JP3855744B2 - Superfinishing method and apparatus - Google Patents

Description

ここで、γ＜１とした場合のＲ0／ｅとγとの関係を図３に示す。図３から分かるように、非線形ではあるが、γ＝０．３〜０．０５であるときに、Ｒ0／ｅが５．６〜２２．０となり、約４倍の範囲の値が得られる。例えば、ｅ＝１５ｍｍとすると、γ＝０．３の場合、ｒ0＝１５×０．３＝４．５ｍｍ、Ｒ0＝５．６×１５＝８４ｍｍとなる。また、γ＝０．０５の場合、ｒ0＝１５×０．０５＝０．７５ｍｍ、Ｒ0＝２２．０×１５＝３３０ｍｍとなる。
【００２４】
また、回転軸２ａの回転角度θに応じて砥石４の先端位置Ｐがｘ軸方向へ移動する移動量ｘsは、次の（４）式により表される。
【００２５】
ｘs＝（ｅ＋ｒ0）sinθ …（４）
上記（４）式により、上記各場合における移動量ｘsは、１９．５sinθ〜１５．７５sinθとなり、例えば移動量ｘs＝３ｍｍとした場合、回転角度θ＝０．０３２π（ｒａｄ）〜０．０４１π（ｒａｄ）となる。
【００２６】
また、上記距離ｒ0を固定値とし、偏心カム５の偏心量ｅを変数とした場合の曲率半径Ｒ0と上記ｒ０の関係を考える。上記（２）式に従えば、曲率半径Ｒ0と上記距離ｒ0との比Ｒ0／ｒ0と、偏心量ｅと上記距離ｒ0との比ｅ／ｒ0との間で、図４に示すような関係が得られる。図４から分かるように、線形的に、ｅ／ｒ0＝０．４〜１．５の範囲で、Ｒ0／ｒ0＝２．０〜６．２となり、約３倍の範囲の値が得られる。例えば、ｒ0＝３５ｍｍとすると、ｅ／ｒ0＝０．４の場合、ｅ＝３５×０．４＝１４ｍｍ、Ｒ0＝３５×２．０＝７０ｍｍとなる。また、ｅ／ｒ0＝１．５の場合、ｅ＝３５×１．５＝５３．５ｍｍ、Ｒ0＝３５×６．２＝２１８ｍｍとなる。
【００２７】
また、上記各場合における移動量ｘsは、上記（４）式により、４９sinθ〜８８．５sinθとなり、例えば移動量ｘs＝２ｍｍとした場合、回転角度θ＝０．０１８π（ｒａｄ）〜０．００７π（ｒａｄ）となる。
【００２８】
このように、回転軸２ａの中心Ｏｓから砥石４の先端位置Ｐまでの直線距離ｒ0および偏心カム５の偏心量ｅを適宜設定することによって、小さい回転角度θの範囲で、被加工物の超仕上げ部位に対応する曲率半径の軌道に沿って砥石４の先端を揺動させることが可能になる。また、この揺動機構を簡素化された構造で実現することが可能となる。さらに、揺動機構全体の質量が小さくすることができるので、揺動速度を増すことが可能になり、加工能率の向上を図ることができる。よって、本方法によれば、構造を簡素化することができ、曲率が小さい超仕上げ対象部位の超仕上げの場合と同様に、高い加工能率で、精度および粗さが良い仕上げを得ることができる超仕上げ装置を提供することができる。
【００２９】
（第1実施の形態）
次に、本発明の第１実施の形態に係る超仕上げ装置について図５ないし図８を参照しながら説明する。図５（ａ）は本発明の第１実施の形態に係る超仕上げ装置の構成を示す上面図、図５（ｂ）は図５（ａ）のＡ−Ａ線に沿って得られた縦断面図、図６（ａ）は図５の偏心カムの正面図、図６（ｂ）は図５の偏心カムの側面図、図６（ｃ）は図５の偏心カムの斜視図、図７（ａ）は図５の砥石ホルダの構成を示す縦断面図、図７（ｂ）は図７（ａ）のＢから見た矢視図、図８（ａ）は砥石ホルダの先端部の他の構成例の正面図、図８（ｂ）は図８（ａ）のＣ−Ｃ線に沿って得られた断面図である。
【００３０】
本実施の形態における超仕上げ装置は、上述した基本構成に基づくものであるが、本実施の形態では、振動を打ち消し合うことが可能な２軸構造とし、各軸を１つの駆動モータで駆動する構成とする。
【００３１】
具体的には、本実施の形態の超仕上げ装置は、図５に示すように、床などの支持面に置かれるベース１１を備える。ベース１１には、２つのスライダ１２，１３が互いに対向するように搭載されている。
【００３２】
スライダ１２は、ベース１１の上面に設けられた一対のガイドレール１４ａ，１４ｂに沿って摺動する複数のリニアガイド１２ａを有し、複数のリニアガイド１２ａによりガイド一対のガイドレール１４ａ，１４ｂに案内されながらベース１１上を移動可能に構成されている。スライダ１２には、ガイドレール１４ａ，１４ｂと直交する方向に伸びるスピンドル１６が回転可能に支持されている。スピンドル１６の一端１６ａには、リンク部材３２が取り付けられ、その他端１６ｂには、砥石ホルダ２０が取り付けられている。この砥石ホルダ２０の詳細構成については後述する。
【００３３】
また、スピンドル１６には、偏心カム１８が取り付けられている。この偏心カム１８は、図６に示すように、リング部１８ａと、リング部１８ａに対して偏心してかつ一体的に連なるカム部１８ｂとから構成され、カム部１８ｂは、リング部１８ａの孔部に対応する部分を切り欠いた円板からなる。偏心カム１８は、リング部１８ａがスピンドル１６と同軸上になるようにスピンドル１６に嵌合されている。これにより、偏心カム１８のカム部１８ｂは、その中心がスピンドル１６の中心に対して偏心量ｅ分だけ偏心してスピンドル１６に取り付けられていることになる。
【００３４】
砥石ホルダ２０は、図７に示すように、スピンドル１６の他端１６ｂに取り付けられているベース部４０を有し、ベース部４０には、ホルダ部４７を案内するための一対のガイドレール４１が設けられている。ホルダ部４７は、かぎ状の形状を有し、そのベース部４０に対向する部位には、ボールねじ機構４２と、各ガイドレール４１に摺動可能に係合する一対のリニアガイド４６とが設けられている。ボールねじ機構４２は、ねじ軸４４と、ホルダ部４７に固定されているナット部４５とを含み、ねじ軸４４はベース部４０に固定されている駆動モータ４３により回転駆動される。ねじ軸４４の回転運動に伴いナット部４５は、ねじ軸４４に沿って移動するので、ホルダ部４７はベース部４０に対して相対的に移動される。ホルダ部４７の先端部位４７ａには、保持部材４８が取り付けられ、この保持部材４８と先端部位４７ａとの間に砥石４９が保持されている。砥石４９は、その先端位置とスピンドル１６の中心との距離がｒ0になるように位置決めされている。被加工物５０（例えば球面ころに相当する）の曲率半径Ｒに一致する曲率Ｒ０で揺動される。ここで、砥石４９による超仕上げの際には、被加工物５０は一対のローラ５１間に挟持されて砥石４９の先端に対して位置決めされるとともに、ローラ５１の回転により被加工物５０が回転される。
【００３５】
このような構成の砥石ホルダを用いることによって、ホルダ部４７の相対移動により、砥石４９を被加工物５０に対して所定の加圧力で押し付けることが可能になる。また、砥石４９の摩耗などによって砥石４９の先端位置が被加工物５０に対して鉛直方向に変化した場合に、砥石４９の先端位置と被加工物５０の鉛直方向の位置調整が可能になる。
【００３６】
スライダ１３は、スライダ１２と同様に、ベース１１の上面に設けられた一対のガイドレール１５ａ，１５ｂに沿って摺動する複数のリニアガイド１３ａを有し、複数のリニアガイド１３ａにより一対のガイドレール１５ａ，１５ｂに案内されながらベース１１上を移動可能に構成されている。スライダ１３には、ガイドレール１５ａ，１５ｂと直交する方向に伸びるスピンドル１７が回転可能に支持されている。スピンドル１７の一端１７ａには、リンク部材３３が取り付けられ、その他端１７ｂには、砥石ホルダ２１が取り付けられている。この砥石ホルダ２１は、砥石ホルダ２０と同じ構成を有し（図７を参照）、ここでは、その説明は省略する。
【００３７】
また、スピンドル１７には、偏心カム１９が取り付けられている。この偏心カム１９は、偏心カム１８と同様に構成され、リング部１９ａとカム部１９ｂとを有する（図６を参照）。これにより、偏心カム１９のカム部１９ｂは、その中心がスピンドル１７の中心に対して偏心量ｅ分だけ偏心してスピンドル１７に取り付けられていることになる。
【００３８】
スライダ１２とスライダ１３との間には、転がり軸受からなる２つの規制部材２３，２４が設けられ、各規制部材２３，２４は軸２２に同軸上に支持されている。軸２２の各端は、それぞれベース１１に設けられている支持部材２２ａ，２２ｂに支持されている。規制部材２３は、その外周面がスピンドル１６に取り付けられた偏心カム１８のカム部１８ｂの外周面に当接するように、規制部材２４は、その外周面がスピンドル１７に取り付けられた偏心カム１９のカム部１９ｂの外周面に当接するようにそれぞれ配置されている。
【００３９】
スライダ１２は、ばね部材３５により、偏心カム１８のカム部１８ｂが規制部材２３に押し付けられる方向に付勢されている。ばね部材３５は、ベース１１に固定されている保持部材３４に保持されている。同様に、スライダ１３は、ばね部材３７により、偏心カム１９のカム部１９ｂが規制部材２４に押し付けられる方向に付勢されている。ばね部材３７は、ベース１１に固定されている保持部材３６に保持されている。
【００４０】
スピンドル１６のリンク部材３２は、図５（ｂ）に示すように、リンク部材３０を介して中間リンク２８のアーム部２８ｂに連結されている。また、スピンドル１７のリンク部材３３は、リンク部材３１を介して中間リンク２８のアーム部２８ｃに連結されている。中間リンク２８には、上記アーム部２８ｂおよびアーム部２８ｃとともに、アーム部２８ａが設けられている。アーム部２８ｂとアーム部２８ｃとは、同一直線上に沿って互いに逆向きに突出し、アーム部２８ａは、アーム部２８ｂに対して垂直に突出する。中間リンク２８は、軸箱２９に支持されている。中間リンク２８のアーム部２８ａは、リンク部材２７の一端に連結され、リンク部材２７の他端は、駆動モータ２５の回転運動を揺動運動に変換するための変換部材２６に連結されている。変換部材２６は駆動モータ２５の出力軸（図示せず）に固定され、変換部材２６におけるリンク部材２７との連結点は、駆動モータ２５の出力軸に対して偏心量Ｅ1分偏心した位置にある。この偏心量Ｅ1は、各スピンドル１６，１７の回転角度θの最大値を規定する。
【００４１】
このようなリンク機構により、駆動モータ２５の回転運動は各スピンドル１６，１７の揺動運動に変換され、各スピンドル１６，１７は、互いに逆向きに角度的に回転運動される。スピンドル１６が例えば一方の方向（図５（ｂ）において時計方向）へ角度的に回転駆動されると、スピンドル１６の回転に伴い偏心カム１８が回転される。この際、偏心カム１８はそのカム部１８ｂが規制部材２３に当接された状態で回転するので、偏心カム１８の回転によりスライダ１２は、ばね部材３５の付勢力に抗しながらガイドレール１４ａ，１４ｂに沿って移動される。これにより、スピンドル１６は、回転しながらその回転角度θに応じてガイドレール１４ａ，１４ｂの案内方向に移動される。
【００４２】
スピンドル１６が一方の方向へ回転駆動された場合には、スピンドル１７は他方の方向（反時計方向）へ角度的に回転駆動される。この場合も、スピンドル１６の場合と同様に、偏心カム１９の回転によりスライダ１３は、ばね部材３７の付勢力に抗しながらガイドレール１５ａ，１５ｂに沿って移動される。これにより、スピンドル１７は、回転しながらその回転角度θに応じてガイドレール１５ａ，１５ｂの案内方向に移動されることになる。
【００４３】
また、スピンドル１６が他方の方向（反時計方向）へ回転駆動された場合には、スピンドル１７は一方の方向（時計方向）へ角度的に回転駆動される。この場合も、同様に、各スピンドル１６，１７は、回転しながらその回転角度θに応じてガイドレール１４ａ，１４ｂ，１５ａ，１５ｂの案内方向に移動されることになる。
【００４４】
