201113447 όζτΐόριΐ 六、發明説明： 【發明所屬之技術領域】 本發明有關於-魏持器、深溝球轴承以及密封轴 承0 【先前技術】 軸承（深溝球）如圖15所示，具備内周形成著圓弧 狀外側軌道面1之外環2、相戦著_賴執道面i 相向的圓弧狀内側軌道面3之内環4、配置在内環4與外 環2之間的保持器5、以及由保持器5支持而轉動自由的 多個滾珠Bo。 保持器5如圖16所示，由具有沿著圓周方向以規定 間隔配設的半球狀凸出部6之2片環狀保持板W組合而 成。亦即，各環狀保持板7由沿著_方向配㈣上述半 球狀凸出部6、相鄰的半球狀凸出部6間的平坦部8所構 成。於經組合的狀態下，平坦部8、8相^合，且該平坦 8、8介隔鉚釘等緊輯9而連結。因此，由各半球狀凸出 «Μ、6^目對向，而形絲狀滾珠嵌合部（套座）。 先刖’存在有肋提高鱗器與滚珠㈣滑狀 專利文獻1)，或者主動供排潤滑油，以提高轴承内 油的流動性者（專利文獻2)等。 y /月 上述專利文獻1所揭示者是在套座的内周側 凹部’具有制㈣存躲麵屬…卩巾賴 藉 =能。藉此，提高套座内的潤滑劑的保持量，從 保持器與滾珠之間的潤滑狀態。 间 201113447 32723pif 而且，上述專利文獻2所揭示者是在套 ::内別連通至外環與保持器之二= 持器之間的轴承空間側，= 因此然用而於===齒輪的磨損粉等異物。 備對形成於其内外環間的軸:空間===承’具 構件’藉㈣止異物侵人至軸承内進心封的接觸型密封 :: 所揭示者是對密封凸緣部所滑動接觸^)。該專利文獻3 環的密封溝的内壁面實施珠擊處、例如軸承旋轉 面的最大粗錢Ry降低至小^ Gt阶一)’使接觸 密封扭矩。 、J以《1。藉此，降低 [先行技術文獻] [專利文獻] [專利文獻1]曰本專利早期公 號公報 j早翊A開公報特開2003-13962 號公^專利文獻2]日本專利早期公開公報特__觸 號公Γ㈣3]日本專利早期公開公報特開丽-画8 201113447 近年來’對汽車用軸承，_料費改善或環境問題而 要求降低扭矩。產生於軸承的扭矩之中主要由保持器 的扭矩中，鋼珠（滾珠）對油（潤滑料潤滑材料j 切阻力佔較多的比例。 d 繼而，該剪切阻力幾乎均為剪切形成於套座内徑面與 套座内的滾珠之間的油膜時的阻力。而且，當套座由沿^ ，珠形狀般的單-曲面形成時，因潤滑劑將通過滾珠與覆 蓋滾珠的保持器套座内侧的細微間隙之故，而產生阻力， 從而成為使扭矩增大的主要原因之一。 上述專利文獻1所揭示者是以附屬凹部作為潤滑劑蓄 積處，在該附屬凹部中儲存潤㈣。而且，專利文獻2所 揭示者’並未使潤滑劑通過細微間隙時的阻力降低。亦即， 在此類軸承中，無法兼顧潤滑劑通過時的阻力減少、與滾 珠運動時所剪切的油膜量減少。因此，先前即便於套座的 内徑面形成有凹部，亦無法實現扭矩降低。 而且’如同專利文獻3的密封軸承等般，若減小接觸 面的表面粗糙絲降低密封扭矩，則此扭崎低效果存在 =度。若製成非賴密封’卿可使密封扭矩為零，但將 =封間隙縮小至Μ夠防止上述齒輪磨損粉等異物之侵入的 ^度’則將因組裝誤差、加I誤差、熱膨脹差等之故，而 難以實現。 【發明内容】 本發明是鑒於上述課題而提供一種能夠實現扭矩降 低的保持如及使时域__縣球轴承，進而提 6 201113447 32723pif 可防止異物侵入轴承内且使密封扭矩充分降低的密 圓周球軸承用保持器，由具有沿著 接使得該套座f與滾==== :::上，=與=〇==:: :無==)::低的面積小於‘ 非接^n、r的轉11，可藉由在料相“設置滾珠 二，來減小潤滑劑通過套座内部時的阻力。而且， 置滾珠非接觸部，來減小形成於滾珠與套座之間 、1 、里於該情形時，若滾珠非接觸部過小，則所剪切 的油膜量的減少量亦會變小’導致無法實現扭矩降低。而 且’若滾珠非接觸部過大’則形成於滾珠與套座之 膜量將變得過小，從而損及滾珠的順滑轉動。因此，可藉 由如本發明般’ a定滾珠非接觸部的範圍，來兼顧潤滑劑 通過套座内部時的阻力降低與所剪切的油膜量減少。 在半球狀凸出部中，可藉由於滾珠相向之反面形成朝 滾珠相反侧突出的凸部，而在滾珠相向面設置朝滾珠相 側凹陷的凹部，並將該凹部作為上述滾珠非接觸部，或者 在半球狀凸出部設置狹縫，並將該狹縫作為上述滾珠非接 201113447 觸部。 較好的是，滾珠非接觸部，血 轴承外徑側。 ，、展珠的郎圓相比配置在 本發明的保持器可為金屬制 者、金屬製之由鱗造所成型者、$ t由衝壓加工所成型 型者。而且，本發明的保持器亦可出成型所成 與樹脂製均可）所成型者。D為由切跡工（金屬製 本發明的深溝球軸承具備：在 的外環、在外周形成有内側軌道成f卜侧軌道面 與外侧軌道面之間轉動的多個滾珠:以 環之間的上祕持[ 及崎在内每與外 5發：的选封軸承’在—對軌道環所相向的軌道面 有經由保持器所保持的多個轉動體，且 成t上述一對軌道環間的軸承空間進行密封的密封L 上=密雜权舰在於：上職封齡是基端固定在任 =的軌道環，且密封凸緣部與另—方的軌道環相接的接 觸在封’至少密封凸緣部的前端材質為高磨損材，其 承在旋轉狀態下使㈣磨損成轉接職封，或者成為接 觸壓顯示為零之程度的輕微接觸，且該密封轴承中的保持 器中使用上述本發明的保持器。再者，此說明書中所謂之 「向磨損材」表示易於產生磨損的材質。 根據此構成，由於使密封構件的至少密封凸緣部的前 端材質為上述高磨損材.，因此，運轉初期曾為接觸型的密 封構件，會因磨損而在例如運轉開始後的早期變成非接觸 8 201113447 32723pif 之程 或者贿損，而變雜顧顯示為零 於該發明中，可使上述密封構件 體或前端為麵贿封餅的料部於_ 2的整 質即高相材部。㈣定為可獲得適當的磨知的材 i述高磨損材可為橡膠材即高磨損橡騎，或者亦可 、不織 向接觸型’村為徑向接翻。例如祕可為軸 為樹脂材。糊軸，糾 :=:ί該發明中，上述密封=:=、不織 ====相，=== 對相向的㈣環為如的仰成為絲封凸緣部 在該發明中，亦可於上述密封構件 封構件吸附於上述另一方之:】防=， 吸附機構為例如設於密封 。使該防 於設置接觸式密遞m的紅用狹缝。 降低，密封:::=道== :會損材料，但直至密封二 [發明之效果] 本發明的保持器 Γ二二觸雄、封相同地產生吸附作用。 可藉由設定滾珠非接觸部的範圍 201113447 32723pif 3=滑劑通過套座内部時的阻力降低與所剪切的油膜 滾珠非接觸部可藉由在滾珠相向面 郎圓相比配置在軸承外徑側，則可降低圓周速率 南的，置上的剪切阻力，從而能夠更敎地實現扭矩降低。 ㈣保持器整體形狀相對簡單，無論金屬製抑或 疋樹月曰襄均施可靠形成。而且，就成型方法而言 屬製’則可利用衝屢加工或鑄造而成型，若為樹脂製則可 利用射出·而成型’故可先前以來f遍伽的各 成型方法來成型，從而能夠實現低成本化。 ， 因此’可實現扭矩的降低，若使用該保 於汽車，則可在燃料費改善的基礎上實現環保之=承用 本發明的密封軸承中，運轉初期為接觸型的密封構 =，會因磨損而在例如運轉開始後的早期變成非接觸型的 选封構件。或者因磨損’而變成接觸軸示為零的程度 輕微接觸。因此’可充分降低密封扭矩。而且，合因: 磨損，而在密封凸緣部與旋轉環之間形成作為最^觸 密封間隙的細微間隙，或者成為如上所逃的輕微接觸。因 此’雖潤滑油能夠通過，但可防止影_承壽命的大奸 異物侵入。其結果，可實現防止異物_ i 分降低密封扭矩。 兄 而且’藉由設置上述狹縫等防吸附機構，而使密封構 件磨損為止___附得以防止’從而避免扭矩增加。 201113447 32723pif 為讓本發明之上述特徵和優點 舉實施例，並配合所關式作詳 下文特 【實施方式】 如下。 圖1表示使用有第！實施形態的 持幻的軸承(深溝球軸承)。該球軸承=承用保 有圓弧狀外側執道面（滚動面）u的外、 ，周形成 =該外難道面u相向_遺_軌、1周= 13的内環14、收納在外側執道面u與内側：道】t ) 的多個滾珠16、支持滾珠16轉動自由 之間 、以及安裝在外環12的軸向端部的密封餐器 等承可稱為密封軸承，並用於汽車變速箱 内初，封裝有潤滑脂。該滾動軸承為以内環14為旋轉= 以外環12為固定環的内環旋轉型。 又 外％ 12、内壤14及滾珠16，由例如SUJ2等高 軸承鋼所構成，保持器15為例如冷軋鋼⑽u_ese Industrial Standard’日本工業規格）規格的spcc (n Plate Cold rolled C〇mmercia卜冷軋低碳鋼）系列等）的帶 ，衝壓加工品。保持器15如圖2與圖3所示，由具有沿著 圓周方向以規疋間隔配設的半球狀凸出部％之2片環狀保 持板27A、27B組合而成。亦即，各環狀保持板27八、276 由沿著圓周方向配設的半球狀凸出部26與相鄰之半球狀 凸出部26間的平坦部28所構成。於經組合的狀態下，平 坦部28、28相重合且該平坦部28、28介隔鉚釘等緊固 201113447 32723pif ϋ而連結。因此，由各半球狀凸出部26相對向，而形 成裱狀的滾珠嵌合部（套座）30。 接著’在該保持器15中’於套座3〇的滾珠相向面設 ，滚珠非接觸部。於該情形時，使該套座％中與滾珠 6接觸的接觸面積，與未設有滚珠非接觸部μ時與滚珠 Μ接觸的接觸面積相比減小15%〜3〇%乂 μ 亦即’藉由在滚珠相向之反面形成朝滾珠相反侧突出 的矩形凸部32，而在滾珠相向面設置朝滾珠相反侧凹陷的 起形凹部33，並以該凹部33形成滾珠非接觸部31。凸部 32如圖4所示，可採用各種類型者。 亦即，圖4Α所示之形狀Α中，將圓周方向長度l設 為LA，圓周方向寬度尺寸W設為WA。而且，圖4B所示 <形狀B中，將圓周方向長度L設為短於LA之LB，圓 确方向寬度尺寸W設為與WA相同之WB。 圖4C所示之形狀C中，將圓周方向長度L設為與LB 相同之LC，圓周方向寬度尺寸W設為大於WA之WC。 圖4D所示之形狀D中，將圓周方向長度L設為與LA相 同之LD，圓周方向寬度尺寸W設為與WA相同之WD。 圖4E所示之形狀E中，將圓周方向長度L設為與LB 相同之LE，圓周方向寬度尺寸W設為與WA相同之WE。 陶4F所示之形狀F中，將圓周方向長度L設為與LB相同 ，圓周方向寬度尺寸W設為與WA相同之WF。 圖4A所示之形狀A、圖4B所示之形狀B、及圖4F 所示之形狀F中，凸部32的中央線〇與滚珠16的節圓 12 201113447 32723pif' PCD 一致’凸部32配設在節圓PCD上。圖4C所示之形 狀C、圖4D所示之形狀D、及圖4E所示之形狀£中，凸 邻32的中央線〇’與滾珠16的節圓卩匸^相比向轴承外徑 侧偏移。於該情形時，圖4C所示之形狀c中，僅略微存 在該偏移，但圖4D所示之形狀D、圖4E所示之形狀£中， 則該偏移較大’使得-方的長邊與滾珠Μ的節圓一 致。 亦即’即便凸部32為圖4A、圖4B、圖4C、圖4D、 圖4E及圖4F所示的各種盤讲丨丨 部料滾珠非接觸部^成的凹 觸部31時與滾珠16接‘=^’=财_祕 即可。 觸的接觸面積相比減小15%〜30% 形（’既可錢轉方向尺寸長純向尺寸之矩 :長於旋轉方向尺寸之 尺寸長於經向尺寸，相反亦==可使旋轉方向 寸。進而，亦可為圓形。 m尺寸長於_方向尺 而且，如圖5A所示，密封構件17且 metal)18、被覆該芯金屬18之由 〃備心金屬（C〇re 成的被覆部（彈性構件”9。繼C膠材等所構 的外環U的内周面上的密封安 ^成於作為固定搭 著外周部。作輕轉細内環…在嵌封= 13 201113447 32723pif 内周部相針應的位置上，形成有包含圓周溝 的内周侧端上之密封凸緣部17:的前 Γ7且二支Γ、封構21的内面滑動接觸。密梅部 17a，/、有刀支為一股狀的兩個軸向凸緣部17 第】抽向凸緣部】7aa，沿著秘承的内侧，與内環14的密 封構21的内側壁面轴向接觸。第2轴向 的二 :轴承的外側’與内環14的密封溝21的外側壁面軸向： 密封凸緣部17a雖形成為上述彈性構件19的 ^ +，使具有兩個軸向凸緣部―、 成的古磨ϋι?:部的部分’為由易於磨損的材料所構 即’密封構件17㈣性構件19 的本體部19a、與該本體部i9a相連而設 二:」二所構成。該情形時，高磨損材部19b由 成，本體部19a由通常的橡膠材構成。密 —今㈣ 轉材硫化卿秘成，該硫化成形時， 附著於彈性構件19。構成高磨損材部19b的高 f 3膠材的種類’根據使用溫度或者與潤滑油的親和性 采送释。 U ^月中，可错由於滾珠相向面設置滾珠非接觸部 p署、Ϊ潤滑劑通過套座内部時的阻力降低。而且，可藉 = ί 非接觸部31 ’來使形成於滾珠16與套座30之 二1、里減少。於該情形時，若滾珠非接觸部過小，則 所寶刀的油膜量的減少量亦會變少，從而導致無法實現扭 201113447 32723pif 矩降低。而且·’紐柄翻部M過大，靡彡成於滾 之間的油膜量會變得過小，從而損及滾珠16 mi 可如如本發明般，設錢珠非接觸 部31的來兼顧潤滑劑通過套座内部時的阻力降低、 與所剪切的賴量減少。因此，便可實餘矩降低，若使 用有該球軸承用保持器的軸承用於汽車，則可在㈣費改 善的基礎上實現環保駕駛。 、 滾珠非接觸部31 ’可藉由於滾珠相向面設置 反侧凹陷的凹部33而可靠地形成。若滾珠非接觸部31， 與滚珠16的節圓相比配置在外徑侧，則可使圓周速率高的 位置上的剪切阻力降低，從而能夠穩定地降低扭矩。门 根據該實施形態的密封軸承，由於與作為旋轉軸的内 環14的密封溝21滑動接觸的密封構件17的密封凸緣部 17a的至少前端部，為易於產生磨損的材料（高磨損橡膠 材）的高磨損材部19b，因此，運轉初期曾為接觸型的密 封構件17,可藉由上述高磨損材部19b的磨損而在 始後的早期（運轉開始後數小時）如圖6中的放大剖面^ 所示’變成非接觸型的密封構件17，從而使密封扭矩充分 降低。例如，運轉開始之後，在油浴或者絕對乾燥條件下77, 60分鐘以内成為非接觸。作為運轉條件之一例，例如，轴 承型號：6207 ( JIS規格）之軸承，旋轉速度4,〇〇〇 rpm， 軸承溫度：30°C，旋轉扭矩為〇.〇75N.m左右，在油浴情 形時’使用礦物油系油於60分鐘以内成為非接觸。 藉此，便可使密封扭矩充分降低。其結果，可使轴承 15 201113447 32723pif 的升溫降低，故可祕與先前所㈣職帅比黏度更低 的潤滑油。而且，用於汽車的變速箱時，可有助於汽車的 省油化。 而且，由於可藉由高磨損材部19b的磨損，而使密封 構件17的密封凸緣部17a與⑽14的密封溝21之間形成 作為最佳迷路的細微間隙，因而，雖潤滑油可通過，但可 防止對軸承壽命造成影響的大粒徑異物之侵人。高磨損材 部19b的磨損，不必直至變成非接觸為止才結束，磨損至 成為接觸壓在f際應財顯示為零的程度的輕微接觸即 可。 再者，該實施形態中，例示了使用高磨損橡膠材作為 構成密封構件Π的高磨損材部1%之易於磨·材料的情 形’但作為易於磨損之材料的其它例，亦可使用樹脂材。 作為構成該高磨損材部19b的材料，除上述之外，亦可 固體潤滑材料、不織布、軟鋼等。而且，在該實施形態中， 如圖5B所不’可在密封構件17巾，設置通氣用的狹縫％ 等防吸附機構。 防吸附機構為防止因軸承的内部壓力降低而使密封 構件17吸附於内環14的機構。