JP4003284B2 - Rolling bearing device with oil supply means - Google Patents

Rolling bearing device with oil supply means Download PDF

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Publication number
JP4003284B2
JP4003284B2 JP08567698A JP8567698A JP4003284B2 JP 4003284 B2 JP4003284 B2 JP 4003284B2 JP 08567698 A JP08567698 A JP 08567698A JP 8567698 A JP8567698 A JP 8567698A JP 4003284 B2 JP4003284 B2 JP 4003284B2
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Japan
Prior art keywords
inner ring
lubricating oil
oil supply
rolling
outer ring
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JPH11280772A (en
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彰 石丸
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NSK Ltd
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NSK Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F16C33/667—Details of supply of the liquid to the bearing, e.g. passages or nozzles related to conditioning, e.g. cooling, filtering
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F16C33/6677—Details of supply of the liquid to the bearing, e.g. passages or nozzles from radial inside, e.g. via a passage through the shaft and/or inner ring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0469—Bearings or seals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts

Description

【０００１】
【発明の属する技術分野】
この発明に係る給油手段付転がり軸受装置は、例えば自動車用自動変速機を構成するリング歯車を回転軸に対して回転自在に支持する為に利用する。
【０００２】
【従来の技術】
自動車用自動変速機として従来から一般的に使用されている遊星歯車式自動変速機には、複数組の遊星歯車機構を組み込んでいる。図５〜６は、このうちの、オーバドライブのＯＮ・ＯＦＦを切り換える為の遊星歯車機構の１例を示している。回転軸１の片半部（図５の左半部）外周面にはスリーブ３を、回転自在に支持している。このスリーブ３の一端部（図５の右端部）外周面には、太陽歯車２を固設している。又、上記回転軸１の中間部外周面にはハウジング４を、給油手段付転がり軸受装置５により、この回転軸１に対する回転自在に支持している。このハウジング４は、片側面（図５の左側面）に遊星歯車機構を構成するリング歯車６を、外周面に入力歯車７を、それぞれ設けている。更に、上記回転軸１の中間部外周面で上記スリーブ３と上記給油手段付転がり軸受装置５との間部分には、支持枠８を固設している。そして、この支持枠８には、それぞれが上記回転軸１と平行な複数本の支持軸９、９を支持し、これら各支持軸９、９の周囲に遊星歯車１０、１０を、回転自在に支持している。そして、これら各遊星歯車１０、１０を、上記太陽歯車２及びリング歯車６と噛合させている。
【０００３】
一方、上記スリーブ３の他端部（図５の左端部）外周には、制御シリンダ１１を設けている。そして、この制御シリンダ１１内への圧油の給排に基づき、上記スリーブ３と上記各支持軸９、９との間に設けたクラッチ機構１２の断接の切り換えを自在としている。即ち、上記制御シリンダ１１内に圧油を送り込み、上記クラッチ機構１２を接続した場合には、上記回転軸１とスリーブ３とが相対回転不能に結合される。この結果、上記各遊星歯車１０、１０が上記各支持軸９、９の周囲で回転する事がなくなり、上記回転軸１が上記ハウジング４と同期して回転自在となる。この状態は、オーバドライブがＯＮされた状態となる。これに対して、上記制御シリンダ１１内の圧油を排出し、上記クラッチ機構１２の接続を断った場合には、上記回転軸１に対してスリーブ３が相対回転自在となる。この結果、上記各遊星歯車１０、１０が上記各支持軸９、９の周囲で回転し、上記リング歯車６と遊星歯車１０、１０と太陽歯車２との噛合に基づいて上記回転軸１が、上記ハウジング４よりも低速で回転する。この状態は、オーバドライブがＯＦＦされた状態となる。
【０００４】
本発明の対象となる、上記給油手段付転がり軸受装置５は、上記ハウジング４の内側に外輪１３を、ストップリング１４により抜け止めを図った状態で内嵌固定している。この外輪１３の内周面には、複列の外輪軌道１５、１５を設けている。一方、上記回転軸１の中間部外周面で上記外輪１３の直径方向内側部分には、内輪１６を固定している。この内輪１６は、それぞれの外周面に内輪軌道１７を形成した１対の内輪素子１８、１８の端面同士を突き合わせて成る。
【０００５】
又、上記各内輪素子１８、１８の突き合わせ端縁には、それぞれ複数個ずつの切り欠き１９、１９を形成している。上記１対の内輪素子１８、１８の端縁同士を突き合わせた状態でこれら各切り欠き１９、１９は、上記内輪１６の軸方向中間部で上記複列の内輪軌道１７、１７の間部分に、上記内輪１６の内径側から供給された潤滑油を上記外輪１３の軸方向中間部内周面に向けて吐出する給油通路を構成する。更に、上記各外輪軌道１５、１５と各内輪軌道１７、１７との間には、それぞれ複数個ずつの転動体２０、２０を転動自在に設けている。尚、上記給油手段付転がり軸受装置５を組み立てた状態で上記１対の内輪素子１８、１８は所定の力で軸方向に（互いに近づく方向に）押圧して、上記各転動体２０、２０に所定の予圧を付与する。又、上記複列の外輪軌道１５、１５と内輪軌道１７、１７との間に複列に設けた転動体２０、２０は、それぞれ保持器２４、２４により転動自在に保持している。