スピンドル１６，１７が回転駆動されると、スピンドル１６，１７に取り付けられている砥石ホルダ２０，２１は、ガイドレール１４ａ，１４ｂ，１５ａ，１５ｂの案内方向に移動しながらスピンドル１６，１７の周りに角度的に回転されることになる。このとき、砥石ホルダ２０，２１の砥石４９の先端位置は、スピンドル１６，１７の中心から砥石２０，２１の先端位置までの直線距離ｒ0および偏心カム１６，１７の偏心量ｅに応じて決定された曲率半径の軌道に沿って移動する。即ち、砥石ホルダ２０，２１を、砥石４９の先端位置が所定位置に保持された被加工物５０の超仕上げ対象部位の曲率半径に沿って移動するように揺動させることができる。
【００４５】
よって、本実施の形態では、２つのスピンドル１６，１７を同時に逆向きに駆動することによって、振動的にバランスを取ることができ、揺動速度をより速くすることが可能である。
【００４６】
なお、本実施の形態では、ホルダ部４７の先端部位４７ａと保持部材４８との間に砥石４９が保持するように構成されているが、この構成は、砥石４９の傾斜成分に誤差が発生せず、また被加工物５０の姿勢（軸方向位置および傾斜）が変わる可能性がないことを前提としたものであるが、超仕上げにおいては、前工程（研削工程）で得られた被加工物５０の超仕上げ対象部位の形状を崩さずに、その粗さを良くすることが望まれているので、上記構成に代えて、砥石４９が被加工物５０の姿勢の変化に追従可能なならい機構を用いることが好ましい。
【００４７】
具体的には、図８に示すように、砥石ホルダのホルダ部４７の先端部位４７ａには、中間部材５２がピボット５３を介して取り付けられ、この中間部材５２と先端部位４７ａとの間には、Ｏリング５５が嵌め込まれている。中間部材５２には、複数のねじ部材５６により保持部材５４が取り付けられ、中間部材５２と保持部材５４との間に砥石４９が挟持されている。この構成により、砥石４９が被加工物５０の姿勢の変化に追従可能になり、前工程（研削工程）で得られた被加工物５０の超仕上げ対象部位の形状を崩さずに、その粗さを良くすることが確実に行われる。
【００４８】
（第２実施の形態）
次に、本発明の第２実施の形態について図９を参照しながら説明する。図９（ａ）は本発明の第２実施の形態に係る超仕上げ装置の主要部構成を示す上面図、図９（ｂ）は図９（ａ）のＤ−Ｄ線に沿って得られた縦断面図である。
【００４９】
上述の第１実施の形態が規制部材として転がり軸受を用いることに対し、本実施の形態では、規制部材としてリニアガイドを用いる。これ以外の構成は上述の第１実施の形態に同じであり、同一の部材には同一の符号を付し、その説明は省略または簡略化する。
【００５０】
具体的には、図９に示すように、スライダ１２とスライダ１３との間には、偏心カム１８，１９のカム部１８ｂ，１９ｂに当接される規制部材６１が設けられている。規制部材６１は、支柱６３に設けられたガイドレール６２に係合しながら鉛直方向に摺動可能なリニアガイドからなる。規制部材６１は、各スピンドル１６，１７の加点に伴い偏心カム１８，１９が回転されると、各偏心カム１８，１９から鉛直方向上向きまたは下向きへの力を受けることになり、この受けた力の方向へ移動される。
【００５１】
このように、規制部材６１としてリニアガイドを用いることによって、さらに構造を簡素化することができる。また、規制部材６１の偏心カム１８，１９のカム部１８ｂ，１９ｂとの当接面が平面であるので、転がり軸受のように誤差が発生しない。さらに、規制部材６１が各偏心カム１８，１９から受ける力は、同一作用線上にあるので、負荷容量、剛性などの観点から、規制部材６１にリニアガイドを用いることは有利である。
【００５２】
（第３実施の形態）
次に、本発明の第３実施の形態について図１０および図１１を参照しながら説明する。図１０（ａ）は本発明の第３実施の形態に係る超仕上げ装置の構成を示す上面図、図１０（ｂ）は図１０（ａ）の超仕上げ装置の正面図、図１１は偏心カム機構の構成例を示す断面図である。
【００５３】
本実施の形態の超仕上げ装置は、図１０に示すように、ベース７１を備え、ベース７１には、２つのスライダ７２，７３が互いに対向するように搭載されている。
【００５４】
スライダ７２は、ベース７１の上面に設けられた一対のガイドレール７４ａ，７４ｂに沿って滑動する複数のリニアガイド７２ａを有し、複数のリニアガイド７２ａにより一対のガイドレール７４ａ，７４ｂに案内されながらベース７１上を移動可能に構成されている。スライダ７２には、ガイドレール７４ａ，７４ｂと直交する方向に伸びるスピンドル７６が回転可能に支持されている。スピンドル７６の一端７６ａには、リンク部材９０が取り付けられ、その他端７６ｂには、砥石ホルダ８０が取り付けられている。この砥石ホルダ８０の構成は、図７に示す構成と同じであり、ここでは、その説明は省略する。
【００５５】
スライダ７３は、スライダ７２と同様に、ベース７１の上面に設けられた一対のガイドレール７５ａ，７５ｂに沿って滑動する複数のリニアガイド７３ａを有し、複数のリニアガイド７３ａにより一対のガイドレール７５ａ，７５ｂに案内されながらベース７１上を移動可能に構成されている。スライダ７３には、ガイドレール７５ａ，７５ｂと直交する方向に伸びるスピンドル７７が回転可能に支持されている。スピンドル７７の一端７７ａには、リンク部材９１が取り付けられ、その他端７７ｂには、砥石ホルダ８１が取り付けられている。この砥石ホルダ８１は、砥石ホルダ８０と同じ構成を有する（図７を参照）。
【００５６】
スライダ７２とスライダ７３との間には、偏心カム機構が設けられている。この偏心カム機構は、ベース７１に固定されている軸箱８８と、軸箱８８に支持されている回転軸８７とを有し、回転軸８７の一端にはリンク部材８９が、その他端には支持板８６が設けられている。支持板８６には、一対の台座８５（一方のみを示す）が締結され、各台座８５には、互いに所定の間隔をおいて配置されている２つの軸８２ａ，８３ａが取り付けられている。ここで、各台座８５は、各軸８２ａ，８３ａが回転軸８７の中心から距離ｅ（偏心量）分離れた位置になるようにそれぞれ配置されている。軸８２ａには円板８２が回転可能に支持され、軸８３ａには、円板８２の直径と同じ直径を有する円板８３が回転可能に支持されている。円板８２はその縁部がスライダ７２に設けられた当接部７２ｂに、円板８３はその縁部がスライダ７３に設けられた当接部７３ｂにそれぞれ当接するように位置決めされている。
【００５７】
スライダ７２は、ばね部材１０３により、当接部７２ｂが円板８２に押し付けられる方向に付勢されている。ばね部材１０３は、ベース７１に固定されている保持部材１０２に保持されている。同様に、スライダ７３は、ばね部材１０５により、当接部７３ｂが円板８３に押し付けられる方向に付勢されている。ばね部材１０５は、ベース７１に固定されている保持部材１０４に保持されている。
【００５８】
スピンドル７６のリンク部材９０は、リンク部材９７を介して中間リンク部材９６に連結され、中間リンク部材９６は、リンク部材９４を介して、回転軸８７のリンク部材８９に連結されている。ここで、中間リンク部材９６は、軸線の周りに回転する円板からなり、中間リンク部材９６におけるリンク部材９７との連結点およびリンク部材９４との連結点は、所定位置に設けられている。スピンドル７７のリンク部材９１は、リンク部材９９を介して中間リンク部材９８に連結され、中間リンク部材９８は、リンク部材９５を介して、回転軸８７のリンク部材８９に連結されている。ここで、中間リンク部材９８は、その軸線の周りに回転する円板からなり、中間リンク部材９８におけるリンク部材９９との連結点およびリンク部材９５との連結点は、所定位置に設けられている。
【００５９】
回転軸８７のリンク部材８９は、回転軸８７と同軸上の円板からなり、上記リンク部材９４，９５とともに、リンク部材９３の一端が連結されている。リンク部材９３の他端は、駆動モータ９２の回転運動を揺動運動に変換するための変換部材（図示せず）に連結されている。この変換部材は駆動モータ９２の出力軸（図示せず）に固定され、変換部材におけるリンク部材９３との連結点は、駆動モータ９２の出力軸に対して偏心量Ｅ2分偏心した位置にある。この偏心量Ｅ2は、各スピンドル７６，７７および回転軸８７の回転角度θの最大値を規定する。
【００６０】
このようなリンク機構により、駆動モータ９２の回転運動は各スピンドル７６，７７および回転軸８７の揺動運動に変換される。回転軸８７は、角度的に回転運動され、これに連動して各スピンドル７６，７７は、互いに逆向きに角度的に回転運動される。例えば回転軸８７が時計方向（図１０（ｂ）において）へ角度的に回転されると、スピンドル７６は反時計方向へ、スピンドル７７は時計方向へ角度的に回転される。また、回転軸８７の回転に伴い支持板８６が回転軸８７の周りに時計方向へ角度的に回転される。この支持板８６の回転に伴い各円板８２，８３が回転軸８７を中心に時計方向へ揺動すると、スライダ７２は、ばね部材１０３の付勢力により、当接部７２ｂが円板８２に当接された状態でガイドレール７４ａ，７４ｂに沿って円板８２に向けて移動される。スライダ７３は、ばね部材１０５の付勢力により、当接部７３ｂが円板８３に当接された状態でガイドレール７５ａ，７５ｂに沿って円板８３に向けて移動される。
【００６１】
また、回転軸８７が反時計方向（図１０（ｂ）において）へ角度的に回転された場合も同様である。
【００６２】
このよう構成により、スピンドル７６，７７に取り付けられている砥石ホルダ８０，８１は、ガイドレール７４ａ，７４ｂ，７５ａ，７５ｂの案内方向に移動しながらスピンドル７６，７７の周りに回転することになる。このとき、砥石ホルダ８０，８１の砥石の先端位置は、スピンドル７６，７７の中心から砥石の先端位置までの直線距離ｒ0および上記偏心カム機構の偏心量ｅに応じて決定された曲率半径の軌道に沿って移動する。即ち、砥石ホルダ８０，８１を、砥石の先端位置が所定位置に保持された被加工物の超仕上げ対象部位の曲率半径に沿って移動するように揺動させることができる。
【００６３】
また、本実施の形態では、２つのスピンドル７６，７７を同時に逆向きに駆動することによって、振動的にバランスを取ることができ、揺動速度をより速くすることが可能である。
【００６４】
また、本実施の形態において、偏心カム機構の偏心量ｅを調整可能にする場合には、図１１に示すような偏心カム機構を用いればよい。この偏心カム機構は、図１１に示すように、回転軸８７に設けられた支持板１１６を有し、この支持板１１６には、あり溝１１６ａが形成されている。支持板１１６には、一対の台座１１５が対応する止めねじ１１９によりあり溝１１６ａを介して締結され、各台座１１５には、それぞれ軸１１３が取り付けられている。各軸１１３には、上記円板８２，８３に相当する転がり軸受１１１が支持されている。各台座１１５は、それぞれの軸１１３が回転軸８７の中心から距離ｅ（偏心量）分離れた位置になるようにそれぞれ配置されている。また、各台座１１５には、止めねじ１１９を受け入れるための位置調整用穴部１１５ａが形成され、各台座１１５間の間隔即ち偏心量ｅは基準プラグ１１７により調整することが可能である。基準プラグ１１７はその軸線が回転軸８７と同軸上になるように支持板１１６に形成された穴に嵌合される。例えば、異なる幅の複数の基準プラグ１１７を準備し、偏心量ｅに応じた幅の基準プラグ１１７を支持板１１６に取り付けることによって、各台座１１５間の間隔即ち軸１１３と回転軸８７との距離（偏心量）ｅを調整することができる。この間隔の調整により、各台座１１５の支持板１１６に対する相対位置が変化した場合、その位置変化に伴い各台座１１５における止めねじ１１９の位置は変化するが、位置調整用穴部１１５ａが設けられているので、各台座１１５の相対位置の調整後も、調整前と同じように、各台座１１５を支持板１１６に止めねじ１１９により取り付けることができる。
