JP2004276119A

JP2004276119A - Locking device for locking shaft member and locking device for cylindrical member lock up

Info

Publication number: JP2004276119A
Application number: JP2003066295A
Authority: JP
Inventors: Ichiro Kitaura; 一郎北浦
Original assignee: Pascal Engineering Corp
Current assignee: Pascal Engineering Corp
Priority date: 2003-01-21
Filing date: 2003-03-12
Publication date: 2004-10-07

Abstract

<P>PROBLEM TO BE SOLVED: To provide a locking device for locking a shaft member, efficiently applying force to the shaft member and having high durability. <P>SOLUTION: A workpiece support 1 includes: a collet member 5 externally fitted to a rod 4, having two or more first tapered surfaces forming a polygonal outer peripheral surface tapered to be reduced in diameter toward one end side, and elastically deformed toward the reduced diameter side; a cylindrical body externally fitted to the collet member 5 to be freely moved in the direction of the shaft center and having two or more tapered surfaces forming a polygonal inner peripheral surface tapered to be reduced in diameter toward one end side and forming a prescribed clearance 34 in a space up to the two or more first tapered surfaces; and two or more roller members 32 mounted to roll in the direction of shaft center of the rod 4 in the clearances 34 between two or more sets of the first and second tapered surfaces. When the cylindrical body 6 is driven to the other end side by a first hydraulic cylinder 7, the collet member 5 is elastically deformed toward the reduced diameter side through the two or more roller members 32. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

【０００１】
【発明の属する技術分野】本発明は、軸部材ロック用のロック装置及び筒部材ロック用のロック装置に関し、特に、軸部材及び筒部材を効率よくロック可能で且つ耐久性に優れたものに関する。
【０００２】
【従来の技術】従来より、本体ハウジングに対して進退不能にロックしたロッドによりワークを下方から支持するワークサポートや、軸状又は筒状のワークを固定するクランプ装置など、本体ハウジングに内嵌あるいは外嵌される軸部材又は筒部材を本体ハウジングに対して所定の位置にロックするロック装置としては、種々の型式のものが提案されているが、その中でも、軸部材に外嵌されたスリーブやコレット等を径縮小側へ弾性変形させて軸部材をロックするように構成されているものがある。