【０００６】
自動変速機の運転時には上記各切り欠き１９、１９に、上記回転軸１の中心部に形成した給油孔２１並びにこの給油孔２１から直径方向外方に分岐した分岐孔２２を通じて、図６に矢印で示す様に、潤滑油を送り込む。この分岐孔２２を通じて上記回転軸１の外周面から吐出した潤滑油は、上記１対の内輪素子１８、１８の突き合わせ部の内周面と上記回転軸１の外周面との間に存在する環状空間２３を流れて円周方向に広がり、上記各切り欠き１９、１９を通じて上記内輪１６の外径側に吐出する。そしてこの潤滑油は、上記各外輪軌道１５、１５及び内輪軌道１７、１７と転動体２０、２０の転動面との当接部を潤滑する。
【０００７】
又、上述した従来構造の他、実用新案登録第２５４０９７９号、実開平４−１３２２２０号、同５−９４５３２号、同６−３５６５３号、同６−３５６５５号、同６−３５６５７号、同６−４５１１７号公報には、上記当接部への潤滑油の供給を、微小隙間又は小通孔を介して行なったり、或は多孔質材に染み込ませた潤滑油を、遠心力に基づいて微量ずつ上記当接部に供給する発明が記載されている。
【０００８】
【発明が解決しようとする課題】
従来の給油手段付転がり軸受装置５の場合、オーバドライブをＯＮした状態、即ち、回転軸１とハウジング４とを同期して回転自在とした状態で、各外輪軌道１５、１５及び内輪軌道１７、１７にフレッチングと呼ばれる摩耗が発生し易い。この理由は、次の通りである。回転軸１とハウジング４とが同期して回転する結果、外輪１３と内輪１６とが相対回転しないと、上記各外輪軌道１５、１５と各内輪軌道１７、１７との間に設けた転動体２０、２０が転動しない。従って、これら各外輪軌道１５、１５及び内輪軌道１７、１７と各転動体２０、２０の転動面とは同じ部分で当接したままとなる。一方、自動変速機の運転時に上記給油手段付転がり軸受装置５には、自動変速機の構成各部材のアンバランスや荷重変動に基づく振動が加わる。
【０００９】
上記各外輪軌道１５、１５及び内輪軌道１７、１７と各転動体２０、２０の転動面との当接部に十分な潤滑油が存在すれば特に問題を生じないが、上記外輪１３と内輪１６とが相対回転しない状態では、必ずしも上記当接部に十分な潤滑油が存在しない場合が考えられる。即ち、上記外輪１３と内輪１６とが相対回転せず、上記各転動体２０、２０が転動しない状態では、切り欠き１９、１９から吐出され、上記外輪１３の内周面中間部で上記両外輪軌道１５、１５の間部分に達した潤滑油の多くが、上記当接部に達する事なく周囲に飛散してしまう。この結果、特に上記切り欠き１９、１９から離れた部分に存在する転動体２０、２０の転動面と上記各外輪軌道１５、１５及び内輪軌道１７、１７との当接部に存在する潤滑油が不足し易くなる。そして、当接部に存在する潤滑油が不足した場合には、上記フレッチングの発生に基づき、上記各外輪軌道１５、１５及び内輪軌道１７、１７と各転動体２０、２０の転動面とに早期剥離等の損傷が発生し易くなる。特に、上記各外輪軌道１５、１５と各転動体２０、２０の転動面との当接部には、遠心力に基づく荷重が加わり、振動に基づいてこの当接部に加わる衝撃力も大きい為、上記損傷が問題となり易い。
【００１０】
上記各切り欠き１９、１９から吐出する潤滑油の量を多くしたり、或はこれら各切り欠き１９、１９の数を多くして、総ての当接部と切り欠き１９、１９との距離を短くすれば、上記フレッチングの発生を防止できる。但し、上記潤滑油の吐出量を多くする事は、他の部分への潤滑油の量を減少させる原因になったり、或は給油ポンプの大型化による動力損失の増大の原因となる為、採用できない場合もある。又、上記各切り欠き１９、１９の数を多くする事は、加工が面倒になりコスト増大の原因となる。しかも、１対の内輪素子１８、１８の突き合わせ端縁同士の接触面積の減少により、これら両内輪素子１８、１８により構成する内輪１６の軸方向に亙る剛性を低下させ、予圧調整が難しくなる。この結果、過大な予圧付与に基づく転がり疲れ寿命の低下や、予圧抜けによるがたつきが発生し易くなる為、やはり採用できない。
【００１１】
又、潤滑油中には、自動変速機を構成する各歯車が摩耗する事により生じる、鉄粉等の異物が混入するが、この異物が潤滑油と共に上記当接部に供給された場合には、上記各外輪軌道１５、１５及び内輪軌道１７、１７と上記各転動体２０、２０の転動面とに、圧痕や摩耗が発生する。この結果、給油手段付転がり軸受装置の転がり疲れ寿命が低下すると共に、この給油手段付転がり軸受装置の運転時に於ける振動特性及び音響特性も劣化する。
【００１２】
更には、上記各切り欠き１９、１９部分に潤滑油の供給を行なうオイルポンプが故障したり、或はエンジンを駆動する事なく自動車を牽引する等により、このオイルポンプが作動する事なく自動変速機を構成する歯車のみが回転した場合に、給油手段付転がり軸受装置５が、比較的早期に焼き付きを起こす可能性がある。
本発明の給油手段付転がり軸受装置は、この様な不都合を何れも解消すべく発明したものである。
【００１３】
【課題を解決する為の手段】
本発明の給油手段付転がり軸受装置は、前述した従来の給油手段付転がり軸受装置と同様に、内周面に複列の外輪軌道を有する外輪と、１対の内輪素子を軸方向に配置して成り、外周面に複列の内輪軌道を有する内輪と、上記各外輪軌道と各内輪軌道との間にそれぞれ複数個ずつ転動自在に設けられた転動体と、上記内輪の軸方向中間部で上記複列の内輪軌道の間部分に設けられ、上記内輪の内径側から供給された潤滑油をこの内輪の外径側に吐出する給油通路とを備える。そして、上記外輪と上記内輪とが相対回転しない状態を含む状態で使用される。
特に、本発明の給油手段付転がり軸受装置に於いては、上記給油通路を通じて送られる潤滑油が浸透及び通過自在であるが、この潤滑油中に混入した異物が通過しにくい円環状のフィルタ部材を、上記両内輪素子同士の間に挟持した状態で配置する事により、このフィルタ部材を上記給油通路に対し直列に設けている。
【００１４】
【作用】
上述の様に構成する本発明の給油手段付転がり軸受装置は、給油通路を通じて内輪の軸方向中間部で複列の内輪軌道の間部分、即ち、１対の内輪素子の間部分でフィルタ部材の内径側から吐出した潤滑油を、このフィルタ部材を介して、円周方向及び軸方向に亙り広く分配できる。従って、外輪と内輪とが同期して回転し、複数の転動体が転動しない状態でも、上記フィルタ部材の外周面のほぼ全面から、複列の外輪軌道及び内輪軌道と複数の転動体の転動面との当接部に十分な潤滑油の供給を行なえる。この結果、フレッチングの発生を防止して、上記複列の外輪軌道及び内輪軌道と複数の転動体の転動面とに、早期剥離等の損傷が発生する事を有効に防止できる。
【００１５】
又、上記給油通路から吐出される潤滑油中に混入した異物は、上記フィルタ部材に捕集されて、上記内輪の外径側には出ない。従って上記当接部側には、異物を除去された清浄な潤滑油を供給する事ができる。この結果、上記異物による圧痕や著しい摩耗の発生を防止して、給油手段付転がり軸受装置の転がり疲れ寿命の低下及び音響の劣化を防止できる。