【００６５】
このような構成の偏心カム機構を設けることによって、偏心量ｅを容易に調整することができる。その結果、砥石の先端位置が描く軌跡の曲率半径を容易に変更することができ、曲率が異なる複数の被加工物の超仕上げに対応することが可能になる。
【００６６】
また、本実施の形態の超仕上げ装置は、球面ころだけでなく、内外輪の軌道溝の超仕上げに適用することも可能である。この場合、一方のスピンドルのみを揺動させ、他方のスピンドルを負荷マスとして追従させるように構成すればよい。
【００６７】
（第４実施の形態）
次に、本発明の第４実施の形態について図１２ないし図１４を参照しながら説明する。図１２は本発明に係る超仕上げ装置を用いた超仕上げラインの構成を模式的に示す図、図１３は図１２の超仕上げラインにおいて被加工物の超仕上げを実施している状態を示す図、図１４は図１２のラインにおけるボックスの移動を模式的に示す図である。
【００６８】
本実施の形態では、研削ラインから受けた被加工物を、上述の各実施の形態で示した超仕上げ装置のいずれかを用いて超仕上げを行うラインを説明する。
【００６９】
現状の研削盤では、３．６秒のサイクルタイムが実現可能であるが、この研削盤のサイクルタイムに１対１で対応するためには、超仕上げラインにおいて、２つの砥石ホルダを設けた場合（２軸の場合）、サイクルタイムを３．６秒で実現する必要がある。この３．６秒のサイクルタイムの実現には、比較的交差角に影響されずに目詰まりが少ない砥石（例えばＣＢＮ砥石）を使用し、被加工物の回転数を増大させることが条件となる。また、被加工物のローディング、アンローディングに要する時間を短くすることが重要である。そこで、超仕上げラインにおいては、被加工物の支持に２ロール方式（図７を参照）を用い、また被加工物の搬送にボックスを用いる。
【００７０】
具体的には、図１２に示すように、本ラインは、研削ラインからの被加工物１５１を受け取る入口部１５０と、超仕上げを行う加工部１６０と、超仕上げ後の被加工物１５１を排出する出口部１７０とを含み、入口部１５０から出口部１７０への被加工物１５１の搬送には、ボックス１５２が用いられる。ボックス１５２には、被加工物１５１をそれぞれ保持する２つの保持部１５２ａが設けられている。
【００７１】
ボックス１５２は、移動台１５３に搭載されている。この移動台１５３には、送りねじ機構およびリニアガイドが組み込まれている。送りねじ機構はねじ軸１５３ａおよび移動台１５３に固定されているナット部（図示せず）を有し、このねじ軸１５３ａは上記ナット部に螺合され、駆動モータ１５６により駆動される。移動台１５３のリニアガイド１５４は水平ガイドレール１５５に摺動可能に係合されている。駆動モータ１５６によりねじ軸１５３ａが駆動されると、移動台１５３は、水平ガイドレール１５５に沿って移動される。
【００７２】
移動台１５３は、図１３に示すように、複数の支持部材１５８に支持され、各支持部材１５８は、ベース１７４に固定されている支柱１７３に設けられた垂直ガイドレール１７２に沿って鉛直方向に移動可能に構成されている。各支持部材１５８には、送りねじ機構１５９および垂直ガイドレース１７２に摺動可能に係合する複数のリニアガイド１７１が設けられている。各支持部材１５８の送りねじ機構１５９は駆動モータ１５７により駆動され、これにより各支持部材１５８は鉛直方向に移動される。各支持部材１５８の鉛直方向への移動により移動台１５３を鉛直方向へ移動させることが可能である。
【００７３】
入口部１５０においては、研削ラインから２つの被加工物１５１を受け取り、各被加工物１５１をボックス１５２に積載する。被加工物１５１を積載したボックス１５２は、移動台１５３の移動により加工部１６０に送られる（図１４のＡ１）。
【００７４】
加工部１６０においては、図１２および１３に示すように、ボックス１５２に積載された２つの被加工物１５１を互いに対向する一対のローラ１６３間に保持する。この際、各被加工物１５１は、２つの砥石ホルダ１６１にそれぞれ保持されている砥石１６２に対してそれぞれ位置決めされ、回転される。各砥石１６２は、上述の各実施の形態において説明したように、対応する被加工物１５１の加工対象部位に押し付けられながらこの部位の曲率半径で揺動する。これにより、各被加工物１５１の加工対象部位が超仕上げされる。
【００７５】
そして、超仕上げ後の被加工物１５１を積載したボックス１５２は、移動台１５３の移動により出口部１７０に送られる。出口部１７０においては、移動台１５３を鉛直方向下方へ向けて移動し（図１４のＡ２）、ボックス１５２に積載されている被加工物１５１を外部に排出する。この後、ボックス１５２は、移動台１５３の移動により入口部１５０に戻され（図１４のＡ３）、移動台１５３は鉛直方向上方へ向けて移動される（図１４のＡ４）。
【００７６】
【発明の効果】
以上説明したように、本発明によれば、偏心カムが規制部材に当接され、回転軸が付勢部材により付勢された状態で回転軸を角度的に回転駆動することにより、回転軸を所定方向へ移動させながら砥石を回転軸の周りに揺動させるので、回転軸の軸線から砥石の先端位置までの直線距離および偏心カム部材の偏心量を適宜設定することによって、被加工物の超仕上げ部位に対応する曲率半径の軌道に沿って砥石の先端を揺動させることが可能になる。また、この揺動機構を簡素化された構造で実現することが可能となる。さらに、揺動機構全体の質量が小さくすることができるので、揺動速度を増すことが可能になり、加工効率の向上を図ることができる。即ち、構造を簡素化することができ、曲率が小さい超仕上げ対象部位の超仕上げの場合と同様に、高い加工効率で、精度および粗さが良い仕上げを得ることができる。
【図面の簡単な説明】
【図１】本発明に係る超仕上げ方法を実現するための装置の基本構成を示す図である。
【図２】図１の砥石先端位置Ｐが回転軸の回転に応じて描く軌跡を示す図である。
【図３】図１の回転軸の中心から砥石先端位置Ｐまでの直線距離ｒ0を変数とした場合の偏心カムの偏心量ｅと曲率半径（超仕上げ加工半径）Ｒ0との関係を示す図である。
【図４】図１の偏心カムの偏心量ｅを変数とした場合の回転軸の中心から砥石先端位置Ｐまでの直線距離ｒ0と曲率半径（超仕上げ加工半径）Ｒ0との関係を示す図である。
【図５】（ａ）は本発明の第１実施の形態に係る超仕上げ装置の構成を示す上面図、（ｂ）は（ａ）のＡ−Ａ線に沿って得られた縦断面図である。
【図６】（ａ）は図５の偏心カムの正面図、（ｂ）は図５の偏心カムの側面図、（ｃ）は図５の偏心カムの斜視図である。
【図７】（ａ）は図５の砥石ホルダの構成を示す縦断面図、（ｂ）は（ａ）のＢから見た矢視図である。
【図８】（ａ）は砥石ホルダの先端部の他の構成例の正面図、（ｂ）は（ａ）のＣ−Ｃ線に沿って得られた断面図である。
【図９】（ａ）は本発明の第２実施の形態に係る超仕上げ装置の主要部構成を示す上面図、（ｂ）は（ａ）のＤ−Ｄ線に沿って得られた縦断面図である。
【図１０】（ａ）は本発明の第３実施の形態に係る超仕上げ装置の構成を示す上面図、（ｂ）は（ａ）の超仕上げ装置の正面図である。
【図１１】偏心カム機構の構成例を示す断面図である。
【図１２】本発明に係る超仕上げ装置を用いた超仕上げラインの構成を模式的に示す図である。
【図１３】図１２の超仕上げラインにおいて被加工物の超仕上げを実施している状態を示す図である。
【図１４】図１２のラインにおけるボックスの移動を模式的に示す図である。
【図１５】従来の超仕上げ装置の主要部構成を示す正面図および側面図である。
【図１６】従来の被加工物における曲率が小さい部位に超仕上げを施す装置の主要部構成を示す正面側断面図、側面側断面図および砥石の先端周囲を示す断面図である。
【符号の説明】
１，１１，７１ ベース
２ａ 回転軸
３，２０，２１ 砥石ホルダ
４，４９ 砥石
５，１８，１９ 偏心カム
６ａ，６ｂ，２３，２４，６１ 規制部材
１６，１７ スピンドル
３５，３７，１０３，１０５ ばね部材[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a superfinishing method and apparatus for a curved surface forming part of a workpiece.
[0002]
[Prior art]
Conventionally, as a method of super-finishing the outer surface of a work piece having a drum shape like a roller of a self-aligning roller bearing, a grindstone for cutting the outer surface of the work piece is processed. Some of them perform superfinishing of the outer surface of the workpiece by swinging around the center position corresponding to the center of curvature of the outer surface of the object.
[0003]
An apparatus configuration for realizing this method will be specifically described with reference to FIG. FIG. 15 is a front view and a side view showing a configuration of main parts of a conventional superfinishing apparatus.
[0004]
As shown in FIGS. 15A and 15B, the conventional superfinishing apparatus includes a base 201 supported by a column 202 that rises in the vertical direction so as to be movable up and down. The base 201 is provided with two rotating shafts 205 that are spaced apart from each other, and one end of the corresponding vertical link arm 203 is rotatably supported on each rotating shaft 205. Each vertical link arm 203 is connected by two horizontal link arms 204. Each end of each horizontal link arm 204 is rotatably connected to a corresponding vertical link arm 203. Two grindstone holders 206 are connected to each horizontal link arm 204. The grindstone holders 206 are arranged at intervals from each other, and a pressure cylinder 207 is attached to each grindstone holder 206. Each pressure cylinder 207 holds the grindstone 208 so that the grindstone 208 can be pressed against the workpiece 212 (for example, a roller of a self-aligning roller bearing).
