JP2004011811A - Antifriction bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a holder for an antifriction bearing having excellent damping performance and excellent resistance against wear. <P>SOLUTION: This holder 10 for the antifriction bearing holding a plurality of balls so as to roll them freely is provided with an outside diameter member 11 arranged on an outer peripheral side, an inside diameter member 12 arranged on an inner peripheral side in a non-contact manner with the outside diameter member 11, and a damping member 13 connected with the outside diameter member 11 and the inside diameter member 12. <P>COPYRIGHT: (C)2004,JPO

Description

【０００１】
【発明の属する技術分野】
本発明は、例えば工作機械用スピンドル等、高速で運転される回転体を支持する転がり軸受に関する。
【０００２】
【従来の技術】
従来の転がり軸受は、例えば実開昭６２−６５３２号公報や特開２０００−２４０６５９号公報に開示されている。
【０００３】
図７は、実開昭６２−６５３２号公報に開示の転がり軸受の保持器を示す。転がり軸受用保持器８０は、合成樹脂製であって、玉軸受８１に用いられており、外輪８２と内輪８３との間の軸受空間内に配されている。玉軸受８１では、外輪８２の軌道面８４と内輪８３の軌道面８５との間に玉８６が配されている。玉８６は、転がり軸受用保持器８０の円周方向に間隔を置いて形成されたポケット８７に回転自在に保持されている。ポケット８７は、玉８６の直径よりもわずかに大きい直径を有する。
【０００４】
また、特開２０００−２４０６５９号公報に開示された転がり軸受用保持器は、転動体である玉との接触面に表面処理を施したマグネシウム合金を用いており、保持器の耐熱性、耐摩耗性、強度、および耐食性などの性能を向上させている。
【０００５】
【発明が解決しようとする課題】
しかしながら、上記公報に記載された転がり軸受用保持器は、転がり軸受用保持器の材質や形状に依存して共振周波数が決まる。そのため、幅広い使用条件下において、この共振周波数が運転時に発生する工作機械用スピンドルの振動周波数や軸受自体の振動周波数と合致しないとは言い難い。一般に、保持器の共振周波数が、工作機械用スピンドルの振動周波数や軸受自体の振動周波数と合致した場合、運転時に共振が発生し、軸受に大きな機械振動が発生することがあり、使用上好ましくない。
【０００６】
また、上記公報に記載された転がり軸受用保持器で、一体形状であって、そのボリュームが大きいため、重量が大きくなる。それによって、運転中に大きな遠心力が発生して摩耗し易いという問題点もある。
【０００７】
本発明は、上記事情に鑑みてなされたもので、その目的は、減衰性能及び耐摩耗性に富む転がり軸受用保持器を備えた転がり軸受を提供することにある。
【０００８】
【課題を解決するための手段】
本発明の目的は、下記構成により達成される。
（１）相対的に回転する外輪および内輪と、前記外輪と前記内輪との間に配置される転動体と、前記外輪と前記内輪との間に配置され、前記転動体を転動自在に保持するポケットを有する保持器と、を有する転がり軸受において、
前記保持器は、外輪側に配置される外径部材と、該外径部材と別体にされ、前記外径部材に非接触にして内輪側に配置される内径部材と、前記外径部材及び前記内径部材との間に配置される減衰部材と、を有することを特徴とする転がり軸受。
（２）前記減衰部材は、前記外径部材及び内径部材の少なくとも一方と減衰係数が異なる（１）の転がり軸受。
【０００９】
上記構成の転がり軸受によれば、保持器は、それぞれ別体とされた外径部材と、内径部材と、減衰部材とから構成され、非接触に組み付けられた外径部材と内径部材との間に減衰部材が配置され外形部材と内径部材を結合している。
したがって、外径部材または内径部材に与えられた振動が、減衰部材によって減衰されて、内径部材または外径部材に直接伝わらない。例え、工作機械用スピンドル等の回転体の振動周波数や軸受自体の振動周波数と合致したとしても、外径部材と内径部材と減衰部材とが別体にされて外径部材と内径部材とが非接触に組み付けられているため、共振することがない。よって、大きな機械振動を発生することなく運転を行うことができる。また、外径部材と内径部材と減衰部材とが別体にされているため、それらのボリュームが小さくなって重量が少なくなっており、運転中に発生する遠心力も小さくなって耐摩耗性を向上することができる。
【００１０】
また、減衰部材の減衰係数が、外径部材または内径部材の少なくとも一方と減衰係数が異なるように選ばれれば、振動の減衰比が更に大きくなる。
したがって、外径部材または内径部材に与えられた振動が、減衰部材によって減衰される際に、より大きな減衰率で減衰されて内径部材または外径部材に対し更に伝わり難くなり、単振動、減衰振動、無周期運動等を発生することなく静粛な運転を行うことができる。
【００１１】
【発明の実施の形態】
以下、本発明の実施形態を図１〜図６に基づいて詳細に説明する。
本発明は、相対的に回転する外輪および内輪と、前記外輪と前記内輪との間に配置される転動体と、前記外輪と前記内輪との間に配置され、前記転動体を転動自在に保持するポケットを有する保持器と、を有する転がり軸受において用いられる保持器に関するものである。
【００１２】
図１は、本発明の第１実施形態の転がり軸受用保持器１０を示す。
転がり軸受用保持器（以下、保持器と称す。）１０は、単一の外径部材１１と、外径部材１１の内周側に配置される一対の内径部材１２と、外径部材１１及び内径部材１２の間に配置される一対の減衰部材１３とから構成されている。
【００１３】
外径部材１１は、断面視Ｔ字形状をなす円環形状にされており、黄銅系合金、鉄系合金、マグネシウム合金、アルミニウム合金、合成樹脂等を素材として成形されている。
外径部材１１の中央部に配置された外径部材本体部１４には、柱部１５を介して円周方向に間隔を置いて配置された複数のポケット１６が形成されている。ポケット１６には、図示しない転動体である玉が挿入される。
【００１４】
外径部材本体１４の外周側には、一対の外周板部１７が形成される。外周板部１７は、外径部材本体１４から薄板状にしてフランジ状に突出している。
外径部材１１は、ポケット１６を有する外径部材本体１４と、一対の薄板状の外周板部１７とからなるため軽量化が図られている。
【００１５】
内径部材１２は、断面視Ｌ字形状をなす円環形状を有し、外径部材１１と同様にして、黄銅系合金、鉄系合金、マグネシウム合金、アルミニウム合金、合成樹脂等を素材として成形されている。
内径部材１２は、その内周側に薄板状をなす内周板部１８を有し、その外方側に薄板状をなす側板部１９を有する。
内径部材１２は、薄板状をなす内周板部１８と、薄板状をなす側板部１９とからなり軽量化が図られている。
【００１６】
減衰部材１３は、ゴムや可撓性のある樹脂等の弾性材を素材として断面視四角形の円環形状に形成されており、外径部材１１及び内径部材１２のもつ減衰係数と異なる減衰係数をもつ。
減衰部材１３は、外径部材１１の外径部材本体１４と外周板部１７、および内径部材１２の内周板部１８と側板部１９に囲まれて形成される四角形の空間に収容されて、外径部材１１及び内径部材１２に一体的に結合されている。
【００１７】
ここで、外径部材１１の外周板部１７と内径部材１２の側板部１９との間及び、外径部材１１の外径部材本体１４と内径部材１２の内周板部１８との間には、隙間ａが形成されている。隙間ａは、外径部材１１と内径部材１２とを非接触に隔てている。
【００１８】
