JP2004263838A - Roller bearing device - Google Patents

Roller bearing device Download PDF

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Publication number
JP2004263838A
JP2004263838A JP2003057382A JP2003057382A JP2004263838A JP 2004263838 A JP2004263838 A JP 2004263838A JP 2003057382 A JP2003057382 A JP 2003057382A JP 2003057382 A JP2003057382 A JP 2003057382A JP 2004263838 A JP2004263838 A JP 2004263838A
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Japan
Prior art keywords
bearing device
roller bearing
ring member
raceway surface
annular
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Pending
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JP2003057382A
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Japanese (ja)
Inventor
Akiyuki Suzuki
章之 鈴木
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Koyo Seiko Co Ltd
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Koyo Seiko Co Ltd
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Publication date
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Priority to JP2003057382A priority Critical patent/JP2004263838A/en
Publication of JP2004263838A publication Critical patent/JP2004263838A/en
Pending legal-status Critical Current

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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
    • 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
    • F16C33/46—Cages for rollers or needles
    • 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
    • F16C19/36—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 a single row of rollers
    • F16C19/364—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 a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • 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
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
    • F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling 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
    • 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
    • F16C33/6674—Details of supply of the liquid to the bearing, e.g. passages or nozzles related to the amount supplied, e.g. gaps to restrict flow of the liquid
    • 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7893—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a cage or integral therewith
    • 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
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/56—Systems consisting of a plurality of bearings with rolling friction in which the rolling bodies of one bearing differ in diameter from those of another
    • 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To solve a problem of excessively large agitation resistance when rollers roll depending on the quantity of oil supplied to raceway surfaces in a roller bearing device. <P>SOLUTION: This roller bearing device is provided with a first lip 44 and a second lip 53 slidable in contact with outer circumferential surfaces 27a and 28a of a small diameter shoulder part 27 in a first inner ring member 22 of a first conical roller bearing device 15, and a small diameter shoulder part 28 in a second inner ring member 47 of a second conical roller bearing device 17. As oil 39 flows into circular spaces 37 and 38, flow is limited for parts where the circular spaces 37 and 38 are closed on the diametrically inner side, and it flows into large diameter side passages 40 and 41 of the circular spaces 37 and 38. Necessary quantity of oil 39 can thus be introduced to the circular spaces 37 and 38, and excessively large agitation resistance can be restricted. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