【００１６】
更に、潤滑油供給用のオイルポンプが非作動状態のまま、自動変速機等の給油手段付転がり軸受装置の設置部分が回転した場合には、遠心力に基づき上記フィルタ部材に染み込んでいる潤滑油が、徐々に染み出して、上記当接部に送られる。この結果、オイルポンプ停止後、転がり軸受装置が焼き付くまでの時間を長くして、この転がり軸受装置を焼き付きにくくできる。
【００１７】
【発明の実施の形態】
図１は、本発明の実施の形態の第１例を示している。尚、本発明の特徴は、外輪１３と内輪１６とが同期して回転する（相対回転しない）状態で、複列の外輪軌道１５、１５及び内輪軌道１７、１７と複数の転動体２０、２０の転動面との当接部に十分な潤滑油を供給すると共に、この潤滑油中に混入した異物を除去し、更にはオイルポンプ停止時の焼き付き防止を図る為の構造にある。その他の部分の構造及び作用は、前述の図５〜６に示した従来構造と同様であるから、同等部分に関する説明は省略若しくは簡略にし、以下、本発明の特徴部分を中心に説明する。
【００１８】
本例の場合には、内輪１６の内径側に存在し、給油通路を構成する分岐孔２２の下流端開口を塞ぐ状態で、上記内輪１６を構成する１対の内輪素子１８、１８の間部分で、円環状のフィルタ部材２５をこれら両内輪素子１８、１８の内端面同士の間で挟持する状態で配置している。尚、上記フィルタ部材２５は、例えば、焼結金属、不織布、フェルト等の多孔質材により造っている。この様な多孔質材としては、その内部に互いに連続する微細な空隙を有し、この空隙を通じて上記フィルタ部材２５の内周面と外周面とが互いに連通しているものであれば、特に例示したものに限定されずに使用できる。
【００１９】
上述の様に構成する本発明の給油手段付転がり軸受装置は、自動変速機の高速運転時、上記内輪１６の回転速度が速く、上記フィルタ部材２５に浸透した潤滑油に作用する遠心力が大きい場合には、このフィルタ部材２５に浸透した潤滑油が、上記遠心力に基づき、このフィルタ部材２５の外周面の全面から染み出す。この様にしてフィルタ部材２５から染み出した潤滑油は、上記分岐孔２２の近傍部分だけでなく、上記外輪１３及び内輪１６の全周に亙ってほぼまんべんなく流れ出す。従って、上記分岐孔２２が円周方向に亙り１乃至数個所しか存在しなくても、上記フィルタ部材２５に染み込んだ潤滑油を、上記分岐孔２２の近傍部分だけでなく、上記外輪１３及び内輪１６の全周に亙り、ほぼまんべんなく供給できる。この結果、複列の外輪軌道１５、１５及び内輪軌道１７、１７と総ての転動体２０、２０の転動面との当接部に、潤滑油を十分に送り込む事ができ、この当接部にフレッチングによる摩耗が発生する事を防止できる。
【００２０】
又、自動変速機の低速運転時、上記内輪１６の回転速度が遅く、上記フィルタ部材２５に浸透した潤滑油に作用する遠心力が小さい場合でも、このフィルタ部材２５に浸透した潤滑油は、上記分岐孔２２からの追加供給に基づいて押し出され、このフィルタ部材２５の外周面から少量ずつ染み出し、上記各内輪軌道１７、１７に付着する。この様にして各内輪軌道１７、１７に付着した潤滑油は、前記回転軸１を中心とする上記外輪１３及び内輪１６と転動体２０、２０との回転運動に基づいて各方向に流下し、上記分岐孔２２の近傍部分だけでなく、上記外輪１３及び内輪１６の全周に亙ってほぼまんべんなく付着する。この結果、複列の外輪軌道１５、１５及び内輪軌道１７、１７と総ての転動体２０、２０の転動面との当接部に、潤滑油を十分に送り込む事ができ、この当接部にフレッチングによる摩耗が発生する事を防止できる。
【００２１】
従って、オーバドライブのＯＮ時、外輪１３と内輪１６とが同期して回転し、複数の転動体２０、２０が転動しない状態でも、フレッチングが発生し易い状態にある複列の外輪軌道１５、１５及び内輪軌道１７、１７と複数の転動体２０、２０の転動面との当接部に十分な潤滑油の供給を行なえる。この結果、フレッチングの発生を防止して、上記複列の外輪軌道１５、１５及び内輪軌道１７、１７と複数の転動体２０、２０の転動面とに、早期剥離等の損傷が発生する事を有効に防止できる。
【００２２】
更に、上記フィルタ部材２５内に存在し、潤滑油を通過させる空隙の断面積が狭いので、上記分岐孔２２から吐出される潤滑油がこのフィルタ部材２５内を通過する際に、この潤滑油中に混入した異物がこのフィルタ部材２５に捕集されて取り除かれる。従って、上記分岐孔２２から吐出される潤滑油中に混入した異物が上記当接部側にまで送られる事を防止できる。この結果、上記異物により複列の外輪軌道１５、１５及び内輪軌道１７、１７と各転動体２０、２０の転動面との当接部に摩耗や圧痕が発生する事を防止して、本発明の給油手段付転がり軸受装置の転がり疲れ寿命の低下及び振動特性、音響特性の劣化を防止できる。
【００２３】
更に、潤滑油供給用のオイルポンプが非作動で、上記分岐孔２２を通じての潤滑油供給が行なわれないまま、回転軸１等が回転した場合には、それ以前の潤滑油供給に基づいて上記フィルタ部材２５内に染み込んでいる潤滑油が、遠心力に基づいて、上記各当接部に送られる。即ち、内部に微細な空隙を有する上記フィルタ部材２５内には、表面張力に基づき、相当量の潤滑油が貯溜されている。この潤滑油は、上記分岐孔２２を通じての新たな潤滑油供給が停止した後にも、遠心力により上記フィルタ部材２５の外周面から徐々に染み出して、上記各当接部を潤滑する。従って、オイルポンプの停止後、これら各当接部が焼き付くまでの時間を長くして、給油手段付転がり軸受装置に焼き付き故障を発生しにくくできる。
【００２４】
尚、焼結金属製のフィルタ部材２５を使用する場合、このフィルタ部材２５の軸方向（図１の左右方向）に亙る幅寸法を規制する事により、本発明の給油手段付転がり軸受装置に組み込まれる転がり軸受の内部隙間（正又は負の隙間）を調整し、この転がり軸受に付与する予圧を適正に規正する事ができる。即ち、上記転がり軸受の内部隙間が適正値となる状態に、前記外輪１３、１対の内輪素子１８、１８、各転動体２０、２０を組み立てたと仮定した場合での、これら１対の内輪素子１８、１８の互いに対向する内端面同士の間隔に見合う寸法に上記フィルタ部材２５の幅寸法を規制すれば、上記転がり軸受に付与する予圧を調整する手間を軽減できる。
【００２５】
尚、上記焼結金属の空隙率は、この焼結金属を構成する焼結用の粉末の粒度を調節する事により、任意に調節できる。この様に空隙率を調整する事により、このフィルタ部材２５内に浸透し、更に通過する潤滑油の量を調整し、上記当接部側に供給する潤滑油の量を任意に設定する事ができる。又、焼結金属に熱処理等を施せば、この焼結金属により造ったフィルタ部材２５の強度や耐摩耗性等を所望通りにする事もできる。
【００２６】