該情形時，於密封構件 的密封凸緣部17a的各轴向凸緣部心、㈣的前端，以 該些轴向凸緣部17aa、17ab與密封溝21的内面相接的狀 態，設置與轴承空間的内外方向達到通氣狀態的狹缝5〇。 狹縫50設於圓周方向的數個部位例如2個部位上。 如此般，由於設置狹、缝50等防吸附機構，故於高磨 201113447 32723pif …H <瑚間，防止密封椹 壓力降低之故，而吸附於内環14 =件Ο因軸承内部 而避免因吸附導致扭矩增加。 ’、封溝21的内面，從 圖7所示之球軸承（深溝球轴 Π的類型。，亦即，圖7所示之球 $具有密封構件 件π、安裝有密封構件17的密封安除I不财密封構 Π的凸緣部17a所接觸的密封溝21= 2()以及密封構件 所示之球軸承（深溝球軸承）相同。自以外’與圖1 因此，圖7所示之軸承（ 所示之球軸承（深溝球軸承）與密封構有圖1 外的作用效果。 冓件17的作用效果以 圖8表示使用有第2實施形態用 承（深溝球軸承)。該情形時的保持器5承=持盗之軸 部26中設有狹縫％，廿' # 、 於半球狀凸出 31。評糾㈣μ ’並以該狹縫35作為滚珠非接觸部 該It形時的狹縫35如圖9所示為 祐 =f滾珠16的節圓PCD-致的節=上 形（’既可為旋轉方向尺寸長於徑向尺寸的矩 ^ 相反亦可為#向尺寸長於旋轉方 矩 =方形)，或者亦可為旋轉方向尺寸與徑向尺寸= 可並非為長方形，而是扁圓或者橢圓形。 寸去、f此之橢_時，既可為旋轉方向尺寸長於徑向尺 亦可為向尺寸長於旋轉方向尺寸者。進而， 乍為狹縫35的配置位置，如圖9所示，既可配設在 17 201113447 32723pif 滚珠16的_ PCD上’村觸圓POD相比配設在外徑 侧。該情形時的偏移量亦可任意設定。亦即’由狹縫35 形成的滾珠非接觸部31縣座对，比未設有滾珠非接 觸部31時與滾珠16接_接觸面積減小15%〜3〇%即 再者’圖9所示之軸承的其它構成因與圖ι所示之轴 承相同，故省略對該些之說明。 8所示’即便滾珠非接觸部31由狹缝％形成時， ^可使；^滑劑通過套座内部時的阻力降低，而且，可使护 =二與t座3〇之間的油膜量減少。如此般，圖: y' ^也具有與上述圖1所示之保持ri 用效果。而且，設有狹縫35者，與設有:部 二一方面維持與不具有滾珠非接觸部31之先前的仵持 盗相同的尺寸，-方面可使扭矩降低。“的保持 件心。二(深輸^ 2構㈣、安裝有密封構件17的密封安“ 了不”密 件η一的凸緣部17a所接觸的密封溝21 ^方及密封 8所示之球輛承（深溝球軸承）相同。因此M外’與 之球轴承（深溝破站系、 匕，圖10所示 球軸承）盥密封槿侏 ’、8所不之球輛承（深溝 封構件17的作用效果以外的作用纷里 + 持态15為上述各實施形態中由衝/果。 ，製保持器，但亦可㈣造而成型 加=而成_ 兩賴，或者―—辦則 18 201113447 32723pif 此處，所謂放電加h是指藉由在電極與被加工物之間以 短週期重複進行的電弧放電來去除被加工物表面之一部分 的機械加工方法。所謂線切割是指放電加工的一種， 屬線施加張力，從而利用放電來加工金屬材料的方法: 而且，作為保持n 15 ’補限於金屬製保持器限，亦 可為合成樹脂的成形品。樹脂製保持器的樹脂材料，可使 用此類保持器先前所用者、’例如聚苯硫醚樹脂（以下，稱 為 PPS (Polyphenylene Sulflde)樹腊）或聚酿胺 46 ^201113447 όζτΐόριΐ VI. Description of the invention: [Technical field of the invention] The present invention relates to a -, a deep groove ball bearing and a sealed bearing 0 [Prior Art] A bearing (deep groove ball) is shown in Fig. 15 and has an inner circumference formed with an arc The outer ring 2 of the outer side raceway surface 2, the inner ring 4 of the arcuate inner raceway surface 3 facing each other, the retainer 5 disposed between the inner ring 4 and the outer ring 2, and A plurality of balls Bo that are freely supported by the holder 5 are rotated. As shown in Fig. 16, the retainer 5 is formed by combining two annular holding plates W having hemispherical projections 6 arranged at predetermined intervals in the circumferential direction. That is, each of the annular holding plates 7 is formed by a flat portion 8 between the hemispherical projections 6 and the adjacent hemispherical projections 6 which are arranged in the _ direction. In the assembled state, the flat portions 8, 8 are joined together, and the flats 8, 8 are joined by a fastening 9 such as a rivet. Therefore, each hemispherical shape protrudes from the "Μ, 6^ mesh, and the wire-shaped ball fitting portion (sleeve).刖 刖 刖 存在 存在 存在 刖 刖 刖 刖 刖 刖 刖 刖 刖 刖 刖 刖 刖 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 y / month The above-mentioned Patent Document 1 discloses that the recessed portion on the inner peripheral side of the sleeve has a system of (4) escaping from the genus. Thereby, the amount of lubricant held in the seat is increased from the lubrication state between the retainer and the ball. Between 201113447 and 32723pif, the above-mentioned Patent Document 2 discloses that the inner side of the sleeve is connected to the bearing space side between the outer ring and the retainer (= 2), and thus the wear of the gear is === Foreign matter such as powder. Prepare the shaft formed between the inner and outer rings: space === bearing 'component' (4) contact type seal that invades the bearing into the inner seal of the bearing: The disclosed person is sliding contact with the sealing flange ^). In the inner wall surface of the seal groove of the patent document 3, the maximum rough money Ry of the bearing rotating surface, for example, is reduced to a small step G) to make the contact sealing torque. J is "1. With this, the [prior art document] [patent document] [patent document 1] 曰 专利 专利 早期 公 2003 2003 2003 2003 2003 2003 2003 2003 -13 -13 -13 -13 -13 -13 -13 -13 -13 -13 -13 -13 -13 -13 -13 -13 -13 -13 -13 -13 -13 -13 -13 -13 -13 -13 -13 _ 触 Γ ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( ( Among the torque generated in the bearing is mainly the torque of the retainer, the steel ball (ball) to the oil (the lubricating material lubricating material j shear resistance accounts for a large proportion. d, then the shear resistance is almost shear formed in the sleeve The resistance of the oil film between the inner diameter surface of the seat and the ball in the seat. Moreover, when the seat is formed by a single-curved surface along the shape of a bead, the lubricant will pass through the retainer sleeve covering the ball and the ball. In the case of the fine gap on the inner side of the seat, resistance is generated, which is one of the main causes of the increase in torque. As disclosed in Patent Document 1, the auxiliary recess is used as a lubricant accumulation portion, and the auxiliary recess is stored in the auxiliary recess. Further, as disclosed in Patent Document 2, the resistance when the lubricant passes through the fine gap is not lowered. That is, in such a bearing, the reduction in the resistance when the lubricant passes and the oil film sheared during the movement of the ball cannot be achieved. Therefore, even if a recess is formed in the inner diameter surface of the sleeve, the torque reduction cannot be achieved. Further, as in the case of the sealed bearing of Patent Document 3, if the contact surface is reduced, If the rough wire reduces the sealing torque, then the low-effect of the twisting is there = degree. If the sealing is made, the sealing torque is zero, but the sealing gap is reduced to prevent the foreign matter such as the gear wear powder from invading. The "degree" is difficult to achieve due to assembly error, addition of I error, thermal expansion difference, etc. [Invention] The present invention has been made in view of the above problems, and provides a time zone __县Ball bearing, and further mention 6 201113447 32723pif A retainer for a close-circle ball bearing that prevents foreign matter from intruding into the bearing and sufficiently reduces the sealing torque, and has a follow-up connection such that the sleeve f and the roll ====:: = and =〇==:: :None ==):: The low area is less than 'non-connected ^n, r's turn 11 can be reduced by the ball in the material phase to reduce the lubricant through the