【０００３】
例えば、特許文献１に記載のコレット式クランプ装置においては、本体ハウジングに挿入されたロッドにコレットが外嵌されており、このコレットのテーパー外周面とこのテーパー外周面に対向するピストン部材のテーパー内周面との間に形成された環状テーパー隙間には、複数のボールが周方向及び軸心方向に並べて介装されている。そして、ピストン部材が下方へ駆動されると、ピストン部材のテーパー内周面から複数のボールに力が作用して、これら複数のボールが転動しながらコレットのテーパー外周面に押し付けられて、コレットが径縮小側に弾性変形してロッドがロックされる。
【０００４】
一方、特許文献２に記載のチャック装置においては、工具ホルダの先端側に設けられたチャック胴の断面円形のテーパー孔に、テーパー孔と対向する断面円形のテーパー外周面を有し工具に外嵌されるコレット状の圧入体が装着されている。ここで、チャック胴のテーパー孔と圧入体のテーパー外周面には複数組の角溝が周方向に形成されており、これら複数組の角溝で形成される隙間には複数のローラが軸心方向に並べて装着されている。そして、締付けリングが操作されて圧入体が軸心方向に移動したときには、複数のローラがチャック胴のテーパー孔と圧入体のテーパー外周面に夫々係合し、これら複数のローラを介して圧入体が縮径側に弾性変形して工具がロックされる。
【０００５】
【特許文献１】特開平１０−１４６７３３号公報（第３−５頁、図１−８）
【特許文献２】国際公開第９５／０７１６１号パンフレット（第７−８頁、図１１−１３）
【０００６】
【発明が解決しようとする課題】特許文献１に記載のクランプ装置においては、ロッドをロックする際に複数のボールがコレットのテーパー外周面に押し付けられることになるが、ボールとテーパー外周面との接触面積はかなり小さく、ほとんど点接触の状態でボールからテーパー外周面に力が伝達される。すると、コレットのテーパー外周面に局所的に大きな力がボールから作用することになるため、クランプ装置を繰り返し使用するにつれて、テーパー外周面にボールの圧痕がついてしまう。そうなると、ピストン部材からコレットに十分な力が伝達されなって確実にロッドをロックできなくなるため、耐久性の面で不利である。
【０００７】
一方、特許文献２に記載のチャック装置においては、チャック胴のテーパー孔と圧入体のテーパー外周面との間にはローラが介装されているので、前記特許文献１のように複数のボールを介装した場合に比べると、ローラとテーパー外周面との接触面積が大きく、線接触の状態でローラからテーパー外周面に力が伝達されるため、テーパー外周面に局所的にそれほど大きな力は作用しなくなる。しかし、チャック胴のテーパー孔と圧入体のテーパー外周面は、夫々断面円形の内周面及び外周面に形成されているため、テーパー孔とテーパー外周面との間には長さの短いローラしか装着することができない。従って、ローラを周方向に数多く並べて装着する必要があるため、製作コスト及び組み付けの面で不利である。
本発明の目的は、軸部材や筒部材に効率よく力を作用させて確実にロックすることが可能で且つ耐久性の高いロック装置を提供することである。
【０００８】
【課題を解決するための手段】請求項１に記載の軸部材ロック用のロック装置は、本体ハウジングに形成された挿通孔に挿通される軸部材を本体ハウジングにロック解除可能にロックするロック装置において、前記軸部材に外嵌され且つ一端側程径縮小側へテーパー化した多角形外周面を形成する複数の第１のテーパー面を有し且つ径縮小側に弾性変形可能なコレット部材と、このコレット部材に軸心方向へ移動自在に外嵌され且つ一端側程径縮小側へテーパー化した多角形内周面を形成すると共に複数の第１のテーパー面との間に所定の隙間を形成する複数の第２のテーパー面を有する筒状体と、前記複数組の第１、第２のテーパー面間の隙間に軸部材の軸心方向へ転動可能に装着された複数のローラ部材と、前記筒状体をコレット部材に対して相対的に他端側へ駆動する第１の駆動手段と、前記筒状体をコレット部材に対して相対的に一端側へ駆動する第２の駆動手段とを有し、前記第１の駆動手段により筒状体を他端側へ駆動するとき、複数のローラ部材を介してコレット部材を径縮小側へ弾性変形させるように構成したことを特徴とするものである。