[0005]
One end of the transmission member 209 is connected to one of the vertical link arms 203, and the other end of the transmission member 209 is connected to a drive arm 210 fixed to the output shaft of the drive motor 211. The rotation output of the drive motor 211 is transmitted to the transmission member 209 via the drive arm 210 to drive the transmission member 209. Due to the movement of the transmission member 209, one vertical link arm 203 swings about the rotation shaft 205 supported at one end thereof. Each horizontal link arm 204 moves in conjunction with the swing of the one vertical link arm 203 to swing the other vertical link link arm 203 around the corresponding rotation shaft 205. Then, each grindstone holder 206 swings around a position that coincides with the center of the curvature R of the outer surface of the workpiece 212. As a result, the grindstone 208 held by the pressure cylinder 207 of the grindstone holder 206 swings along an arc having a curvature equal to the curvature R of the outer surface of the workpiece 212. At this time, the grindstone 208 is pressed against the workpiece 212 by the pressure cylinder 207 with a predetermined pressure.
[0006]
On the other hand, when superfinishing is performed on a portion having a small curvature in the workpiece, such as a raceway groove of an inner ring of a ball bearing, the apparatus shown in FIG. 16 is used. FIG. 16 is a front cross-sectional view, a side cross-sectional view, and a cross-sectional view showing the periphery of the tip of a grindstone showing the main part configuration of an apparatus for superfinishing a portion having a small curvature in a conventional workpiece.
[0007]
As shown in FIGS. 16A and 16B, this apparatus includes a grindstone holder 221 for holding a grindstone 222. In the grindstone holder 221, a pressurizing piston 224 of a pressurizing mechanism for pressing the grindstone 222 against a finish target portion having a small curvature R of the workpiece 220 (for example, a raceway groove of an inner ring of a ball bearing) is incorporated. A V-shaped groove is formed in the head portion of the pressure piston 224 as shown in FIG. An O-ring 223 is incorporated at the tip of the grindstone holder 221. The grindstone holder 221 is swung around the swing center Os.
[0008]
When performing superfinishing, the grindstone holder 221 is positioned so that the swing center Os coincides with the center of curvature R of the part to be finished of the workpiece 222. Then, the grindstone 221 is swung with the rocking radius R about the rocking center Os in a state where the grindstone 220 is pressed against the finishing target portion of the workpiece 220. Thereby, the finishing target part of the workpiece 220 is superfinished.
[0009]
[Problems to be solved by the invention]
In the case of an apparatus (shown in FIG. 16) for superfinishing a portion having a small curvature in the workpiece, such as a raceway groove of an inner ring of a ball bearing, the structure is simple and the swing radius R (the curvature of the workpiece) is small. Therefore, it is possible to reduce the size, and since the swing speed is usually as high as about 1000 times per minute, the super-finishing processing efficiency can be increased. Further, by adopting a biaxial structure (balance weight structure) and moving them in opposite directions, it is possible to balance vibrationally. For this reason, the finishing with good processing accuracy and roughness can be obtained. Further, the vibration as the apparatus is small, and the influence of the vibration on the processing apparatus (for example, grinding machine) in the vicinity can be reduced.
[0010]
However, when superfinishing is performed on a portion having a large curvature R such as the outer surface of a spherical roller, the size adjustment range becomes large with respect to the large curvature R, and the apparatus itself becomes large. Further, the mass of the grindstone holder increases, and vibration due to centrifugal force increases due to a synergistic effect with the large curvature R.
[0011]
In addition, in the case of a device (shown in FIG. 15) that superfinishes a finishing target part having a large curvature R, the structure is complicated, the mass of the entire swing mechanism is large, and furthermore, it is impossible to balance vibrationally. The rocking speed needs to be suppressed to about 200 times per minute, and the processing efficiency is lowered. In addition, a finish with good accuracy and roughness cannot be obtained.
[0012]
The object of the present invention is to achieve a super-finishing that can simplify the structure and obtain a finish with high machining efficiency and good precision and roughness, as in the case of super-finishing of a part to be super-finished with a small curvature. It is to provide an apparatus and method.