図２に示すように、減衰部材１３の径方向の幅寸法Ｌ１は、外径部材１１の外径部材本体１４の内径幅寸法Ｌ２よりも小さく、内径部材１２の側板部１９の内径幅寸法Ｌ３よりも大きい。そのため、外径部材１１の外周板部１７と内径部材１２の側板部１９との間に隙間ａが形成される。
【００１９】
また、減衰部材１３の高さ寸法ｈ１は、外径部材１１の外周側板１７の内径高さ寸法ｈ２よりも小さく、内径部材１２の内周板部１８の内径高さ寸法ｈ３よりも大きい。そのため、外径部材１１の外径部材本体１４と内径部材１２の内周板部１８との間に隙間ａが形成される。その結果、外径部材１１と内径部材１２とが非接触に配置される。
【００２０】
このような構造の保持器１０では、減衰部材１３を介して、外径部材１１と内径部材１２は、接着、溶接、或いは機械加工等による係り代の設置により結合される。
【００２１】
減衰部材１３としては、オーリングや油性ダンパーに使用される油等の高い減衰性能をもったものを用いても良い。そして、減衰部材１３の減衰係数は、外径部材１１及び内径部材１２の少なくとも一方の減衰係数と異なるようにしても良い。
【００２２】
第１実施形態の保持器１０によれば、外径部材１１と内径部材１２と減衰部材１３とが別体にされ、減衰部材１３の減衰係数が、外径部材１２及び内径部材１２の減衰係数と異なるように選ばれ、非接触に組み付けられた外径部材１１と内径部材１２とに減衰部材１３が結合される。
【００２３】
したがって、外径部材１１または内径部材１２に与えられた振動が、減衰部材１３によって減衰されて、内径部材１２または外径部材１１に直接伝わらない。ここで、減衰部材１３の減衰係数は、外径部材１１及び内径部材１２の減衰係数と異なるように選ばれているため、外径部材１１または内径部材１２に与えられた振動が減衰部材１３によって減衰される際に、大きな減衰率で減衰される。よって、内径部材１２または外径部材１１に振動が伝わり難くなり、単振動、減衰振動、無周期運動等を発生することがない。
【００２４】
そして、例え、工作機械用スピンドル等の回転体の振動周波数や軸受自体の振動周波数と合致したとしても、外径部材１１と内径部材１２と減衰部材１３とが別体にされて外径部材１１と内径部材１２とが非接触に組み付けられているため、共振が抑制され、大きな機械振動を発生することなく静粛な運転を行うことができる。
【００２５】
また、外径部材１１と内径部材１２と減衰部材１３とが別体にされているため、それらのボリュームの減少にともない重量が小さくなって軽量化が図られている。その結果、運転中に発生する遠心力も小さくなって耐摩耗性を向上することができる。
【００２６】
図３は、本発明の第２実施形態の保持器を示す。なお、以下に説明する実施形態において、既に説明した部材等と同様な構成・作用を有する部材等については、図中に相当符号を付すことにより、説明を簡略化或いは省略する。
図３に示す保持器２０は、一対の外径部材２１と、外径部材２１の内周側に配置される単一の内径部材２２と、外径部材２１及び内径部材２２の間に配置される一対の減衰部材２３とから構成されている。
【００２７】
外径部材２１は、断面視Ｌ字形状をなす円環形状を有し、黄銅系合金、鉄系合金、マグネシウム合金、アルミニウム合金、合成樹脂等を素材として成形されている。
外径部材２１は、その外周側に薄板状をなす外周板部２４を有し、その外方側に薄板状をなす側板部２５を有する。
外径部材２１は、薄板状をなす外周板部２４と、薄板状をなす側板部２５とからなり軽量化が図られている。
【００２８】
内径部材２２は、断面視Ｔ字形状をなす円環形状を有し、外径部材２１と同様にして、黄銅系合金、鉄系合金、マグネシウム合金、アルミニウム合金、合成樹脂等を素材として成形されている。
内径部材２２の中央部に配置された内径部材本体２６には、柱部２７を介して円周方向に間隔を置いて配置された複数のポケット２８が形成されている。ポケット２８には、図示しない転動体である玉が挿入される。
【００２９】
内径部材本体２６の内周側には、一対の内周板部２９が形成されている。内周板部２９は、内径部材本体２６から薄板状にしてフランジ状に突出している。
内径部材２２は、ポケット２８を有する外径部材本体２６と、一対の薄板状の内周板部２９とからなり軽量化が図られている。
【００３０】
減衰部材２３は、ゴムや可撓性のある樹脂等の弾性材を素材として断面視四角形の円環形状に形成されており、外径部材２１及び内径部材２２のもつ減衰係数と異なる減衰係数をもつ。
減衰部材２３は、外径部材２１の外周板部２４と側板部２５、および内径部材２２の内径部材本体２６と内周板部２９に囲まれて形成される四角形の空間に収容されて、外径部材２１及び内径部材２２に一体的に結合されている。
【００３１】
ここで、減衰部材２３の径方向の幅寸法Ｌ４は、内径部材２２の内径部材本体２６の内径幅寸法Ｌ５よりも小さく、外径部材２１の側板部２５の内径幅寸法Ｌ６よりも大きい。そのため、外径部材２１の側板部２５と内径部材２２の内周板部２９との間に隙間ａが形成される。
【００３２】
また、減衰部材２３の高さ寸法ｈ４は、内径部材２２の内径部材本体２６の内径高さ寸法ｈ５よりも小さく、外径部材２１の外周板部２４の内径高さ寸法ｈ６よりも大きい。そのため、内径部材２２の内径部材本体２６と外径部材２１の外周板部２４との間に隙間ａが形成される。その結果、外径部材２１と内径部材２２とが非接触に配置される。
【００３３】
第２実施形態の保持器２０によれば、外径部材２１と内径部材２２と減衰部材２３とが別体にされ、減衰部材２３の減衰係数が、外径部材２２及び内径部材２２の減衰係数と異なるように選ばれ、非接触に組み付けられた外径部材２１と内径部材２２とに減衰部材２３が結合される。
【００３４】
したがって、外径部材２１または内径部材２２に与えられた振動が、減衰部材２３によって減衰されて、内径部材２２または外径部材２１に直接伝わらない。ここで、減衰部材２３の減衰係数が、外径部材２１及び内径部材２２の減衰係数と異なるように選ばれているため、外径部材２１または内径部材２２に与えられた振動が減衰部材２３によって減衰される際に、大きな減衰率で減衰される。よって、内径部材２２または外径部材２１に振動が伝わり難くなり、単振動、減衰振動、無周期運動等を発生することがない。
【００３５】
そして、例え、工作機械用スピンドル等の回転体の振動周波数や軸受自体の振動周波数と合致したとしても、外径部材２１と内径部材２２と減衰部材２３とが別体にされて外径部材２１と内径部材２２とが非接触に組み付けられているため、共振が抑制され、大きな機械振動を発生することなく静粛な運転を行うことができる。
【００３６】
また、外径部材２１と内径部材２２と減衰部材２３とが別体にされているため、それらのボリュームが小さくなって軽量化が図られている。その結果、運転中に発生する遠心力も小さくなって耐摩耗性を向上することができる。
【００３７】
図４は、本発明の第３実施形態の保持器を示す。
図４に示す保持器３０は、単一の外径部材３１と、外径部材３１の内周側に配置される単一の内径部材３２と、外径部材３１及び内径部材３２の間に配置される一対の減衰部材３３とから構成されている。
【００３８】
外径部材３１は、断面視Ｌ字形状をなす円環形状を有し、黄銅系合金、鉄系合金、マグネシウム合金、アルミニウム合金、合成樹脂等を素材として成形されている。
外径部材３１の中央部に配置された外径部材本体３４には、図示しない柱部を介して円周方向に間隔を置いて配置された複数の外径部材側ポケット３６ａが形成されている。
【００３９】
外径部材本体３４の外周側には、一対の外周板部３７を有する。外周板部３７は、外径部材本体３４から薄板状にしてフランジ状に突出している。
外径部材３１は、外径部材側ポケット３６ａを有する外径部材本体３４と、一対の薄板状の外周板部３７とからなり、軽量化が図られている。
【００４０】
内径部材３２は、断面視Ｉ字形状をなす円環形状にされており、外径部材３１と同様にして、黄銅系合金、鉄系合金、マグネシウム合金、アルミニウム合金、合成樹脂等を素材として成形されている。
内径部材３２には、外径部材本体３４の外径部材側ポケット３６ａと同一位置であって、柱部３５を介して円周方向に間隔を置いて配置された複数の内径部材側ポケット３６ｂが形成されている。内径部材側ポケット３６ｂと、外径部材３１の外径部材側ポケット３６ａとに、図示しない玉が挿入される。
内径部材３２は、薄板状をなし、軽量化が図られている。
【００４１】
減衰部材３３は、ゴムや可撓性のある樹脂等の弾性材を素材として断面視円形の円環形状に形成されており、外径部材３１及び内径部材３２のもつ減衰係数と異なる減衰係数をもつ。
