200902856 九、發明說明 【發明所屬之技術領域】 本發明是關於軸爲中心使葉輪透過固定在中央的軸承 支撐成自由旋轉，並且’利用循環水的潤滑形成滑動的水 中滑動軸承泵。 【先前技術】 所謂水中滑動軸承泵的泵浦，具有滑動部’利用軸承 和軸承板的旋轉滑動產生泵作用。 該水中滑動軸承泵的一例，例如已提案日本專利第 3099434號公報及日本特開2006-200427號公報所揭示之 構造的水中滑動軸承泵。 此種泵浦，是以專利文獻1所謂的磁泵或專利文獻2 所謂的DC無刷栗爲代表。 針對習知泵浦是使用第1 2圖的D C無刷泵進行說明。 該泵浦2是以馬達1具備已配設有線圈的繞組3產生磁場 ，利用控制部4控制該磁場產生。爲了能夠追隨該產生磁 場，隔著分離板5固定有永久磁鐵6的葉輪7是由軸8支 撐成自由旋轉。如此一來，追隨著旋轉磁場的葉輪7的旋 轉就能夠進行循環水的吸排水。 軸8是由設置在分離板5中央的分離板軸支撐5a和 設置在殼9中央的殼軸支撐9a固定著。爲讓葉輪7支撐 成可相對於軸8自由旋轉’於葉輪7的中心固定著軸承1 〇 ，軸8和軸承1 0是形成旋轉滑動。再加上，在軸承1 〇的 -4 - 200902856 兩端面和殻軸支撐9a及分離板軸支撐5a之間，分別設有 第一軸承板1 1及第二軸承板1 2，藉由執行推力方向的旋 轉滑動。於軸8的兩側形成只有端面部爲d形狀，藉此防 止第一軸承板11和第二軸承板1 2的轉動。 接著，該泵浦針對軸承1 0的全長和第一軸承板1 1及 第二軸承板12之厚度的和，以可在殻軸支撐9a和分離板 軸支撐5 a間保留有些許間隙f的考量，避免組裝落差造 成葉輪7鎖住。 此外，於軸8的端面和殼軸支撐底部9d之間，亦設 有組裝落差吸收用的空隙g。由於零件尺寸落差的累積會 集中在該空隙g，因此會產生若干尺寸落差。 該泵浦中，隨著葉輪7的旋轉停止，於軸8會施加有 推力方向的力。因此，軸8會以該空隙g份量的移動量逐 漸往殼9移動。如此一來，第二軸承板丨2的推壓就消失 ’使第二軸承板1 2成爲自由狀態，有時會因水流而跳動 產生異常聲音。爲了防止該狀況，於空隙g插入壓縮著矽 橡膠等彈性體形成的緩衝材1 3，藉此壓制軸8的浮動。 殼9和分離板5是以間設有0環或襯墊1 4形成密封 ’防止栗室內的循環水滲漏。殼9和分離板5，一般是以 螺絲1 5固定。 其次，對構成爲上述的泵浦的動作進行說明。隨著繞 組3所產生的旋轉磁場，葉輪7是透過形成固定的永久磁 鐵6的吸引排斥而追隨旋轉。藉此產生泵浦作用，從箭頭 符號A方向吸入循環水，往箭頭符號B方向吐出循環水。 -5- 200902856 此時，A和B的差壓會造成葉輪7被推壓往殼9側，使 第1軸承板1 1和軸承1 〇的端面形成旋轉滑動。 軸承10和第二軸承12的滑動幾乎不會發生，只限於 啓動停止時的一瞬間，或在沒有循環水的狀態下運轉泵浦 之空運轉等異常運轉時才會發生。因此，一般第一軸承板 1 1的材質使用陶瓷’另外第二軸承板1 2的材質使用SUS (不銹鋼）的狀況較多。於軸8和軸承10的滑動部，及 於軸承1 0的兩灣面和第一軸承板1 1及第二軸承板12之 間的滑動部形成有循環水的水膜，隔著水膜可使兩者有良 好的滑動。 【發明內容】 殼9和分離板5，如上述一般是隔著0環或襯墊形成 螺絲固定’但若因使用條件、環境條件以致無法使用橡膠 時’或爲了降低成本而打算放棄使用0環或襯墊時，則是 進行熔焊固定。 第1 3圖中圖示著殼9和分離板5利用熔焊形成結合 時的熔焊狀祝橫剖面圖。第1 4圖爲熔焊前狀態的熔焊部 1 6剖面圖，第1 5圖爲熔焊後的熔焊部1 6剖面圖。 熔焊時，泵浦2是朝向上面設置在承接固定工具21， 號筒20會下降。號筒20是壓在熔焊部16的上面，由該 號筒20產生超音波或振動使運動能量傳播至殼熔焊部9b 和分離板熔焊部5 b。此時，運動能量會集中在熔焊部轉換 成熱能，樹脂形成的熔焊部1 6會因此熔化使殼9和分離 -6- 200902856 板5結合。欲熔化的部份，設有小突起或邊緣藉此確保容 易熔化的形狀。 號高20的振動’基本上是會傳播至號筒2〇壓住的部 份使該部份熔焊’但於一部份會有整體的振動傳播。因此 ’當號筒20壓在殻9時，振動也會傳播至殻9中央附近 所配置的殻軸支撐9a ’使該殼軸支撐9a往上下振動。於 殼軸支撐底部9d和軸8的端面間配設有緩衝材1 3，但因 其是彈性體所以無法抑制殼軸支撐9 a的上下振動。因此 ，第一軸承板1 1就會斷續地受到殼軸支撐9a碰撞，以致 產生龜裂等破損狀況。 於是，本發明’其目的是提供一種即使號筒的振動傳 播至殼軸支擦造成殼軸支撐上下振動，但還是能夠防止第 一軸承板龜裂’此外能夠廢除使用軸浮動抑制用緩衝材的 水中滑動軸承泵。 本發明之一的水中滑動軸承泵形態，其特徵爲，具備 有：循環水吸排用的葉輪；上述葉輪固定用的軸；固定在 上述葉輪可將上述葉輪支撐成相對於軸自由旋轉的軸承； 收納著上述葉輪可形成泵室的殼及分離板；設置在上述殼 中央’對上述軸的一端加以固定的殼軸支撐；及設置在上 述分離板中央，對上述軸的另一端側加以固定的分離板軸 支撐，構成以熔焊使上述殼和上述分離板形成密封•固定 藉此形成上述泵室的同時，於上述殻軸支撐的底部設有突 起。 200902856 【實施方式】 [發明之最佳實施形態] 本發明的實施形態，水中滑動軸承泵，具備有：循環 水吸排用的葉輪；上述葉輪固定用的軸；固定在上述葉輪 可將上述葉輪支撐成相對於軸自由旋轉的軸承；收納著上 述葉輪可形成泵室的殻及分離板；設置在上述殻中央，對 上述軸的一端加以固定的殻軸支撐；及設置在上述分離板 中央，對上述軸的另一端側加以固定的分離板軸支撐，構 成以溶焊使上述殼和上述分離板形成密封•固定藉此形成 上述泵室的同時，於上述殼軸支撐的底部設有突起。 如此一來，即使號筒的熔焊振動傳播至殼軸支撐造成 振動時，還是能夠因爲突起的一部份溶化結合在軸的前端 藉此吸收振動能量，能夠防止來自於該殼軸支撐的碰撞造 成第一軸承板龜裂。再加上，沿著具有落差的空隙熔化突 起，以零嵌合就能壓住軸，因此能夠廢除習知所需的軸浮 動抑制用緩衝材。 此外’本發明的實施形態中，水中滑動軸承泵是構成 爲上述突起配置在上述殼軸支撐的中央或對中心成對稱的 位置。 如上述，上述突起配置在上述殼軸支撐的中央或對中 心成對稱的位置，可使突起平衡熔焊（熔化）在軸上，因 此殼軸支撐沒有應力殘留，或不會對本來需要的溶焊部造 成不良影響。 另外’本發明的實施形態中，水中滑動軸承泵是構成 -8- 200902856 爲對應著形成在上述殼軸支撐底部的上述突起前 於上述軸的端面設有可和上述突起前端形狀嵌合 或凸形狀。 如上述，對應著形成在殼軸支撐底部的突起 ，於軸的端面設有可和上述突起前端形狀嵌合的 凸形狀，能夠確保該等嵌合部位的表面積更大， 效果溶化。如此一來，以零肷合就能壓住軸，因 緩衝材。 此外，本發明的實施形態中’水中滑動軸承 爲利用旋轉熔焊使上述殼和上述分離板形成密封 此形成上述栗室。 如上述，採用旋轉熔焊是可使熔焊時的號筒 動而是形成爲旋轉方向的運動’因此也能夠在不 軸承板的狀況下使殼和分離板形成密封·固定。 再加上，當樹脂的玻璃含量多若採超音波熔 到玻璃纖維而無法期待熔焊部具有充分強度時， 旋轉熔焊是能夠使殻和分離板充份熔焊結合，因 現所期望的強度。 [實施例] 以下是本發明最佳實施形態以實施例爲圖示 附圖的同時進行更具體的說明。 於此，在附圖中，與習知泵浦相同的構件是 圖號，並省略重覆說明。另，於此的說明’由於 端形狀， 的凹形狀 前端形狀 凹形狀或 使突起有 此可廢除 栗是構成 •固定藉 不上下振 影響第一 焊會影響 藉由採用 此能夠實 ，在參照 標示相同 是說明本 -9- 200902856 發明的最佳實施形態，因此本發明是不限於該實施形態（ 實施例）。 (實施例1 ) 第1圖爲本發明實施例1的泵浦橫剖面圖，第2圖及 桌3圖爲本發明實施例1的殼軸支撐透視圖，第4圖爲本 發明實施例1的熔焊後殼軸支撐部橫剖面圖。 本實施例的泵浦，是一種軸爲中心使葉輪透過固定在 中央的軸承支撐成自由旋轉，並且利用循環水的潤滑形成 滑動的水中滑動軸承泵。該泵浦，例如是使用在燃料電池 裝置或熱泵裝置或者各種冷卻系統等。 於該泵浦的馬達1設有已配備線圈的繞組3。該馬達 1是以通電至繞組3來產生旋轉磁場，接受來自於省略圖 示位置檢測部的訊號利用控制部4控制旋轉磁場。泵浦部 2的外廓是由殼9和分離5構成，由該等的熔焊部16執行 固定·密封。 馬達1和泵部2是由分離板5區隔成密封著。於分離 板5的中心設有對軸8另一端側部加以固定的分離板軸支 撑5 a，於殼9的中心設有對軸8 —端側部加以固定的殼軸 支撐9 a。軸8的兩端部均是形成爲剖面大致D形狀。其 中，軸8的一端是隔著中心孔12a爲D形狀的第二軸承板 12固定在上述分離板軸支撐5a’藉此防止上述軸8的旋 轉，此外防止第二軸承板1 2的浮動。 此外，軸8的另一端（他端）’同樣地隔著中心孔 -10- 200902856 lla爲D形狀的第一軸承板11固定在上述殼9，藉此防止 上述軸8的旋轉。 葉輪7是被支撐成相對於軸8成自由旋轉，在第一軸 承板1 1和第二軸承板1 2之間配設有軸承1 〇。此時，以組 裝落差不會造成軸承1 〇鎖住地相對於軸承1 0的全長和第 一軸承板1 1及第二軸承板1 2的厚度之和，在殼軸支撐9 a 和分離板軸支撐5 a間設有些許空隙f。另外，於軸8的一 端和殼軸支撐底部9d間，也是以組裝落差爲考量形成有 些許空隙g。 本實施例的水中滑動軸承泵是隨著對繞組3通電產生 的旋轉磁場使固定在葉輪7的永久磁鐵6受到吸引排斥， 藉此使上述葉輪7以上述軸8爲中心進行旋轉。於葉輪7 的中心因是固定著軸承1 〇，所以該軸承1 〇和上述軸8會 形成旋轉滑動。一般，軸8的材質是以SUS (不銹鋼）或 陶瓷形成。另一方面，軸承10是多數由具碳或滑動性的 樹脂等形成。第一軸承板1 1及第二軸承板1 2是和軸8相 同以SUS或陶瓷形成。 接著，該水中滑動軸承栗是隨著葉輪7的旋轉產生泵 浦作用，使循環水從吸入口 A吸入從吐出口 B吐出。此時 ，葉輪7是根據吸入和吐出的壓差被推往殼9側形成旋轉 滑動。即，葉輪7是於推力方向（軸8的軸方向）以軸承 1 〇的端面和第一軸承板1 1接觸的狀態形成旋轉滑動。泵 浦功能愈高，則上述受推的壓力就愈大，使滑動阻力變高 -11 - 200902856 因此，多數的狀況，第一軸承板11，爲了降低滑動阻 力實現良好滑動是以陶瓷形成。因此，第1軸承板1 1，當 施加有來自於葉輪7的強大碰撞時有可能龜裂。於軸8外 徑部份和軸承1 0內徑部份的滑動部，及於軸承1 0兩端面 和第一軸承板1 1或第二軸承板1 2的滑動部，分別形成有 循環水的水膜，隔著該水膜能夠使兩者有良好的滑動。 第2圖是圖示著組裝前的殼軸支撐9a。於該殼軸支撐 9 a的底部9 a的中央，設有一處往上方突出的圓錐形突起 9c。該突起9c並不一定是於中央形成一處，如第3圖所 示，也可以是複數個設置在以中心爲對稱的位置。不過， 軸8的端面，如上述因剖面形狀爲D形狀以致局部缺角， 因此突起9c需要考慮到缺角部形成對稱配置。