[0013]
[Means for Solving the Problems]
The present invention relates to a superfinishing method of a curved surface forming portion of a workpiece, and a rotation axis supported on a base so as to be movable in a first direction orthogonal to the axis is orthogonal to the axis of the rotation axis A whetstone is attached at a predetermined distance in the second direction, an eccentric cam member that is eccentric with respect to the rotation shaft is coaxially attached, and the regulating member that contacts the eccentric cam member and the eccentric cam member are the first An urging member for urging the regulating member toward the regulating member is provided on the base, and the eccentric cam is in contact with the regulating member and the rotating shaft is urged by the urging member. By rotating the rotary shaft angularly, the grindstone is swung around the rotary shaft while moving the rotary shaft in the first direction.
[0014]
Further, the present invention provides a superfinishing apparatus for a curved surface forming part of a workpiece, and a rotating shaft supported so as to be movable on the base in a first direction orthogonal to the axis. A grindstone that is attached to the rotary shaft at a predetermined distance in a second direction orthogonal to the axis of the rotary shaft, and an eccentric cam member that is coaxially attached to the rotary shaft and eccentric with respect to the rotary shaft A regulating member provided on the base and in contact with the eccentric cam member; and provided on the base and biasing the eccentric cam member toward the regulating member in the first direction. An urging member and a drive mechanism that rotationally drives the rotation shaft angularly are provided.
[0015]
In the present invention, the eccentric cam is brought into contact with the restricting member, and the rotating shaft is angularly rotated while the rotating shaft is urged by the urging member, so that the grindstone is moved while moving the rotating shaft in a predetermined direction. Since it swings around the rotation axis, by setting the linear distance from the axis of the rotation axis to the tip position of the grindstone and the amount of eccentricity of the eccentric cam member, the radius of curvature corresponding to the superfinished part of the workpiece is set. The tip of the grindstone can be swung along the track. In addition, this swing mechanism can be realized with a simplified structure. Furthermore, since the mass of the entire swing mechanism can be reduced, the swing speed can be increased, and the machining efficiency can be improved.
[0016]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[0017]
First, the basic configuration of an apparatus for realizing the superfinishing method according to the present invention will be described with reference to FIGS. FIG. 1 is a side view and a front view showing a basic configuration of an apparatus for realizing a superfinishing method according to the present invention, and FIG. 2 is a diagram showing a locus drawn by a grindstone tip position P in FIG. 1 according to the rotation of a rotating shaft. FIG. 3 is a diagram showing the relationship between the eccentric amount e of the eccentric cam and the radius of curvature (superfinishing radius) R0 when the linear distance r0 from the center of the rotating shaft of FIG. 1 to the grinding wheel tip position P is a variable. FIG. 4 is a diagram showing the relationship between the linear distance r0 from the center of the rotating shaft to the grinding wheel tip position P and the radius of curvature (superfinishing radius) R0 when the eccentric amount e of the eccentric cam in FIG. 1 is a variable. .
[0018]
As shown in FIG. 1, the basic configuration of the superfinishing apparatus includes a base 1 provided with a guide rail portion 1a. A spindle device 2 is mounted on the base 1, and the spindle device 2 is configured to be movable in the x-axis direction while being guided by a guide rail portion 1a (see FIG. 1B). The spindle device 2 has a rotating shaft 2a extending in a direction orthogonal to the guide direction of the guide rail 1a, and a grindstone holder 3 is attached to one end of the rotating shaft 2a. The grindstone holder 3 is composed of a hook-shaped member, and a grindstone 4 is attached to the tip 3a thereof. An eccentric cam 5 and a pulley 7 are attached to the other end of the rotating shaft 2a. The eccentric cam 5 is made of a disc that is eccentrically attached to the rotary shaft 2a. A timing belt 8 is wound around the pulley 7 for transmitting a driving force of a driving motor (not shown). On both sides of the eccentric cam 5, restricting members 6a and 6b are arranged, respectively. One regulating member 6 a is fixed to the base 1 and positioned so as to contact the side surface of the eccentric cam 5. The other regulating member 6b is attached to the base 1 so as to be movable in the x-axis direction, and is biased so as to be pressed against the side surface of the eccentric cam 5 by a spring member (not shown).
[0019]
Here, consider a case where the rotary shaft 2a is rotated angularly in the direction of the arrow shown in FIG. First, when the rotary shaft 2a is angularly rotated in one direction (clockwise in FIG. 1B) by the drive motor, the eccentric cam 5 is rotated with the rotation of the rotary shaft 2a. At this time, since the eccentric cam 5 rotates while abutting against the fixed-side regulating member 6a, the regulating member 6b is moved in the x-axis direction against the urging force of the spring member by the rotation of the eccentric cam 5. become. Thereby, the rotating shaft 2a is moved in the x-axis direction according to the rotation angle θ while rotating. When the rotary motor 2a is angularly rotated in the other direction (counterclockwise in FIG. 1B) by the drive motor, similarly, the rotary shaft 2a is rotated according to the rotation angle θ. It is moved in the x-axis direction.
[0020]
When the rotating shaft 2a rotates while moving in the x-axis direction, the grindstone holder 3 attached to the rotating shaft 2a rotates around the rotating shaft 2a while moving in the x-axis direction. At this time, the locus P (x, y) drawn by the tip position P of the grindstone 4 of the grindstone holder 3 is represented by the following equation (1) as seen from the origin O of the xy coordinate system, as shown in FIG. The ellipse is represented.
[0021]
{X / (r0 + e)} ² + (Y / r0) ² = 1 (1)
r0: Linear distance from the center Os of the rotating shaft 2a to the tip position P of the grindstone 4
e: Eccentricity of the eccentric cam 5 with respect to the rotating shaft 2a
Oc: Center of the eccentric cam 5 (moves according to the rotation angle θ of the rotating shaft 2a)
Next, consider the relationship between the eccentric amount e of the eccentric cam 5, the distance r0, and the curvature radius R0. The curvature radius R0 is a curvature radius when x = 0 in the xy coordinate system, and the tip position P of the grindstone 4 should be drawn with respect to the superfinishing target portion of the workpiece held at a predetermined position. It represents the radius of curvature of the trajectory. This curvature radius R0 is expressed by the following equation (2).
[0022]
R0 = (r0 + e) ² / R0 = (1 + e / r0) ² ・ R0 (2)
First, when the eccentricity e of the eccentric cam 5 is a fixed value and the distance r0 is a variable, the relationship between these and the radius of curvature R0 is considered. Here, if the relationship between the distance r0 and the amount of eccentricity e is expressed by r0 = γ · e, the ratio R0 / e of the radius of curvature R0 and the amount of eccentricity e is calculated from the above equation (2) as the following (3) It is expressed by a formula.
[0023]

FIG. 3 shows the relationship between R0 / e and γ when γ <1. As can be seen from FIG. 3, R0 / e is 5.6 to 22.0 when γ = 0.3 to 0.05, although it is non-linear, and a value in the range of about four times is obtained. For example, when e = 15 mm, when γ = 0.3, r0 = 15 × 0.3 = 4.5 mm and R0 = 5.6 × 15 = 84 mm. When γ = 0.05, r0 = 15 × 0.05 = 0.75 mm and R0 = 22.0 × 15 = 330 mm.
[0024]
Further, the movement amount xs by which the tip position P of the grindstone 4 moves in the x-axis direction according to the rotation angle θ of the rotation shaft 2a is expressed by the following equation (4).
[0025]
xs = (e + r0) sinθ (4)
From the above equation (4), the movement amount xs in each case is 19.5 sin θ to 15.75 sin θ. For example, when the movement amount x s is 3 mm, the rotation angle θ is 0.032π (rad) to 0.041π ( rad).
[0026]
Consider the relationship between the radius of curvature R0 and r0 when the distance r0 is a fixed value and the amount of eccentricity e of the eccentric cam 5 is a variable. According to the above equation (2), there is a relationship as shown in FIG. 4 between the ratio R0 / r0 of the curvature radius R0 and the distance r0 and the ratio e / r0 of the eccentricity e and the distance r0. can get. As can be seen from FIG. 4, in a linear range of e / r0 = 0.4 to 1.5, R0 / r0 = 2.0 to 6.2, and a value in the range of about three times is obtained. For example, if r0 = 35 mm, when e / r0 = 0.4, e = 35 × 0.4 = 14 mm and R0 = 35 × 2.0 = 70 mm. When e / r0 = 1.5, e = 35 × 1.5 = 53.5 mm and R0 = 35 × 6.2 = 218 mm.
[0027]
Further, the movement amount xs in each case is 49 sin θ to 88.5 sin θ according to the above equation (4). For example, when the movement amount xs = 2 mm, the rotation angle θ = 0.018π (rad) to 0.007π ( rad).
[0028]
In this way, by appropriately setting the linear distance r0 from the center Os of the rotating shaft 2a to the tip position P of the grindstone 4 and the eccentric amount e of the eccentric cam 5, the workpiece can be processed in a range of a small rotation angle θ. It is possible to swing the tip of the grindstone 4 along a track having a radius of curvature corresponding to the finished portion. In addition, this swing mechanism can be realized with a simplified structure. Furthermore, since the mass of the entire swing mechanism can be reduced, the swing speed can be increased, and the machining efficiency can be improved. Therefore, according to this method, the structure can be simplified, and a finish with good accuracy and roughness can be obtained with high machining efficiency, as in the case of superfinishing of a superfinishing target portion having a small curvature. A superfinishing device can be provided.
[0029]
(First embodiment)
Next, the superfinishing apparatus according to the first embodiment of the present invention will be described with reference to FIGS. FIG. 5A is a top view showing the configuration of the superfinishing apparatus according to the first embodiment of the present invention, and FIG. 5B is a longitudinal section taken along the line AA in FIG. 6 (a) is a front view of the eccentric cam of FIG. 5, FIG. 6 (b) is a side view of the eccentric cam of FIG. 5, FIG. 6 (c) is a perspective view of the eccentric cam of FIG. 5A is a longitudinal sectional view showing the configuration of the grindstone holder of FIG. 5, FIG. 7B is an arrow view seen from B of FIG. 7A, and FIG. 8A is another view of the tip of the grindstone holder. FIG. 8B is a cross-sectional view taken along the line CC of FIG. 8A.