減衰部材３３は、外径部材３１の外径部材本体３４と外周板部３７、および内径部材３２に囲まれて形成される四角形の空間に収容されて、外径部材３１及び内径部材３２に一体的に結合されている。
【００４２】
ここで、減衰部材３３の径ｄ１は、外径部材３１の外径部材本体３４の内径幅寸法Ｌ７よりも大きい。そのため、外径部材３１の外径部材本体３４と内径部材３２との間に隙間ａが形成される。その結果、外径部材３１と内径部材３２とが非接触に配置される。
【００４３】
第３実施形態の保持器３０によれば、外径部材３１と内径部材３２と減衰部材３３とが別体にされ、減衰部材３３の減衰係数が、外径部材３１及び内径部材３２の減衰係数と異なるように選ばれ、非接触に組み付けられた外径部材３１と内径部材３２とに減衰部材３３が結合される。
【００４４】
したがって、外径部材３１または内径部材３２に与えられた振動が、減衰部材３３によって減衰されて、内径部材３２または外径部材３１に直接伝わらない。ここで、減衰部材３３の減衰係数が、外径部材３１及び内径部材３２の減衰係数と異なるように選ばれているため、外径部材３１または内径部材３２に与えられた振動が減衰部材３３によって減衰される際に、大きな減衰率で減衰される。よって、内径部材３２または外径部材３１に振動が伝わり難くなり、単振動、減衰振動、無周期運動等を発生することがない。
【００４５】
そして、例え、工作機械用スピンドル等の回転体の振動周波数や軸受自体の振動周波数と合致したとしても、外径部材３１と内径部材３２と減衰部材３３とが別体にされて外径部材３１と内径部材３２とが非接触に組み付けられているため、共振することがない。よって、大きな機械振動を発生することなく静粛な運転を行うことができる。
【００４６】
また、外径部材３１と内径部材３２と減衰部材３３とが別体にされているため、それらのボリュームの減少にともない重量が小さくなって軽量化が図られている。その結果、運転中に発生する遠心力も小さくなって耐摩耗性を向上することができる。
【００４７】
図５に、本発明第４実施形態の保持器を示す。
図５に示す保持器４０は、単一の外径部材４１と、外径部材４１の内周側に配置される単一の内径部材４２と、外径部材４１及び内径部材４２の間に配置される一対の減衰部材４３とから構成されている。
【００４８】
外径部材４１は、円環形状にされており、黄銅系合金、鉄系合金、マグネシウム合金、アルミニウム合金、合成樹脂等を素材として成形されている。
外径部材４１の中央部には、図示しない柱部を介して円周方向に間隔を置いて配置された複数の外径部材側ポケット４６ａが形成されている。
【００４９】
外径部材４１の外径部材側ポケット４６ａの両外側には、一対の減衰部材収容部４１ａが形成されている。減衰部材収容部４１ａは、外径部材４１の内周面から外周に向けて四角形に切除した凹溝状をなし、周方向に連続している。
外径部材４１は、内周側に凹溝状に切除した減衰部材収容部４１ａが形成されているため、全体的に薄肉になっており軽量化が図られている。
【００５０】
内径部材４２は、外径部材４１と同様にして、黄銅系合金、鉄系合金、マグネシウム合金、アルミニウム合金、合成樹脂等を素材として円環形状に形成されている。
内径部材４２の中央部には、柱部４５を介して円周方向に間隔を置いて配置された複数の内径部材側ポケット４６ｂが形成されている。内径部材側ポケット４６ｂと外径部材４１の外径部材側ポケット４６ａとに、図示しない玉が挿入される。
【００５１】
内径部材４２の内径部材側ポケット４６ｂの両外側には、一対の減衰部材収容部４２ａが形成されている。減衰部材収容部４２ａは、内径部材４２の外周面から内周に向けて四角形に切除した凹溝状をなし、周方向に連続している。
内径部材４２は、外周側に凹溝状に切除した減衰部材収容部４２ａが形成されているため、全体的に薄肉になっており軽量化が図られている。
【００５２】
減衰部材４３は、ゴムや可撓性のある樹脂等の弾性材を素材として断面視四角形の円環形状に形成されており、外径部材４１及び内径部材４２のもつ減衰係数と異なる減衰係数をもつ。
減衰部材４３は、外径部材４１の減衰部材収容部４１ａと、内径部材４２の減衰部材収容部４２ａに囲まれて形成される四角形の空間に収容されて、外径部材４１及び内径部材４２に一体的に結合されている。
【００５３】
ここで、減衰部材４３の径方向の幅寸法Ｌ８は、外径部材４１の減衰部材収容部４１ａの深さ寸法Ｌ９と内径部材４２の減衰部材収容部４２ａの深さ寸法Ｌ１０との合算値よりも大きい。そのため、外径部材４１と内径部材４２との間に隙間ａが形成される。その結果、外径部材４１と内径部材４２とが非接触に配置される。
【００５４】
第４実施形態の保持器４０によれば、外径部材４１と内径部材４２と減衰部材４３とが別体にされ、減衰部材４３の減衰係数が、外径部材４１及び内径部材４２の減衰係数と異なるように選ばれ、非接触に組み付けられた外径部材４１と内径部材４２とに減衰部材４３が結合される。
【００５５】
したがって、外径部材４１または内径部材４２に与えられた振動が、減衰部材４３によって減衰されて、内径部材４２または外径部材４１に直接伝わらない。ここで、減衰部材４３の減衰係数が、外径部材４１及び内径部材４２の減衰係数と異なるように選ばれているため、外径部材４１または内径部材４２に与えられた振動が減衰部材４３によって減衰される際に、大きな減衰率で減衰する。よって、内径部材４２または外径部材４１に対し伝わり難くなり、単振動、減衰振動、無周期運動等を発生することがない。
【００５６】
そして、例え、工作機械用スピンドル等の回転体の振動周波数や軸受自体の振動周波数と合致したとしても、外径部材４１と内径部材４２と減衰部材４３とが別体にされて外径部材４１と内径部材４２とが非接触に組み付けられているため、共振することがない。よって、大きな機械振動を発生することなく静粛な運転を行うことができる。
【００５７】
また、外径部材４１と内径部材４２と減衰部材４３とが別体にされているため、それらのボリュームの減少にともない重量が小さく軽量化が図られている。その結果、運転中に発生する遠心力も小さくなって耐摩耗性を向上することができる。
【００５８】
図６に、本発明第５実施形態の保持器を示す。
図６に示す保持器５０は、単一の外径部材５１と、外径部材５１の内周側に配置される単一の内径部材５２と、外径部材５１及び内径部材５２の間に配置される単一の減衰部材５３とから構成されている。
【００５９】
外径部材５１は、円環形状にされており、黄銅系合金、鉄系合金、マグネシウム合金、アルミニウム合金、合成樹脂等を素材として成形されている。
外径部材５１には、図示しない柱部を介して円周方向に間隔を置いて配置された複数の外径部材側ポケット５６ａが形成されている。
外径部材５１の内周面には、減衰部材結合部５１ａが形成されている。
外径部材５１は、全体的に薄肉になっており軽量化が図られている。
【００６０】
内径部材５２は、外径部材５１と同様にして、黄銅系合金、鉄系合金、マグネシウム合金、アルミニウム合金、合成樹脂等を素材として円環形状に形成されている。
内径部材５２には、柱部５５を介して円周方向に間隔を置いて配置された複数の内径部材側ポケット５６ｂが形成されている。
【００６１】
内径部材５２の外周面には、減衰部材結合部５２ａが形成されている。
内径部材５２は、全体的に薄肉になっているため、重量が少ない。
【００６２】
減衰部材５３は、ゴムや可撓性のある樹脂等の弾性材を素材として、外径部材５３及び内径部材５４と同様な円環形状に形成されており、外径部材５１及び内径部材５２のもつ減衰係数と異なる減衰係数をもつ。
減衰部材５３には、図示しない柱部を介して円周方向に間隔を置いて配置された複数の減衰部材側ポケット５６ｃが形成されている。減衰部材側ポケット５６ｃと外径部材側ポケット５６ａと内径部材側ポケット５６ｂとに、図示しない玉が挿入される。
【００６３】
減衰部材５３は、外径部材５１の減衰部材結合部５１ａと、内径部材５２の減衰部材結合部５２ａとの間に挟まれて、外径部材５１及び内径部材５２に一体的に結合されている。減衰部材５３によって、外径部材５１及び内径部材５２が非接触に結合される。
【００６４】
第５実施形態の保持器５０によれば、外径部材５１と内径部材５２と減衰部材５３とが別体にされている。そして、減衰部材５３の減衰係数が、外径部材５１及び内径部材５２の減衰係数と異なるように選ばれ、非接触に組み付けられた外径部材５１と内径部材５２とに減衰部材５３が結合される。