【０００１】
【発明の属する技術分野】
本発明は、ころ軸受装置に関する。
【０００２】
【従来の技術】
一般に、車両にはデファレンシャル装置が付設され、このデファレンシャル装置のピニオン軸は、ころ軸受装置を介してデフケースに回転自在に支持されている。（例えば、特許文献１参照）
前記ころ軸受装置は、デフケース内に嵌着される外輪部材と、ピニオン軸の途中に外嵌する内輪部材と、外輪部材および内輪部材間に転動自在に配置される複数個の円すいころと、これら円すいころを円周方向等配位置に保持する保持器とを有する。この種のデファレンシャル装置では、ピニオン軸の回転とともにデフケース内のオイルがころ軸受装置の軌道面に供給される。
【０００３】
しかし、上記ころ軸受装置では、軌道面に供給されるオイル量によっては、円すいころが転動する際の攪拌抵抗が大きくなりすぎる場合が考えられる。
【０００４】
そこで、図９に示すように、外輪部材１００および内輪部材１０１の間の環状空間１０２内にオイルの流入を阻止するために、保持器１０３の鍔部１０４にシール１０５を設ける技術がある（特許文献２）。
【０００５】
【特許文献１】
特開平１１−４８８０５号（図１，第３頁）
【特許文献２】
実開昭５９−７２３１８号（図４）
【０００６】
【発明が解決しようとする課題】
しかし、保持器１０３の鍔部１０４にシール１０５を設けてオイルの流入を阻止すると、今度はオイルの量が不足する場合が考えられる。
【０００７】
【課題を解決するための手段】
本発明のころ軸受装置は、外輪軌道面を内周面に有する外輪部材と、該外輪部材の径方向内方に同心に配置されるとともに、内輪軌道面を外周面に有する内輪部材と、前記外輪軌道面および前記内輪軌道面の間に転動自在に配置される複数個のころと、これらころを円周方向所定間隔に保持するための保持器とが設けられ、前記保持器の幅方向一方側端部に、潤滑油量制限用の環状弾性体が、前記内輪軌道面の幅方向一方側端部の近傍、または前記外輪軌道面の幅方向一方側端部の近傍に接触して摺動可能に設けられ、前記外輪部材と前記内輪部材との間の環状空間内を、その一方側から他方側に向けて潤滑油が通過する場所で使用される。
【０００８】
上記ころ軸受装置において、軌道輪、すなわち外輪部材あるいは内輪部材の肩部に接触可能な弾性を有する環状弾性体の存在によって、潤滑油が流入可能な面積が小さく絞られているため、潤滑油が必要な量だけ環状空間内に一方側から他方側へ向けて流入する。このため、ころが転動する際の潤滑油による攪拌抵抗が最小限に抑えられる。
【０００９】
また、本発明のころ軸受装置は、外輪軌道面を内周面に有する外輪部材と、該外輪部材の径方向内方に同心に配置されるとともに、内輪軌道面を外周面に有する内輪部材と、前記外輪軌道面および前記内輪軌道面の間に転動自在に配置される複数個の円すいころと、これら円すいころを円周方向所定間隔に保持するための保持器とが設けられ、前記保持器の小端側端部に、潤滑油量制限用の環状弾性体が、前記内輪部材の小端側肩部に接触して摺動可能に設けられ、前記外輪部材と前記内輪部材との間の環状空間内を、その小端側から大端側に向けて潤滑油が通過する場所で使用される。
【００１０】
上記構成において内輪部材の肩部に接触可能な弾性を有する環状弾性体の存在によって、潤滑油が流入可能な面積が小さく絞られているため、潤滑油が必要な量だけ環状空間内に小端側から大端側へ向けて流入する。このため、ころが転動する際の潤滑油による攪拌抵抗が最小限に抑えられる。
【００１１】
【発明の実施の形態】
以下、本発明の実施の形態を、ころ軸受装置の一例としての円すいころ軸受装置を例に図面に基づいて説明する。この実施の形態では、円すいころ軸受装置を車両に設けられるデファレンシャル装置に用いている。
【００１２】
図１はデファレンシャル装置の全体構成を示す断面図、図２は円すいころ軸受装置の使用状態を示す拡大断面図、図３は図２の要部をさらに拡大した断面図、図４は一方の円すいころ軸受装置の正面図である。
【００１３】
図１に示すように、デファレンシャル装置１は、デファレンシャルケース２を有する。デファレンシャルケース２は、フロントケース３とリヤケース４とからなり、両者はボルト・ナット５により取付けられている。
【００１４】
このデファレンシャルケース２は、左右の車輪を差動連動する差動変速機構６、一側にピニオンギヤ７を有するピニオン軸８（ドライブピニオン）を内装している。ピニオンギヤ７は、差動変速機構６のリングギヤ９に噛合されている。ピニオン軸８の軸部１０は、ピニオンギヤ側に比べて反ピニオンギヤ側ほど小径となるよう段状に形成されている。
【００１５】
フロントケース３の内方に、ころ軸受装置装着用の環状壁１１，１２が形成されている。ピニオン軸８の軸部１０のピニオンギヤ側は、第一円すいころ軸受装置１５を介して環状壁１１に軸心１６周りに回転自在に支持されている。ピニオン軸８の軸部１０の反ピニオンギヤ側は、第二円すいころ軸受装置１７を介して環状壁１２に軸心１６周りに回転自在に支持されている。
【００１６】
図２に示すように、第一円すいころ軸受装置１５は、内周面に外輪軌道面１８を有する環状の第一外輪部材２０と、第一組品２１とから構成されている。この第一組品２１は、ピニオン軸８の軸部１０のピニオンギヤ側に外嵌挿通する第一内輪部材２２と、複数個の第一円すいころ２３と、これら第一円すいころ２３を円周方向等配位置に保持するための、環状でプレス製の第一保持器２４とを有する。
【００１７】
第一内輪部材２２の軸方向各側に、環状の大径肩部２５および環状の小径肩部２７が形成されている。大径肩部２５および小径肩部２７間の第一内輪部材２２の外周面が、傾斜した内輪軌道面３０とされる。外輪軌道面１８と内輪軌道面３０との間に前記第一円すいころ２３が転動自在に配置されている。
【００１８】
第一保持器２４は、円周方向に等配位置に形成されたポケット３２と、これらポケット３２の反ピニオンギヤ側に、第一内輪部材２２の小径肩部２７側位置に径方向内方に向けて折曲された第一環状鍔部３４とを有する。第一保持器２４は、ポケット３２のピニオンギヤ側に幅方向（傾斜方向）に延長された環状部３５を有する。第一外輪部材２０と第一内輪部材２２との間の環状空間３７は、第一保持器２４によって、オイル（潤滑油）３９の大径側流路４０と小径側流路４２とを有する。
【００１９】