[0030]
The superfinishing apparatus according to the present embodiment is based on the basic configuration described above, but in this embodiment, a two-axis structure capable of canceling vibrations is used, and each axis is driven by one drive motor. The configuration.
[0031]
Specifically, the superfinishing apparatus of the present embodiment includes a base 11 placed on a support surface such as a floor, as shown in FIG. Two sliders 12 and 13 are mounted on the base 11 so as to face each other.
[0032]
The slider 12 has a plurality of linear guides 12a that slide along a pair of guide rails 14a and 14b provided on the upper surface of the base 11, and is guided to the pair of guide rails 14a and 14b by the plurality of linear guides 12a. However, it is configured to be movable on the base 11. A spindle 16 extending in a direction orthogonal to the guide rails 14a and 14b is rotatably supported on the slider 12. A link member 32 is attached to one end 16a of the spindle 16, and a grindstone holder 20 is attached to the other end 16b. The detailed configuration of the grindstone holder 20 will be described later.
[0033]
An eccentric cam 18 is attached to the spindle 16. As shown in FIG. 6, the eccentric cam 18 includes a ring portion 18 a and a cam portion 18 b that is eccentric to the ring portion 18 a and is integrally connected. The cam portion 18 b is a hole portion of the ring portion 18 a. It consists of a disk with a portion corresponding to the notched. The eccentric cam 18 is fitted to the spindle 16 so that the ring portion 18 a is coaxial with the spindle 16. As a result, the cam portion 18 b of the eccentric cam 18 is attached to the spindle 16 with its center decentered from the center of the spindle 16 by the amount of eccentricity e.
[0034]
As shown in FIG. 7, the grindstone holder 20 has a base portion 40 attached to the other end 16 b of the spindle 16, and the base portion 40 has a pair of guide rails 41 for guiding the holder portion 47. Is provided. The holder portion 47 has a hook-like shape, and a ball screw mechanism 42 and a pair of linear guides 46 that are slidably engaged with the respective guide rails 41 are provided at a portion facing the base portion 40. It has been. The ball screw mechanism 42 includes a screw shaft 44 and a nut portion 45 fixed to the holder portion 47, and the screw shaft 44 is rotationally driven by a drive motor 43 fixed to the base portion 40. The nut portion 45 moves along the screw shaft 44 as the screw shaft 44 rotates, so that the holder portion 47 is moved relative to the base portion 40. A holding member 48 is attached to the tip portion 47a of the holder portion 47, and a grindstone 49 is held between the holding member 48 and the tip portion 47a. The grindstone 49 is positioned so that the distance between its tip position and the center of the spindle 16 is r0. The workpiece 50 (eg, corresponding to a spherical roller) is swung with a curvature R0 that coincides with a curvature radius R of the workpiece 50 (e.g., corresponding to a spherical roller). Here, when superfinishing with the grindstone 49, the workpiece 50 is sandwiched between a pair of rollers 51 and positioned with respect to the tip of the grindstone 49, and the workpiece 50 is rotated by the rotation of the roller 51. Is done.
[0035]
By using the grindstone holder having such a configuration, the grindstone 49 can be pressed against the workpiece 50 with a predetermined pressure by the relative movement of the holder portion 47. Further, when the position of the tip of the grindstone 49 changes in the vertical direction with respect to the workpiece 50 due to wear of the grindstone 49 or the like, the position of the tip of the grindstone 49 and the position of the workpiece 50 in the vertical direction can be adjusted.
[0036]
Similar to the slider 12, the slider 13 has a plurality of linear guides 13a that slide along a pair of guide rails 15a and 15b provided on the upper surface of the base 11, and the pair of guide rails is formed by the plurality of linear guides 13a. It is configured to be movable on the base 11 while being guided by 15a and 15b. A spindle 17 extending in a direction orthogonal to the guide rails 15a and 15b is rotatably supported on the slider 13. A link member 33 is attached to one end 17a of the spindle 17, and a grindstone holder 21 is attached to the other end 17b. The grindstone holder 21 has the same configuration as the grindstone holder 20 (see FIG. 7), and description thereof is omitted here.
[0037]
An eccentric cam 19 is attached to the spindle 17. The eccentric cam 19 is configured in the same manner as the eccentric cam 18, and includes a ring portion 19a and a cam portion 19b (see FIG. 6). As a result, the cam portion 19 b of the eccentric cam 19 is attached to the spindle 17 with its center decentered from the center of the spindle 17 by the amount of eccentricity e.
[0038]
Between the slider 12 and the slider 13, two restricting members 23 and 24 made of rolling bearings are provided, and the restricting members 23 and 24 are supported coaxially by the shaft 22. Each end of the shaft 22 is supported by support members 22a and 22b provided on the base 11, respectively. The regulating member 24 has a circumferential surface of the eccentric cam 19 attached to the spindle 17 so that its outer circumferential surface comes into contact with the outer circumferential surface of the cam portion 18b of the eccentric cam 18 attached to the spindle 16. It arrange | positions so that it may contact | abut to the outer peripheral surface of the cam part 19b.
[0039]
The slider 12 is biased by the spring member 35 in a direction in which the cam portion 18 b of the eccentric cam 18 is pressed against the regulating member 23. The spring member 35 is held by a holding member 34 that is fixed to the base 11. Similarly, the slider 13 is biased by the spring member 37 in a direction in which the cam portion 19 b of the eccentric cam 19 is pressed against the restriction member 24. The spring member 37 is held by a holding member 36 that is fixed to the base 11.
[0040]
The link member 32 of the spindle 16 is connected to the arm portion 28b of the intermediate link 28 via the link member 30 as shown in FIG. Further, the link member 33 of the spindle 17 is connected to the arm portion 28 c of the intermediate link 28 via the link member 31. The intermediate link 28 is provided with an arm portion 28a together with the arm portion 28b and the arm portion 28c. The arm portion 28b and the arm portion 28c protrude in opposite directions along the same straight line, and the arm portion 28a protrudes perpendicularly to the arm portion 28b. The intermediate link 28 is supported by the axle box 29. The arm portion 28a of the intermediate link 28 is connected to one end of the link member 27, and the other end of the link member 27 is connected to a conversion member 26 for converting the rotational motion of the drive motor 25 into a swing motion. The conversion member 26 is fixed to an output shaft (not shown) of the drive motor 25, and the connection point of the conversion member 26 with the link member 27 is at a position eccentric from the output shaft of the drive motor 25 by the amount of eccentricity E1. . The eccentricity E1 defines the maximum value of the rotation angle θ of each spindle 16 and 17.
[0041]
By such a link mechanism, the rotational motion of the drive motor 25 is converted into the swing motion of the spindles 16 and 17, and the spindles 16 and 17 are angularly rotated in opposite directions. For example, when the spindle 16 is angularly rotated in one direction (clockwise in FIG. 5B), the eccentric cam 18 is rotated as the spindle 16 rotates. At this time, since the eccentric cam 18 rotates with its cam portion 18b in contact with the regulating member 23, the slider 12 moves against the urging force of the spring member 35 by the rotation of the eccentric cam 18. 14b. Thus, the spindle 16 is moved in the guide direction of the guide rails 14a and 14b according to the rotation angle θ while rotating.
[0042]
When the spindle 16 is rotationally driven in one direction, the spindle 17 is rotationally driven angularly in the other direction (counterclockwise). Also in this case, as in the case of the spindle 16, the slider 13 is moved along the guide rails 15 a and 15 b while resisting the biasing force of the spring member 37 by the rotation of the eccentric cam 19. Thereby, the spindle 17 is moved in the guide direction of the guide rails 15a and 15b according to the rotation angle θ while rotating.
[0043]
Further, when the spindle 16 is rotationally driven in the other direction (counterclockwise), the spindle 17 is rotationally driven angularly in one direction (clockwise). Similarly, in this case, the spindles 16 and 17 are moved in the guide directions of the guide rails 14a, 14b, 15a, and 15b according to the rotation angle θ while rotating.
[0044]
When the spindles 16 and 17 are rotationally driven, the grindstone holders 20 and 21 attached to the spindles 16 and 17 move around the spindles 16 and 17 while moving in the guide directions of the guide rails 14a, 14b, 15a, and 15b. It will be rotated angularly. At this time, the tip position of the grindstone 49 of the grindstone holder 20, 21 is determined according to the linear distance r 0 from the center of the spindle 16, 17 to the tip position of the grindstone 20, 21 and the eccentric amount e of the eccentric cams 16, 17. Move along the trajectory of the radius of curvature. That is, the grindstone holders 20 and 21 can be swung so as to move along the radius of curvature of the superfinishing target portion of the workpiece 50 in which the tip position of the grindstone 49 is held at a predetermined position.
[0045]
Therefore, in the present embodiment, by simultaneously driving the two spindles 16 and 17 in the opposite directions, it is possible to balance vibrationally, and it is possible to increase the rocking speed.
[0046]
In the present embodiment, the grindstone 49 is configured to be held between the tip portion 47a of the holder portion 47 and the holding member 48. However, this configuration does not cause an error in the inclination component of the grindstone 49. In addition, it is premised that there is no possibility that the posture (axial position and inclination) of the workpiece 50 is changed, but in super-finishing, the workpiece obtained in the previous step (grinding step) Since it is desired to improve the roughness without destroying the shape of the superfinishing target portion 50, a mechanism that allows the grindstone 49 to follow the change in the posture of the workpiece 50 instead of the above configuration. Is preferably used.