【００６５】
したがって、外径部材５１または内径部材５２に与えられた振動が、減衰部材５３によって減衰されて、内径部材５２または外径部材５１に直接伝わらない。ここで、減衰部材５３の減衰係数が、外径部材５１及び内径部材５２の減衰係数と異なるように選ばれているため、外径部材５１または内径部材５２に与えられた振動が減衰部材５３によって減衰される際に、振動は大きな減衰率で減衰する。よって、内径部材５２または外径部材５１に対し伝わり難くなり、単振動、減衰振動、無周期運動等を発生することがない。
【００６６】
そして、例え、工作機械用スピンドル等の回転体の振動周波数や軸受自体の振動周波数と合致したとしても、外径部材５１と内径部材５２と減衰部材５３とが別体にされて外径部材５１と内径部材５２とが非接触に組み付けられているため、共振することがない。したがって、大きな機械振動を発生することなく静粛な運転を行うことができる。
【００６７】
また、外径部材５１と内径部材５２と減衰部材５３とが別体にされているため、それらのボリュームの減少にともない重量が小さくなって軽量化が図られている。その結果、運転中に発生する遠心力も小さくなって耐摩耗性を向上することができる。
【００６８】
なお、本発明は、上述した実施形態に限定されるものではなく、適宜な変形、改良等が可能である。
例えば、ポケット部分にのみ、金属製や樹脂製を素材として成形した円筒形の部材を嵌入しても良い。特に、第５実施形態に用いるのが好ましい。その場合、ポケットに装着される玉から受ける振動の減衰率を更に向上させることができる。
そして、保持器の形状は、軸受の内輪、外輪または玉により案内されるものとして適宜変更される。
【００６９】
【発明の効果】
以上説明したように、本発明の転がり軸受によれば、外径部材と内径部材と減衰部材とが別体にされ、非接触に組み付けられた外径部材と内径部材とに減衰部材が結合される。
したがって、外径部材または内径部材に与えられた振動が、減衰部材によって減衰されて、内径部材または外径部材に直接伝わらない。例え、工作機械用スピンドル等の回転体の振動周波数や軸受自体の振動周波数と合致したとしても、外径部材と内径部材と減衰部材とが別体にされて外径部材と内径部材とが非接触に組み付けられているため、共振することがない。よって、大きな機械振動を発生することなく運転を行うことができる。
【００７０】
また、外径部材と内径部材と減衰部材とが別体にされているため、それらのボリュームが小さくなって重量が少なくなっている。その結果、運転中に発生する遠心力も小さくなって耐摩耗性を向上することができる。以上の結果、減衰性能及び耐摩耗性に富む転がり軸受用保持器を提供することができる。
【００７１】
また、減衰部材の減衰係数が、外径部材または内径部材の少なくとも一方と減衰係数が異なるように選ばれるので、振動の減衰比が大きくなる。
したがって、外径部材または内径部材に与えられた振動が、減衰部材によって減衰される際に、より大きな減衰率で減衰されて内径部材または外径部材に対し更に伝わり難くなり、単振動、減衰振動、無周期運動等を発生することなく静粛な運転を行うことができる。
【図面の簡単な説明】
【図１】第１実施形態の一部断面外観図である。
【図２】図１の断面図である。
【図３】第２実施形態の断面図である。
【図４】第３実施形態の断面図である。
【図５】第４実施形態の断面図である。
【図６】第５実施形態の断面図である。
【図７】従来の保持器の断面図である。
【符号の説明】
１０，２０，３０，４０，５０　転がり軸受用保持器（保持器）
１１，２１，３１，４１，５１　外径部材
１２，２２，３２，４２，５２　内径部材
１３，２３，３３，４３，５３　減衰部材[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a rolling bearing that supports a high-speed rotating body such as a spindle for a machine tool.
[0002]
[Prior art]
Conventional rolling bearings are disclosed in, for example, Japanese Utility Model Application Laid-Open No. Sho 62-6532 and Japanese Patent Application Laid-Open No. 2000-240659.
[0003]
FIG. 7 shows a cage of a rolling bearing disclosed in Japanese Utility Model Laid-Open Publication No. Sho 62-6532. The roller bearing retainer 80 is made of a synthetic resin, is used for the ball bearing 81, and is disposed in a bearing space between the outer ring 82 and the inner ring 83. In the ball bearing 81, a ball 86 is arranged between a raceway surface 84 of the outer ring 82 and a raceway surface 85 of the inner ring 83. The balls 86 are rotatably held in pockets 87 formed at intervals in the circumferential direction of the roller bearing retainer 80. The pocket 87 has a diameter slightly larger than the diameter of the ball 86.
[0004]
The rolling bearing retainer disclosed in Japanese Patent Application Laid-Open No. 2000-240659 uses a magnesium alloy whose surface is in contact with a ball that is a rolling element and is subjected to surface treatment. Improves performance such as strength, strength, and corrosion resistance.
[0005]
[Problems to be solved by the invention]
However, in the rolling bearing cage described in the above publication, the resonance frequency is determined depending on the material and shape of the rolling bearing cage. Therefore, under a wide range of operating conditions, it is difficult to say that this resonance frequency does not match the vibration frequency of the machine tool spindle or the vibration frequency of the bearing itself generated during operation. In general, when the resonance frequency of the cage matches the vibration frequency of the spindle for machine tools or the vibration frequency of the bearing itself, resonance occurs during operation, and large mechanical vibration may occur in the bearing, which is not preferable in use. .