図３および図４に示すように、第一環状鍔部３４の径方向内方端部に、環状弾性体としての、合成ゴム製の第一リップ４４が加硫成型によって形成されている。この第一リップ４４は、先尖形状に形成されており、その尖端部４４ａは小径肩部２７の外周面２７ａ、すなわち第一内輪部材２２の内輪軌道面３０の軸方向外方近傍部位に接触して摺動可能とされている。
【００２０】
第一組品２１は、予め環状壁１１に嵌着されている第一外輪部材２０に組付けられるもので、第一組品２１は、第一内輪部材２２をピニオン軸８に挿通した状態でデフケース内に、ピニオンギヤ側から反ピニオンギヤ側に向けて軸心１６方向から挿入され、かつ第一円すいころ２３の転動面が外輪軌道面１８に接触するよう組付けられる。
【００２１】
図２に示すように、第二円すいころ軸受装置１７は、内周面に外輪軌道面１９を有する環状の第二外輪部材４５と、第二組品４６とから構成されている。この第二組品４６は、ピニオン軸８の軸部１０の反ピニオンギヤ側に外嵌挿通する第二内輪部材４７と、複数個の第二円すいころ５０と、これら第二円すいころ５０を円周方向等配位置に保持するための、環状でプレス製の第二保持器５１とを有する。
【００２２】
第二内輪部材４７の軸方向各側に、環状の大径肩部２６および環状の小径肩部２８が形成されている。大径肩部２６および小径肩部２８間の第二内輪部材４７の外周面が、内輪軌道面３１とされる。外輪軌道面１９と内輪軌道面３１との間に前記第二円すいころ５０が転動自在に配置されている。
【００２３】
第二保持器５１は、円周方向に等配位置に形成されたポケット３３と、これらポケット３３のピニオンギヤ側に、第二内輪部材４７の小径肩部２８側位置に径方向内方に向けて折曲された第二環状鍔部５２とを有する。第二保持器５１は、ポケット３３の反ピニオンギヤ側に幅方向（傾斜方向）に延長された環状部３６を有する。第二外輪部材４５と第二内輪部材４７との間の環状空間３８は、第二保持器５１によって、オイル３９の大径側流路４１と小径側流路４３とを有する。
【００２４】
図３に示すように、第二環状鍔部５２の端部に環状弾性体としての、合成ゴム製の第二リップ５３が加硫成型によって形成されている。この第二リップ５３は、先尖形状に形成されており、その尖端部５３ａは小径肩部２８、すなわち内輪軌道面３１の軸方向外方近傍部位の外周面２８ａに接触して摺動可能とされている。
【００２５】
第二組品４６は、予め環状壁１２に嵌着されている第二外輪部材４５に組付けられるもので、第二組品４６は、第二内輪部材４７をピニオン軸８に外嵌挿通するようにデフケース内に、反ピニオンギヤ側からピニオンギヤ側に向けて軸心１６方向から挿入され、第二円すいころ５０の転動面を外輪軌道面１９に接触するよう組付けられる。
【００２６】
ピニオン軸８の軸部１０の途中で第一内輪部材２２と第二内輪部材４７との間に、予圧設定用の塑性スペーサ５５が配置されている。第二内輪部材４７は塑性スペーサ５５と遮蔽板５６とで軸心１６方向から挟持されている。
【００２７】
図１に示すように、フロントケース３の外壁とピニオンギヤ側の環状壁１１の間に、オイル循環路５７が形成されており、このオイル循環路５７のオイル入口５８はリングギヤ側に開口され、オイル循環路５７のオイル出口６０は、環状壁１１，１２間に開口されている。
【００２８】
デファレンシャル装置１は、コンパニオンフランジ６５を有する。このコンパニオンフランジ６５は、胴部６６と、この胴部６６に一体的に形成されるフランジ部６７とを有する。胴部６６は、ピニオン軸８の軸部１０の反ピニオンギヤ側、すなわち不図示のドライブシャフト側に外嵌するものである。
【００２９】
胴部６６のピニオンギヤ側端面と第二円すいころ軸受装置１７の第二内輪部材４７端面との間に、前記遮蔽板５６が介装されている。胴部６６の外周面とフロントケース３の反ピニオンギヤ側開口内周面との間に、オイルシール７０が配置されている。
【００３０】
オイルシール７０を覆うためのシール保護カップ７１が、フロントケース３の反ピニオンギヤ７側開口部に取付けられている。軸部１０の反ピニオンギヤ７側外端部にねじ部７２が形成され、このねじ部７２は、フランジ部６７の中心凹部７３に突出している。ねじ部７２に、ナット７４が螺着されている。
【００３１】
このように、ねじ部７２にナット７４が螺着されることで、第一円すいころ軸受装置１５の第一内輪部材２２、および第二円すいころ軸受装置１７の第二内輪部材４７がピニオンギヤ７の端面とコンパニオンフランジ６５の端面とで軸心１６方向に挟み込まれ、遮蔽板５６および塑性スペーサ５５を介して、第一円すいころ軸受装置１５および第二円すいころ軸受装置１７に対して所定の予圧が付与された状態となる。
【００３２】
上記構成のデファレンシャル装置１において、ドライブシャフトの回転に伴なってピニオン軸８が第一円すいころ軸受装置１５、および第二円すいころ軸受装置１７に支持された状態で軸心１６周りに回転する。ピニオン軸８の回転に伴なって第一円すいころ軸受装置１５の第一内輪部材２２、および第二円すいころ軸受装置１７の第二内輪部材４７がそれぞれ軸心１６周りに回転する。
【００３３】
このとき、第一リップ４４、第二リップ５３は、それぞれ第一内輪部材２２、第二内輪部材４７の小径肩部２７，２８の外周面２７ａ，２８ａに接触して摺動する。また、ピニオン軸８の回転に伴なってリングギヤ９が回転する。
【００３４】
オイル３９は、リングギヤ９の回転に伴って跳ね上げられ、フロントケース３内のオイル循環路５７を通って第一円すいころ軸受装置１５、および第二円すいころ軸受装置１７側に供給されるように導かれる。続いて、第一円すいころ軸受装置１５の環状空間３７、第二円すいころ軸受装置１７の環状空間３８に流入して軌道面を潤滑した後、環状空間３７，３８それぞれから排出される。
【００３５】
ところで、第一リップ４４、第二リップ５３は、それぞれ第一内輪部材２２、第二内輪部材４７の小径肩部２７，２８の外周面２７ａ，２８ａに接触しており、このため環状空間３７，３８の径方向内方側は塞がれ、環状空間３７，３８の径方向外方が開放されているのみである。
【００３６】
このため、オイル３９が環状空間３７，３８それぞれに流入するとき、環状空間３７，３８の径方向内方側が塞がれている分だけ流量を制限されて、大径側流路４０，４１から環状空間３７，３８に流入する。従って、必要な量のオイル３９を環状空間３７，３８内に導入することができ、第一円すいころ２３、第二円すいころ５０の転動時の攪拌抵抗が大きくなるのを抑えることができる。
【００３７】
環状空間３７，３８内に流入したオイル３９は、環状空間３７，３８内でそれぞれ大径側流路４０，４１から小径側流路４２，４３に分岐して流れ、第一円すいころ軸受装置１５、および第二円すいころ軸受装置１７の軌道面を潤滑し、例えば第一内輪部材２２、第二内輪部材４７の回転に伴なう遠心力によって、環状空間３７，３８から外部へ排出される。
【００３８】
なお、第一リップ４４、第二リップ５３それぞれは、製造時の公差によっては初期状態で尖端部４４ａ，５３ａが、第一内輪部材２２、第二内輪部材４７の小径肩部２７，２８の外周面に接触しにくい場合も考えられるが、第一円すいころ２３、第二円すいころ５０の転動動作に伴なって接触し、摺動する。
【００３９】
そして使用による摺動動作に伴なって尖端部４４ａ，５３ａが摩耗し、次第に小径肩部２７，２８の外周面との接触面積も大きくなり、確実にオイル３９の流入を抑え、攪拌抵抗を抑えることができる。
【００４０】
上記実施の形態は、本発明を円すいころ軸受装置を例に説明した。しかし本発明は、円筒ころ軸受装置にも適用できる。図５〜図８は円筒ころ軸受装置の実施の形態を示す。