一方、上記フィルタ部材２５を不織布、フェルト等で造った場合にも、上記分岐孔２２から吐出される潤滑油は、上記不織布、フェルト等の内部に存在する空隙内に入り込み、このフィルタ部材２５全体に浸透する。そして、供給される潤滑油の圧力及び遠心力の作用に基づいてこのフィルタ部材２５の外周面のほぼ全面から上記外輪軌道１５、１５及び上記内輪軌道１７、１７と上記各転動体２０、２０の転動面との当接部に供給される。尚、上記焼結金属等の硬質の部材によりフィルタ部材の本体部分を造り、この本体部分に溝、孔、切り欠き等の凹部を設け、この凹部に不織布等の軟質な部材を組み込む事により、上記フィルタ部材を構成する事もできる。
【００２７】
次に、図２は、本発明の実施の形態の第２例を示している。上述の図１に示した第１例が、転動体２０、２０としてテーパころを使用していたのに対して、本例の場合には、転動体２０ａ、２０ａとして玉を使用している。この様に、転動体２０ａ、２０ａとして玉を使用した事に伴い、複列の外輪軌道１５ａ、１５ａ及び内輪軌道１７ａ、１７ａ同士の間隔を大きくしている。そして、各内輪素子１８、１８同士の間に設けたフィルタ部材２５ａの幅を広くしている。又、上記各転動体２０ａ、２０ａを転動自在に保持する為の保持器２４ａ、２４ａとして、玉を保持するのに適当な形状のものを使用している。その他の構成及び作用は、上述した第１例の場合と同様である。
【００２８】
次に、図３は、本発明の実施の形態の第３例を示している。本例の場合は、前述の図１に示した第１例と、先発明（特願平９−７７９５３号）とを組み合わせた例を示している。本例の場合、複列の外輪軌道１５、１５と内輪軌道１７、１７との間にそれぞれ複数個ずつ設けた転動体２０、２０をそれぞれ転動自在に保持する為の保持器２６、２６を、それぞれ耐油性を有する合成樹脂を射出成形する事により形成している。そして、これら両保持器２６、２６の内端部（給油手段付転がり軸受装置の軸方向中央寄りで、互いに対向する端部）内周面に、円周方向に長く、分岐孔２２から吐出された潤滑油を一時的に貯溜自在な凹溝２７、２７を設けている。これら各凹溝２７、２７は、上記内輪１６を構成する１対の内輪素子１８、１８の間に設けられたフィルタ部材２５の外周面に対向する部分に存在する。
【００２９】
上述の様に構成される本例の給油手段付転がり軸受装置の運転時、上記分岐孔２２を直径方向内側から外側に向けて流れ、上記フィルタ部材２５の外周面から染み出した潤滑油は、回転に伴う遠心力の影響で周囲に飛散し、そのうちの一部が上記各凹溝２７、２７に捕集される。自動変速機の高速運転時、これら各凹溝２７、２７を設けた上記両保持器２６、２６の回転速度が速く、上記各凹溝２７、２７に捕集された潤滑油に作用する遠心力が大きい場合には、これら各凹溝２７、２７に捕集された潤滑油がそのままこれら各凹溝２７、２７内に溜り、遂にはこれら各凹溝２７、２７から溢れ出す。この様にして各凹溝２７、２７から溢れ出した潤滑油は、上記分岐孔２２の近傍部分だけでなく、外輪１３及び内輪１６の全周に亙ってまんべんなく流れ出す。この結果、複列の外輪軌道１５、１５及び内輪軌道１７、１７と総ての転動体２０、２０の転動面との当接部に、潤滑油を十分に送り込む事ができ、この当接部にフレッチングによる摩耗が発生する事を防止できる。
【００３０】
又、自動変速機の低速運転時、上記各保持器２６、２６の回転速度が遅く、上記各凹溝２７、２７に捕集された潤滑油に作用する遠心力が小さい場合には、上記各凹溝２７、２７に捕集された潤滑油は、重力の作用に基づいてこれら各凹溝２７、２７から流下し、対向する内輪軌道１７、１７に付着する。この様にして各内輪軌道１７、１７に付着した潤滑油は、前記回転軸１を中心とする上記外輪１３及び内輪１６と転動体２０、２０との回転運動に基づいて各方向に流下し、上記分岐孔２２の近傍部分だけでなく、上記外輪１３の全周に亙ってまんべんなく付着する。この結果、複列の外輪軌道１５、１５及び内輪軌道１７、１７と総ての転動体２０、２０の転動面との当接部に、潤滑油を十分に送り込む事ができ、この当接部にフレッチングによる摩耗が発生する事を防止できる。この結果、上記複列の外輪軌道１５、１５及び内輪軌道１７、１７と複数の転動体２０、２０の転動面とに、早期剥離等の損傷が発生する事を有効に防止できる。その他の構成及び作用は、前述した第１例の場合と同様である。尚、上述の様に作用する先発明を、本発明の第１例の構造と組み合わせる事により、本発明の給油手段付転がり軸受装置の性能を更に向上させる事ができる。
【００３１】
次に、図４は、本発明の実施の形態の第４例を示している。上述の図３に示した第３例が、転動体２０、２０としてテーパころを使用していたのに対して、本例の場合には、転動体２０ａ、２０ａとして玉を使用している。言い換えれば、上述の第３例に示した先発明の特徴部分である凹溝２７、２７を、本発明の第２例の構造と組み合わせている。この様な本例の給油手段付転がり軸受装置の場合も、上述した第３例の場合と同様の作用により、フレッチングの発生を防止し、早期剥離等の損傷防止を図る。
【００３２】
【発明の効果】
本発明の給油手段付転がり軸受装置は、以上に述べた通り構成され作用する為、他の部分への潤滑油の供給量を少なくしたり、給油ポンプを大型化する事なく、複列の外輪軌道及び内輪軌道と複数の転動体の転動面とに、早期剥離等の損傷が発生する事を有効に防止できて、高性能でしかも優れた耐久性を有する自動変速機を実現できる等、各種機械装置の性能向上に寄与する事ができる。更には、オイルポンプの停止時にも焼き付きを発生しにくくできて、故障時に於ける信頼性の向上も図れる。
【図面の簡単な説明】
【図１】本発明の実施の形態の第１例を示す、図５のＡ部に相当する断面図。
【図２】同第２例を示す、図１と同様の図。
【図３】同第３例を示す、図１と同様の図。
【図４】同第４例を示す、図１と同様の図。
【図５】本発明の対象となる給油手段付転がり軸受装置を組み込んだ自動車用自動変速機の部分断面図。
【図６】給油手段付転がり軸受装置部分のみを取り出して示す、図５の拡大Ｂ−Ｂ断面図。
【符号の説明】
１ 回転軸
２ 太陽歯車
３ スリーブ
４ ハウジング
５ 給油手段付転がり軸受装置
６ リング歯車
７ 入力歯車
８ 支持枠
９ 支持軸
１０ 遊星歯車
１１ 制御シリンダ
１２ クラッチ機構
１３ 外輪
１４ ストップリング
１５、１５ａ 外輪軌道
１６ 内輪
１７ １７ａ 内輪軌道
１８ 内輪素子
１９ 切り欠き
２０、２０ａ 転動体
２１ 給油孔
２２ 分岐孔
２３ 環状空間
２４、２４ａ 保持器
２５、２５ａ フィルタ部材
２６ 保持器
２７ 凹溝[0001]
BACKGROUND OF THE INVENTION
The rolling bearing device with oil supply means according to the present invention is used, for example, to support a ring gear constituting an automatic transmission for an automobile so as to be rotatable with respect to a rotating shaft.