[0006]
Further, the rolling bearing retainer described in the above-mentioned publication has an integral shape and a large volume, so that the weight increases. As a result, there is also a problem that a large centrifugal force is generated during the operation and wear is likely.
[0007]
The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a rolling bearing provided with a rolling bearing retainer having excellent damping performance and wear resistance.
[0008]
[Means for Solving the Problems]
The object of the present invention is achieved by the following configurations.
(1) An outer ring and an inner ring that rotate relatively, a rolling element disposed between the outer ring and the inner ring, and a rolling element disposed between the outer ring and the inner ring to hold the rolling element rotatably. And a cage having a pocket that performs
The retainer is an outer diameter member disposed on the outer ring side, and is separated from the outer diameter member, and an inner diameter member disposed on the inner ring side in non-contact with the outer diameter member, and the outer diameter member and A damping member disposed between the inner diameter member and the inner diameter member.
(2) The rolling bearing according to (1), wherein the damping member has a different damping coefficient from at least one of the outer diameter member and the inner diameter member.
[0009]
According to the rolling bearing having the above-described configuration, the retainer includes the outer diameter member, the inner diameter member, and the damping member that are separately formed, and is provided between the outer diameter member and the inner diameter member that are assembled in a non-contact manner. A damping member is disposed on the outside of the housing to connect the outer member and the inner member.
Therefore, the vibration applied to the outer diameter member or the inner diameter member is attenuated by the damping member and is not directly transmitted to the inner diameter member or the outer diameter member. For example, even if the vibration frequency of a rotating body such as a spindle for a machine tool or the vibration frequency of the bearing itself is matched, the outer diameter member, the inner diameter member, and the damping member are separated from each other, and the outer diameter member and the inner diameter member are not separated. Because it is mounted on the contact, it does not resonate. Therefore, operation can be performed without generating large mechanical vibration. In addition, since the outer diameter member, inner diameter member and damping member are separated, their volume is reduced and their weight is reduced, and the centrifugal force generated during operation is also reduced, improving wear resistance. can do.
[0010]
Further, if the damping coefficient of the damping member is selected to be different from that of at least one of the outer diameter member and the inner diameter member, the vibration damping ratio is further increased.
Therefore, when the vibration applied to the outer diameter member or the inner diameter member is attenuated by the damping member, the vibration is attenuated at a larger damping rate, and is more difficult to be transmitted to the inner diameter member or the outer diameter member. In addition, quiet operation can be performed without generating aperiodic motion or the like.
[0011]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, embodiments of the present invention will be described in detail with reference to FIGS.
The present invention provides an outer ring and an inner ring that rotate relatively, a rolling element disposed between the outer ring and the inner ring, and a rolling element disposed between the outer ring and the inner ring to allow the rolling element to roll freely. The present invention relates to a retainer having a holding pocket and a retainer used in a rolling bearing having the retainer.
[0012]
FIG. 1 shows a rolling bearing retainer 10 according to a first embodiment of the present invention.
Roller bearing retainer (hereinafter, referred to as retainer) 10 includes a single outer diameter member 11, a pair of inner diameter members 12 arranged on the inner peripheral side of outer diameter member 11, and outer diameter members 11 and 11. And a pair of damping members 13 arranged between the inner diameter members 12.
[0013]
The outer diameter member 11 is formed in an annular shape having a T-shaped cross section, and is formed using a brass alloy, an iron alloy, a magnesium alloy, an aluminum alloy, a synthetic resin, or the like as a material.
A plurality of pockets 16 are formed in the outer diameter member main body portion 14 arranged at the center of the outer diameter member 11 with a column portion 15 arranged at intervals in the circumferential direction. A ball, which is a rolling element (not shown), is inserted into the pocket 16.
[0014]
A pair of outer peripheral plate portions 17 are formed on the outer peripheral side of the outer diameter member main body 14. The outer peripheral plate portion 17 is formed in a thin plate shape from the outer diameter member main body 14 and protrudes in a flange shape.
The outer diameter member 11 is composed of an outer diameter member main body 14 having a pocket 16 and a pair of thin plate-shaped outer peripheral plate portions 17, so that the weight is reduced.
[0015]
The inner diameter member 12 has an annular shape having an L-shaped cross section, and is formed of a brass-based alloy, an iron-based alloy, a magnesium alloy, an aluminum alloy, a synthetic resin, or the like in the same manner as the outer diameter member 11. ing.
The inner diameter member 12 has a thin plate-shaped inner peripheral plate portion 18 on its inner circumferential side, and a thin plate-shaped side plate portion 19 on its outer side.
The inner diameter member 12 is composed of an inner peripheral plate portion 18 having a thin plate shape and a side plate portion 19 having a thin plate shape, so that the weight is reduced.
[0016]
The damping member 13 is formed of an elastic material such as rubber or a flexible resin into a ring shape having a rectangular shape in cross section, and has a damping coefficient different from that of the outer diameter member 11 and the inner diameter member 12. Have.
The damping member 13 is housed in a rectangular space formed by the outer diameter member main body 14 and the outer peripheral plate portion 17 of the outer diameter member 11 and the inner peripheral plate portion 18 and the side plate portion 19 of the inner diameter member 12. The outer diameter member 11 and the inner diameter member 12 are integrally connected.
[0017]
Here, between the outer peripheral plate portion 17 of the outer diameter member 11 and the side plate portion 19 of the inner diameter member 12, and between the outer diameter member body 14 of the outer diameter member 11 and the inner peripheral plate portion 18 of the inner diameter member 12. , A gap a is formed. The gap a separates the outer diameter member 11 and the inner diameter member 12 in a non-contact manner.
[0018]
As shown in FIG. 2, the radial width L1 of the damping member 13 is smaller than the inner diameter width L2 of the outer diameter member main body 14 of the outer diameter member 11, and the inner diameter width L3 of the side plate 19 of the inner diameter member 12 is reduced. Greater than. Therefore, a gap a is formed between the outer peripheral plate 17 of the outer diameter member 11 and the side plate 19 of the inner diameter member 12.
[0019]
Further, the height h1 of the damping member 13 is smaller than the inner diameter height h2 of the outer peripheral side plate 17 of the outer diameter member 11, and is larger than the inner diameter height h3 of the inner peripheral plate portion 18 of the inner diameter member 12. Therefore, a gap a is formed between the outer diameter member main body 14 of the outer diameter member 11 and the inner peripheral plate portion 18 of the inner diameter member 12. As a result, the outer diameter member 11 and the inner diameter member 12 are arranged in a non-contact manner.
[0020]
In the cage 10 having such a structure, the outer diameter member 11 and the inner diameter member 12 are connected to each other through the damping member 13 by bonding, welding, or setting a buckle by machining.
[0021]
As the damping member 13, a material having high damping performance such as oil used for an O-ring or an oil damper may be used. The damping coefficient of the damping member 13 may be different from at least one of the outer diameter member 11 and the inner diameter member 12.
[0022]
According to the retainer 10 of the first embodiment, the outer diameter member 11, the inner diameter member 12, and the damping member 13 are separated, and the damping coefficient of the damping member 13 is smaller than that of the outer diameter member 12 and the inner diameter member 12. The damping member 13 is connected to the outer diameter member 11 and the inner diameter member 12 which are selected so as to be in a non-contact manner.