將突起9c 配置在以中心爲對稱的位置，於熔焊時及熔焊後，可使應 力不殘留在殻軸支撐9a，此外突起9c的均等熔化也能夠 使振動均等傳播至本來的分離板5和殼9的熔焊部1 6，實 現良好的熔焊結合。 如上述將熔焊在軸8端面的突起9 c設置在殼軸支撐 9a的水中滑動軸承泵中，當分離板5和殼9的熔焊部16 形成熔合時，振動能量會傳播至熔焊部1 6，如第1 4圖及 第1 5圖所示，殼熔焊部9 b和分離板熔焊部5 b會熔化形 成結合。 此時，局部的振動能量也會傳播至殻軸支撐9a。殼軸 支撐9 a會因振動能量而欲往上下振動。但是，此時振動 能量會因集中在突起9c前端而轉換成熱能，如第4圖所 -12- 200902856 示’突起9c的前端會熔化結合於軸8的端面。如此一來 ，殼軸支撐9a ’就會因爲熔化結合在軸8端面而使其上下 的振動受到抑制，即不會碰撞第一軸承板1 1造成破損’ 能夠獲得良好的熔化結合。 再加上，如第4圖所示，殼軸支撐底部9 d和軸8端 面的空隙g是成爲突起9 c 一部份殘留狀態，能夠以零嵌 合壓住軸8端面，所以不需要緩衝材的推壓。因此’即使 因成品落差造成空隙g尺寸若干改變時還是能夠調整突起 9 c的熔化長度，能夠確實壓住軸8。 (實施例2) 實施例1是將形成在殼軸支撐底部9d的突起9 c形狀 爲圓錐形，但該突起9 c的形狀並不限於圓錐形，如第5 ( a )圖、第5 ( b )圖所示，突起9c的形狀也可以是剖面大 致三角形。肋部，可以是1個也可以是複數個，此外，爲 複數個時只要考慮到軸8的缺角部形成對稱位置配置即可 (實施例3 ) 實施例1或實施例2中，特別是形成適合超音波熔焊 的突起形狀’以能量集中於一點使突起達到端面熔化的目 的’因此前端形狀是形成爲銳角形，熔焊部是形成爲點接 觸或線接觸的形狀。 近年來，基於泵浦耐水壓提昇的要求，是以樹脂材質 -13- 200902856 含有玻璃纖維達到樹脂強度的提昇’因此逐漸有使用玻璃 強化級樹脂的趨勢。 超音波熔焊時的熔焊時間短且爲1秒前後’熔焊部16 的尺寸也有所限制，因此玻璃纖維含量多時殼9和分離板 5就不會混練，難以獲得充分的熔焊強度。該狀況下，轉 熔焊就成爲有效的熔焊方法。 旋轉熔焊是將軸芯爲中心，利用一方爲固定，一方形 成旋轉造成的磨擦熱使樹脂熔化結合的方法。 第6圖中圖示著旋轉熔焊時的橫剖面圖，第7圖中圖 示著熔焊部旋轉熔焊前的狀態橫剖面圖，第8圖中圖示著 熔焊部旋轉熔焊後的狀態橫剖面圖。 第6圖中，號筒2〇是形成有對應著殻9表面凹凸形 狀的局部缺口 20a。該缺口 20a ’其形狀是形成於號筒20 旋轉時可和該號筒20成一體使殼9旋轉地嵌合著該殼9 凹凸形狀。如此一來，當號筒20和殼9 一起旋轉時，即 使熔焊部16的阻力增大，但號筒2 0和殼9不會滑脫，能 夠使殼9追隨著號筒2 0旋轉。分離板5側是隔著馬達1 固定在承接固定工具21，確實固定成不會隨著殻9的旋轉 而旋轉移動。 朝第6圖前頭符號C方向旋轉號筒2〇，使殻9與號 筒2〇 —起旋轉的同時，朝該圖箭頭符號D方向進行加壓 ，藉此嘁行烙知。如此一來，如第7圖所示，摩擦熱會產 生在殼熔焊部9b及分離板5b，使兩者熔化混練’藉此執 行第8圖所示的密封•固定。熔焊部16，因其熔化量大， -14- 200902856 所以玻璃纖維能夠充分混練結合達到充分的熔焊強度° 旋轉熔焊和超音波熔焊不同，並不是朝上下D方向振 動號筒2 0，而是以軸8爲中心一邊旋轉的同時，一邊加壓 達到指定高度就停止，所以熔焊中不會影響到第一軸承板 11。因此，不會有第一軸承板龜裂等不利狀況產生，能夠 使殻9和分離板5形成密封·固定。 旋轉熔焊，因是利用旋轉的摩擦熱進行熔焊，所以突 起9c是形成爲不同於超音波熔焊時的形狀。若是形成爲 超音波熔焊所示的如第2圖、第3圖、第5圖所示的形狀 時，則熔焊部爲點接觸或線接觸，因此接觸面積小而無法 產生充分的摩擦，導致突起9C難以熔化。 第9圖中圖示著適合旋轉熔焊的突起9c形狀。突起 9c，爲了確保接觸面積，即使是如第9(a)圖所不於突起 9的前端單純形成著平面22也是可行。不過’若接觸面積 太大，則會影響到本來爲熔焊部的殼熔焊部9b及分離板 熔焊部5b的熔焊，因此需要適當的尺寸。突起9前端平 面22的面積，會根據殻熔焊部9b及分離板熔焊部5b的 熔焊量而有所不同。 其他，如第9(b)圖所示’即使是中空圓筒狀的突起 9c還是能夠形成熔焊結合。 此外，無法獲得充分的摩擦熱時’也可考量採用可使 對應突起9 c的軸8的端面8 a的平面部表面粗糙度變粗的 手段。 -15- 200902856 (實施例4) 小型的泵浦時，軸8的直徑小’即使想要加大突起9 c 的接觸面積’但有礙於尺寸方面無法加大時’如第1 0圖 所示，可將突起9<:的前端形成爲半球狀。 另外，如第11 (a)圖所示，對應上述突起9c前端半 球狀將相對應的軸8的端面8a也設有可嵌合上述突起9c 前端半球狀的凹形狀半球狀部8b ’藉此兩者的凹凸形狀彼 此會形成接觸’如此一來就能夠使兩者的接觸面積比平面 還大。半球狀部8b是可在突起9c或軸8的端面8a的任 —方設置成凹凸。第11 (b)圖是圖示著於突起9c前端形 成有凹形狀的凹形狀部9e ’該凹形狀部9e可對應嵌合在 軸8的端面8 a所形成的凸形狀之凸形狀部8 c的例子。 此外，實施例4除了上述凹凸形狀的嵌合以外，還能 夠加以組合使用可使上述軸8的端面8a的平面部表面粗 糙度變粗的手段。 [產業上之可利用性] 根據本發明時，藉由在殼軸支撐的中央附近設置突起 ’即使號筒的振動傳播至殻軸支撐導致其上下振動，但因 突起的一部份是熔化結合在軸的前端因此能夠吸收振能量 ，能夠防止來自於該殼軸支撐的碰撞造成第一軸承板龜裂 【圖式簡單說明】 -16 - 200902856 第1圖爲實施例1的泵浦橫剖面圖。 第2圖爲表示實施例1的殼軸支撐一例透視圖。 第3圖爲表示實施例1的殼軸支撐另一例透視圖。 第4圖爲實施例1的熔焊後殻軸支撐部橫剖面圖。 第5 ( a )圖爲表示實施例2的殼軸支撐一例透視圖， 第5(b)圖爲表示實施例2的殻軸支撐另一例透視圖。 第6圖爲利用旋轉熔焊使殼和分離板形成固定的例子 該栗熔焊狀態的橫剖面圖。 第7圖爲表示旋轉熔焊前的殼和分離板的熔焊部份要 部放大剖面圖。 第8圖爲表示旋轉熔焊後的殼和分離板的熔焊部份要 部放大剖面圖。 第9(a)圖爲表示突起前端成平面的殼軸支撐一例透 視圖，第9(b)圖爲表示突起前端成圓筒狀的殼軸支撐一 例透視圖。 第10圖爲表示突起前端成半球狀的殼軸支撐一例透 視圖。 第1 1 ( a )圖爲對應半球狀的突起前端形狀而將軸的 端面形成可和該突起前端形狀嵌合的凹形狀時的要部放大 剖面，第1 1 ( b )圖爲對應突起前端形成爲凹形狀而將軸 的端面形成可和該突起前端形狀嵌合的凸形狀時的要部放 大剖面。 第1 2圖爲習知泵浦的橫剖面圖。 第1 3圖爲具有熔焊構造的習知泵浦熔焊狀態橫剖面 -17- 200902856 圖。 第1 4圖爲溶焊前狀態的熔焊部橫剖面圖。 第1 5圖爲熔焊後狀態的熔焊部橫剖面圖。 【主要元件符號說明】 1 :馬達 2 :泵浦 3 :繞組 4 :控制部 5 :分離板 5 a :分離板軸支撐 5 b ·‘分離板溶焊部 6 :永久磁鐵 7 :葉輪 8 :軸 8 a ϋ而面 8b :凹形狀半球狀部 8c :凸形狀部 9 :殼 9a :殼軸支撐 9b :殼熔焊部 9c :突起 9d :殼軸支撐底部 9e :凹形狀的凹形狀部 -18 - 200902856 1 〇 :軸承 1 1 :第一軸承板 1 1 a :中心孔 1 2 :第二軸承板 1 2 a :中心孔 1 3 :緩衝材 1 4 :襯墊 1 5 :螺絲 1 6 :溶焊部 20 :號筒 2 0 a :局部缺口 21 :承接固定工具 22 :平面 A :吸入方向 B :吐出方向 C :旋轉方向 D :加壓方向 f、g :空隙BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a water-sliding bearing pump in which a shaft is centered so that an impeller is rotatably supported by a bearing fixed at a center, and a sliding water is formed by lubrication of circulating water. [Prior Art] The pumping of the so-called underwater plain bearing pump has a sliding portion which generates a pump by the rotational sliding of the bearing and the bearing plate. An example of the underwater plain bearing pump is a water sliding bearing pump having a structure disclosed in Japanese Patent No. 3099434 and Japanese Patent Laid-Open No. Hei. No. 2006-200427. Such a pump is represented by a so-called magnetic pump of Patent Document 1 or a so-called DC brushless pump of Patent Document 2. The conventional pump is described using the D C brushless pump of Fig. 2 . In the pump 2, a magnetic field is generated by the motor 1 having the coil 3 in which the coil is disposed, and the control unit 4 controls the generation of the magnetic field. In order to follow this generated magnetic field, the impeller 7 to which the permanent magnet 6 is fixed via the separating plate 5 is rotatably supported by the shaft 8. As a result, the suction and drainage of the circulating water can be performed following the rotation of the impeller 7 of the rotating magnetic field. The shaft 8 is fixed by a separating plate shaft support 