[0002]
[Prior art]
A plurality of planetary gear mechanisms are incorporated in a planetary gear type automatic transmission that has been generally used as an automatic transmission for automobiles. FIGS. 5 to 6 show an example of a planetary gear mechanism for switching overdrive ON / OFF. A sleeve 3 is rotatably supported on the outer peripheral surface of one half (left half in FIG. 5) of the rotary shaft 1. A sun gear 2 is fixed to the outer peripheral surface of one end (the right end in FIG. 5) of the sleeve 3. A housing 4 is supported on the outer peripheral surface of the intermediate portion of the rotary shaft 1 by a rolling bearing device 5 with oil supply means so as to be rotatable with respect to the rotary shaft 1. The housing 4 is provided with a ring gear 6 constituting a planetary gear mechanism on one side surface (left side surface in FIG. 5) and an input gear 7 on the outer peripheral surface. Further, a support frame 8 is fixedly provided at a portion between the sleeve 3 and the rolling bearing device 5 with oil supply means on the outer peripheral surface of the intermediate portion of the rotary shaft 1. The support frame 8 supports a plurality of support shafts 9 and 9 that are parallel to the rotary shaft 1, and planetary gears 10 and 10 are rotatable around the support shafts 9 and 9. I support it. These planetary gears 10 and 10 are meshed with the sun gear 2 and the ring gear 6.
[0003]
On the other hand, a control cylinder 11 is provided on the outer periphery of the other end (left end in FIG. 5) of the sleeve 3. Based on the supply and discharge of the pressure oil into the control cylinder 11, the connection and disconnection of the clutch mechanism 12 provided between the sleeve 3 and the support shafts 9 and 9 can be freely switched. That is, when pressure oil is fed into the control cylinder 11 and the clutch mechanism 12 is connected, the rotary shaft 1 and the sleeve 3 are coupled so as not to be relatively rotatable. As a result, the planetary gears 10, 10 do not rotate around the support shafts 9, 9, and the rotary shaft 1 can rotate in synchronization with the housing 4. In this state, the overdrive is turned on. On the other hand, when the pressure oil in the control cylinder 11 is discharged and the clutch mechanism 12 is disconnected, the sleeve 3 is rotatable relative to the rotary shaft 1. As a result, the planetary gears 10 and 10 rotate around the support shafts 9 and 9, and the rotary shaft 1 is rotated based on the meshing of the ring gear 6, the planetary gears 10 and 10 and the sun gear 2. It rotates at a lower speed than the housing 4. In this state, the overdrive is turned off.
[0004]
In the rolling bearing device 5 with oil supply means, which is the subject of the present invention, the outer ring 13 is fitted and fixed inside the housing 4 in a state in which the stop ring 14 prevents the outer ring 13 from coming off. Double row outer ring raceways 15 and 15 are provided on the inner peripheral surface of the outer ring 13. On the other hand, an inner ring 16 is fixed to a radially inner portion of the outer ring 13 on the outer peripheral surface of the intermediate portion of the rotating shaft 1. The inner ring 16 is formed by abutting the end faces of a pair of inner ring elements 18 and 18 each having an inner ring raceway 17 formed on each outer peripheral surface.
[0005]
A plurality of notches 19 and 19 are formed at the butt end edges of the inner ring elements 18 and 18, respectively. In the state where the edges of the pair of inner ring elements 18, 18 are abutted with each other, the notches 19, 19 are located in the middle portion of the inner ring 16 in the axial direction between the double row inner ring raceways 17, 17. An oil supply passage for discharging the lubricating oil supplied from the inner diameter side of the inner ring 16 toward the inner peripheral surface in the axial direction intermediate portion of the outer ring 13 is configured. Further, a plurality of rolling elements 20, 20 are provided between the outer ring races 15, 15 and the inner ring races 17, 17, respectively, so as to be freely rollable. In the assembled state of the rolling bearing device 5 with the oil supply means, the pair of inner ring elements 18 and 18 are pressed in the axial direction (in a direction approaching each other) with a predetermined force to be applied to the rolling elements 20 and 20. A predetermined preload is applied. Further, the rolling elements 20 and 20 provided in a double row between the double row outer ring raceways 15 and 15 and the inner ring raceways 17 and 17 are rotatably held by cages 24 and 24, respectively.
[0006]
When the automatic transmission is operated, the notches 19, 19 are filled with an oil supply hole 21 formed in the central portion of the rotary shaft 1 and a branch hole 22 branched outward from the oil supply hole 21 in the diametrical direction in FIG. As shown by, feed the lubricant. The lubricating oil discharged from the outer peripheral surface of the rotating shaft 1 through the branch hole 22 is an annular shape that exists between the inner peripheral surface of the butted portion of the pair of inner ring elements 18 and 18 and the outer peripheral surface of the rotating shaft 1. It flows through the space 23 and spreads in the circumferential direction, and is discharged to the outer diameter side of the inner ring 16 through the notches 19 and 19. The lubricating oil lubricates the contact portions of the outer ring raceways 15 and 15 and the inner ring raceways 17 and 17 with the rolling surfaces of the rolling elements 20 and 20.
[0007]
In addition to the above-described conventional structure, utility model registration No. 2540979, Japanese Utility Model Laid-Open No. 4-132220, No. 5-94532, No. 6-35653, No. 6-35655, No. 6-35657, No. 6- In Japanese Patent No. 45117, the lubricating oil is supplied to the abutting portion through a minute gap or a small through hole, or the lubricating oil soaked into the porous material is added in small amounts based on centrifugal force. An invention for supplying to the contact portion is described.
[0008]
[Problems to be solved by the invention]
In the case of the conventional rolling bearing device 5 with oil supply means, the outer ring raceways 15, 15 and the inner ring raceways 17, with the overdrive turned on, that is, with the rotary shaft 1 and the housing 4 being rotatable in synchronization. In FIG. 17, wear called fretting is likely to occur. The reason for this is as follows. If the outer ring 13 and the inner ring 16 do not rotate relative to each other as a result of the rotation shaft 1 and the housing 4 rotating synchronously, the rolling elements 20 provided between the outer ring raceways 15 and 15 and the inner ring raceways 17 and 17 are provided. 20 does not roll. Accordingly, the outer ring raceways 15 and 15 and the inner ring raceways 17 and 17 and the rolling surfaces of the rolling elements 20 and 20 remain in contact with each other at the same portion. On the other hand, during the operation of the automatic transmission, the rolling bearing device with oil supply means 5 is subjected to vibration based on unbalance and load fluctuation of each component constituting the automatic transmission.
[0009]
If there is sufficient lubricating oil at the contact portions of the outer ring raceways 15 and 15 and the inner ring raceways 17 and 17 and the rolling surfaces of the rolling elements 20 and 20, no problem will occur. In a state in which the motor 16 does not relatively rotate, there may be a case where sufficient lubricating oil is not necessarily present in the contact portion. That is, when the outer ring 13 and the inner ring 16 do not rotate relative to each other and the rolling elements 20 and 20 do not roll, the outer ring 13 and the inner ring 16 are discharged from the notches 19 and 19, and are Most of the lubricating oil that has reached the portion between the outer ring raceways 15 and 15 is scattered around without reaching the contact portion. As a result, in particular, the lubricating oil present at the contact portion between the rolling surfaces of the rolling elements 20 and 20 existing in the part away from the notches 19 and 19 and the outer ring raceways 15 and 15 and the inner ring raceways 17 and 17. Is likely to be insufficient. When the lubricating oil present in the contact portion is insufficient, the outer ring raceways 15, 15 and the inner ring raceways 17, 17 and the rolling surfaces of the rolling elements 20, 20 are generated based on the occurrence of fretting. Damage such as early peeling tends to occur. In particular, a load based on the centrifugal force is applied to the contact portion between each outer ring raceway 15 and 15 and the rolling surface of each rolling element 20 and 20, and the impact force applied to this contact portion based on vibration is also large. The damage is likely to be a problem.