inside of the seat The resistance of the time. Moreover, the non-contact portion of the ball is placed to reduce the amount of oil film that is formed between the ball and the seat, and if the ball non-contact portion is too small, the amount of oil film sheared is also reduced. Will become smaller 'causing failure to achieve torque reduction. And 'if the ball is not If the contact portion is too large, the amount of film formed on the ball and the sleeve will become too small, thereby impairing the smooth rotation of the ball. Therefore, the lubrication can be achieved by the range of the ball non-contact portion as in the present invention. The decrease in the resistance of the agent when passing through the inside of the sleeve and the amount of the oil film to be sheared are reduced. In the hemispherical projection, the convex portion protruding toward the opposite side of the ball may be formed by the opposite side of the ball facing direction, and the opposite side of the ball may be disposed toward the opposite side of the ball. a concave portion recessed on the side of the ball phase, and the concave portion is used as the ball non-contact portion, or a slit is provided in the hemispherical convex portion, and the slit is used as the contact portion of the ball non-contact 201113447. Preferably, the ball is not The contact portion, the outer diameter side of the blood bearing, and the holder of the bead of the present invention can be made of a metal molder, a metal mold made of a scale, or a stamper. . Further, the retainer of the present invention may be molded into a resin or a resin. D is a notch cutter (the deep groove ball bearing of the present invention has a plurality of balls that are rotated between the inner ring and the outer track surface formed on the outer circumference of the outer ring in the outer circumference: between the rings The upper secret holding [5 rounds of each of the outer and outer seals: the selected bearing on the orbital ring has a plurality of rotating bodies held by the retainer, and is t between the pair of orbital rings The sealing space of the bearing space is sealed. The upper part is: the upper seal is the base end fixed to the rail ring of any =, and the contact of the sealing flange with the other orbital ring is sealed at least The front end of the sealing flange portion is made of a high-wear material, which is worn in a rotating state to cause (4) wear into an adapter seal, or a slight contact to the extent that the contact pressure is displayed to zero, and is used in the retainer in the sealed bearing. In the above description, the "wearing material" means a material which is prone to wear. According to this configuration, at least the front end of the sealing flange portion of the sealing member is made of the above-mentioned high-wear material. Therefore, In the early stage, the contact type sealing member may become a non-contact 8 201113447 32723pif or a bribe due to wear, for example, in the early stage after the start of the operation, and the sealing member may be made in the invention. Or the front end of the material part of the bribe is the high-phase material part of the _ 2. (4) The material that can be properly grounded, the high-wear material can be a rubber material, that is, a high-wearing rubber ride, or The non-woven contact type 'village is a radial connection. For example, the shaft can be a resin material. The paste shaft, correction:=: ί In the invention, the above seal =:=, non-woven ==== phase, == In the invention, the sealing member sealing member may be adsorbed to the other one of the above-mentioned (four) rings, and the sealing member may be adsorbed to the other one: the anti-injection mechanism is provided, for example, in a seal. It is used to prevent the red slit of the contact type m from being set. Lowering, sealing:::=道== : The material will be damaged, but until the seal is two [Effect of the invention] The retainer of the present invention is two-two-touch, sealed The adsorption is produced in the same way. By setting the range of the ball non-contact portion 201113447 32723pif 3=slip The lowering of the resistance through the inside of the sleeve and the non-contact portion of the oil film ball that is sheared can be reduced on the outer diameter side of the bearing by the round face of the ball, thereby reducing the shear rate of the circumferential rate south. Therefore, the torque reduction can be realized more sturdyly. (4) The overall shape of the retainer is relatively simple, whether it is formed by metal or eucalyptus, and it can be formed by the molding method. In addition, if it is made of a resin, it can be molded by injection and can be molded. Therefore, it can be molded by each molding method of f gamma, and the cost can be reduced. Therefore, the torque can be reduced. In the case of the sealed bearing of the present invention, the sealed bearing of the present invention is a contact type seal structure at the initial stage of operation, and becomes non-contact type in the early stage after the start of the operation, for example, due to wear. Select the sealing member. Or, due to wear, the contact axis is shown to be zero. Therefore, the sealing torque can be sufficiently reduced. Further, the cause: wear, and a fine gap which is the most contact sealing gap is formed between the sealing flange portion and the rotating ring, or becomes a slight contact as escaped as described above. Therefore, although the lubricating oil can pass, it can prevent the invasion of foreign objects due to the life of the shadow. As a result, it is possible to prevent the foreign matter from decreasing the sealing torque. Brother, and by providing the anti-adsorption mechanism such as the slit described above, the sealing member is worn out ___ to prevent it from being prevented, thereby avoiding an increase in torque. 