5a provided at the center of the separating plate 5 and a shell shaft support 9a provided at the center of the casing 9. In order to support the impeller 7 to be freely rotatable relative to the shaft 8, the bearing 1 固定 is fixed to the center of the impeller 7, and the shaft 8 and the bearing 10 are formed to form a rotational slip. Further, between the two end faces of the bearing 1 -4 - 4 - 200902856 and the shell shaft support 9a and the split plate shaft support 5a, the first bearing plate 1 1 and the second bearing plate 1 2 are respectively provided by performing the thrust Rotate the direction of rotation. Only the end faces are formed in a d shape on both sides of the shaft 8, thereby preventing the rotation of the first bearing plate 11 and the second bearing plate 12. Next, the pump is directed to the sum of the total length of the bearing 10 and the thicknesses of the first bearing plate 11 and the second bearing plate 12 so as to retain a slight gap f between the housing shaft support 9a and the separating plate shaft support 5a. Considering, avoiding the assembly drop causes the impeller 7 to lock. Further, between the end surface of the shaft 8 and the bottom support bottom portion 9d, a gap g for assembling the drop absorption is also provided. Since the accumulation of the dimensional drop of the part is concentrated in the gap g, a number of size drops are generated. In this pump, as the rotation of the impeller 7 is stopped, a force in the thrust direction is applied to the shaft 8. Therefore, the shaft 8 is gradually moved toward the casing 9 by the amount of movement of the gap g. As a result, the pressing of the second bearing plate 2 disappears. The second bearing plate 12 is in a free state, and an abnormal sound may occur due to the flow of water. In order to prevent this, the cushioning material 13 formed by compressing an elastic body such as ruthenium rubber is inserted into the gap g, whereby the floating of the shaft 8 is pressed. The casing 9 and the separating plate 5 are formed with a ring of 0 or a gasket 14 to form a seal to prevent leakage of circulating water in the chestnut chamber. The casing 9 and the separating plate 5 are generally fixed by screws 15. Next, the operation of the above-described pump will be described. With the rotating magnetic field generated by the winding 3, the impeller 7 follows the rotation by the attraction repulsion which forms the fixed permanent magnet 6. Thereby, a pumping action is generated, and the circulating water is sucked from the direction of the arrow A, and the circulating water is discharged in the direction of the arrow B. -5- 200902856 At this time, the differential pressure between A and B causes the impeller 7 to be pushed toward the side of the casing 9, so that the end faces of the first bearing plate 11 and the bearing 1 are rotationally slid. The sliding of the bearing 10 and the second bearing 12 hardly occurs, and is limited to an instant when the start is stopped, or when the abnormal operation such as the dry operation of the pump is operated without circulating water. Therefore, in general, the material of the first bearing plate 1 1 is ceramic. The material of the second bearing plate 1 2 is often made of SUS (stainless steel). A sliding film of the shaft 8 and the bearing 10, and the sliding surfaces between the two vane surfaces of the bearing 10 and the first bearing plate 11 and the second bearing plate 12 are formed with a water film of circulating water, which is separated by a water film. Make the two have a good slip. SUMMARY OF THE INVENTION The case 9 and the separating plate 5 are generally fixed by a ring or a gasket as described above, but if the rubber is not used due to the use conditions and environmental conditions, or the purpose of reducing the cost is to abandon the use of the 0 ring. Or when the gasket is used, it is welded and fixed. Fig. 13 is a cross-sectional view showing a welded state in which the casing 9 and the separating plate 5 are joined by fusion welding. Fig. 14 is a cross-sectional view of the welded portion in the state before welding, and Fig. 15 is a cross-sectional view of the welded portion 16 after welding. At the time of fusion welding, the pump 2 is disposed above the receiving fixing tool 21, and the horn 20 is lowered. The horn 20 is pressed against the upper surface of the welded portion 16, and ultrasonic waves or vibrations are generated by the horn 20 to propagate the kinetic energy to the shell welded portion 9b and the split plate welded portion 5b. At this time, the kinetic energy is concentrated on the fusion-welded portion to be converted into thermal energy, and