[0010]
The amount of lubricating oil discharged from each of the notches 19 and 19 is increased, or the number of these notches 19 and 19 is increased so that the distance between all the contact portions and the notches 19 and 19 is increased. If this is shortened, the occurrence of fretting can be prevented. However, increasing the discharge amount of the lubricating oil may cause a decrease in the amount of lubricating oil to other parts, or increase the power loss due to an increase in the size of the oil pump. Sometimes it is not possible. Further, increasing the number of the notches 19 and 19 makes the processing troublesome and causes an increase in cost. In addition, the reduction in the contact area between the butted edges of the pair of inner ring elements 18, 18 reduces the rigidity of the inner ring 16 constituted by these inner ring elements 18, 18 in the axial direction, making it difficult to adjust the preload. As a result, the rolling fatigue life is reduced due to excessive preloading, and rattling due to preload loss tends to occur.
[0011]
In addition, foreign materials such as iron powder generated by wear of the gears constituting the automatic transmission are mixed in the lubricating oil. When this foreign material is supplied to the abutting portion together with the lubricating oil, Indentations and wear are generated on the outer ring raceways 15 and 15 and the inner ring raceways 17 and 17 and the rolling surfaces of the rolling elements 20 and 20. As a result, the rolling fatigue life of the rolling bearing device with oil supply means decreases, and the vibration characteristics and acoustic characteristics during operation of the rolling bearing device with oil supply means also deteriorate.
[0012]
Furthermore, when the oil pump that supplies the lubricating oil to the notches 19 and 19 breaks down, or when the vehicle is pulled without driving the engine, the oil pump does not operate and the automatic shift is performed. When only the gears constituting the machine rotate, there is a possibility that the rolling bearing device with oil supply means 5 will seize relatively early.
The rolling bearing device with oil supply means of the present invention has been invented to eliminate all of these disadvantages.
[0013]
[Means for solving the problems]
The rolling bearing device with oil supply means of the present invention comprises an outer ring having a double row outer ring raceway on the inner peripheral surface and a pair of inner ring elements in the axial direction, similar to the conventional rolling bearing device with oil supply means. An inner ring having a double-row inner ring raceway on the outer peripheral surface, a plurality of rolling elements provided in a freely rotatable manner between each outer ring raceway and each inner ring raceway, and an axially intermediate portion of the inner ring And an oil supply passage which is provided in a portion between the double-row inner ring raceways and discharges lubricating oil supplied from the inner diameter side of the inner ring to the outer diameter side of the inner ring. The outer ring and the inner ring are used in a state including a state where they do not rotate relative to each other.
In particular, in the rolling bearing device with oil supply means according to the present invention, the lubricating oil sent through the oil supply passage can penetrate and pass through, but an annular filter member in which foreign matter mixed in the lubricating oil hardly passes. Is disposed in a state of being sandwiched between the inner ring elements, so that the filter member is provided in series with the oil supply passage.
[0014]
[Action]
The rolling bearing device with oil supply means of the present invention configured as described above has a filter member at a portion between the inner ring raceways of the double row at the axial intermediate portion of the inner ring through the oil supply passage , that is, between the pair of inner ring elements. The lubricating oil discharged from the inner diameter side can be widely distributed over the circumferential direction and the axial direction through this filter member. Therefore, even when the outer ring and the inner ring rotate synchronously and the plurality of rolling elements do not roll, the double row outer ring raceway and the inner ring raceway and the plurality of rolling elements roll from almost the entire outer peripheral surface of the filter member. Sufficient lubricating oil can be supplied to the contact portion with the moving surface. As a result, the occurrence of fretting can be prevented, and the occurrence of damage such as early separation can be effectively prevented from occurring on the double row outer ring raceway and inner ring raceway and the rolling surfaces of the plurality of rolling elements.
[0015]
Further, foreign matter mixed in the lubricating oil discharged from the oil supply passage is collected by the filter member and does not come out to the outer diameter side of the inner ring. Therefore, clean lubricant oil from which foreign matter has been removed can be supplied to the contact portion side. As a result, it is possible to prevent the occurrence of indentation and significant wear due to the foreign matter, and to prevent the rolling fatigue life and the sound deterioration of the rolling bearing device with oil supply means.
[0016]
Furthermore, when the installation part of the rolling bearing device with oil supply means such as an automatic transmission is rotated while the oil pump for supplying the lubricant is not operated, the lubricant soaked in the filter member based on centrifugal force. Gradually exudes and is sent to the contact portion. As a result, after the oil pump is stopped, the time until the rolling bearing device is seized can be lengthened, and the rolling bearing device can be made difficult to seize .
[0017]
DETAILED DESCRIPTION OF THE INVENTION
FIG. 1 shows a first example of an embodiment of the present invention. The feature of the present invention is that the outer ring 13 and the inner ring 16 are rotated synchronously (not relatively rotated), and the double-row outer ring raceways 15 and 15 and the inner ring raceways 17 and 17 and the plurality of rolling elements 20 and 20 are rotated. In this structure, sufficient lubricating oil is supplied to the abutting portion with the rolling surface, foreign matter mixed in the lubricating oil is removed, and further, seizure prevention is performed when the oil pump is stopped. Since the structure and operation of the other parts are the same as those of the conventional structure shown in FIGS. 5 to 6 described above, description of the equivalent parts will be omitted or simplified, and the following description will focus on the characteristic parts of the present invention.
[0018]
In the case of this example, a portion between the pair of inner ring elements 18, 18 constituting the inner ring 16 in the state of being present on the inner diameter side of the inner ring 16 and closing the downstream end opening of the branch hole 22 constituting the oil supply passage. Thus, the annular filter member 25 is disposed so as to be sandwiched between the inner end faces of the inner ring elements 18 and 18. The filter member 25 is made of a porous material such as sintered metal, non-woven fabric, or felt. Examples of such a porous material include a porous material having fine voids that are continuous with each other, and the inner and outer peripheral surfaces of the filter member 25 communicate with each other through the void. It can use without being limited to what was done.
[0019]
The rolling bearing device with oil supply means of the present invention configured as described above has a high rotational speed of the inner ring 16 and a large centrifugal force acting on the lubricating oil that has penetrated the filter member 25 during high-speed operation of the automatic transmission. In this case, the lubricating oil that has permeated the filter member 25 oozes out from the entire outer peripheral surface of the filter member 25 based on the centrifugal force. In this way, the lubricating oil that has oozed out of the filter member 25 flows out almost uniformly over the entire circumference of the outer ring 13 and the inner ring 16 as well as the vicinity of the branch hole 22. Therefore, even if there are only one to several branch holes 22 in the circumferential direction, the lubricating oil soaked into the filter member 25 is not only in the vicinity of the branch holes 22 but also in the outer ring 13 and the inner ring. It can be supplied almost evenly over the entire circumference of 16. As a result, the lubricating oil can be sufficiently fed into the contact portions between the double-row outer ring raceways 15 and 15 and the inner ring raceways 17 and 17 and the rolling surfaces of all the rolling elements 20 and 20. The occurrence of wear due to fretting can be prevented.