【００４１】
図５〜図８に示す円筒ころ軸受装置７５は、例えばトランスミッションに用いられ、何れも外輪部材７６、内輪部材７７、複数個の円筒ころ７８、およびこれら円筒ころ７８を円周方向等配位置に保持する保持器７９とから構成されている。円筒ころ７８は、外輪部材７６の内周面に形成された外輪軌道面８０および内輪部材７７の外周面に形成された内輪軌道面８１間に転動自在に配置されている。なお、保持器７９はプレス製保持器であっても、もみ抜き保持器であってもよい。
【００４２】
図５で示す円筒ころ軸受装置７５は、内輪部材７７の軸方向両側に内輪軌道面８１より大径の肩部８２，８３を有する。また保持器７９は、軸方向両側に径方向内方に折曲された環状部８４，８５を有する。一方側（オイル流入側）の環状部８４に、一方側の肩部８２外周面に接触する環状リップ８６が設けられている。リップ８６の形状は上記実施の形態と同様であり、尖端部８６ａが一方側の肩部８２の外周面に接触して摺動可能とされている。
【００４３】
図６で示す円筒ころ軸受装置７５は、内輪部材７７の軸方向両側に内輪軌道面８１より大径の肩部８２，８３を有する。また保持器７９は、軸方向両側に径方向外方に折曲された環状部８４，８５を有する。一方側（オイル流入側）の環状部８４に、外輪部材７６の一方側の肩部７６ａ内周面に接触するリップ８６が設けられている。リップ８６の形状は上記実施の形態と同様であり、尖端部８６ａが一方側の肩部７６ａの内周面に接触して摺動可能とされている。
【００４４】
図７で示す円筒ころ軸受装置７５は、外輪部材７６の軸方向両側に外輪軌道面８０より小径の肩部７６ａ，７６ｂを有する。また保持器７９は、軸方向両側に径方向内方に折曲された環状部８４，８５を有する。一方側（オイル流入側）の環状部８４に、内輪部材７７の一方側の肩部８２外周面に接触するリップ８６が設けられている。リップ８６の形状は上記実施の形態と同様であり、尖端部８６ａが一方側の肩部８２の外周面に接触して摺動可能とされている。
【００４５】
図８で示す円筒ころ軸受装置７５は、外輪部材７６の軸方向両側に外輪軌道面８０より小径の肩部７６ａ，７６ｂを有する。また保持器７９は、軸方向両側に径方向外方に折曲された環状部８４，８５を有する。一方側（オイル流入側）の環状部８４に、外輪部材７６の一方側の肩部７６ａ外周面に接触するリップ８６が設けられている。リップ８６の形状は上記実施の形態と同様であり、尖端部８６ａが一方側の肩部７６ａの外周面に接触して摺動可能とされている。
【００４６】
これら何れの円筒ころ軸受装置７５においても、オイルの流量を抑えて、円筒ころ７８転動時の攪拌抵抗の上昇を抑えることができる。
【００４７】
【発明の効果】
以上の説明から明らかな通り、本発明のころ軸受装置によれば、外輪部材あるいは内輪部材の軌道面近傍に接触可能な環状弾性体の存在によって、潤滑油が必要な量だけ環状空間内に流入するため、ころが転動する際の潤滑油による攪拌抵抗を最小限に抑えることができる。
【図面の簡単な説明】
【図１】本発明のデファレンシャル装置の全体構成を示す断面図である。
【図２】同じく円すいころ軸受装置の使用状態を示す拡大断面図である。
【図３】同じく図２の要部をさらに拡大した断面図である。
【図４】同じく一方の円すいころ軸受装置の正面図である。
【図５】別の実施の形態を示す円筒ころ軸受装置の半断面図である。
【図６】別の実施の形態を示す円筒ころ軸受装置の半断面図である。
【図７】別の実施の形態を示す円筒ころ軸受装置の半断面図である。
【図８】別の実施の形態を示す円筒ころ軸受装置の半断面図である。
【図９】従来の円すいころ軸受装置の半断面図である。
【符号の説明】
１ デファレンシャル装置
２ デファレンシャルケース
６ 差動変速機構
８ ピニオン軸
９ リングギヤ
１１，１２ 環状壁
１５ 第一円すいころ軸受装置
１７ 第二円すいころ軸受装置
１８，１９ 外輪軌道面
２０ 第一外輪部材
２１ 第一組品
２２ 第一内輪部材
２３ 第一円すいころ
２４ 第一保持器
２５ 大径肩部
２７ 小径肩部
３０ 内輪軌道面
３４ 第一環状鍔部
３５ 環状部
３７ 環状空間
３９ オイル
４０ 大径側流路
４２ 小径側流路
４４ 第一リップ
４４ａ 尖端部
２７ａ 小径肩部の外周面
１８ 外輪軌道面
４５ 第二外輪部材
４６ 第二組品
４７ 第二内輪部材
５０ 第二円すいころ
５１ 第二保持器[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a roller bearing device.
[0002]
[Prior art]
Generally, a differential device is attached to a vehicle, and a pinion shaft of the differential device is rotatably supported by a differential case via a roller bearing device. (For example, see Patent Document 1)
The roller bearing device includes an outer ring member fitted in a differential case, an inner ring member fitted outside the pinion shaft, and a plurality of tapered rollers that are arranged to be rollable between the outer ring member and the inner ring member, And a retainer for retaining these tapered rollers at equally spaced positions in the circumferential direction. In this type of differential device, the oil in the differential case is supplied to the raceway surface of the roller bearing device as the pinion shaft rotates.
[0003]
However, in the above-described roller bearing device, depending on the amount of oil supplied to the raceway surface, the stirring resistance when the tapered rollers roll may be too large.
[0004]
Therefore, as shown in FIG. 9, there is a technique in which a seal 105 is provided on a flange 104 of a retainer 103 in order to prevent oil from flowing into an annular space 102 between an outer ring member 100 and an inner ring member 101. Reference 2).