the fusion-welded portion 16 formed of the resin is thus melted to bond the casing 9 and the separation -6-200902856 plate 5. The portion to be melted is provided with small projections or edges to ensure a shape that is easily melted. The vibration of the height 20 is basically propagated to the portion of the horn 2 that is pressed to weld the portion, but there is an overall vibrational propagation in one portion. Therefore, when the horn 20 is pressed against the casing 9, the vibration also propagates to the casing shaft support 9a' disposed near the center of the casing 9, causing the casing shaft support 9a to vibrate up and down. The cushioning material 13 is disposed between the bottom of the shell shaft support bottom 9d and the end surface of the shaft 8, but since it is an elastic body, the up and down vibration of the shell shaft support 9a cannot be suppressed. Therefore, the first bearing plate 11 is intermittently collided by the shell shaft support 9a, so that a crack or the like is generated. Accordingly, the present invention has an object of providing an underwater water that can prevent the first bearing plate from being cracked even if the vibration of the horn propagates to the shell shaft to cause the shell shaft support to vibrate up and down. Sliding bearing pump. An underwater sliding bearing pump according to another aspect of the present invention includes: an impeller for circulating water suction and discharge; a shaft for fixing the impeller; and a bearing fixed to the impeller to support the impeller so as to be rotatable relative to a shaft; a casing and a separating plate that can form a pump chamber, an outer casing that is disposed at a center of the casing and that fixes one end of the shaft; and a center of the separating plate that fixes the other end side of the shaft The separating plate shaft support is configured to form a seal by the welding and the above-mentioned separating plate and the separating plate, and to form the pump chamber, and a protrusion is provided at the bottom of the shell shaft support. [Best Mode for Carrying Out the Invention] According to an embodiment of the present invention, an underwater sliding bearing pump includes: an impeller for circulating water suction and discharge; a shaft for fixing the impeller; and the impeller supported by the impeller a bearing that is freely rotatable relative to the shaft; a casing and a separating plate that accommodates the impeller to form a pump chamber; a casing shaft that is disposed at a center of the casing to fix one end of the shaft; and is disposed at a center of the separating plate, The other end side of the shaft is supported by a fixed separating plate shaft, and the shell and the separating plate are sealed and fixed by welding, and the pump chamber is formed thereby, and a protrusion is provided at a bottom portion of the shell shaft support. In this way, even if the welding vibration of the horn propagates to the shell shaft support to cause vibration, it is possible to absorb the vibration energy by a part of the protrusion being melted and coupled to the front end of the shaft, thereby preventing the collision from the shell shaft support. The first bearing plate is cracked. Further, since the shaft is melted and protruded along the gap having the difference, the shaft can be pressed by the zero fitting, so that the cushioning material for shaft floating suppression which is conventionally required can be eliminated. Further, in the embodiment of the present invention, the underwater sliding bearing pump is configured such that the projection is disposed at a center of the shell shaft support or at a position symmetrical with respect to the center. As described above, the protrusion is disposed at a center of the shell shaft support or at a position symmetrical with respect to the center, so that the protrusion can be welded (melted) on the shaft in a balanced manner, so that the shell shaft support has no stress residual or does not dissolve the originally required. The weld has an adverse effect. Further, in the embodiment of the present invention, the underwater plain bearing pump is configured to be -8-200902856. The end surface of the shaft is fitted to the end surface of the shaft before the projection formed on the bottom of the shell shaft support. shape. As described above, in correspondence with the projection formed on the bottom of the shell shaft support, a convex shape that can be fitted to the tip end of the projection is provided on the end surface of the shaft, and the surface area of the fitting portion can be ensured to be larger, and the effect is melted. In this way, the