[0020]
Further, when the automatic transmission is operated at a low speed, even when the rotational speed of the inner ring 16 is slow and the centrifugal force acting on the lubricating oil that has permeated the filter member 25 is small, the lubricating oil that has permeated the filter member 25 It is extruded based on the additional supply from the branch hole 22, oozes out little by little from the outer peripheral surface of the filter member 25, and adheres to the inner ring raceways 17, 17. The lubricating oil adhering to the inner ring raceways 17 and 17 in this way flows down in each direction based on the rotational movement of the outer ring 13 and the inner ring 16 around the rotating shaft 1 and the rolling elements 20 and 20. It adheres almost evenly over the entire circumference of the outer ring 13 and the inner ring 16 as well as the vicinity of the branch hole 22. As a result, the lubricating oil can be sufficiently fed into the contact portions between the double-row outer ring raceways 15 and 15 and the inner ring raceways 17 and 17 and the rolling surfaces of all the rolling elements 20 and 20. The occurrence of wear due to fretting can be prevented.
[0021]
Therefore, when the overdrive is ON, the outer ring 13 and the inner ring 16 rotate synchronously, and even when the plurality of rolling elements 20 and 20 do not roll, the double-row outer ring raceway 15 is in a state where fretting is likely to occur. 15 and the inner ring raceways 17 and 17 and sufficient contact with the rolling surfaces of the rolling elements 20 and 20 can be supplied with sufficient lubricating oil. As a result, the occurrence of fretting is prevented, and damage such as early peeling occurs on the double-row outer ring raceways 15 and 15 and the inner ring raceways 17 and 17 and the rolling surfaces of the plurality of rolling elements 20 and 20. Can be effectively prevented.
[0022]
Further, since the cross-sectional area of the air gap that exists in the filter member 25 and allows the lubricating oil to pass therethrough is narrow, when the lubricating oil discharged from the branch hole 22 passes through the filter member 25, The foreign matter mixed in is collected by the filter member 25 and removed. Accordingly, it is possible to prevent foreign matters mixed in the lubricating oil discharged from the branch hole 22 from being sent to the contact portion side. As a result, it is possible to prevent wear and indentation from occurring at the contact portions between the outer ring raceways 15 and 15 and the inner ring raceways 17 and 17 and the rolling surfaces of the rolling elements 20 and 20 due to the foreign matter. It is possible to prevent the rolling fatigue life of the rolling bearing device with oil supply means of the invention from being lowered and the vibration characteristics and acoustic characteristics from being deteriorated.
[0023]
Furthermore, when the oil pump for supplying lubricating oil is not operated and the rotating shaft 1 or the like rotates without supplying the lubricating oil through the branch hole 22, the above-described lubricating oil is supplied based on the previous lubricating oil supply. Lubricating oil soaked into the filter member 25 is sent to each contact portion based on centrifugal force. That is, a considerable amount of lubricating oil is stored in the filter member 25 having fine voids inside based on the surface tension. Even after the supply of new lubricating oil through the branch hole 22 is stopped, the lubricating oil gradually oozes out from the outer peripheral surface of the filter member 25 by the centrifugal force to lubricate the contact portions. Therefore, after the oil pump is stopped, the time until these contact portions are seized can be lengthened, so that seizure failures are less likely to occur in the rolling bearing device with the oil supply means.
[0024]
When a sintered metal filter member 25 is used, the width of the filter member 25 in the axial direction (left-right direction in FIG. 1) is regulated to incorporate the filter member 25 in the rolling bearing device with oil supply means of the present invention. The internal clearance (positive or negative clearance) of the rolling bearing can be adjusted to properly regulate the preload applied to the rolling bearing. That is, it is assumed that the outer ring 13, the pair of inner ring elements 18, 18, and the rolling elements 20, 20 are assembled in a state where the internal clearance of the rolling bearing is an appropriate value. If the width dimension of the filter member 25 is restricted to a dimension commensurate with the interval between the inner end faces facing each other, the effort for adjusting the preload applied to the rolling bearing can be reduced.
[0025]
The porosity of the sintered metal can be arbitrarily adjusted by adjusting the particle size of the sintering powder constituting the sintered metal. By adjusting the porosity in this way, the amount of lubricating oil that penetrates into the filter member 25 and passes therethrough can be adjusted, and the amount of lubricating oil supplied to the contact portion side can be arbitrarily set. it can. Further, if heat treatment or the like is performed on the sintered metal, the strength and wear resistance of the filter member 25 made of the sintered metal can be made as desired.
[0026]
On the other hand, even when the filter member 25 is made of non-woven fabric, felt, etc., the lubricating oil discharged from the branch holes 22 enters into the gaps existing inside the non-woven fabric, felt, etc., and this filter member 25 as a whole. To penetrate. The outer ring raceways 15 and 15 and the inner ring raceways 17 and 17 and the rolling elements 20 and 20 are formed from almost the entire outer peripheral surface of the filter member 25 based on the pressure of the supplied lubricating oil and centrifugal force. It is supplied to the contact portion with the rolling surface. In addition, by making a main body portion of the filter member with a hard member such as the sintered metal, by providing a concave portion such as a groove, a hole, and a notch in the main body portion, and incorporating a soft member such as a nonwoven fabric into the concave portion, The filter member can also be configured.
[0027]
Next, FIG. 2 shows a second example of the embodiment of the present invention. In the case of this example, balls are used as the rolling elements 20a and 20a, whereas the first example shown in FIG. 1 described above uses tapered rollers as the rolling elements 20 and 20. As described above, with the use of balls as the rolling elements 20a and 20a, the intervals between the double row outer ring raceways 15a and 15a and the inner ring raceways 17a and 17a are increased. And the width | variety of the filter member 25a provided between each inner ring | wheel elements 18 and 18 is made wide. In addition, as the cages 24a and 24a for holding the rolling elements 20a and 20a so as to be freely rollable, those having an appropriate shape for holding balls are used. Other configurations and operations are the same as those of the first example described above.
[0028]
Next, FIG. 3 shows a third example of the embodiment of the present invention. In the case of this example, an example is shown in which the first example shown in FIG. 1 described above and the prior invention (Japanese Patent Application No. 9-77953) are combined. In the case of this example, cages 26 and 26 for holding a plurality of rolling elements 20 and 20 provided between the outer ring raceways 15 and 15 and the inner ring races 17 and 17 in a double row are respectively provided so as to freely roll. These are formed by injection molding synthetic resins each having oil resistance. Then, the inner ends of these cages 26, 26 (ends facing the center in the axial direction of the rolling bearing device with oil supply means and facing each other) are circumferentially long and discharged from the branch hole 22. Concave grooves 27 and 27 for temporarily storing lubricating oil are provided. Each of these concave grooves 27, 27 exists in a portion facing the outer peripheral surface of the filter member 25 provided between the pair of inner ring elements 18, 18 constituting the inner ring 16.