[0005]
[Patent Document 1]
JP-A-11-48805 (FIG. 1, page 3)
[Patent Document 2]
No. 59-72318 (Fig. 4)
[0006]
[Problems to be solved by the invention]
However, when the seal 105 is provided on the flange 104 of the retainer 103 to prevent the inflow of oil, the amount of oil may be insufficient this time.
[0007]
[Means for Solving the Problems]
The roller bearing device of the present invention is an outer ring member having an outer ring raceway surface on an inner peripheral surface, and an inner ring member which is disposed concentrically radially inward of the outer ring member and has an inner ring raceway surface on an outer peripheral surface, A plurality of rollers arranged rotatably between the outer raceway surface and the inner raceway surface, and a retainer for holding these rollers at predetermined circumferential intervals are provided, and a width direction of the retainer is provided. At one end, an annular elastic body for limiting the amount of lubricating oil slides in contact with the vicinity of one end in the width direction of the inner raceway surface or the vicinity of one end in the width direction of the outer raceway surface. It is movably provided and is used in a place where lubricating oil passes from one side to the other side in the annular space between the outer ring member and the inner ring member.
[0008]
In the above roller bearing device, the raceway, that is, the presence of the annular elastic body having elasticity capable of contacting the shoulder of the outer ring member or the inner ring member reduces the area through which the lubricating oil can flow, so that the lubricating oil is reduced. A necessary amount flows into the annular space from one side to the other side. For this reason, the stirring resistance by the lubricating oil when the rollers roll is minimized.
[0009]
Further, the roller bearing device of the present invention includes an outer ring member having an outer ring raceway surface on an inner peripheral surface, and an inner ring member disposed concentrically radially inward of the outer ring member and having an inner ring raceway surface on an outer peripheral surface. A plurality of tapered rollers arranged rotatably between the outer raceway surface and the inner raceway surface, and a retainer for holding these tapered rollers at predetermined intervals in a circumferential direction; An annular elastic body for restricting the amount of lubricating oil is provided at the small end side end of the container so as to be slidable in contact with the small end side shoulder of the inner ring member, and between the outer ring member and the inner ring member. Is used in a place where lubricating oil passes from the small end to the large end in the annular space.
[0010]
In the above configuration, the area through which the lubricating oil can flow is narrowed down due to the presence of the annular elastic body having elasticity capable of contacting the shoulder of the inner ring member. From the side toward the large end. For this reason, the stirring resistance by the lubricating oil when the rollers roll is minimized.
[0011]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings, taking a tapered roller bearing device as an example of a roller bearing device as an example. In this embodiment, a tapered roller bearing device is used for a differential device provided in a vehicle.
[0012]
1 is a cross-sectional view showing the entire configuration of a differential device, FIG. 2 is an enlarged cross-sectional view showing a tapered roller bearing device in use, FIG. 3 is a cross-sectional view showing a further enlarged main part of FIG. 2, and FIG. It is a front view of a roller bearing device.
[0013]
As shown in FIG. 1, the differential device 1 has a differential case 2. The differential case 2 includes a front case 3 and a rear case 4, both of which are attached by bolts and nuts 5.
[0014]
The differential case 2 includes a differential transmission mechanism 6 for differentially interlocking left and right wheels, and a pinion shaft 8 (drive pinion) having a pinion gear 7 on one side. The pinion gear 7 is meshed with a ring gear 9 of the differential transmission mechanism 6. The shaft portion 10 of the pinion shaft 8 is formed in a stepped shape so as to have a smaller diameter on the side opposite to the pinion gear than on the side of the pinion gear.
[0015]
Inside the front case 3, annular walls 11, 12 for mounting the roller bearing device are formed. The pinion gear side of the shaft portion 10 of the pinion shaft 8 is rotatably supported on the annular wall 11 around the axis 16 via the first tapered roller bearing device 15. The anti-pinion gear side of the shaft portion 10 of the pinion shaft 8 is rotatably supported around the axis 16 on the annular wall 12 via a second tapered roller bearing device 17.
[0016]
As shown in FIG. 2, the first tapered roller bearing device 15 includes an annular first outer ring member 20 having an outer ring raceway surface 18 on an inner peripheral surface, and a first assembly 21. The first assembly 21 includes a first inner ring member 22 that is externally inserted into the shaft portion 10 of the pinion shaft 8 on the pinion gear side, a plurality of first tapered rollers 23, and these first tapered rollers 23 are arranged in the circumferential direction. It has an annular, press-made first retainer 24 for holding in an evenly distributed position.
[0017]
An annular large-diameter shoulder 25 and an annular small-diameter shoulder 27 are formed on each axial side of the first inner ring member 22. The outer peripheral surface of the first inner race member 22 between the large-diameter shoulder portion 25 and the small-diameter shoulder portion 27 is an inclined inner raceway surface 30. The first tapered roller 23 is arranged between the outer raceway surface 18 and the inner raceway surface 30 so as to roll freely.
[0018]
The first retainer 24 has a plurality of pockets 32 formed at equidistant positions in the circumferential direction, and a radially inward position on the anti-pinion gear side of these pockets 32 at a position on the small diameter shoulder 27 side of the first inner ring member 22. And a first annular flange 34 bent. The first retainer 24 has an annular portion 35 extending in the width direction (inclination direction) on the pinion gear side of the pocket 32. The annular space 37 between the first outer ring member 20 and the first inner ring member 22 has a large diameter channel 40 and a small diameter channel 42 of oil (lubricating oil) 39 by the first retainer 24.
[0019]
As shown in FIGS. 3 and 4, a first lip 44 made of synthetic rubber as an annular elastic body is formed by vulcanization molding at a radially inner end of the first annular flange portion 34. The first lip 44 is formed in a pointed shape, and its pointed end 44 a contacts the outer peripheral surface 27 a of the small-diameter shoulder 27, that is, the portion near the axially outer side of the inner raceway surface 30 of the first inner race member 22. Slidable.