shaft can be pressed with zero twist, due to the cushioning material. Further, in the embodiment of the present invention, the underwater sliding bearing is formed by sealing the casing and the separating plate by spin welding to form the chestnut chamber. As described above, by the use of the rotary welding, the movement of the welding can be performed in the direction of rotation. Therefore, the casing and the separating plate can be sealed and fixed without the bearing plate. In addition, when the glass content of the resin is too large, if the ultrasonic wave is melted to the glass fiber and the welded portion cannot be expected to have sufficient strength, the rotary welding can sufficiently weld the shell and the separator to be welded, as desired. strength. [Embodiment] Hereinafter, the best mode for carrying out the invention will be described in more detail with reference to the accompanying drawings. Here, in the drawings, the same members as those of the conventional pump are the reference numerals, and the repeated description is omitted. In addition, the description here is based on the shape of the end shape, the shape of the concave shape of the front end of the concave shape, or the fact that the protrusion has such a reusable weight. The fixing is not affected by the up and down vibration, and the influence of the first welding is affected by the use of this. The same is a description of the preferred embodiment of the invention of the present invention, and the present invention is not limited to the embodiment (the embodiment). (Embodiment 1) FIG. 1 is a cross-sectional view of a pump according to Embodiment 1 of the present invention, and FIG. 2 and Table 3 are perspective views of a housing shaft support according to Embodiment 1 of the present invention, and FIG. 4 is a first embodiment of the present invention. A cross-sectional view of the support shaft of the welded shell. The pump of this embodiment is a water-sliding bearing pump in which the shaft is centered so that the impeller is supported by the fixed bearing in the center to be freely rotated, and the lubricating water is used to form a sliding water. The pump is used, for example, in a fuel cell device or a heat pump device or various cooling systems. The pumped motor 1 is provided with a winding 3 which is already equipped with a coil. The motor 1 generates a rotating magnetic field by being energized to the winding 3, and receives a signal from the position detecting unit (not shown) to control the rotating magnetic field by the signal control unit 4. The outer periphery of the pumping portion 2 is composed of a casing 9 and a separator 5, and the welding portion 16 performs fixing and sealing. The motor 1 and the pump portion 2 are separated by a partition plate 5 to be sealed. A split plate shaft support 5a for fixing the other end side portion of the shaft 8 is provided at the center of the separating plate 5, and a shell shaft support 9a for fixing the shaft 8-end side portion is provided at the center of the casing 9. Both ends of the shaft 8 are formed in a substantially D-shaped cross section. Here, the second bearing plate 12 having a D shape at one end of the shaft 8 via the center hole 12a is fixed to the separating plate shaft support 5a' to prevent the rotation of the shaft 8 and prevent the second bearing plate 12 from floating. Further, the other end (the other end) of the shaft 8 is similarly fixed to the above-described casing 9 via a first bearing plate 11 having a D shape with a center hole -10-200902856 lla, thereby preventing the rotation of the shaft 8. The impeller 7 is supported to be freely rotatable relative to the shaft 8, and a bearing 1 is disposed between the first bearing plate 1 1 and the second bearing plate 1 2 . At this time, the assembly drop does not cause the bearing 1 to be locked in relation to the total length of the bearing 10 and the sum of the thicknesses of the first bearing plate 1 1 and the second bearing plate 1 2, and the housing shaft 9 a and the separating plate There is a slight gap f between the shaft supports 5a. Further, between the one end of the shaft 8 and the bottom portion of the shaft support 9d, a slight gap g is formed in consideration of the assembly drop. In the underwater sliding bearing pump of the present embodiment, the permanent magnet 6 fixed to the impeller 7 is attracted and repelled by the rotating magnetic field generated by energization of the winding 3, whereby the impeller 7 is rotated about the shaft 8. Since the bearing 1 is fixed to the center of the impeller 7, the bearing 1 and the shaft 8 are rotationally slid. Generally, the material of the shaft 