[0047]
Specifically, as shown in FIG. 8, an intermediate member 52 is attached to a tip portion 47a of the holder portion 47 of the grindstone holder via a pivot 53, and between the intermediate member 52 and the tip portion 47a. The O-ring 55 is fitted. A holding member 54 is attached to the intermediate member 52 by a plurality of screw members 56, and a grindstone 49 is sandwiched between the intermediate member 52 and the holding member 54. With this configuration, the grindstone 49 can follow the change in the posture of the workpiece 50, and the roughness of the workpiece 50 obtained in the previous process (grinding process) can be obtained without breaking the shape of the superfinished target portion. It is definitely done to improve.
[0048]
(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. FIG. 9A is a top view showing the configuration of the main part of the superfinishing apparatus according to the second embodiment of the present invention, and FIG. 9B is obtained along the line DD in FIG. 9A. It is a longitudinal cross-sectional view.
[0049]
In contrast to the first embodiment described above using a rolling bearing as the restricting member, the present embodiment uses a linear guide as the restricting member. Other configurations are the same as those of the first embodiment described above, and the same members are denoted by the same reference numerals, and description thereof is omitted or simplified.
[0050]
Specifically, as shown in FIG. 9, a regulating member 61 is provided between the slider 12 and the slider 13 so as to come into contact with the cam portions 18 b and 19 b of the eccentric cams 18 and 19. The restricting member 61 is composed of a linear guide that can slide in the vertical direction while engaging with a guide rail 62 provided on the column 63. When the eccentric cams 18 and 19 are rotated as the spindles 16 and 17 are added, the restricting member 61 receives a force upward or downward in the vertical direction from the eccentric cams 18 and 19. Moved in the direction of.
[0051]
Thus, the structure can be further simplified by using the linear guide as the restricting member 61. Further, since the contact surfaces of the eccentric cams 18 and 19 of the regulating member 61 with the cam portions 18b and 19b are flat, no error occurs as in a rolling bearing. Furthermore, since the force that the restricting member 61 receives from each of the eccentric cams 18 and 19 is on the same line of action, it is advantageous to use a linear guide for the restricting member 61 from the viewpoint of load capacity and rigidity.
[0052]
(Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIGS. 10A is a top view showing the configuration of the superfinishing apparatus according to the third embodiment of the present invention, FIG. 10B is a front view of the superfinishing apparatus of FIG. 10A, and FIG. 11 is an eccentric cam. It is sectional drawing which shows the structural example of a mechanism.
[0053]
As shown in FIG. 10, the superfinishing apparatus of the present embodiment includes a base 71, and two sliders 72 and 73 are mounted on the base 71 so as to face each other.
[0054]
The slider 72 has a plurality of linear guides 72a that slide along a pair of guide rails 74a and 74b provided on the upper surface of the base 71, and is guided to the pair of guide rails 74a and 74b by the plurality of linear guides 72a. It is configured to be movable on the base 71. A spindle 76 extending in a direction orthogonal to the guide rails 74a and 74b is rotatably supported by the slider 72. A link member 90 is attached to one end 76a of the spindle 76, and a grindstone holder 80 is attached to the other end 76b. The configuration of the grindstone holder 80 is the same as the configuration shown in FIG. 7, and the description thereof is omitted here.
[0055]
Like the slider 72, the slider 73 has a plurality of linear guides 73a that slide along a pair of guide rails 75a and 75b provided on the upper surface of the base 71, and the pair of guide rails 75a by the plurality of linear guides 73a. , 75b while being guided on the base 71. A spindle 77 extending in a direction orthogonal to the guide rails 75a and 75b is rotatably supported by the slider 73. A link member 91 is attached to one end 77a of the spindle 77, and a grindstone holder 81 is attached to the other end 77b. The grindstone holder 81 has the same configuration as the grindstone holder 80 (see FIG. 7).
[0056]
An eccentric cam mechanism is provided between the slider 72 and the slider 73. This eccentric cam mechanism has a shaft box 88 fixed to the base 71 and a rotating shaft 87 supported by the shaft box 88. A link member 89 is provided at one end of the rotating shaft 87, and the other end. A support plate 86 is provided. A pair of pedestals 85 (only one is shown) is fastened to the support plate 86, and two shafts 82 a and 83 a that are arranged at a predetermined interval are attached to each pedestal 85. Here, each pedestal 85 is arranged such that each shaft 82a, 83a is at a position separated from the center of the rotation shaft 87 by a distance e (an eccentric amount). A disc 82 is rotatably supported on the shaft 82a, and a disc 83 having the same diameter as that of the disc 82 is rotatably supported on the shaft 83a. The disc 82 is positioned so that the edge thereof is in contact with the abutting portion 72 b provided on the slider 72, and the disc 83 is positioned so that the edge is in contact with the abutting portion 73 b provided on the slider 73.
[0057]
The slider 72 is urged by the spring member 103 in a direction in which the contact portion 72 b is pressed against the disc 82. The spring member 103 is held by a holding member 102 that is fixed to the base 71. Similarly, the slider 73 is urged by the spring member 105 in the direction in which the contact portion 73 b is pressed against the disc 83. The spring member 105 is held by a holding member 104 fixed to the base 71.
[0058]
The link member 90 of the spindle 76 is connected to the intermediate link member 96 via the link member 97, and the intermediate link member 96 is connected to the link member 89 of the rotating shaft 87 via the link member 94. Here, the intermediate link member 96 is formed of a disk that rotates around an axis, and the connection point with the link member 97 and the connection point with the link member 94 in the intermediate link member 96 are provided at predetermined positions. The link member 91 of the spindle 77 is connected to the intermediate link member 98 via the link member 99, and the intermediate link member 98 is connected to the link member 89 of the rotating shaft 87 via the link member 95. Here, the intermediate link member 98 is formed of a disk that rotates around its axis, and the connection point with the link member 99 and the connection point with the link member 95 in the intermediate link member 98 are provided at predetermined positions. .
[0059]
The link member 89 of the rotating shaft 87 is a disk coaxial with the rotating shaft 87, and one end of the link member 93 is connected to the link members 94 and 95. The other end of the link member 93 is connected to a conversion member (not shown) for converting the rotational motion of the drive motor 92 into a swing motion. This conversion member is fixed to an output shaft (not shown) of the drive motor 92, and the connection point of the conversion member with the link member 93 is at a position eccentric with respect to the output shaft of the drive motor 92 by an eccentric amount E2. The eccentricity E2 defines the maximum value of the rotation angle θ of each of the spindles 76 and 77 and the rotating shaft 87.
[0060]
By such a link mechanism, the rotational motion of the drive motor 92 is converted into the swing motion of the spindles 76 and 77 and the rotary shaft 87. The rotary shaft 87 is rotationally moved angularly, and in conjunction with this, the spindles 76 and 77 are rotationally moved angularly in opposite directions. For example, when the rotary shaft 87 is angularly rotated clockwise (in FIG. 10B), the spindle 76 is rotated counterclockwise and the spindle 77 is rotated clockwise. Further, as the rotation shaft 87 rotates, the support plate 86 is angularly rotated clockwise around the rotation shaft 87. When each of the disks 82 and 83 swings clockwise about the rotation shaft 87 along with the rotation of the support plate 86, the slider 72 causes the contact portion 72b to contact the disk 82 by the biasing force of the spring member 103. In the contact state, it is moved toward the disc 82 along the guide rails 74a and 74b. The slider 73 is moved toward the disc 83 along the guide rails 75 a and 75 b in a state where the abutting portion 73 b is in contact with the disc 83 by the biasing force of the spring member 105.
[0061]
The same applies to the case where the rotating shaft 87 is rotated angularly in the counterclockwise direction (in FIG. 10B).
[0062]
With this configuration, the grindstone holders 80 and 81 attached to the spindles 76 and 77 rotate around the spindles 76 and 77 while moving in the guide direction of the guide rails 74a, 74b, 75a, and 75b. At this time, the tip position of the grindstone of the grindstone holders 80 and 81 is a trajectory having a radius of curvature determined according to the linear distance r0 from the center of the spindles 76 and 77 to the tip position of the grindstone and the eccentric amount e of the eccentric cam mechanism. Move along. In other words, the grindstone holders 80 and 81 can be swung so as to move along the radius of curvature of the superfinishing target portion of the workpiece whose tip position is held at a predetermined position.
[0063]
Further, in the present embodiment, by simultaneously driving the two spindles 76 and 77 in the opposite directions, it is possible to balance vibrationally and to increase the swing speed.
[0064]
In the present embodiment, when the eccentric amount e of the eccentric cam mechanism can be adjusted, an eccentric cam mechanism as shown in FIG. 11 may be used. As shown in FIG. 11, the eccentric cam mechanism has a support plate 116 provided on the rotating shaft 87, and a dovetail groove 116 a is formed in the support plate 116. A pair of pedestals 115 is fastened to the support plate 116 by corresponding set screws 119 via grooves 116 a, and shafts 113 are attached to the respective pedestals 115. Each shaft 113 supports a rolling bearing 111 corresponding to the disks 82 and 83. Each pedestal 115 is arranged such that each shaft 113 is located at a position e (an eccentricity) separated from the center of the rotation shaft 87. Each pedestal 115 is formed with a position adjusting hole 115 a for receiving the set screw 119, and the interval between the pedestals 115, that is, the eccentricity e can be adjusted by the reference plug 117. The reference plug 117 is fitted into a hole formed in the support plate 116 so that its axis is coaxial with the rotation shaft 87. For example, by preparing a plurality of reference plugs 117 having different widths and attaching the reference plugs 117 having a width corresponding to the eccentricity e to the support plate 116, the distance between the bases 115, that is, the distance between the shaft 113 and the rotation shaft 87. (Eccentricity) e can be adjusted. When the relative position of each pedestal 115 with respect to the support plate 116 changes due to the adjustment of the interval, the position of the set screw 119 on each pedestal 115 changes with the change in position, but a position adjusting hole 115a is provided. Therefore, after the adjustment of the relative position of each pedestal 115, each pedestal 115 can be attached to the support plate 116 with the set screw 119 in the same manner as before the adjustment.