【０００９】
このロック装置は、本体ハウジングの挿通孔に挿通される、ワークサポート又はクランプ装置のロッド、あるいは、機械加工に供されるワーク等の軸部材を、本体ハウジングにロック解除可能にロックするものである。軸部材にはコレット部材が外嵌され、さらに、筒状体がこのコレット部材に軸心方向に移動自在に外嵌されている。コレット部材には、一端側程径縮小側へテーパー化した多角形外周面を形成する複数の第１のテーパー面が設けられており、筒状体には、一端側程径縮小側へテーパー化した多角形内周面を形成する複数の第２のテーパー面が設けられている。
【００１０】
ここで、第１の駆動手段により筒状体をコレット部材に対して相対的に他端側へ駆動すると、複数のローラ部材が第１、第２のテーパー面間の隙間において転動しつつ第１、第２のテーパー面に係合し、これら複数のローラ部材を介してコレット部材が径縮小側へ押圧されて弾性変形して、コレット部材により軸部材がロックされる。逆に、軸部材がロックされた状態から第２の駆動手段により筒状体をコレット部材に対して相対的に一端側へ駆動すると、コレット部材に力が作用しなくなってその弾性変形が解除され、軸部材のロック状態も解除される。
【００１１】
請求項２の軸部材ロック用のロック装置は、請求項１の発明において、前記第１、第２の駆動手段の少なくとも一方が、本体ハウジング内に配設された流体圧シリンダを有することを特徴とするものである。従って、流体圧シリンダにより筒状体がコレット部材に対して相対的に一端側又は他端側へ駆動されることになる。
【００１２】
請求項３の軸部材ロック用のロック装置は、請求項２の発明において、前記第１の駆動手段が流体圧シリンダを有し、この流体圧シリンダは、本体ハウジング内に摺動自在に配設され且つ筒状体に外嵌された筒状ピストン部材を有することを特徴とするものである。流体圧シリンダの筒状ピストン部材が本体ハウジング内で他端側へ移動したときに、筒状体も筒状ピストン部材と共に他端側へ移動し、複数のローラ部材を介してコレット部材が径縮小側へ弾性変形することになる。
【００１３】
請求項４の軸部材ロック用のロック装置は、請求項３の発明において、前記第２の駆動手段が流体圧シリンダの駆動力に抗して筒状体を一端側へ駆動する圧縮バネ部材を有することを特徴とするものである。従って、この圧縮バネ部材により第１の駆動手段の流体圧シリンダの駆動力に抗して筒状体を一端側へ駆動すると、コレット部材に力が作用しなくなって軸部材のロック状態が解除される。
【００１４】
請求項５の軸部材ロック用のロック装置は、請求項１〜４の発明において、前記筒状体の他端側部分に、前記複数のローラ部材を他端側から受け止めるローラ受け部材を設けたことを特徴とするものである。第１の駆動手段により筒状体をコレット部材に対して他端側へ駆動したときには、複数のローラ部材が第１、第２のテーパー面間の隙間を転動しつつこれら第１、第２のテーパー面に確実に係合し、第１の駆動手段の駆動力が効率よくコレット部材に伝達されることになる。
【００１５】
請求項６の軸部材ロック用のロック装置は、請求項１〜５の発明において、前記複数のローラ部材のコレット部材に対する周方向の位置を規制する位置規制部を設けたことを特徴とするものである。従って、第１、第２のテーパー面間の隙間において、ローラ部材が周方向に移動することなく軸心方向にのみ転動するため、第１の駆動手段の駆動力が効率よくコレット部材に伝達される。
【００１６】
請求項７の軸部材ロック用のロック装置は、本体ハウジングと、この本体ハウジングにその軸心方向に相対移動可能に装着される軸部材とを有し、軸部材を本体ハウジングにロック解除可能にロックするロック装置において、前記軸部材に外嵌され且つ一端側程径縮小側へテーパー化した多角形外周面を形成する複数の第１のテーパー面を有し且つ径縮小側に弾性変形可能なコレット部材と、このコレット部材に軸心方向へ移動自在に外嵌され且つ一端側程径縮小側へテーパー化した多角形内周面を形成すると共に複数の第１のテーパー面との間に所定の隙間を形成する複数の第２のテーパー面を有する筒状体と、前記複数組の第１、第２のテーパー面間の隙間に軸部材の軸心方向へ転動可能に装着された複数のローラ部材と、前記筒状体をコレット部材に対して相対的に他端側へ駆動する第１の駆動手段と、前記筒状体をコレット部材に対して相対的に一端側へ駆動する第２の駆動手段とを有し、前記第１の駆動手段により筒状体を他端側へ駆動するとき、複数のローラ部材を介してコレット部材を径縮小側へ弾性変形させるように構成したことを特徴とするものである。
