第19B圖係解析模型圖。 第2〇A圖係習知之滾筒式洗衣乾燦機之轴連結支持構 件在=:速_件下之正面側之應力分布圖 第20B圖係同滾筒式洗衣乾 職Pm之高速_仏背_ 二支持構件在 第霞圖係同滾筒式洗衣乾燥機之布圖。 1600rpm之冑輯轉條件下對 、’°丨構件在 之變形量、傾斜角之敎結果之圖。、，·。支持構件之旋轉轴 30 1373541 第20D圖係解析模型圖。 【主要元件符號說明】Fig. 4 is an exploded perspective view of the main portion of the front side of the drum type washing and drying machine. Fig. 5 is a perspective view of the water of the three-dimensional figure dryer attached to the back of the drum type first groove and supported by the bearing support member of the rotating shaft, and the motor is mounted on the front side. Looking at the figure of the wheel bearing support member of Fig. 5, a partial cross-sectional view of the rotating drum of the trick-type washing machine 28 dryer of the present invention is seen from the front side. Fig. 7B is a cross-sectional view of the β·β line of Fig. 7A. Fig. 8 is a front side of the drum type laundry back side of the embodiment of the present invention. * iL side view is attached to almost half of the back side half of the sink line connecting machine and the water tank provided with the mesh sleeve. Two circles. Feng Department II, drum type washing and drying machine - half of the mesh sleeve:::" face side view of the same type of drum type 'washing dryer mesh holder ==::: see _ type - machine, knot Fig. 12 is a perspective view of a half of the shaft connecting support member of the drum type laundry dryer viewed from the back side. , ··· The 13th series shows the stress distribution diagram of the drum type washing and drying machine under the condition of 1600-high catching rotation. , : Picture: shows the same type of drum type washing machine ~ := speed rotation condition kiss ^ speed The supporting member is in the high-speed rotation condition of the 1600 rpm of the drum type washing and drying machine in the figure (10): Figure: (4) The drum-type washer-drying machine is connected to the support member at a speed of 1600 rpm. The map of the maximum stress. 29 1373541 Fig. 15 is a schematic view showing the entire configuration of a conventional drum type laundry dryer. Fig. 16 is a partial cross-sectional view showing a rotating shaft of a rotary drum to which the connecting support member is coupled to the drum type laundry dryer, supported by a bearing support member in the water tank, and coupled to the motor. The figure is a half cross-sectional view showing the installation state of the mesh sleeve and the shaft coupling support member installed at the bottom of the rotary drum of the drum type laundry dryer. 0 Cross section of the bearing support member of the different drum type washer dryer Figure β (10) shows a front view of the bearing support member of the drum type laundry dryer. Figure 18C is a rear view showing the bearing support of the drum type laundry dryer. The first word: the stress distribution diagram of the bearing support member of the drum type washing and drying machine under the condition of 160 rpm commercial speed rotation. Figure 19B is an analytical model diagram. Figure 2A is a diagram of the stress distribution on the front side of the drum-type washing and drying machine. The 20B is the same as the drum-type washing machine. The layout of the second supporting member in the same diagram as the drum type laundry dryer. The result of the deformation amount and the inclination angle of the '°丨 member under the condition of 1600 rpm. ,,·. Supporting member's axis of rotation 30 1373541 Figure 20D is an analytical model diagram. [Main component symbol description]
3b...本體部、底部嵌合筒壁 8g..3b...body part, bottom fitting tube wall 8g..