201113447 32723pif The above-described features and advantages of the present invention will be described in detail with reference to the accompanying drawings. Figure 1 shows the use of the first! The phantom bearing (deep groove ball bearing) of the embodiment. The ball bearing = the outside of the arc-shaped outer road surface (rolling surface) u, and the circumference formation = the outer road surface u phase _ left _ rail, 1 week = 13 inner ring 14, housed outside The bearing surface u and the inner side: a plurality of balls 16 of the road t), the free rotation of the supporting balls 16, and a sealed meal mounted on the axial end of the outer ring 12 may be referred to as a sealed bearing and used for At the beginning of the car's gearbox, it is packaged with grease. The rolling bearing is an inner ring rotating type in which the inner ring 14 is rotated = the outer ring 12 is a fixed ring. Further, the outer portion 12, the inner soil 14 and the ball 16, are composed of a high-strength steel such as SUJ2, and the retainer 15 is, for example, a cold-rolled steel (10) u_ese Industrial Standard's Japanese industrial specification) spcc (n Plate Cold rolled C〇mmercia Rolled low carbon steel series, etc.), stamped products. As shown in Figs. 2 and 3, the retainer 15 is composed of two annular retaining plates 27A and 27B having a hemispherical projection portion % arranged at regular intervals along the circumferential direction. That is, each of the annular holding plates 27, 276 is composed of a hemispherical projection 26 disposed along the circumferential direction and a flat portion 28 between the adjacent hemispherical projections 26. In the assembled state, the flat portions 28, 28 are overlapped and the flat portions 28, 28 are joined by fastening rivets and the like. Therefore, the hemispherical projections 26 are opposed to each other to form a bead-shaped ball fitting portion (sleeve) 30. Next, in the holder 15, a ball non-contact portion is provided on the ball facing surface of the housing 3〇. In this case, the contact area of the seat portion 6 in contact with the ball 6 is reduced by 15% to 3% by mass compared with the contact area in contact with the ball ball when the ball non-contact portion μ is not provided. By forming the rectangular convex portion 32 that protrudes toward the opposite side of the ball on the opposite side of the ball, a lifting recess 33 that is recessed toward the opposite side of the ball is provided on the ball opposing surface, and the ball non-contact portion 31 is formed by the concave portion 33. As shown in Fig. 4, the convex portion 32 can be of various types. That is, in the shape Α shown in Fig. 4A, the circumferential length l is set to LA, and the circumferential width dimension W is set to WA. Further, in the shape B shown in Fig. 4B, the circumferential length L is set to be shorter than LA of LB, and the circular direction width dimension W is set to WB which is the same as WA. In the shape C shown in Fig. 4C, the circumferential length L is set to be the same as the LC of LB, and the circumferential width dimension W is set to WC larger than WA. In the shape D shown in Fig. 4D, the circumferential length L is set to be the same LD as LA, and the circumferential width dimension W is set to be the same WD as WA. In the shape E shown in Fig. 4E, the circumferential length L is set to be the same as LE of LB, and the circumferential width dimension W is set to the same WE as WA. In the shape F shown by the pottery 4F, the circumferential length L is set to be the same as LB, and the circumferential width dimension W is set to be the same WF as WA. In the shape A shown in FIG. 4A, the shape B shown in FIG. 4B, and the shape F shown in FIG. 4F, the center line 凸 of the convex portion 32 coincides with the pitch circle 12 201113447 32723pif' PCD of the ball 16 'the convex portion 32 Set on the pitch circle PCD. In the shape C shown in FIG. 4C, the shape D shown in FIG. 4D, and the shape shown in FIG. 4E, the center line 〇' of the convex portion 32 is compared with the pitch circle 滚 of the ball 16 toward the outer diameter side of the bearing. Offset. In this case, in the shape c shown in FIG. 4C, only the offset exists slightly, but in the shape D shown in FIG. 4D and the shape shown in FIG. 4E, the offset is larger. The long side is consistent with the pitch circle of the ball. That is, even if the convex portion 32 is the concave contact portion 31 formed by the various non-contact portions of the ball portion shown in FIGS. 4A, 4B, 4C, 4D, 4E, and 4F, the ball 16 is formed. Connect '=^'=财_秘. The contact area of the contact is reduced by 15%~30%. (The size of the length of the pure direction of the money can be changed: the dimension longer than the direction of rotation is longer than the warp dimension, and the opposite is also == the direction of rotation can be made. Further, it may be circular. The m dimension is longer than the _ directional ruler, and as shown in FIG. 5A, the sealing member 17 and the metal 18 are covered with the core metal (the cladding portion of the core metal (C〇re) Elastic member" 9. The seal on the inner peripheral surface of the outer ring U constructed by the C-clay material or the like is formed as a fixed outer peripheral portion. The light inner ring is lightly turned...in the inner seal = 13 201113447 32723pif inner circumference At the position of the needle portion, the front cymbal 7 including the seal flange portion 17 on the inner peripheral side end of the circumferential groove is formed, and the inner surfaces of the two dams and the seal 21 are in sliding contact. The merma 17a, /, The two axial flange portions 17 having the knives are in a single shape are drawn toward the flange portion 7aa, and are axially contacted with the inner side wall surface of the sealing structure 21 of the inner ring 14 along the inner side of the secret bearing. The second direction: the outer side of the bearing and the outer wall surface of the seal groove 21 of the inner ring 14 are axial: the seal flange portion 17a is formed as the above-described elastic member 1 ^^, the portion of the portion having the two axial flange portions, which is formed by a material that is easy to wear, that is, the body portion 19a of the sealing member 17 (four) member 19, The main body portion i9a is connected to each other and has two configurations: In this case, the high-wear material portion 19b is formed, and the main body portion 19a is made of a normal rubber material. The dense-to-the-fourth (four) material is vulcanized and formed during vulcanization. Attached to the elastic member 19. The type of the high f 3 adhesive material constituting the high-wear material portion 19b is released according to the use temperature or