【００１７】
この軸部材ロック用のロック装置は、本体ハウジングに対してその軸心方向に相対移動可能な軸部材を本体ハウジングにロック解除可能にロックするものであるが、その作用は請求項１と略同様であるので、説明を省略する。
【００１８】
請求項８の筒部材ロック用のロック装置は、本体ハウジングに外嵌される筒部材を本体ハウジングにロック解除可能にロックするロック装置において、前記筒部材に内嵌され且つ一端側程径縮小側へテーパー化した多角形内周面を形成する複数の第１のテーパー面を有し且つ径拡大側に弾性変形可能なコレット部材と、このコレット部材に軸心方向へ移動自在に内嵌され且つ一端側程径縮小側へテーパー化した多角形外周面を形成すると共に複数の第１のテーパー面との間に所定の隙間を形成する複数の第２のテーパー面を有するピストン部材と、前記複数組の第１、第２のテーパー面間の隙間に筒部材の軸心方向へ転動可能に装着された複数のローラ部材と、前記ピストン部材をコレット部材に対して相対的に一端側へ駆動する第１の駆動手段と、前記ピストン部材をコレット部材に対して相対的に他端側へ駆動する第２の駆動手段とを有し、前記第１の駆動手段によりピストン部材を一端側へ駆動するとき、複数のローラ部材を介してコレット部材を径拡大側へ弾性変形させるように構成したことを特徴とするものである。
【００１９】
このロック装置は、本体ハウジングに外嵌される、筒状のワークなどの筒部材を、本体ハウジングにロック解除可能にロックするものである。筒部材にはコレット部材が外嵌され、さらに、ピストン部材がこのコレット部材に軸心方向に移動自在に内嵌されている。コレット部材には、一端側程径縮小側へテーパー化した多角形内周面を形成する複数の第１のテーパー面が設けられており、ピストン部材には、一端側程径縮小側へテーパー化した多角形外周面を形成する複数の第２のテーパー面が設けられている。
【００２０】
ここで、第１の駆動手段によりピストン部材をコレット部材に対して相対的に一端側へ駆動すると、複数のローラ部材が第１、第２のテーパー面間の隙間において転動しつつ第１、第２のテーパー面に係合し、これら複数のローラ部材を介してコレット部材が径拡大側へ押圧されて弾性変形して、コレット部材により筒部材がロックされる。逆に、筒部材がロックされた状態から第２の駆動手段により筒状体をコレット部材に対して相対的に他端側へ駆動すると、コレット部材に力が作用しなくなってその弾性変形が解除され、筒部材のロック状態も解除される。
【００２１】
【発明の実施の形態】本発明の実施の形態について説明する。本実施形態は、機械加工に供するワークを下方から支持してワークの弾性変形や振動を防止するワークサポートに本発明を適用した一例である。尚、図１、図２における上下方向を上下方向として以下説明する。
【００２２】
図１〜図５に示すように、ワークサポート１は、本体ハウジング３と、この本体ハウジング３に形成された挿通孔１２に挿通された出力部材としてのロッド４（軸部材に相当する）と、ロッド４に外嵌され径縮小側に弾性変形可能なコレット部材５と、本体ハウジング３内に配設されてコレット部材５に軸心方向へ移動自在に外嵌された筒状体６と、筒状体６をコレット部材５に対して相対的に下方へ駆動する第１油圧シリンダ７と、筒状体６をコレット部材５に対して相対的に上方へ駆動するコイルバネ８（圧縮バネ部材）と、ロッド４を上方へ進出駆動する第２油圧シリンダ９などを有する。そして、ワーク２に機械加工を施す際には、図１に示すように、複数のワークサポート１のロッド４を下方からワーク２に当接させてワーク２を支持する。
【００２３】
図２〜図５に示すように、本体ハウジング３は、略筒状の上部本体１０と、この上部本体１０の下半部に内嵌された略筒状の下部本体１１からなる。上部本体１０の上端側部分には、ロッド４を挿通する為の挿通孔１２が形成され、さらに、上部本体１０の内部には、この挿通孔１２の下端に連なる第１油圧シリンダ７のシリンダ穴１３も形成されている。挿通孔１２の上端部には、塵や切削切粉等が本体ハウジング３内に侵入するのを防止するダストシール１４が装着されている。
【００２４】