[0020]
The first assembly 21 is attached to the first outer ring member 20 that has been fitted to the annular wall 11 in advance, and the first assembly 21 is in a state where the first inner ring member 22 is inserted through the pinion shaft 8. It is inserted into the differential case from the pinion gear side toward the anti-pinion gear side from the axial center 16 direction, and is assembled so that the rolling surface of the first tapered roller 23 contacts the outer ring raceway surface 18.
[0021]
As shown in FIG. 2, the second tapered roller bearing device 17 includes an annular second outer ring member 45 having an outer ring raceway surface 19 on an inner peripheral surface, and a second assembly 46. The second assembly 46 includes a second inner ring member 47 that is fitted and inserted into the shaft portion 10 of the pinion shaft 8 on the side opposite to the pinion gear, a plurality of second tapered rollers 50, and the second tapered rollers 50. It has an annular, press-made second retainer 51 for holding in the direction equidistant position.
[0022]
An annular large-diameter shoulder 26 and an annular small-diameter shoulder 28 are formed on each axial side of the second inner ring member 47. The outer peripheral surface of the second inner ring member 47 between the large-diameter shoulder portion 26 and the small-diameter shoulder portion 28 is an inner raceway surface 31. The second tapered roller 50 is disposed between the outer raceway surface 19 and the inner raceway surface 31 so as to freely roll.
[0023]
The second retainer 51 is provided with pockets 33 formed at equal positions in the circumferential direction, and on the pinion gear side of these pockets 33, toward the small-diameter shoulder 28 side of the second inner ring member 47, radially inward. And a second annular flange 52 that is bent. The second retainer 51 has an annular portion 36 extending in the width direction (inclination direction) on the anti-pinion gear side of the pocket 33. The annular space 38 between the second outer ring member 45 and the second inner ring member 47 has a large diameter channel 41 and a small diameter channel 43 of the oil 39 by the second retainer 51.
[0024]
As shown in FIG. 3, a second lip 53 made of synthetic rubber as an annular elastic body is formed at the end of the second annular flange 52 by vulcanization molding. The second lip 53 is formed in a pointed shape, and its pointed end 53a is slidable in contact with the small-diameter shoulder portion 28, that is, the outer peripheral surface 28a of the inner ring raceway surface 31 in the vicinity of the outer side in the axial direction. Have been.
[0025]
The second assembly 46 is attached to the second outer ring member 45 that has been fitted to the annular wall 12 in advance, and the second assembly 46 externally inserts and inserts the second inner ring member 47 into the pinion shaft 8. As described above, the second tapered roller 50 is inserted into the differential case from the direction opposite to the pinion gear toward the pinion gear from the direction of the shaft center 16 so that the rolling surface of the second tapered roller 50 contacts the outer ring raceway surface 19.
[0026]
A plastic spacer 55 for setting a preload is disposed between the first inner ring member 22 and the second inner ring member 47 in the middle of the shaft portion 10 of the pinion shaft 8. The second inner ring member 47 is sandwiched between the plastic spacer 55 and the shielding plate 56 from the axial center 16 direction.
[0027]
As shown in FIG. 1, an oil circulation path 57 is formed between the outer wall of the front case 3 and the annular wall 11 on the pinion gear side, and an oil inlet 58 of the oil circulation path 57 is opened to the ring gear side, and The oil outlet 60 of the circulation path 57 is open between the annular walls 11 and 12.
[0028]
The differential device 1 has a companion flange 65. The companion flange 65 has a trunk 66 and a flange 67 integrally formed with the trunk 66. The body 66 is fitted to the shaft portion 10 of the pinion shaft 8 on the side opposite to the pinion gear, that is, on the drive shaft (not shown).
[0029]
The shielding plate 56 is interposed between the pinion gear side end surface of the body 66 and the end surface of the second inner ring member 47 of the second tapered roller bearing device 17. An oil seal 70 is arranged between the outer peripheral surface of the body 66 and the inner peripheral surface of the front case 3 on the side opposite to the pinion gear.
[0030]
A seal protection cup 71 for covering the oil seal 70 is attached to the opening on the anti-pinion gear 7 side of the front case 3. A screw portion 72 is formed at the outer end of the shaft portion 10 on the side opposite to the pinion gear 7, and the screw portion 72 protrudes from a central concave portion 73 of the flange portion 67. A nut 74 is screwed into the screw portion 72.
[0031]
As described above, the nut 74 is screwed into the screw portion 72, so that the first inner ring member 22 of the first tapered roller bearing device 15 and the second inner ring member 47 of the second tapered roller bearing device 17 are connected to the pinion gear 7. A predetermined preload is sandwiched between the end face and the end face of the companion flange 65 in the direction of the axis 16, and a predetermined preload is applied to the first tapered roller bearing device 15 and the second tapered roller bearing device 17 via the shielding plate 56 and the plastic spacer 55. It will be in the granted state.
[0032]
In the differential device 1 having the above-described configuration, the pinion shaft 8 rotates around the axis 16 while being supported by the first tapered roller bearing device 15 and the second tapered roller bearing device 17 with the rotation of the drive shaft. As the pinion shaft 8 rotates, the first inner ring member 22 of the first tapered roller bearing device 15 and the second inner ring member 47 of the second tapered roller bearing device 17 rotate around the axis 16.
[0033]
At this time, the first lip 44 and the second lip 53 come into contact with the outer peripheral surfaces 27a and 28a of the small-diameter shoulders 27 and 28 of the first inner ring member 22 and the second inner ring member 47 and slide. Further, the ring gear 9 rotates with the rotation of the pinion shaft 8.
[0034]
The oil 39 is jumped up with the rotation of the ring gear 9, and is supplied to the first tapered roller bearing device 15 and the second tapered roller bearing device 17 through an oil circulation path 57 in the front case 3. Be guided. Subsequently, after flowing into the annular space 37 of the first tapered roller bearing device 15 and the annular space 38 of the second tapered roller bearing device 17 to lubricate the raceway surface, the fluid is discharged from the annular spaces 37 and 38, respectively.