8 is formed of SUS (stainless steel) or ceramic. On the other hand, the bearing 10 is mostly formed of a resin having carbon or slidability. The first bearing plate 1 1 and the second bearing plate 12 are formed of SUS or ceramic in the same manner as the shaft 8. Then, the underwater sliding bearing pump generates a pumping action in accordance with the rotation of the impeller 7, and the circulating water is sucked from the suction port A and discharged from the discharge port B. At this time, the impeller 7 is pushed to the side of the casing 9 in accordance with the pressure difference between the suction and the discharge to form a rotational slip. That is, the impeller 7 is rotationally slid in the thrust direction (the axial direction of the shaft 8) in a state where the end surface of the bearing 1 接触 is in contact with the first bearing plate 11 . The higher the pumping function, the greater the pressure to be pushed and the higher the sliding resistance. -11 - 200902856 Therefore, in many cases, the first bearing plate 11 is formed of ceramic in order to reduce the sliding resistance and achieve good sliding. Therefore, the first bearing plate 1 1 may be cracked when a strong collision from the impeller 7 is applied. The sliding portion of the outer diameter portion of the shaft 8 and the inner diameter portion of the bearing 10, and the sliding surfaces of the end faces of the bearing 10 and the first bearing plate 1 1 or the second bearing plate 12 are respectively formed with circulating water. The water film can slide both well through the water film. Fig. 2 is a view showing the shell shaft support 9a before assembly. In the center of the bottom portion 9a of the shell shaft support 9a, a conical projection 9c projecting upward is provided. The projection 9c does not have to be formed at one center in the center. As shown in Fig. 3, a plurality of the projections 9c may be disposed at positions symmetrical with respect to the center. However, since the end face of the shaft 8 has a D shape in the cross section as described above so as to be partially cornered, the projection 9c needs to be formed in a symmetrical arrangement in consideration of the notch portion. The protrusion 9c is disposed at a position symmetrical with respect to the center, and the stress does not remain in the shell shaft support 9a during the welding and after the welding, and the uniform melting of the protrusion 9c enables the vibration to be equally transmitted to the original separation plate 5 A good fusion bonding is achieved with the welded portion 16 of the shell 9. As described above, the projection 9c welded to the end face of the shaft 8 is disposed in the underwater sliding bearing pump of the casing shaft support 9a, and when the separation plate 5 and the welded portion 16 of the casing 9 are fused, the vibration energy is transmitted to the welded portion. 16. As shown in Figs. 14 and 15, the shell welded portion 9b and the split plate welded portion 5b are melted to form a bond. At this time, the local vibration energy also propagates to the shell shaft support 9a. The shell shaft support 9 a will vibrate up and down due to the vibration energy. However, at this time, the vibration energy is converted into heat energy by being concentrated on the front end of the projection 9c, as shown in Fig. 4-12-200902856, the front end of the projection 9c is melted and bonded to the end surface of the shaft 8. As a result, the shell shaft support 9a' is suppressed from being vibrated by the end surface of the shaft 8 so that the upper and lower vibrations are suppressed, i.e., does not collide with the first bearing plate 11 to cause a good melt bond. Further, as shown in Fig. 4, the gap g between the bottom portion of the shell shaft support 9d and the end surface of the shaft 8 is a portion of the projection 9c remaining, and the end face of the shaft 8 can be pressed with a zero fitting, so that no buffer is required. The pushing of the material. Therefore, even if the size of the gap g is changed due to the difference in the finished product, the melting length of the projection 9c can be adjusted, and the shaft 8 can be surely pressed. (Embodiment 2) Embodiment 1 is that the protrusion 9c formed on the bottom portion 9d of the shell shaft support has a conical shape, but the shape of the protrusion 9c is not limited to a conical shape, as shown in Fig. 5(a) and 5( b) As shown in the figure, the shape of the protrusion 9c may be substantially triangular in cross section. The ribs may be one or plural, and in addition, in a plurality of cases, it may be considered that the notched portion of the shaft 8 is formed in a