下部本体１１の上端部には、上方へ突出する筒部１１ａが設けられ、下部本体１１の内部には、第２油圧シリンダ９のシリンダ穴１５が形成されている。さらに、下部本体１１の上端側部分には、コイルバネ８を受け止める受け部１１ｂが形成されている。
【００２５】
ロッド４は、略円筒状のロッド本体４ａと、このロッド本体４ａの先端部に螺合された出力部４ｂを有し、ロッド４は本体ハウジング３に対して昇降自在に挿通孔１２に挿通されている。ロッド本体４ａの下端部には円筒穴１６が形成され、さらに、ロッド本体４ａには、中間壁部１７を隔てて円筒穴１６の上端に連なり円筒穴１６よりも小径のバネ収容穴１８も形成されている。バネ収容穴１８には、ロッド４を上方へ付勢するコイルバネ１９と、このコイルバネ１９を下方から受けるバネ受け部材２０が配設されており、バネ受け部材２０は、第２油圧シリンダ９のピストン部材５１に連結され中間壁部１７の連通穴を貫通する連結ロッド２１により下方から支持されている。ここで、連結ロッド２１の上端部は連通穴よりも大径に形成されており、バネ受け部材２０が下方へ移動したときに、連結ロッド２１と中間壁部１７とが係合してロッド４が下方へ押し下げられるように構成されている。
【００２６】
図４〜図８に示すように、コレット部材５は、ロッド本体４ａの下半部に外嵌されており、さらに、コレット部材５の下端は下部本体１１の上端部に当接し、コレット部材５は下方へ移動しないように規制されている。このコレット部材５は、周方向に並ぶ複数（例えば、１０個）のコレット分割体３０と、これらコレット分割体３０と一体的に形成された基部３１を備え、複数のコレット分割体３０の間には夫々複数のスリット３０ａが形成され、これら複数のスリット３０ａによりコレット部材５は径縮小側に弾性変形可能に構成されている。複数のコレット分割体３０の上端部には、夫々径方向外側へ突出する突出部３０ｂが形成され、さらに、複数のコレット分割体３０の外面部には、夫々第１テーパー面３０ｃが形成されている。そして、図７、図８に示すように、これら複数の第１テーパー面３０ｃにより、コレット部材５に上端側程径縮小側へテーパー化した略正五角形の外周面が形成されている。
【００２７】
図４〜図９に示すように、筒状体６の下側２／３の部分は、複数のコレット分割体３０に軸心方向へ移動自在に外嵌されており、筒状体６は、上端側程径縮小側へテーパー化した略正五角形の内周面を形成すると共に複数の第１テーパー面３０ｃとの間に所定の隙間を形成する複数の第２テーパー面６ａを有する。
即ち、筒状体６の上半部の内周面は、径の変化しない略正五角形の内周面に形成され、一方、筒状体６の下半部の内周面は、複数の第２テーパー面６ａにより上端側程径縮小側へテーパー化した略正五角形の内周面に形成されている。さらに、筒状体６の外周面は円柱面に形成されており、この筒状体６には、第１油圧シリンダ７の筒状ピストン部材４０が外嵌されている。
【００２８】
ところで、複数組の第１、第２のテーパー面３０ｃ，６ａ間の隙間３４には、複数（例えば、各々の隙間３４に５つ）のローラ部材３２が夫々ロッド４の軸心方向へ転動可能に装着されている。そして、後述の第１油圧シリンダ７により筒状体６が下方へ駆動されたときには、これら複数のローラ部材３２を介してコレット部材５に第１油圧シリンダ７の駆動力が作用し、コレット部材５が径縮小側へ弾性変形するように構成されている。
【００２９】
ここで、図７、図８に示すように、各ローラ部材３２は、コレット部材５及び筒状体６の正五角形の内外周面の一面を形成する２組の第１、第２テーパー面３０ｃ，６ａの間に装着されるため、ローラ部材３２の長さを十分長くすることができる。これら複数のローラ部材３２は、筒状体６の下端側部分に設けられたローラ受け部材３３により下方から受け止められ、さらに、複数のローラ部材３２はコレット部材５の突出部３０ｂにより上方へそれ以上転動しないように規制されている。尚、図６〜図８に示すように、コレット分割体３０のスリット３０ａ側の端部には、複数のローラ部材３２のコレット部材５に対する周方向の位置を規制する位置規制部３０ｄが径方向外側に突出するように設けられている。
【００３０】
第１油圧シリンダ７は、上部本体１０に形成されたシリンダ穴１３と、このシリンダ穴１３に摺動自在に内嵌された筒状ピストン部材４０と、この筒状ピストン部材４０を下方へ駆動する環状油室４１などを備えている。