[0035]
By the way, the first lip 44 and the second lip 53 are in contact with the outer peripheral surfaces 27a and 28a of the small diameter shoulders 27 and 28 of the first inner ring member 22 and the second inner ring member 47, respectively. The inner side in the radial direction of 38 is closed, and the outer sides in the radial direction of the annular spaces 37 and 38 are only open.
[0036]
For this reason, when the oil 39 flows into the annular spaces 37 and 38, the flow rate is limited by the amount that the radially inner sides of the annular spaces 37 and 38 are closed, and the oil 39 flows from the large-diameter channels 40 and 41. It flows into the annular spaces 37 and 38. Therefore, a required amount of oil 39 can be introduced into the annular spaces 37 and 38, and it is possible to suppress an increase in agitating resistance when the first tapered roller 23 and the second tapered roller 50 roll.
[0037]
The oil 39 that has flowed into the annular spaces 37, 38 branches off from the large-diameter flow passages 40, 41 to the small-diameter flow passages 42, 43 in the annular spaces 37, 38, respectively, and flows through the first tapered roller bearing device 15. And the raceway surface of the second tapered roller bearing device 17 is lubricated and discharged to the outside from the annular spaces 37 and 38 by, for example, centrifugal force accompanying rotation of the first inner ring member 22 and the second inner ring member 47.
[0038]
Note that the first lip 44 and the second lip 53 each have a pointed end 44 a, 53 a in an initial state depending on a tolerance at the time of manufacturing, and the outer periphery of the small diameter shoulders 27, 28 of the first inner ring member 22 and the second inner ring member 47. Although it is conceivable that the first tapered roller 23 and the second tapered roller 50 roll, they may come into contact with each other and slide.
[0039]
The tip portions 44a, 53a wear due to the sliding operation, and the contact area with the outer peripheral surfaces of the small-diameter shoulder portions 27, 28 gradually increases, thereby reliably suppressing the inflow of the oil 39 and suppressing the stirring resistance. be able to.
[0040]
In the above-described embodiment, the present invention has been described by taking a tapered roller bearing device as an example. However, the invention is also applicable to cylindrical roller bearing devices. 5 to 8 show an embodiment of a cylindrical roller bearing device.
[0041]
The cylindrical roller bearing device 75 shown in FIGS. 5 to 8 is used, for example, in a transmission, and each of them is an outer ring member 76, an inner ring member 77, a plurality of cylindrical rollers 78, and these cylindrical rollers 78 are arranged at equal circumferential positions. And a retainer 79 for holding. The cylindrical roller 78 is rotatably disposed between an outer raceway surface 80 formed on the inner peripheral surface of the outer race member 76 and an inner raceway surface 81 formed on the outer peripheral surface of the inner race member 77. The retainer 79 may be a press-made retainer or a machined retainer.
[0042]
The cylindrical roller bearing device 75 shown in FIG. 5 has shoulders 82 and 83 larger in diameter than the inner ring raceway surface 81 on both axial sides of the inner ring member 77. Further, the retainer 79 has annular portions 84 and 85 bent radially inward on both axial sides. The annular portion 84 on one side (oil inflow side) is provided with an annular lip 86 that contacts the outer peripheral surface of the shoulder 82 on one side. The shape of the lip 86 is the same as that of the above-described embodiment, and the pointed end portion 86a comes into contact with the outer peripheral surface of the shoulder portion 82 on one side and is slidable.
[0043]
The cylindrical roller bearing device 75 shown in FIG. 6 has shoulders 82 and 83 larger in diameter than the inner raceway surface 81 on both axial sides of the inner race member 77. The retainer 79 has annular portions 84 and 85 bent radially outward on both axial sides. A lip 86 is provided on one side (oil inflow side) of the annular portion 84 so as to be in contact with the inner peripheral surface of the shoulder 76a on one side of the outer race member 76. The shape of the lip 86 is the same as that of the above-described embodiment, and the pointed end portion 86a is slidable by contacting the inner peripheral surface of the shoulder portion 76a on one side.
[0044]
The cylindrical roller bearing device 75 shown in FIG. 7 has shoulder portions 76 a and 76 b smaller in diameter than the outer raceway surface 80 on both axial sides of the outer race member 76. Further, the retainer 79 has annular portions 84 and 85 bent radially inward on both axial sides. A lip 86 that contacts the outer peripheral surface of the shoulder 82 on one side of the inner ring member 77 is provided on the annular portion 84 on one side (oil inflow side). The shape of the lip 86 is the same as that of the above-described embodiment, and the pointed end portion 86a comes into contact with the outer peripheral surface of the shoulder portion 82 on one side and is slidable.
[0045]
The cylindrical roller bearing device 75 shown in FIG. 8 has shoulders 76 a and 76 b smaller in diameter than the outer raceway surface 80 on both axial sides of the outer race member 76. The retainer 79 has annular portions 84 and 85 bent radially outward on both axial sides. A lip 86 is provided on one side (oil inflow side) of the annular portion 84 so as to be in contact with the outer peripheral surface of the shoulder portion 76a on one side of the outer race member 76. The shape of the lip 86 is the same as that of the above embodiment, and the pointed end 86a is slidable in contact with the outer peripheral surface of the shoulder 76a on one side.
[0046]
In any of these cylindrical roller bearing devices 75, the flow rate of the oil can be suppressed, and the rise of the stirring resistance during the rolling of the cylindrical roller 78 can be suppressed.
[0047]
【The invention's effect】
As is apparent from the above description, according to the roller bearing device of the present invention, a necessary amount of lubricating oil flows into the annular space due to the presence of the annular elastic body that can be brought into contact with the outer race member or the inner race member in the vicinity of the raceway surface. Therefore, the stirring resistance due to the lubricating oil when the rollers roll can be minimized.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing the entire configuration of a differential device according to the present invention.