[0023]
Therefore, the vibration applied to the outer diameter member 11 or the inner diameter member 12 is attenuated by the damping member 13 and is not directly transmitted to the inner diameter member 12 or the outer diameter member 11. Here, since the damping coefficient of the damping member 13 is selected so as to be different from the damping coefficient of the outer diameter member 11 and the inner diameter member 12, the vibration given to the outer diameter member 11 or the inner diameter member 12 is reduced by the damping member 13. When it is attenuated, it is attenuated at a large attenuation rate. Therefore, the vibration is hardly transmitted to the inner diameter member 12 or the outer diameter member 11, and a simple vibration, a damped vibration, an aperiodic motion and the like are not generated.
[0024]
And, even if the vibration frequency of a rotating body such as a spindle for a machine tool or the vibration frequency of the bearing itself is matched, the outer diameter member 11, the inner diameter member 12, and the damping member 13 are separated and the outer diameter member 11 is formed. Because the and the inner diameter member 12 are assembled in a non-contact manner, resonance is suppressed, and quiet operation can be performed without generating large mechanical vibration.
[0025]
Further, since the outer diameter member 11, the inner diameter member 12, and the damping member 13 are provided separately, the weight is reduced and the weight is reduced with the decrease in the volume. As a result, the centrifugal force generated during operation is reduced, and the wear resistance can be improved.
[0026]
FIG. 3 shows a cage according to a second embodiment of the present invention. In the embodiments described below, members having the same configurations and operations as the members and the like already described are denoted by corresponding reference numerals in the drawings, and description thereof will be simplified or omitted.
The retainer 20 shown in FIG. 3 includes a pair of outer diameter members 21, a single inner diameter member 22 disposed on the inner peripheral side of the outer diameter member 21, and is disposed between the outer diameter member 21 and the inner diameter member 22. And a pair of damping members 23.
[0027]
The outer diameter member 21 has an annular shape having an L-shaped cross section, and is formed using a brass alloy, an iron alloy, a magnesium alloy, an aluminum alloy, a synthetic resin, or the like as a material.
The outer diameter member 21 has a thin plate-shaped outer peripheral plate portion 24 on its outer peripheral side, and has a thin plate-shaped side plate portion 25 on its outer side.
The outer diameter member 21 is composed of a thin plate-shaped outer peripheral plate portion 24 and a thin plate-shaped side plate portion 25 to reduce the weight.
[0028]
The inner diameter member 22 has an annular shape having a T-shape in cross section, and is formed from a brass-based alloy, an iron-based alloy, a magnesium alloy, an aluminum alloy, a synthetic resin, or the like as the outer diameter member 21. ing.
A plurality of pockets 28 are formed in the inner diameter member main body 26 disposed at the center of the inner diameter member 22 at intervals in the circumferential direction via a column 27. A ball, which is a rolling element (not shown), is inserted into the pocket 28.
[0029]
A pair of inner peripheral plate portions 29 are formed on the inner peripheral side of the inner diameter member main body 26. The inner peripheral plate portion 29 is formed in a thin plate shape from the inner diameter member main body 26 and protrudes in a flange shape.
The inner diameter member 22 is composed of an outer diameter member main body 26 having a pocket 28 and a pair of thin plate-shaped inner peripheral plate portions 29 to reduce the weight.
[0030]
The damping member 23 is formed in an annular shape having a rectangular shape in cross section using an elastic material such as rubber or a flexible resin as a material, and has a damping coefficient different from the damping coefficient of the outer diameter member 21 and the inner diameter member 22. Have.
The damping member 23 is housed in a quadrangular space formed by being surrounded by the outer peripheral plate portion 24 and the side plate portion 25 of the outer diameter member 21 and the inner diameter member main body 26 and the inner peripheral plate portion 29 of the inner diameter member 22. The diameter member 21 and the inner diameter member 22 are integrally connected.
[0031]
Here, the radial width L4 of the damping member 23 is smaller than the inner diameter width L5 of the inner diameter member body 26 of the inner diameter member 22 and larger than the inner diameter width L6 of the side plate 25 of the outer diameter member 21. Therefore, a gap a is formed between the side plate portion 25 of the outer diameter member 21 and the inner peripheral plate portion 29 of the inner diameter member 22.
[0032]
The height dimension h4 of the damping member 23 is smaller than the inner diameter height dimension h5 of the inner diameter member main body 26 of the inner diameter member 22 and larger than the inner diameter height dimension h6 of the outer peripheral plate portion 24 of the outer diameter member 21. Therefore, a gap a is formed between the inner diameter member main body 26 of the inner diameter member 22 and the outer peripheral plate portion 24 of the outer diameter member 21. As a result, the outer diameter member 21 and the inner diameter member 22 are arranged in a non-contact manner.
[0033]
According to the retainer 20 of the second embodiment, the outer diameter member 21, the inner diameter member 22, and the damping member 23 are separated from each other, and the damping coefficient of the damping member 23 is smaller than that of the outer diameter member 22 and the inner diameter member 22. The damping member 23 is coupled to the outer diameter member 21 and the inner diameter member 22 which are selected so as to be in a non-contact manner.
[0034]
Therefore, the vibration applied to the outer diameter member 21 or the inner diameter member 22 is attenuated by the damping member 23 and is not directly transmitted to the inner diameter member 22 or the outer diameter member 21. Here, since the damping coefficient of the damping member 23 is selected so as to be different from the damping coefficient of the outer diameter member 21 and the inner diameter member 22, the vibration given to the outer diameter member 21 or the inner diameter member 22 is reduced by the damping member 23. When it is attenuated, it is attenuated at a large attenuation rate. Therefore, the vibration is not easily transmitted to the inner diameter member 22 or the outer diameter member 21, and a simple vibration, a damped vibration, an aperiodic motion, and the like do not occur.
[0035]
And, even if the vibration frequency of the rotating body such as a spindle for a machine tool or the vibration frequency of the bearing itself is matched, the outer diameter member 21, the inner diameter member 22, and the damping member 23 are separated and the outer diameter member 21 is formed. Since the and the inner diameter member 22 are assembled in a non-contact manner, resonance is suppressed, and quiet operation can be performed without generating large mechanical vibration.
[0036]
Further, since the outer diameter member 21, the inner diameter member 22, and the damping member 23 are formed separately, their volumes are reduced, and the weight is reduced. As a result, the centrifugal force generated during operation is reduced, and the wear resistance can be improved.
[0037]
FIG. 4 shows a cage according to a third embodiment of the present invention.
4 includes a single outer diameter member 31, a single inner diameter member 32 disposed on the inner peripheral side of the outer diameter member 31, and a single outer diameter member 31 disposed between the outer diameter member 31 and the inner diameter member 32. And a pair of attenuation members 33.
[0038]
The outer diameter member 31 has an annular shape having an L-shape in cross section, and is formed using a brass-based alloy, an iron-based alloy, a magnesium alloy, an aluminum alloy, a synthetic resin, or the like as a material.
A plurality of outer diameter member side pockets 36a are formed in the outer diameter member main body 34 arranged at the central portion of the outer diameter member 31 and arranged at intervals in the circumferential direction via a column (not shown). .
[0039]
On the outer peripheral side of the outer diameter member main body 34, a pair of outer peripheral plate portions 37 is provided. The outer peripheral plate portion 37 is formed as a thin plate from the outer diameter member main body 34 and protrudes in a flange shape.
The outer diameter member 31 is composed of an outer diameter member main body 34 having an outer diameter member side pocket 36a and a pair of thin outer peripheral plate portions 37, so that the weight is reduced.
[0040]
The inner diameter member 32 is formed in an annular shape having an I-shaped cross section, and is formed of a brass-based alloy, an iron-based alloy, a magnesium alloy, an aluminum alloy, a synthetic resin, or the like in the same manner as the outer diameter member 31. Have been.