the affinity with the lubricating oil. In the middle of the month, it is possible to set the ball non-ball due to the ball facing surface. The resistance of the contact portion is reduced when the lubricant passes through the inside of the sleeve, and the non-contact portion 31' can be used to reduce the formation of the ball 16 and the sleeve 30. In this case, If the non-contact portion of the ball is too small, the amount of oil film reduction of the knife will be reduced, resulting in a failure to reduce the torque of 201113447 32723pif. Moreover, the 'overturned M is too large, and the oil film is formed between the rolls. The amount will become too small, which will damage the ball 16 mi. In the same manner as in the present invention, the non-contact portion 31 of the money bead is reduced in resistance when the lubricant passes through the inside of the sleeve, and the amount of shearing is reduced. Therefore, the real residual moment can be reduced, and if the ball bearing is used, If the bearing of the retainer is used in a car, the eco-driving can be achieved on the basis of the (four) cost improvement. The ball non-contact portion 31' can be reliably formed by providing the concave portion 33 recessed on the opposite side of the ball facing surface. If the ball non-contact portion 31. When it is disposed on the outer diameter side of the pitch circle of the ball 16, the shear resistance at a position having a high circumferential speed can be lowered, and the torque can be stably reduced. The sealing bearing according to the embodiment is rotated as a rotation. At least the front end portion of the seal flange portion 17a of the seal member 17 in which the seal groove 21 of the inner ring 14 of the shaft is in sliding contact is a high-wear material portion 19b of a material (high-wear rubber material) which is likely to be worn, and therefore, at the beginning of the operation The contact type sealing member 17 can be made into a non-contact by the wear of the high-wear material portion 19b in the early stage (a few hours after the start of the operation) as shown in the enlarged cross section of Fig. 6 Type seal member 17, so that the seal torque is sufficiently reduced. For example, after the start of the operation, it becomes non-contact within 77 minutes and 60 minutes in an oil bath or absolute drying condition. As an example of the operating conditions, for example, bearing type: 6207 (JIS specification) bearing, rotation speed 4, 〇〇〇 rpm, bearing temperature: 30 ° C, rotation torque is 〇. 〇 75 N.m, in the oil bath case When using 'mineral oils', it becomes non-contact within 60 minutes. Thereby, the sealing torque can be sufficiently reduced. As a result, the temperature rise of the bearing 15 201113447 32723pif can be reduced, so that it can be compared with the lubricating oil of the previous (four) job title. Moreover, when used in a gearbox of a car, it can contribute to fuel economy of the car. Further, since the wear of the high-wear portion 19b can cause a fine gap which is optimally lost between the seal flange portion 17a of the seal member 17 and the seal groove 21 of the (10) 14, the lubricating oil can pass, However, it can prevent the intrusion of large-sized foreign matter that affects the life of the bearing. The wear of the high-wear material portion 19b does not have to be completed until it becomes non-contact, and is worn until it is a slight contact in which the contact pressure is zero in the f-note. In this embodiment, a high-wear rubber material is used as the case where the high-wear material portion constituting the sealing member 1 is easily rubbed and the material is 1%. However, as another example of a material that is easy to wear, a resin material may be used. . The material constituting the high-wear material portion 19b may be a solid lubricating material, a non-woven fabric, a mild steel or the like in addition to the above. Further, in this embodiment, as shown in Fig. 5B, an anti-adsorption mechanism such as a slit for ventilation can be provided in the sealing member 17. The anti-adsorption mechanism is a mechanism for preventing the sealing member 17 from being attracted to the inner ring 14 due to a decrease in the internal pressure of the bearing. In this case, in the state in which the axial flange portions 17aa and 17ab of the seal flange portion 17a of the seal member are in contact with the inner surface of the seal groove 21, the axial flange portions and the tip end of the seal flange portion 17a are provided in contact with each other. The slit 5 达到 of the ventilating state in the inner and outer directions of the bearing space. The slit 50 is provided in a plurality of locations, for example, two locations in the circumferential direction. In this way, because of the anti-adsorption mechanism such as narrow slits and slits 50, the high friction 201113447 32723pif ... H < between the corals prevents the pressure of the sealing jaw from decreasing, and the adsorption on the inner ring 14 = the inner part of the bearing is avoided. Adsorption causes an increase in torque. ', the inner surface of the sealing groove 21, from the ball bearing shown in Fig. 7 (the type of the deep groove ball axis ,, that is, the ball shown in Fig. 7 has the sealing member π, the sealing member with the sealing member 17 is installed. The sealing groove 21=2() which the flange portion 17a of the I-free sealing structure is in contact with and the ball bearing (deep groove ball bearing) shown by the sealing member are the same. From the outside and FIG. 1, therefore, the bearing shown in FIG. (The ball bearing (deep groove ball bearing) shown and the sealing structure have the effect other than that shown in Fig. 1. The effect of the element 17 is shown in Fig. 8. The bearing (the deep groove ball bearing) of the second embodiment is used. The retainer 5 is provided with a slit %, 廿' #, and a hemispherical projection 31. The correction (4) μ' and the slit 35 are used as the ball non-contact portion. The slit 35 is as shown in FIG. 9 as the pitch circle PCD of the y=f ball 16=upper shape ('the moment may be the moment in which the rotation direction dimension is longer than the radial dimension^ or the #direction dimension is longer than the rotation square moment = square), or it can be the direction of rotation and the radial dimension = not rectangular, but oblate or elliptical. In the case of the ellipse _, the dimension in the direction of rotation may be longer than the radial dimension or the dimension in the direction of rotation may be longer than the dimension in the direction of rotation. Further, the position of the slit 35 may be arranged as shown in FIG. In the 17 201113447 32723pif ball 16 _ PCD 'village touch POD compared to the outer diameter side. In this case, the offset can also be arbitrarily set. That is, the ball non-contact portion 31 formed by the slit 35 The seat pair is connected to the ball 16 when the ball non-contact portion 31 is not provided. The contact area is reduced by 15% to 3〇%, that is, the other structure of the bearing shown in Fig. 9 is the same as the bearing shown in Fig. Therefore, the description of the above is omitted. 