1.. .水槽 la...背部開口 2.. .旋轉軸 2a...凸緣部 2b...外端 3.. .旋轉滾筒 3a...底部開口 3al...折曲壁 3c...中央開口 3d...播止孔 4…馬達 4a...定子 4b...轉子 4bl...内周側轉子 4b2·.·外周側轉子 5.. .軸承 6.. .軸承支持構件 6a...轴套部 6b...座盤 6c...切除部 6cl...開放端部區域 7.. .送風口 8.. .轴連結支持構件 8a...軸連結部 8b...放射狀腕 8c...環狀密封壁 8d...凸部環狀凸條 8e...立體增強架橋 8f...架橋壁 .突起 9.. .網狀套 9A...内周 9a...中央部 9b...周邊部 9c...放射狀補強區域 9d...區段領域 9e...環狀凹部 9f...凸部環狀凸條 9g…凹部 9h...補強肋部 14.. .螺栓 15.. .螺栓 20.. .螺栓 31 1373541 21.. .放射狀增強部 22.. .放射狀補強肋部 23.. .環狀補強肋部 24.. .輪廓部補強肋部 25.. .架橋增強部 26.. .箱型增強部 27.. .放射狀均衡增強部 28.. .箱型補強肋部 30.. .安裝孔 31.. .安裝孔 31a...安裝孔 31b...安裝孔 32.. .增厚增強部 33.. .增強部 34.. .輪靡增強部 41.. .外周部環狀密封區域 42.. .内周部環狀密封區域 43.. .金屬蓋 44.. .螺絲 45.. .曲徑間隙 51.. .卡合部 100.. .滾筒式洗衣乾燥機 101.. .洗衣機本體 102.. .水槽 102a···背部開口 103.. .旋轉滚筒 103a...底部開口 103b...本體部、底部嵌合筒壁 104.. .馬達 104a...定子 105.. .旋轉軸 105a...凸緣部 106.. .轴承 107.. .送風扇 108.. .送風口 109.. .循環送風路徑 109a...送風側 111.. .軸承支持構件 llla. ..軸套部 lllb. ..座盤 lllc. ..切除部 llld. ..安裝孔 112.. .軸連結支持構件 112a...軸連結部 112b...放射狀腕 112c...環狀密封壁 112d...中央縱肋部 112e...肋部 32 1373541 112f...周邊肋部 113.. .密封構件 114.. .機械軸封 115.. .密封構件 116...網狀套 116a...區段領域 116b...網孔 331.. sink sink... back opening 2.. rotating shaft 2a... flange portion 2b... outer end 3.. rotating drum 3a... bottom opening 3al... bending wall 3c ...the central opening 3d...the venting hole 4...the motor 4a...the stator 4b...the rotor 4b1 the inner circumference side rotor 4b2·.the outer circumference side rotor 5...the bearing 6...the bearing Support member 6a... Bushing portion 6b... Seat plate 6c... Cut-out portion 6cl... Open end portion 7: Air supply port 8.. Shaft connection support member 8a... Shaft connection portion 8b...radious wrist 8c...annular sealing wall 8d...protrusion annular rib 8e...three-dimensional reinforced bridge 8f...bridge wall.protrusion 9.. mesh cover 9A.. Inner circumference 9a... Center part 9b... Peripheral part 9c... Radial reinforcement area 9d... Section area 9e... Annular recessed part 9f... Protrusion part Annular rib 9g... Recessed part 9h...reinforcing ribs 14...Bolts 15..Bolts 20..Bolts 31 1373541 21.. Radial reinforcement 22: Radial reinforcement ribs 23.. Annular reinforcement ribs 24.. contour reinforcement ribs 25.. bridge reinforcements 26.. box reinforcements 27.. radial equalization reinforcements 28.. box reinforcement ribs 30.. installation holes 31. . mounting hole 31a... mounting hole 31b... Hole 32.. Thickening reinforcement 33.. Reinforcement 34.. Rim reinforcement 41.. Outer peripheral annular seal area 42.. Inner circumference annular seal area 43.. Metal cover 44.. . Screw 45.. . Bending clearance 51.. Engagement part 100.. Drum type laundry dryer 101.. Washing machine body 102.. Sink 102a···Back opening 103.. Rotate Roller 103a... bottom opening 103b... body portion, bottom fitting cylinder wall 104.. motor 104a... stator 105.. rotating shaft 105a... flange portion 106.. bearing 107.. Sending fan 108.. venting port 109.. Circulating air supply path 109a...air supply side 111.. bearing support member llla... bushing part lllb... seat plate lllc... cutting part llld. .. mounting hole 112.. shaft coupling support member 112a... shaft coupling portion 112b... radial wrist 112c... annular sealing wall 112d... central longitudinal rib 112e... rib 32 1373541 112f... peripheral rib 113.. sealing member 114.. mechanical shaft seal 115.. sealing member 116... mesh sleeve 116a... section field 116b... mesh 33