FIG. 2 is an enlarged sectional view showing a tapered roller bearing device in use.
FIG. 3 is a sectional view showing a further enlarged main part of FIG. 2;
FIG. 4 is a front view of one tapered roller bearing device.
FIG. 5 is a half sectional view of a cylindrical roller bearing device showing another embodiment.
FIG. 6 is a half sectional view of a cylindrical roller bearing device showing another embodiment.
FIG. 7 is a half sectional view of a cylindrical roller bearing device showing another embodiment.
FIG. 8 is a half sectional view of a cylindrical roller bearing device showing another embodiment.
FIG. 9 is a half sectional view of a conventional tapered roller bearing device.
[Explanation of symbols]
REFERENCE SIGNS LIST 1 differential device 2 differential case 6 differential transmission mechanism 8 pinion shaft 9 ring gear 11, 12 annular wall 15 first tapered roller bearing device 17 second tapered roller bearing device 18, 19 outer ring raceway surface 20 first outer ring member 21 first set Article 22 First inner ring member 23 First tapered roller 24 First retainer 25 Large diameter shoulder 27 Small diameter shoulder 30 Inner ring raceway surface 34 First annular flange 35 Annular portion 37 Annular space 39 Oil 40 Large diameter side flow path 42 Small diameter side flow path 44 First lip 44a Pointed end 27a Outer peripheral surface 18 of small diameter shoulder Outer ring raceway surface 45 Second outer ring member 46 Second assembly 47 Second inner ring member 50 Second tapered roller 51 Second cage

Claims (2)

外輪軌道面を内周面に有する外輪部材と、該外輪部材の径方向内方に同心に配置されるとともに、内輪軌道面を外周面に有する内輪部材と、前記外輪軌道面および前記内輪軌道面の間に転動自在に配置される複数個のころと、これらころを円周方向所定間隔に保持するための保持器とが設けられ、
前記外輪部材と前記内輪部材との間の環状空間内を、その一方側から他方側に向けて潤滑油が通過する場所で使用されるころ軸受装置において、
前記保持器の幅方向一方側端部に、潤滑油量制限用の環状弾性体が、前記内輪軌道面の幅方向一方側端部の近傍、または前記外輪軌道面の幅方向一方側端部の近傍に接触して摺動可能に設けられている、ことを特徴とするころ軸受装置。An outer race member having an outer raceway surface on an inner peripheral surface, an inner race member disposed concentrically radially inward of the outer race member and having an inner raceway surface on an outer peripheral surface; the outer raceway surface and the inner raceway surface A plurality of rollers that are arranged to be able to roll freely between them, and a retainer for holding these rollers at predetermined intervals in the circumferential direction are provided,
In a roller bearing device used in a place where lubricating oil passes from one side to the other side in an annular space between the outer ring member and the inner ring member,
At one end in the width direction of the retainer, an annular elastic body for limiting the amount of lubricating oil is provided in the vicinity of one end in the width direction of the inner raceway surface, or one end in the width direction of the outer raceway surface. A roller bearing device, which is provided so as to be slidable in contact with the vicinity. 外輪軌道面を内周面に有する外輪部材と、該外輪部材の径方向内方に同心に配置されるとともに、内輪軌道面を外周面に有する内輪部材と、前記外輪軌道面および前記内輪軌道面の間に転動自在に配置される複数個の円すいころと、これら円すいころを円周方向所定間隔に保持するための保持器とが設けられ、
前記外輪部材と前記内輪部材との間の環状空間内を、その小端側から大端側に向けて潤滑油が通過する場所で使用されるころ軸受装置において、
前記保持器の小端側端部に、潤滑油量制限用の環状弾性体が、前記内輪部材の小端側肩部に接触して摺動可能に設けられている、ことを特徴とするころ軸受装置。An outer race member having an outer raceway surface on an inner peripheral surface, an inner race member disposed concentrically radially inward of the outer race member and having an inner raceway surface on an outer peripheral surface; the outer raceway surface and the inner raceway surface A plurality of tapered rollers arranged rotatably between, and a retainer for holding these tapered rollers at predetermined intervals in the circumferential direction are provided,
In a roller bearing device used in a place where lubricating oil passes from the small end side to the large end side in the annular space between the outer ring member and the inner ring member,
An annular elastic body for limiting the amount of lubricating oil is provided at the small end side end of the retainer so as to be slidable in contact with the small end side shoulder of the inner race member. Bearing device.
JP2003057382A 2003-03-04 2003-03-04 Roller bearing device Pending JP2004263838A (en)

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006258202A (en) * 2005-03-17 2006-09-28 Nsk Ltd Tapered roller bearing device
JP2008101714A (en) * 2006-10-19 2008-05-01 Honda Motor Co Ltd Bearing device including rolling bearing
WO2015012214A1 (en) * 2013-07-22 2015-01-29 株式会社ジェイテクト Tapered roller bearing and power transmission device using tapered roller bearing
JP2019173710A (en) * 2018-03-29 2019-10-10 本田技研工業株式会社 Pump shaft support structure

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006258202A (en) * 2005-03-17 2006-09-28 Nsk Ltd Tapered roller bearing device
JP2008101714A (en) * 2006-10-19 2008-05-01 Honda Motor Co Ltd Bearing device including rolling bearing
JP4531031B2 (en) * 2006-10-19 2010-08-25 本田技研工業株式会社 Bearing device provided with rolling bearing
WO2015012214A1 (en) * 2013-07-22 2015-01-29 株式会社ジェイテクト Tapered roller bearing and power transmission device using tapered roller bearing
CN105393007A (en) * 2013-07-22 2016-03-09 株式会社捷太格特 Tapered roller bearing and power transmission device using tapered roller bearing
JP2019173710A (en) * 2018-03-29 2019-10-10 本田技研工業株式会社 Pump shaft support structure

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