symmetrical position (Example 3), in Embodiment 1 or Embodiment 2, in particular The shape of the protrusion suitable for ultrasonic welding is formed so that the energy concentrates at one point to cause the protrusion to melt toward the end surface. Therefore, the shape of the front end is formed into an acute angle, and the welded portion is formed in a shape of a point contact or a line contact. In recent years, based on the requirement of pump water pressure increase, the resin material -13-200902856 contains glass fiber to increase the resin strength, so there is a tendency to use glass-reinforced grade resin. The welding time during ultrasonic welding is short and the size of the welded portion 16 is limited before and after 1 second. Therefore, when the glass fiber content is high, the shell 9 and the separating plate 5 are not kneaded, and it is difficult to obtain sufficient welding strength. . In this case, the fusion welding becomes an effective fusion welding method. Rotary welding is a method in which the core is centered and the resin is melted and bonded by the frictional heat caused by the rotation of one square. Fig. 6 is a cross-sectional view showing the state of the rotary welding, and Fig. 7 is a cross-sectional view showing the state before the welding of the welding portion, and Fig. 8 is a view showing the state after the welding of the welding portion. State cross section. In Fig. 6, the horn 2 is formed with a partial notch 20a corresponding to the uneven shape of the surface of the casing 9. The notch 20a' has a shape that is formed integrally with the horn 20 when the horn 20 is rotated, and the casing 9 is rotatably fitted to the casing 9 in a concavo-convex shape. As a result, when the horn 20 and the casing 9 are rotated together, even if the resistance of the welded portion 16 is increased, the horn 20 and the casing 9 are not slipped, and the casing 9 can be rotated following the horn 20. The side of the separating plate 5 is fixed to the receiving fixing tool 21 via the motor 1, and is fixed so as not to rotate in rotation with the rotation of the casing 9. The horn 2 is rotated in the direction of the front symbol C in the sixth drawing, and the casing 9 and the horn 2 are rotated together, and the direction is indicated by the arrow D in the figure. As a result, as shown in Fig. 7, frictional heat is generated in the shell welded portion 9b and the separating plate 5b, and the two are melted and kneaded, thereby performing the sealing and fixing shown in Fig. 8. The welded portion 16 has a large amount of melting, -14-200902856, so that the glass fiber can be sufficiently kneaded to achieve sufficient welding strength. The rotary welding and the ultrasonic welding are different, and the horn is not vibrated in the upper and lower directions D, On the other hand, while rotating around the shaft 8, the pressure is stopped when the pressure reaches a predetermined height, so that the first bearing plate 11 is not affected during welding. Therefore, there is no disadvantage such as cracking of the first bearing plate, and the casing 9 and the separating plate 5 can be sealed and fixed. Since the spin welding is performed by the frictional heat of the rotation, the projection 9c is formed into a shape different from that of the ultrasonic welding. When the shape shown in FIG. 2, FIG. 3, and FIG. 5 is formed by ultrasonic welding, the welded portion is in point contact or line contact, so that the contact area is small and sufficient friction cannot be generated. This causes the protrusion 9C to be difficult to melt. The shape of the projection 9c suitable for the spin welding is illustrated in Fig. 9. In order to secure the contact area, it is also possible to form the flat surface 22 simply by the projections 9c as shown in Fig. 9(a). However, if the contact area is too large, the welding of the shell welded portion 9b and the separator welded portion 5b which are originally the welded portion is affected, and therefore an appropriate size is required. The area of the front end flat surface 22 of the projection 9 varies depending on the amount of welding of the shell welded portion 9b and the split plate welded portion 5b. Others, as shown in Fig. 9(b), even a hollow cylindrical projection 9c can form a fusion bond. Further, when sufficient frictional heat cannot be obtained, a means for making the surface roughness of the flat surface portion of the end face 8a of the shaft 8 corresponding to the projection 9c thick can be considered. -15- 200902856 (Embodiment 4) When the pump is small, the diameter of the shaft 8 is small 'even if it is desired to increase the contact area of