[0065]
By providing the eccentric cam mechanism having such a configuration, the eccentricity e can be easily adjusted. As a result, the radius of curvature of the locus drawn by the tip position of the grindstone can be easily changed, and it is possible to cope with super finishing of a plurality of workpieces having different curvatures.
[0066]
Further, the superfinishing apparatus of the present embodiment can be applied not only to spherical rollers but also to superfinishing of inner and outer raceway grooves. In this case, only one spindle may be oscillated and the other spindle followed as a load mass.
[0067]
(Fourth embodiment)
Next, a fourth embodiment of the present invention will be described with reference to FIGS. FIG. 12 is a diagram schematically showing the configuration of a superfinishing line using the superfinishing apparatus according to the present invention, and FIG. 13 is a diagram showing a state in which superfinishing of a workpiece is performed in the superfinishing line of FIG. FIG. 14 is a diagram schematically showing the movement of the box in the line of FIG.
[0068]
In the present embodiment, a line for superfinishing a workpiece received from a grinding line using any of the superfinishing apparatuses described in the above embodiments will be described.
[0069]
In the current grinder, a cycle time of 3.6 seconds can be realized. However, in order to cope with the grinder cycle time on a one-to-one basis, two grindstone holders are provided in the superfinishing line. (In the case of 2 axes), it is necessary to realize the cycle time in 3.6 seconds. In order to realize the 3.6 second cycle time, it is necessary to use a grindstone (for example, CBN grindstone) that is relatively unaffected by the crossing angle and has little clogging, and to increase the rotational speed of the workpiece. . It is also important to shorten the time required for loading and unloading the workpiece. Therefore, in the superfinishing line, a two-roll system (see FIG. 7) is used for supporting the workpiece, and a box is used for conveying the workpiece.
[0070]
Specifically, as shown in FIG. 12, this line discharges the inlet portion 150 that receives the workpiece 151 from the grinding line, the machining portion 160 that performs superfinishing, and the workpiece 151 after superfinishing. The box 152 is used for conveying the workpiece 151 from the inlet 150 to the outlet 170. The box 152 is provided with two holding portions 152a for holding the workpiece 151, respectively.
[0071]
The box 152 is mounted on the movable table 153. This moving table 153 incorporates a feed screw mechanism and a linear guide. The feed screw mechanism has a screw shaft 153a and a nut portion (not shown) fixed to the moving base 153. The screw shaft 153a is screwed into the nut portion and driven by a drive motor 156. The linear guide 154 of the moving table 153 is slidably engaged with the horizontal guide rail 155. When the screw shaft 153 a is driven by the drive motor 156, the moving table 153 is moved along the horizontal guide rail 155.
[0072]
As shown in FIG. 13, the movable table 153 is supported by a plurality of support members 158, and each support member 158 is vertically aligned with a vertical guide rail 172 provided on a column 173 fixed to the base 174. It is configured to be movable. Each support member 158 is provided with a plurality of linear guides 171 slidably engaged with the feed screw mechanism 159 and the vertical guide race 172. The feed screw mechanism 159 of each support member 158 is driven by a drive motor 157, whereby each support member 158 is moved in the vertical direction. It is possible to move the movable table 153 in the vertical direction by moving each support member 158 in the vertical direction.
[0073]
In the inlet portion 150, two workpieces 151 are received from the grinding line, and each workpiece 151 is loaded on the box 152. The box 152 loaded with the workpiece 151 is sent to the processing unit 160 by the movement of the moving table 153 (A1 in FIG. 14).
[0074]
In the processing unit 160, as shown in FIGS. 12 and 13, the two workpieces 151 stacked on the box 152 are held between a pair of rollers 163 facing each other. At this time, each workpiece 151 is positioned and rotated with respect to the grindstone 162 respectively held by the two grindstone holders 161. As described in each of the above-described embodiments, each grindstone 162 swings at the radius of curvature of this portion while being pressed against the portion to be processed of the corresponding workpiece 151. Thereby, the process target site | part of each workpiece 151 is superfinished.
[0075]
Then, the box 152 on which the workpiece 151 after superfinishing is loaded is sent to the outlet portion 170 by the movement of the moving table 153. In the exit part 170, the movable table 153 is moved downward in the vertical direction (A2 in FIG. 14), and the work 151 loaded in the box 152 is discharged to the outside. Thereafter, the box 152 is returned to the entrance 150 by the movement of the moving table 153 (A3 in FIG. 14), and the moving table 153 is moved upward in the vertical direction (A4 in FIG. 14).
[0076]
【The invention's effect】
As described above, according to the present invention, the rotating shaft is rotated angularly while the eccentric cam is in contact with the regulating member and the rotating shaft is urged by the urging member. Since the grindstone is swung around the rotation axis while being moved in a predetermined direction, the linear distance from the axis of the rotation shaft to the tip position of the grindstone and the eccentric amount of the eccentric cam member are appropriately set, so It is possible to swing the tip of the grindstone along a track having a radius of curvature corresponding to the finished portion. In addition, this swing mechanism can be realized with a simplified structure. Furthermore, since the mass of the entire swing mechanism can be reduced, the swing speed can be increased, and the processing efficiency can be improved. That is, the structure can be simplified, and a finish with high accuracy and roughness can be obtained with high processing efficiency, as in the case of superfinishing of a superfinishing target portion having a small curvature.
[Brief description of the drawings]
FIG. 1 is a diagram showing a basic configuration of an apparatus for realizing a superfinishing method according to the present invention.
FIG. 2 is a diagram showing a locus drawn by the grindstone tip position P of FIG. 1 according to the rotation of a rotation shaft.
3 is a diagram showing the relationship between the eccentric amount e of the eccentric cam and the curvature radius (superfinishing radius) R0 when the linear distance r0 from the center of the rotating shaft to the grinding wheel tip position P in FIG. 1 is a variable. is there.
4 is a diagram showing the relationship between the linear distance r0 from the center of the rotating shaft to the grinding wheel tip position P and the radius of curvature (superfinishing radius) R0 when the amount of eccentricity e of the eccentric cam in FIG. 1 is a variable. is there.
5A is a top view showing the configuration of the superfinishing apparatus according to the first embodiment of the present invention, and FIG. 5B is a longitudinal sectional view taken along the line AA in FIG. 5A. is there.
6A is a front view of the eccentric cam of FIG. 5, FIG. 6B is a side view of the eccentric cam of FIG. 5, and FIG. 6C is a perspective view of the eccentric cam of FIG.
7A is a longitudinal sectional view showing the configuration of the grindstone holder of FIG. 5, and FIG. 7B is an arrow view seen from B of FIG.
8A is a front view of another configuration example of the tip portion of the grindstone holder, and FIG. 8B is a cross-sectional view taken along the line CC of FIG. 8A.
FIG. 9A is a top view showing the configuration of the main part of the superfinishing apparatus according to the second embodiment of the present invention, and FIG. 9B is a longitudinal section taken along the line DD in FIG. FIG.
FIG. 10A is a top view showing a configuration of a superfinishing apparatus according to a third embodiment of the present invention, and FIG. 10B is a front view of the superfinishing apparatus of FIG.
FIG. 11 is a cross-sectional view showing a configuration example of an eccentric cam mechanism.
FIG. 12 is a diagram schematically showing a configuration of a superfinishing line using a superfinishing apparatus according to the present invention.
13 is a diagram showing a state in which the superfinishing of the workpiece is performed in the superfinishing line of FIG. 12;
14 is a diagram schematically showing movement of a box in the line of FIG.
FIGS. 15A and 15B are a front view and a side view showing a main part configuration of a conventional superfinishing apparatus. FIGS.
FIGS. 16A and 16B are a front side sectional view, a side side sectional view, and a sectional view showing the periphery of the tip of a grindstone, showing the main part configuration of an apparatus for superfinishing a portion having a small curvature in a conventional workpiece.
[Explanation of symbols]
1,11,71 base
2a Rotating shaft
3, 20, 21 Wheel holder
4,49 Whetstone
5, 18, 19 Eccentric cam
6a, 6b, 23, 24, 61 regulating member
16, 17 spindle
35, 37, 103, 105 Spring member

Claims (2)

In the superfinishing method of the curved surface forming part of the workpiece, the second direction perpendicular to the axis of the rotation axis is supported on the rotation axis supported on the base so as to be movable in the first direction orthogonal to the axis. A whetstone is attached at a predetermined distance to the shaft, and an eccentric cam member that is eccentric with respect to the rotation shaft is coaxially attached. An urging member that urges toward the restriction member is provided on the base, and the rotation shaft is angled with the eccentric cam being in contact with the restriction member and the rotation shaft being urged by the urging member. A super-finishing method characterized in that the grindstone is swung around the rotating shaft while moving the rotating shaft in the first direction by rotationally driving the rotating shaft. In a superfinishing apparatus for a curved surface forming part of a workpiece, a base, a rotary shaft supported so as to be movable on the base in a first direction orthogonal to the axis, and the rotation on the rotary shaft A grindstone mounted at a predetermined distance in a second direction orthogonal to the axis of the shaft, an eccentric cam member coaxially mounted on the rotating shaft and eccentric with respect to the rotating shaft, and the base A regulating member that is provided and abutted against the eccentric cam member; and a biasing member that is provided on the base and biases the eccentric cam member toward the regulating member in the first direction; A super-finishing device comprising: a drive mechanism that rotationally drives the rotary shaft angularly.

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