8 Even when the ball non-contact portion 31 is formed by the slit %, ^ can reduce the resistance when the slip agent passes through the inside of the sleeve, and can make the protection = two and The amount of oil film between the three blocks of t is reduced. In this way, the figure: y' ^ also has the effect of maintaining the ri effect as shown in Fig. 1. Moreover, the slit 35 is provided, and the second part is provided. Maintaining the same size as the previous smashing thief without the ball non-contact portion 31, the torque can be reduced. 2. The deep bearing is formed by the sealing groove 21 of the sealing member 17 and the sealing groove 21 of the sealing member 17 which is in contact with the sealing member 17 and the ball bearing (the deep groove ball) shown by the sealing 8 The bearing is the same. Therefore, the M-outer ball bearing (the deep groove breaking station system, the cymbal, the ball bearing shown in Fig. 10) is sealed, and the ball bearing is not included (the effect of the deep groove sealing member 17 is not included). The role + the state 15 is the above-mentioned various embodiments from the punch / fruit., the holder, but also (four) made and formed plus = _ two, or "- do 18" 201113447 32723pif here, the so-called The discharge plus h refers to a machining method in which a part of the surface of the workpiece is removed by arc discharge which is repeatedly performed between the electrode and the workpiece in a short cycle. The wire cutting refers to a method of processing a metal material by applying a tension to a wire, and applying a tension to the wire. Further, as a metal retainer limit, the n 15 ′ is limited to a metal retainer. The resin material of the resin retainer can be used by those previously used, such as polyphenylene sulfide resin (hereinafter referred to as PPS (Polyphenylene Sulflde) tree wax) or polystyrene 46 ^
Cpoiyamide) 46)。尤制如汽車較流發電機所用的轴 承等要求更*溫度（例如2 〇 〇 或綱。c以上）範圍的長期 财熱性者，可使用親碰_(町，成為pi(pGiyimide) 樹脂）、聚醯胺醯亞胺樹脂（以下，稱為 (polyamide-imide)樹脂）或者聚醚醚酮樹脂（以下，稱 為 PEEK (polyetheretherketone)樹脂）等材料。 冉 該樹脂製保持器，例如可由射出成型而成型。而且， 亦可由切削加工而成型。樹脂製保持器，亦可 接觸部，使套座3G中與滾珠16接_接_積，比未 衰t非接觸部31時與滾珠16接觸的接觸面積減小 在樹脂製保持器中設置滾珠非接觸部31的情形時， =i所'，可藉由於滚珠相向之反面形成朝滾珠相反侧 犬出的矩祕部32，而在滾珠相向面設置朝滾珠相反侧凹 陷的矩形凹部33，並以該凹部33作為滾珠非接觸部. 而且，亦可設置狹縫35，並以該狹缝35作為滾珠非接觸 19 201113447 部3卜因此，樹脂製保持器 保持器相同的作用效果。 /、有一圖1所不之金屬製 ，11A與圖ι1Β表示密封構件1<7的變形 , 蚪的岔封構件17的密封凸緣部丨 心情形 環Μ的密封溝21徑向接觸的一個㈣而與内 封凸緣部17a之具有徑向凸緣部17&，至少前端:c :费 :磨損的材料所構成的高磨損材部19b之情形，：者f f損材部19b由高磨損橡膠材所構成之情形以及= 成，與圖5A所示之密封構件17相同。 /、構 該圖11A與圖11B所示之密封構件n，亦可防 物對軸承内之侵人以及使密封扭矩充分降低，故用車 的變速箱時，有助於汽車的省油化。 圖12A與圖12B表示密封構件17的其它變形例。該 密封構件17的密封凸緣部17a，僅具有沿軸承的内側而= 内環14的密封溝21的内側壁面軸向接觸的一個軸向凸^ 部17aa。使密封凸緣部17a之具有上述軸向凸緣部17aa 的至少包含前端部的部分19b為由易於磨損之材料所構成 的高磨損材部之情形、或者該高磨損材部19b由高磨損橡 膠材所構成之情形以及其它構成，與圖5A所示之密封構 件17相同。 該圖12A與圖12B所示之密封構件π，可防止異物 對輛承内之侵入以及使密封扭矩充分降低，故用於汽車的 變迷箱時，有助於汽車的省油化。 以上，對本發明的實施形態進行了說明，但本發明並 20 201113447 32723pii 二=上態:：是可進行各種變形，滾珠非接 對旋轉方向傾斜。而且，作為所形 觸：相 並非僅限於相對半球狀凸出部26為一個，亦=:二 二出：26中设置兩個或兩個以上的滾珠非 ^形^既可沿著圓周方向配置多個，亦可沿徑向配置多 無論設置長方形乃至正方形的凸部32 方形乃至正方形的狹縫35，均可使各角部為弧开 ’當設置長方形乃至正方形的凸部％的情二 較好的是’使凸部32的突出詈（叫邱μ从、 、 保持板27Α、27Β的魏或㈣以下。亦即=)過= 狀 變得過A，從而可能導致密封構件二 文裝，或者變得大型化。 』傅1干雜Μ [實施例] 實施例1 製作圖4所示之形狀a、b、c、d、e =則加工品)，並使用該些來組 定所產生的扭矩。其結果示於以下的表ΤΓ 品。所明標準品是指未形成有滾珠非接觸部31的先前產 21 201113447 όζ/ΐόρη [表i]Cpoiyamide) 46). In the case of a long-term heat-preserving person who requires a temperature range (for example, 2 〇〇 or more. c or more), such as a bearing used in a car-flow generator, you can use a pro-touch _ (machi, become pi (pGiyimide) resin), A material such as a polyamidamine resin (hereinafter referred to as a "polyamide-imide resin") or a polyetheretherketone resin (hereinafter referred to as a PEEK (polyetheretherketone) resin).冉 The resin holder can be molded, for example, by injection molding. Moreover, it can also be molded by cutting. The resin holder may also be in contact with the portion to make the contact with the ball 16 in the sleeve 3G, and the contact area with the ball 16 when the non-contact portion 31 is not reduced is reduced. The ball is placed in the resin holder. In the case of the non-contact portion 31, =i"', the rectangular portion 33 which is formed on the opposite side of the ball toward the opposite side of the ball, and which is recessed toward the opposite side of the ball is provided on the opposite side of the ball, and The recessed portion 33 serves as a ball non-contact portion. Further, the slit 35 may be provided, and the slit 35 may be used as the ball non-contact 19 201113447 portion 3, so that the resin retainer holder has the same operational effect. /, there is a metal made of Fig. 1, 11A and Fig. 1 denote the deformation of the sealing member 1 <7, and the sealing flange portion of the crucible sealing member 17 is in a radial contact with the sealing groove 21 of the ring (four) Further, in the case where the inner seal flange portion 17a has the radial flange portion 17&, at least the front end: c: the high wear material portion 19b composed of the worn material, the ff loss portion 19b is made of high wear rubber. The condition of the material and the formation of the material are the same as those of the sealing member 17 shown in Fig. 5A. The sealing member n shown in Fig. 11A and Fig. 11B can also prevent the intrusion of the inside of the bearing and the sealing torque sufficiently, so that when the vehicle's gearbox is used, it contributes to fuel economy of the automobile. 