[0029]
During operation of the rolling bearing device with oil supply means of the present example configured as described above, the lubricating oil that flows from the inner side to the outer side of the branch hole 22 and exudes from the outer peripheral surface of the filter member 25, Due to the centrifugal force associated with the rotation, it scatters to the surroundings, and part of it is collected in the concave grooves 27 and 27. During the high speed operation of the automatic transmission, the rotational speeds of the cages 26, 26 provided with the concave grooves 27, 27 are fast, and the centrifugal force acting on the lubricating oil collected in the concave grooves 27, 27. Is large, the lubricating oil collected in each of the concave grooves 27 and 27 accumulates in the concave grooves 27 and 27 as they are, and finally overflows from the concave grooves 27 and 27. Thus, the lubricating oil overflowing from the concave grooves 27, 27 flows out not only in the vicinity of the branch hole 22 but also over the entire circumference of the outer ring 13 and the inner ring 16. As a result, the lubricating oil can be sufficiently fed into the contact portions between the double-row outer ring raceways 15 and 15 and the inner ring raceways 17 and 17 and the rolling surfaces of all the rolling elements 20 and 20. The occurrence of wear due to fretting can be prevented.
[0030]
Further, when the automatic transmission is operated at a low speed, the rotational speeds of the cages 26 and 26 are slow and the centrifugal force acting on the lubricating oil collected in the concave grooves 27 and 27 is small. The lubricating oil collected in the concave grooves 27 and 27 flows down from the concave grooves 27 and 27 based on the action of gravity, and adheres to the opposed inner ring raceways 17 and 17. The lubricating oil adhering to the inner ring raceways 17 and 17 in this way flows down in each direction based on the rotational movement of the outer ring 13 and the inner ring 16 around the rotating shaft 1 and the rolling elements 20 and 20. It adheres not only in the vicinity of the branch hole 22 but also over the entire circumference of the outer ring 13. As a result, the lubricating oil can be sufficiently fed into the contact portions between the double-row outer ring raceways 15 and 15 and the inner ring raceways 17 and 17 and the rolling surfaces of all the rolling elements 20 and 20. The occurrence of wear due to fretting can be prevented. As a result, it is possible to effectively prevent the occurrence of damage such as early peeling on the double-row outer ring raceways 15 and 15 and the inner ring raceways 17 and 17 and the rolling surfaces of the plurality of rolling elements 20 and 20. Other configurations and operations are the same as those of the first example described above. In addition, the performance of the rolling bearing device with the oil supply means of the present invention can be further improved by combining the prior invention which operates as described above with the structure of the first example of the present invention.
[0031]
Next, FIG. 4 shows a fourth example of the embodiment of the present invention. While the third example shown in FIG. 3 uses tapered rollers as the rolling elements 20 and 20, in this example, balls are used as the rolling elements 20a and 20a. In other words, the concave grooves 27 and 27 which are the characteristic portions of the prior invention shown in the third example are combined with the structure of the second example of the present invention. Also in the case of such a rolling bearing device with oil supply means of this example, the occurrence of fretting is prevented and damage such as early peeling is prevented by the same action as in the third example.
[0032]
【The invention's effect】
Since the rolling bearing device with oil supply means of the present invention is configured and operates as described above, it is possible to reduce the amount of lubricating oil supplied to other parts and to increase the size of the oil pump without increasing the size of the oil pump. It is possible to effectively prevent the occurrence of damage such as early peeling on the raceway and inner ring raceway and the rolling surfaces of a plurality of rolling elements, and to realize an automatic transmission having high performance and excellent durability. It can contribute to the performance improvement of various mechanical devices. Furthermore, seizure is less likely to occur when the oil pump is stopped, and the reliability in the event of a failure can be improved.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing a first example of an embodiment of the present invention and corresponding to part A of FIG.
FIG. 2 is a view similar to FIG. 1, showing the second example.
FIG. 3 is a view similar to FIG. 1, showing the third example.
FIG. 4 is a view similar to FIG. 1, showing the fourth example.
FIG. 5 is a partial cross-sectional view of an automatic transmission for an automobile incorporating a rolling bearing device with oil supply means that is a subject of the present invention.
6 is an enlarged cross-sectional view taken along the line BB in FIG. 5, showing only the rolling bearing device portion with oil supply means.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Rotating shaft 2 Sun gear 3 Sleeve 4 Housing 5 Rolling bearing device 6 with oil supply means 6 Ring gear 7 Input gear 8 Support frame 9 Support shaft 10 Planetary gear 11 Control cylinder 12 Clutch mechanism 13 Outer ring 14 Stop ring 15, 15a Outer ring track 16 Inner ring 17 17a Inner ring raceway 18 Inner ring element 19 Notch 20, 20a Rolling element 21 Oil supply hole 22 Branch hole 23 Annular space 24, 24a Retainer 25, 25a Filter member 26 Retainer 27 Concave groove

Claims (1)

内周面に複列の外輪軌道を有する外輪と、１対の内輪素子を軸方向に配置して成り、外周面に複列の内輪軌道を有する内輪と、上記各外輪軌道と各内輪軌道との間にそれぞれ複数個ずつ転動自在に設けられた転動体と、上記内輪の軸方向中間部で上記複列の内輪軌道の間部分に設けられ、上記内輪の内径側から供給された潤滑油をこの内輪の外径側に吐出する給油通路とを備え、上記外輪と上記内輪とが相対回転しない状態を含む状態で使用される給油手段付転がり軸受装置に於いて、上記給油通路を通じて送られる潤滑油が浸透及び通過自在であるが、この潤滑油中に混入した異物が通過しにくい円環状のフィルタ部材を、上記両内輪素子同士の間に挟持した状態で配置する事により、このフィルタ部材を上記給油通路に対し直列に設けた事を特徴とする給油手段付転がり軸受装置。An outer ring having a double row outer ring raceway on the inner peripheral surface, an inner ring having a pair of inner ring elements arranged in the axial direction and having a double row inner ring raceway on the outer peripheral surface, each outer ring raceway and each inner ring raceway, A plurality of rolling elements provided between each of the inner rings, and a lubricating oil provided at an intermediate portion in the axial direction of the inner ring between the double row inner ring raceways and supplied from an inner diameter side of the inner ring In a rolling bearing device with oil supply means that is used in a state including a state in which the outer ring and the inner ring do not rotate relative to each other, and is fed through the oil supply passage. This filter member is formed by arranging an annular filter member that allows the lubricating oil to permeate and pass, but is difficult for foreign matters mixed in the lubricating oil to pass between the inner ring elements. It was provided in series with the oil supply passage Rolling bearing device with oil supply means characterized by the above.
JP08567698A 1998-03-31 1998-03-31 Rolling bearing device with oil supply means Expired - Lifetime JP4003284B2 (en)

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JP2002081443A (en) * 2000-09-05 2002-03-22 Nsk Ltd Lubricant feeder
JP4759824B2 (en) * 2001-03-23 2011-08-31 日本精工株式会社 Toroidal continuously variable transmission
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