The inner diameter member 32 has a plurality of inner diameter member side pockets 36b at the same positions as the outer diameter member side pockets 36a of the outer diameter member main body 34 and arranged at intervals in the circumferential direction via the pillar portions 35. Is formed. A ball (not shown) is inserted into the inner diameter member side pocket 36b and the outer diameter member side pocket 36a of the outer diameter member 31.
The inner diameter member 32 has a thin plate shape, and is lightened.
[0041]
The damping member 33 is formed of an elastic material such as rubber or flexible resin into a circular shape having a circular cross section, and has a damping coefficient different from that of the outer diameter member 31 and the inner diameter member 32. Have.
The damping member 33 is accommodated in a square space formed by the outer diameter member main body 34 and the outer peripheral plate portion 37 of the outer diameter member 31 and the inner diameter member 32, and is integrated with the outer diameter member 31 and the inner diameter member 32. Are combined.
[0042]
Here, the diameter d1 of the damping member 33 is larger than the inner diameter width L7 of the outer diameter member main body 34 of the outer diameter member 31. Therefore, a gap a is formed between the outer diameter member main body 34 of the outer diameter member 31 and the inner diameter member 32. As a result, the outer diameter member 31 and the inner diameter member 32 are arranged in a non-contact manner.
[0043]
According to the cage 30 of the third embodiment, the outer diameter member 31, the inner diameter member 32, and the damping member 33 are separated, and the damping coefficient of the damping member 33 is smaller than the damping coefficient of the outer diameter member 31 and the inner diameter member 32. The damping member 33 is coupled to the outer diameter member 31 and the inner diameter member 32 which are selected so as to be in a non-contact manner.
[0044]
Therefore, the vibration applied to the outer diameter member 31 or the inner diameter member 32 is attenuated by the damping member 33 and is not directly transmitted to the inner diameter member 32 or the outer diameter member 31. Here, since the damping coefficient of the damping member 33 is selected so as to be different from the damping coefficient of the outer diameter member 31 and the inner diameter member 32, the vibration given to the outer diameter member 31 or the inner diameter member 32 is When it is attenuated, it is attenuated at a large attenuation rate. Therefore, it is difficult for the vibration to be transmitted to the inner diameter member 32 or the outer diameter member 31, and a simple vibration, a damped vibration, an aperiodic motion, or the like does not occur.
[0045]
And, even if the vibration frequency of the rotating body such as a spindle for a machine tool or the vibration frequency of the bearing itself is matched, the outer diameter member 31, the inner diameter member 32, and the damping member 33 are separated and the outer diameter member 31 is formed. Because the and the inner diameter member 32 are assembled in a non-contact manner, no resonance occurs. Therefore, quiet operation can be performed without generating large mechanical vibration.
[0046]
In addition, since the outer diameter member 31, the inner diameter member 32, and the damping member 33 are provided separately, the weight is reduced and the weight is reduced as their volume is reduced. As a result, the centrifugal force generated during operation is reduced, and the wear resistance can be improved.
[0047]
FIG. 5 shows a cage according to a fourth embodiment of the present invention.
The retainer 40 shown in FIG. 5 includes a single outer diameter member 41, a single inner diameter member 42 disposed on the inner peripheral side of the outer diameter member 41, and a single outer diameter member 41 disposed between the outer diameter member 41 and the inner diameter member 42. And a pair of damping members 43.
[0048]
The outer diameter member 41 is formed in an annular shape, and is formed of a material such as a brass alloy, an iron alloy, a magnesium alloy, an aluminum alloy, or a synthetic resin.
In the center of the outer diameter member 41, a plurality of outer diameter member side pockets 46a are formed at intervals in the circumferential direction via a column (not shown).
[0049]
On both outer sides of the outer diameter member-side pocket 46a of the outer diameter member 41, a pair of damping member housing portions 41a are formed. The damping member accommodating portion 41a has a concave groove shape cut in a rectangular shape from the inner peripheral surface of the outer diameter member 41 toward the outer periphery, and is continuous in the circumferential direction.
Since the outer diameter member 41 is formed with an attenuating member accommodating portion 41a cut in a concave groove shape on the inner peripheral side, the outer diameter member 41 is thin as a whole, and the weight is reduced.
[0050]
Like the outer diameter member 41, the inner diameter member 42 is formed in an annular shape using a material such as a brass alloy, an iron alloy, a magnesium alloy, an aluminum alloy, or a synthetic resin.
At the center of the inner diameter member 42, a plurality of inner diameter member-side pockets 46b are formed at intervals in the circumferential direction via the column portion 45. A ball (not shown) is inserted into the inner diameter member side pocket 46b and the outer diameter member side pocket 46a of the outer diameter member 41.
[0051]
On both outer sides of the inner diameter member side pocket 46b of the inner diameter member 42, a pair of attenuation member accommodating portions 42a are formed. The damping member accommodating portion 42a has a concave groove shape cut in a rectangular shape from the outer peripheral surface of the inner diameter member 42 toward the inner periphery, and is continuous in the circumferential direction.
Since the inner diameter member 42 is formed with a damping member accommodating portion 42a cut into a concave groove shape on the outer peripheral side, the inner diameter member 42 is thinner as a whole, and the weight is reduced.
[0052]
The damping member 43 is formed in an annular shape having a rectangular shape in cross section by using an elastic material such as rubber or flexible resin as a material, and has a damping coefficient different from that of the outer diameter member 41 and the inner diameter member 42. Have.
The damping member 43 is accommodated in a rectangular space formed by being surrounded by the damping member accommodating portion 41a of the outer diameter member 41 and the damping member accommodating portion 42a of the inner diameter member 42. They are integrally connected.
[0053]
Here, the radial width L8 of the damping member 43 is calculated from the sum of the depth L9 of the damping member housing portion 41a of the outer diameter member 41 and the depth L10 of the damping member housing portion 42a of the inner diameter member 42. Is also big. Therefore, a gap a is formed between the outer diameter member 41 and the inner diameter member 42. As a result, the outer diameter member 41 and the inner diameter member 42 are arranged in a non-contact manner.
[0054]
According to the retainer 40 of the fourth embodiment, the outer diameter member 41, the inner diameter member 42, and the damping member 43 are separated from each other, and the damping coefficient of the damping member 43 is smaller than that of the outer diameter member 41 and the inner diameter member 42. The damping member 43 is connected to the outer diameter member 41 and the inner diameter member 42 which are selected so as to be in a non-contact manner.
[0055]
Therefore, the vibration applied to the outer diameter member 41 or the inner diameter member 42 is attenuated by the damping member 43 and is not directly transmitted to the inner diameter member 42 or the outer diameter member 41. Here, since the damping coefficient of the damping member 43 is selected so as to be different from the damping coefficients of the outer diameter member 41 and the inner diameter member 42, the vibration given to the outer diameter member 41 or the inner diameter member 42 is When it is attenuated, it attenuates at a large rate. Therefore, the vibration is not easily transmitted to the inner diameter member 42 or the outer diameter member 41, and a simple vibration, a damped vibration, an aperiodic motion or the like does not occur.
[0056]
And, even if the vibration frequency of a rotating body such as a spindle for a machine tool or the vibration frequency of the bearing itself is matched, the outer diameter member 41, the inner diameter member 42, and the damping member 43 are separated and the outer diameter member 41 is formed. Since the and the inner diameter member 42 are assembled in a non-contact manner, resonance does not occur. Therefore, quiet operation can be performed without generating large mechanical vibration.
[0057]
In addition, since the outer diameter member 41, the inner diameter member 42, and the damping member 43 are provided separately, the weight is reduced and the weight is reduced as the volume is reduced. As a result, the centrifugal force generated during operation is reduced, and the wear resistance can be improved.
[0058]
FIG. 6 shows a cage according to a fifth embodiment of the present invention.