12A and 12B show other modifications of the sealing member 17. The seal flange portion 17a of the seal member 17 has only one axial projection 17aa which is axially contacted along the inner side of the bearing and the inner wall surface of the seal groove 21 of the inner ring 14. The portion 19b of the seal flange portion 17a having the axial flange portion 17aa including at least the front end portion is a high-wear material portion composed of a material that is easily worn, or the high-wear material portion 19b is made of high-wear rubber. The configuration of the material and other constitutions are the same as those of the sealing member 17 shown in Fig. 5A. The sealing member π shown in Fig. 12A and Fig. 12B can prevent the intrusion of foreign matter into the bearing body and sufficiently reduce the sealing torque, so that it is useful for fuel economy of the automobile when it is used in a car singular box. Although the embodiment of the present invention has been described above, the present invention 20 201113447 32723pii 2 = upper state: various deformations are possible, and the ball is not tilted in the direction of rotation. Moreover, as the shape touch: the phase is not limited to one of the relatively hemispherical projections 26, and also: two or two out: 26 is provided with two or more balls which are not arranged in the circumferential direction. A plurality of or more slits 35 may be arranged in the radial direction, such as a rectangular or even square convex portion 32, or a square slit 35, so that each corner portion can be arc-opened when the rectangular portion or the square convex portion is provided. It is good that 'the protrusion 詈 of the convex portion 32 (called Qiu μ, , or the holding plate 27Α, 27Β Wei or (4) or less. That is, =) over = shape becomes A, which may cause the sealing member to be installed. Or become larger.傅傅干杂Μ [Examples] In the first embodiment, the shapes a, b, c, d, and e = the processed product shown in Fig. 4 were produced, and the generated torque was set using the above. The results are shown in the following table. The standard product refers to the previous production in which the ball non-contact portion 31 is not formed. 21 201113447 όζ/ΐόρη [Table i]
* 1 是使形狀 Α 之P.C.D *2是使_.之位置自RC.D上=; 在表1中’形狀A中的I.6x9.0表示尺寸|為i 6mm， 圓周方向長度L為9.Gmm。形狀B中的16χ5 5表示尺寸 W為1.6一 mm，圓周方向長度L為55咖。形狀c中的26 X5.5表不尺寸W為2.6 mm，圓周方向長度L為5 5 mm。 形狀D中的*1表示形狀A中自ρα)向外徑侧偏移〇8 mm。形狀D的*2絲形狀B中自pcD向外徑侧偏移〇 8 mm在表1中，鋼珠一保祷器接觸面積中形狀a〜形狀F 為止之攔表示以標準品面積為1G()%時的比例（％)。而且， 作為轴承，使用外環12的外徑尺寸為72 〇麵，外環12 的=徑尺寸為60.2 mm，内環14的外徑尺寸為47 〇 mm， 内環14的内徑尺寸為35 〇 mm，滚珠（鋼珠）16的外徑 尺寸為11.1 mm者。 作為該些的實驗條件是在施加50〇N的徑向荷重狀態 下’提供4000 r/min的旋轉速度。並使其一部分浸潰於3〇 C 的潤滑油（豐田原廠 ATF ( Automatic Transmission 22 201113447 32723pif* 1 is the shape of the PCD *2 is such that the position of _. is from RC.D =; In Table 1, 'I.6x9.0 in shape A indicates size|is 6 mm, and the length L in the circumferential direction is 9 .Gmm. 16χ5 5 in the shape B indicates a dimension W of 1.6 mm and a circumferential length L of 55 coffee. The 26 X5.5 in the shape c indicates a dimension W of 2.6 mm and a circumferential length L of 55 mm. *1 in the shape D indicates that the shape A is shifted from ρα) to the outer diameter side by 8 mm. In the shape 2 of the *2 wire shape B, the distance from the pcD to the outer diameter side is 〇8 mm. In Table 1, the shape of the steel ball-prayer contact area from the shape a to the shape F is indicated by the standard area of 1G (). Proportion (%) at %. Further, as the bearing, the outer ring 12 has an outer diameter of 72 〇, the outer ring 12 has a diameter of 60.2 mm, the inner ring 14 has an outer diameter of 47 〇 mm, and the inner ring 14 has an inner diameter of 35 35 mm. 〇mm, the outer diameter of the ball (steel ball) 16 is 11.1 mm. The experimental conditions for these were to provide a rotational speed of 4000 r/min under a radial load condition of 50 〇N. And partially immersed in 3 〇 C lubricant (Toyota original ATF ( Automatic Transmission 22 201113447 32723pif
Fluid’自動變速箱油）T_4)中。此處，所謂一部分浸潰是 指將軸承軸心線保持水平，僅其鉛垂方向最下方的滾珠完 全浸潰。 圖13中表示使接觸面積更改後自pcD向外徑侧偏移 的情形時扭矩變化的示意圖。如此般，由表丨與圖13可知， 可藉由使接觸面積減小15%，而使扭矩約降低5〇%。而且， 可藉由使接觸面積減小30%，並且自PCD向外徑側偏移 0.8 mm，來使扭矩約降低60〇/〇。 實施例2 ”如圖9所示，製作具有狹縫35的保持器（金屬製保 持器.衝壓加工品）’並使用其組裝圖8所示之球軸承，測 定所產生的扭矩。該情形時，使接觸面積比標準品（不1 有狹縫35的保持器）減小3〇%。與上述實施例丄相同了 在施加5GGN的徑向荷重狀態τ，提供4_f/min的旋轉 速度。使其一部分浸潰於如艽的潤滑油（豐田原廠Ατρ =4)中。於該情形時，降低了約4〇%的扭矩。亦即，標準 品為0.152 Nm，而具有狹缝35的保持器為〇 〇93 Nm ^而 且，作為ϋ承，使用外環12的外徑尺寸為72 〇mm，外環 12的内徑尺寸為60 2 mm，内環14的外徑尺寸 mm」内環14的内徑尺寸為35 〇匪，滾珠（鋼珠）16的 外徑尺寸為11.1 mm者。再者，下述比較例i、2中， 使用相同尺寸者。 r 、 比較例1 取代掉凸部32或狹縫35而將半球狀凸出部26的輛 23 201113447 承内徑以及軸承外徑侧切削製作成金屬製保持器，並使用 其組裝圖8所示之球轴承’測疋所產生的扭矩。使接觸面 積比標準品（不具有狹縫35的保持器）降低了 Μ%。測 定條件與上述實施例相同。該情形時，降低了約11%的扭 矩。亦即，標準品為0.152ΝΙΠ，將軸承内徑以及軸承外徑 側切削而成的保持器為0.135 Nm。 比較例2 另外’製作將半球狀凸出部26的軸承外徑侧切削而 成的樹脂製保持器，並使用其組裝圖8所示之球軸承，測 定所產生的扭矩。該情形時，保持器的樹脂材料為pA66， 使接觸面積比標準品降低了 30%。測定條件與上 相同。該情形時，降低了約18%的扭矩。亦即，標準品為 0.152 Nm，將軸承内徑以及轴承外徑侧切削而成的保持器 為 0.124 Nm。 ' 實施例3 圖14是以圖表來表示該實施形態的密封軸承的旋轉 扭矩，與先前的密封軸承比較後的測試結果。如圖14A所 :以：品相比，實施形態的密封軸承中，旋轉扭矩 έ而Α ^。其原因在於，就旋轉扭矩的主要因素的明 所示’㈣於総產品中轉有潤滑脂 、保持盗剪切阻力+滚動阻力）以及密奋 &形_密_承騎出了密封扭矩之主要因素。Λ [產業上的可利用性] 作為輛承，既可為内環旋轉型滚動轴承，亦可為外環 24 201113447 32723pit 旋轉型滾動軸承。 雖然本發明已以實施例揭露如上，麸 本發明，任何所屬技術領域中具有通以限定 發明之保護顧當視後附之申請專^ /飾’故本 【圖式簡單·】 ❻如圍所界定者為準。 器的軸 承之剖面圖 圖1為使用有表示本發明第丨實 糾面圖。 ^貝施开场的保持 ;32:=:r以 圖 主要部分簡=了有保持益的凸部之圖1所示的保持器的 的主要圖二=有保持器的凸部之保持器的第]變形例 的主要圖二=有保持器的凸部之保持器的第2變形例 Ci:有保持器的凸部之保持器的第3變形例 的主‘部分:略:有保持^的凸部之保持器的第4變形例 的主要部分it有保持器的凸部之保持器的第5變形例 大剖m。 、匕在封構件恤大剖面圖。 201113447 ^Z/Zjpil 不之密封構件的主要部分放大剖面圖。 面圖。/ 上述圖2所示之保持器的其它軸承的剖 承的:』使用有表不本發明第2實施形態之保持器的軸 圖9為圖8的保持器的主要部分簡略圖。 =3-7封轴承的其它實施形態的剖面圖。 大剖面Γ上述圖UA的密封軸承的密封構件之放 =ΠΑ為表示密封軸承的其它實 大剖=為表示上述_的密封軸承的密封構件之放 圖表圖13為表示接觸面積降低率與扭矩降低率之關係的 圖14Α為密封軸承的旋轉杻矩與 後所表示的圖表。 產α〇加以比較 圖MB為表示旋轉與扭矩的要因明細矣 圖15為使贱前的保持器的軸承 回° 圖16為先前的保持器的立體圖。。面圖。 【主要元件符號說明】 1、 11 :圓弧狀外側執道面（滾動面） 3、13 .