the projection 9 c', but it is not possible to increase the size. The front end of the protrusion 9 <: can be formed in a hemispherical shape. Further, as shown in Fig. 11(a), the end surface 8a of the corresponding shaft 8 corresponding to the tip end of the projection 9c is also provided with a concave hemispherical portion 8b which can fit the hemispherical shape of the tip end of the projection 9c. The concave and convex shapes of the two form a contact with each other' such that the contact area between the two can be made larger than the plane. The hemispherical portion 8b is provided with irregularities on either of the projections 9c or the end faces 8a of the shaft 8. Fig. 11(b) is a view showing a concave portion 9e having a concave shape formed at the tip end of the projection 9c. The concave portion 9e can correspond to the convex shape portion 8 formed by the end surface 8a of the shaft 8 An example of c. Further, in the fourth embodiment, in addition to the fitting of the uneven shape described above, a means for making the surface roughness of the flat surface portion of the end surface 8a of the shaft 8 thick can be used in combination. [Industrial Applicability] According to the present invention, by providing a protrusion near the center of the shell shaft support, even if the vibration of the horn propagates to the shell shaft support, it vibrates up and down, but a part of the protrusion is melted and bonded. The front end of the shaft can thus absorb the vibration energy, and the first bearing plate crack can be prevented from being caused by the collision of the shell shaft support. [FIG. 1] FIG. 1 is a pump cross-sectional view of the first embodiment. Fig. 2 is a perspective view showing an example of the shell shaft support of the first embodiment. Fig. 3 is a perspective view showing another example of the shell shaft support of the first embodiment. Fig. 4 is a cross-sectional view showing the support portion of the shell shaft after welding in the first embodiment. Fig. 5(a) is a perspective view showing an example of the shell shaft support of the embodiment 2, and Fig. 5(b) is a perspective view showing another example of the shell shaft support of the second embodiment. Fig. 6 is a cross-sectional view showing a state in which the shell and the separator are fixed by spin welding. Figure 7 is an enlarged cross-sectional view showing the welded portion of the shell and the separator before the spin-welding. Fig. 8 is an enlarged cross-sectional view showing the welded portion of the shell and the separator after the spin-welding. Fig. 9(a) is a perspective view showing an example of a shell shaft support in which the tip end of the projection is flat, and Fig. 9(b) is a perspective view showing a shell shaft support in which the tip end of the projection is cylindrical. Fig. 10 is a perspective view showing an example of a shell shaft support in which the tip end of the projection is hemispherical. The first 1 ( a ) is an enlarged cross section of the main part when the end surface of the shaft is formed in a concave shape that fits the shape of the tip end of the protrusion corresponding to the shape of the tip end of the hemispherical projection, and the first 1 (b) diagram corresponds to the front end of the protrusion. When the end surface of the shaft is formed into a concave shape and the end surface of the shaft is formed into a convex shape that can be fitted to the tip end shape of the protrusion, an enlarged cross section of the main portion is formed. Figure 12 is a cross-sectional view of a conventional pump. Figure 13 is a cross-section of a conventional pump fusion state with a welded construction -17- 200902856. Fig. 14 is a cross-sectional view of the welded portion before the welding. Fig. 15 is a cross-sectional view of the welded portion in the state after welding. [Description of main component symbols] 1 : Motor 2 : Pump 3 : Winding 4 : Control part 5 : Separation plate 5 a : Separation plate shaft support 5 b · 'Separation plate welding part 6 : Permanent magnet 7 : Impeller 8 : Axis 8 a ϋ face 8b: concave shape hemispherical portion 8c: convex shape portion 9: case 9a: case shaft support 9b: case weld portion 9c: protrusion 9d: case shaft support bottom portion 9e: concave shape concave portion -18 - 200902856 1 〇: Bearing 1 1 : First bearing plate 1 1 a : Center hole 1 2 : Second bearing plate 1 2 a : Center hole 1 3 : Cushioning material 1 4 : Liner 1 5 : Screw 1 6 : Dissolving Weld portion 20: horn 2 0 a : partial notch 21 : receiving fixing tool 22 : plane A : suction direction B : discharge direction C : direction of rotation D : pressure direction f, g : gap