The retainer 50 shown in FIG. 6 includes a single outer diameter member 51, a single inner diameter member 52 disposed on the inner peripheral side of the outer diameter member 51, and a single outer diameter member 51 disposed between the outer diameter member 51 and the inner diameter member 52. And a single damping member 53.
[0059]
The outer diameter member 51 is formed in an annular shape, and is formed using a brass-based alloy, an iron-based alloy, a magnesium alloy, an aluminum alloy, a synthetic resin, or the like as a material.
The outer diameter member 51 is formed with a plurality of outer diameter member side pockets 56a which are arranged at intervals in the circumferential direction via a column (not shown).
On the inner peripheral surface of the outer diameter member 51, a damping member coupling portion 51a is formed.
The outer diameter member 51 is thinner as a whole, and its weight is reduced.
[0060]
Like the outer diameter member 51, the inner diameter member 52 is formed in an annular shape using a material such as a brass alloy, an iron alloy, a magnesium alloy, an aluminum alloy, or a synthetic resin.
The inner diameter member 52 is formed with a plurality of inner diameter member side pockets 56b arranged at intervals in the circumferential direction via the column portion 55.
[0061]
On the outer peripheral surface of the inner diameter member 52, a damping member coupling portion 52a is formed.
Since the inner diameter member 52 is entirely thin, it has a small weight.
[0062]
The damping member 53 is made of an elastic material such as rubber or flexible resin, and is formed in the same annular shape as the outer diameter member 53 and the inner diameter member 54. It has a different damping coefficient from that of
The damping member 53 is formed with a plurality of damping member side pockets 56c arranged at intervals in the circumferential direction via a not-shown column. A ball (not shown) is inserted into the damping member side pocket 56c, the outer diameter member side pocket 56a, and the inner diameter member side pocket 56b.
[0063]
The damping member 53 is sandwiched between the damping member connecting portion 51a of the outer diameter member 51 and the damping member connecting portion 52a of the inner diameter member 52, and is integrally connected to the outer diameter member 51 and the inner diameter member 52. . The outer diameter member 51 and the inner diameter member 52 are connected by the damping member 53 in a non-contact manner.
[0064]
According to the retainer 50 of the fifth embodiment, the outer diameter member 51, the inner diameter member 52, and the damping member 53 are formed separately. Then, the damping coefficient of the damping member 53 is selected so as to be different from the damping coefficient of the outer diameter member 51 and the inner diameter member 52, and the damping member 53 is joined to the outer diameter member 51 and the inner diameter member 52 which are assembled in a non-contact manner. You.
[0065]
Therefore, the vibration applied to the outer diameter member 51 or the inner diameter member 52 is attenuated by the damping member 53, and is not directly transmitted to the inner diameter member 52 or the outer diameter member 51. Here, since the damping coefficient of the damping member 53 is selected to be different from the damping coefficient of the outer diameter member 51 and the inner diameter member 52, the vibration given to the outer diameter member 51 or the inner diameter member 52 is reduced by the damping member 53. When damped, the vibration is damped at a large rate. Therefore, the vibration is not easily transmitted to the inner diameter member 52 or the outer diameter member 51, and a simple vibration, a damped vibration, an aperiodic motion, and the like are not generated.
[0066]
And, even if the vibration frequency of the rotating body such as a spindle for a machine tool or the vibration frequency of the bearing itself is matched, the outer diameter member 51, the inner diameter member 52, and the damping member 53 are separated and the outer diameter member 51 is formed. Since the and the inner diameter member 52 are assembled in a non-contact manner, resonance does not occur. Therefore, quiet operation can be performed without generating large mechanical vibration.
[0067]
Further, since the outer diameter member 51, the inner diameter member 52, and the damping member 53 are formed separately, the weight is reduced and the weight is reduced as the volume is reduced. As a result, the centrifugal force generated during operation is reduced, and the wear resistance can be improved.
[0068]
Note that the present invention is not limited to the above-described embodiment, and appropriate modifications and improvements can be made.
For example, a cylindrical member molded from metal or resin may be fitted only in the pocket portion. In particular, it is preferably used for the fifth embodiment. In that case, the attenuation rate of the vibration received from the ball mounted on the pocket can be further improved.
Then, the shape of the cage is appropriately changed so as to be guided by the inner ring, the outer ring or the ball of the bearing.
[0069]
【The invention's effect】
As described above, according to the rolling bearing of the present invention, the outer diameter member, the inner diameter member, and the damping member are separated from each other, and the damping member is connected to the outer diameter member and the inner diameter member assembled in a non-contact manner. You.
Therefore, the vibration applied to the outer diameter member or the inner diameter member is attenuated by the damping member and is not directly transmitted to the inner diameter member or the outer diameter member. For example, even if the vibration frequency of a rotating body such as a spindle for a machine tool or the vibration frequency of the bearing itself is matched, the outer diameter member, the inner diameter member, and the damping member are separated from each other, and the outer diameter member and the inner diameter member are not separated. Because it is mounted on the contact, it does not resonate. Therefore, operation can be performed without generating large mechanical vibration.
[0070]
Further, since the outer diameter member, the inner diameter member, and the damping member are formed separately, their volumes are reduced, and the weight is reduced. As a result, the centrifugal force generated during operation is reduced, and the wear resistance can be improved. As a result, it is possible to provide a cage for a rolling bearing having excellent damping performance and wear resistance.
[0071]
Further, since the damping coefficient of the damping member is selected so that the damping coefficient is different from that of at least one of the outer diameter member and the inner diameter member, the vibration damping ratio is increased.
Therefore, when the vibration applied to the outer diameter member or the inner diameter member is attenuated by the damping member, the vibration is attenuated at a larger damping rate, and is more difficult to be transmitted to the inner diameter member or the outer diameter member. In addition, quiet operation can be performed without generating aperiodic motion or the like.
[Brief description of the drawings]
FIG. 1 is a partial cross-sectional external view of a first embodiment.
FIG. 2 is a sectional view of FIG.
FIG. 3 is a sectional view of a second embodiment.
FIG. 4 is a sectional view of a third embodiment.
FIG. 5 is a sectional view of a fourth embodiment.
FIG. 6 is a sectional view of a fifth embodiment.
FIG. 7 is a sectional view of a conventional cage.
[Explanation of symbols]
10,20,30,40,50 Rolling bearing cage (cage)
11, 21, 31, 41, 51 Outer diameter member
12, 22, 32, 42, 52 Inner diameter member
13,23,33,43,53 Damping member

Claims (2)

相対的に回転する外輪および内輪と、前記外輪と前記内輪との間に配置される転動体と、前記外輪と前記内輪との間に配置され、前記転動体を転動自在に保持するポケットを有する保持器と、を有する転がり軸受において、
前記保持器は、外輪側に配置される外径部材と、該外径部材と別体にされ、前記外径部材に非接触にして内輪側に配置される内径部材と、前記外径部材及び前記内径部材との間に配置される減衰部材と、を有することを特徴とする転がり軸受。An outer ring and an inner ring that rotate relatively, a rolling element disposed between the outer ring and the inner ring, and a pocket that is disposed between the outer ring and the inner ring and holds the rolling element so as to roll freely. And a rolling bearing having:
The retainer is an outer diameter member disposed on the outer ring side, and is separated from the outer diameter member, and an inner diameter member disposed on the inner ring side in non-contact with the outer diameter member, and the outer diameter member and A damping member disposed between the inner diameter member and the inner diameter member. 前記減衰部材は、前記外径部材及び内径部材の少なくとも一方と減衰係数が異なることを特徴とする請求項１に記載の転がり軸受。The rolling bearing according to claim 1, wherein the damping member has a different damping coefficient from at least one of the outer diameter member and the inner diameter member.

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