圓弧狀内側執道面（滾動面） 2、 12 :外環 26 201113447 32723pif 4、 14 :内環 5、 15 ··保持器 16、Bo :滾珠 17:密封構件 17a:密封凸緣部 17aa :第1軸向凸緣部 17bb :第2軸向凸緣部 17ac :徑向凸緣部 18 :芯金屬（core metal) 19 :被覆部（彈性構件） 19a :本體部 19b :高磨損材部 20 :密封安裝溝 21 :密封溝 6、 26 :半球狀凸出部 7、 27A、27B :環狀保持板 8、 28 :平坦部 9、 29 :緊固件 10、 30 :套座 31 :滚珠非接觸部 32 :凸部 33 凹部 35、50 :狹缝 01 :中央線 27 201113447Fluid' automatic transmission oil) T_4). Here, the term "partial impregnation" means that the bearing axis is kept horizontal, and only the ball at the lowest position in the vertical direction is completely immersed. Fig. 13 is a view showing the change in torque when the contact area is changed and the distance from the pcD to the outer diameter side is shifted. As such, from Table 丨 and Figure 13, it can be seen that the torque can be reduced by about 5% by reducing the contact area by 15%. Moreover, the torque can be reduced by about 60 〇/〇 by reducing the contact area by 30% and by shifting from the PCD to the outer diameter side by 0.8 mm. Example 2 As shown in Fig. 9, a retainer (metal retainer, press-worked product) having a slit 35 was produced, and a ball bearing shown in Fig. 8 was assembled using the same, and the generated torque was measured. The contact area is made smaller than the standard (not the holder having the slit 35) by 3%. As in the above-described embodiment, the radial load state τ of 5 GGN is applied to provide a rotational speed of 4_f/min. A part of it is immersed in a lubricant such as 艽 丰田 (Toyota original Ατρ = 4). In this case, the torque is reduced by about 4%. That is, the standard is 0.152 Nm, and the slit 35 is maintained. The device is 〇〇93 Nm ^ and, as the bearing, the outer ring 12 has an outer diameter of 72 〇mm, the outer ring 12 has an inner diameter of 60 2 mm, and the inner ring 14 has an outer diameter of mm" inner ring 14 The inner diameter of the ball is 35 〇匪, and the outer diameter of the ball (steel) 16 is 11.1 mm. In addition, in the following comparative examples i and 2, the same size was used. r, Comparative Example 1 Instead of the convex portion 32 or the slit 35, the inner diameter and the outer diameter side of the bearing 23 201113447 of the hemispherical projection 26 were cut into a metal holder, and assembled using the same as shown in FIG. The ball bearing 'measures the torque generated by the sputum. The contact area is reduced by Μ% compared to the standard (the holder without the slit 35). The measurement conditions are the same as those of the above embodiment. In this case, the torque is reduced by about 11%. That is, the standard is 0.152 ΝΙΠ, and the holder for cutting the inner diameter of the bearing and the outer diameter side of the bearing is 0.135 Nm. Comparative Example 2 In addition, a resin holder in which the outer diameter side of the bearing of the hemispherical projection 26 was cut was prepared, and the ball bearing shown in Fig. 8 was assembled using the ball bearing, and the generated torque was measured. In this case, the resin material of the holder was pA66, which reduced the contact area by 30% compared with the standard. The measurement conditions are the same as above. In this case, about 18% of the torque is reduced. That is, the standard is 0.152 Nm, and the retainer with the inner diameter of the bearing and the outer diameter side of the bearing is 0.124 Nm. 'Embodiment 3> Fig. 14 is a graph showing the results of a test in which the rotational torque of the sealed bearing of the embodiment is compared with the conventional sealed bearing. As shown in Fig. 14A, in the sealed bearing of the embodiment, the rotational torque is έ 。. The reason is that the main factors of the rotational torque are shown as '(4) in the product, the grease is transferred, the shear resistance is maintained, the rolling resistance is maintained), and the dense force & The main factor. Λ [Industrial Applicability] As a bearing, it can be either an inner ring rotating type rolling bearing or an outer ring 24 201113447 32723pit rotary rolling bearing. Although the present invention has been disclosed in the above embodiments by way of example, the present invention has any application in the art to which the invention is protected, and the application of the invention is attached to the application. The definition is subject to change. Cross-sectional view of the bearing of the device Fig. 1 is a view showing the third surface of the present invention. ^Bei Shi's opening of the hold; 32:=:r to the main part of the figure = the main part of the retainer shown in Figure 1 with the convex portion of the retaining benefit = the retainer of the retainer with the retainer Fig. 2 is a second modification of the holder having the convex portion of the retainer Ci: a main portion of the third modification of the retainer having the convex portion of the retainer: a slight: a convex having a hold The main part of the fourth modification of the holder of the holder has a large section m of the fifth modification of the holder of the projection of the holder. And squatting on the large section of the closure. 201113447 ^Z/Zjpil The enlarged cross-section of the main part of the sealing member. Surface map. The other bearing of the retainer shown in Fig. 2 is cut away from the shaft of the retainer of the second embodiment of the present invention. Fig. 9 is a schematic view of a main portion of the retainer of Fig. 8. = 3-7 sectional view of another embodiment of the bearing. The large-section 密封 of the sealing member of the sealed bearing of the above-mentioned figure UA is shown in FIG. 13 as a view showing the sealing member of the sealed bearing of the above-mentioned _. FIG. 13 is a graph showing the contact area reduction rate and the torque reduction. Figure 14 is a graph showing the relationship between the rotational moments of the sealed bearings and the latter. Comparison of the production of α〇 Fig. MB is a breakdown of the factors indicating the rotation and the torque. Fig. 15 is a view showing the bearing of the holder in front of the crucible. Fig. 16 is a perspective view of the former holder. . Surface map. [Description of main component symbols] 1, 11: Arc-shaped outer road surface (rolling surface) 3, 13 . Arc-shaped inner road surface (rolling surface) 2, 12: outer ring 26 201113447 32723pif 4, 14 : Ring 5, 15 · Retainer 16, Bo: Ball 17: Sealing member 17a: Sealing flange portion 17aa: First axial flange portion 17bb: Second axial flange portion 17ac: Radial flange portion 18: Core metal 19: covering portion (elastic member) 19a: main body portion 19b: high-wear material portion 20: seal mounting groove 21: sealing groove 6, 26: hemispherical projections 7, 27A, 27B: annular Holding plates 8, 28: flat portions 9, 29: fasteners 10, 30: sleeve 31: ball non-contact portion 32: convex portion 33 concave portion 35, 50: slit 01: center line 27 201113447
JZ/ZjpiI L:圓周方向長度 W :圓周方向寬度尺寸 PCD :節圓JZ/ZjpiI L: circumferential length W: circumferential width dimension PCD: pitch circle