筒状ピストン部材４０は、上端部の小径筒部４０ａと、この小径筒部４０ａの下端から周方向へ拡がる壁部４０ｂと、壁部４０ｂから下方へ延びる大径筒部４０ｃとを一体形成したものである。小径筒部４０ａは、上部本体１０の挿通孔１２に摺動自在に内嵌され、挿通孔１２と小径筒部４０ａとの間にはシール部材４２が装着されている。一方、大径筒部４０ｃは、シリンダ穴１３に摺動自在に内嵌され、大径筒部４０ｃの下端部は、上部本体１０と下部本体１１との間に形成された環状隙間４３に挿入され、下部本体１１と大径筒部４０ｃとの間にもシール部材４４が装着されている。
【００３１】
壁部４０ｂとシリンダ穴１３の上端部との間には環状油室４１が形成されており、この環状油室４１に、後述の第２油圧シリンダ９に供給された油圧の一部が、下部本体１１内の油路４５、環状隙間４３、シリンダ穴１３と大径筒部４０ｃとの間に形成された油路（図示略）を介して供給可能に構成されている。
【００３２】
第２油圧シリンダ９は、下部本体１１に形成されたシリンダ穴１５と、このシリンダ穴１５に摺動自在に装着されたピストン部材５１と、ピストン部材５１を上方へ駆動する駆動力を発生させる油室５２と、ピストン部材５１を下方へ付勢するコイルバネ５３を有する。ピストン部材５１の上半部には、連結ロッド２１の下端部が螺合連結されており、ピストン部材５１は、連結ロッド２１、バネ受け部材２０を介してロッド４と連結されている。
【００３３】
ピストン部材５１の下側には油室５２が形成されており、この油室５２には、図示しない外部の油圧供給源との間で油圧が給排される。また、油室５２は、油路４５、環状隙間４３、及びシリンダ穴１３と大径筒部４０ｃとの間の油路（図示略）を介して、第１油圧シリンダ７の環状油室４１と連通している。コイルバネ５３は、下部本体１１内に形成されたバネ収容室５４内に配設され、コイルバネ５３の下端はピストン部材５１の上端に当接している。
【００３４】
筒状体６を上方へ付勢するコイルバネ８は、下部本体１１と筒状体６の間に形成されたバネ収容室６０に配設されており、このコイルバネ８は、ローラ受け部材３３と下部本体１１のバネ受け部１１ｂに夫々当接している。従って、筒状体６はコイルバネ８により付勢されて、筒状体６の上端が筒状ピストン部材４０の壁部４０ｂの下面に当接し、筒状体６は筒状ピストン部材４０と一体的に上下に移動可能である。そして、第１油圧シリンダ７の環状油室４１から油圧が排出されて第１油圧シリンダ７の駆動力が低下したときには、コイルバネ８は第１油圧シリンダ７の駆動力に抗して筒状体６を上方へ駆動する。
【００３５】
次に、ワークサポート１の作用について説明する。
図４に示すように、ロッド４が最大限退入している状態から、第２油圧シリンダ９の油室５２に油圧を供給すると、油室５２に発生した駆動力によりピストン部材５１がコイルバネ５３の付勢力に抗して上方へ駆動される。すると、ピストン部材５１に連結ロッド２１を介して連結されたバネ受け部材２０もコイルバネ１９の付勢力に抗して上方へ駆動され、ロッド４が上方へ進出する。
【００３６】
同時に、油室５２から、油路４５、環状隙間４３を介して第１油圧シリンダ７の環状油室４１にも油圧が供給されて、環状油室４１に発生した第１油圧シリンダの駆動力により筒状ピストン部材４０が下方へ駆動され、筒状体６も筒状ピストン部材４０と共にコレット部材５に対してコイルバネ８の付勢力に抗して下方へ移動する。このとき、コレット部材５の第１テーパー面３０ｃと筒状体６の第２テーパー面６ａとの間の隙間３４において、複数のローラ部材３２が軸心方向に転動しつつ第１、第２テーパー面３０ｃ，６ａに夫々係合するため、第１、第２テーパー面３０ｃ，６ａ間の摩擦が低減されて、第１油圧シリンダ７の駆動力がコレット部材５に効率よく伝達され、コレット部材５が径縮小側に弾性変形する。そして、コレット部材５によりロッド４の下半部が確実に把持され、ロッド４が進出した状態でロックされて、図５に示すように、出力部４ｂがワーク２に当接してワーク２が下方から支持される。
【００３７】
逆に、図５に示すように、ロッド４が進出位置でロックされている状態から、油室の油圧を排出していくと、環状油室４１からも油圧が排出されて筒状体６及び筒状ピストン部材４０がコイルバネ８の付勢力により上方へ駆動される。すると、コレット部材５に径縮小側へ弾性変形させる力が作用しなくなり、ロッド４のロック状態が解除されて、コイルバネ８の付勢力によりロッド４が下方へ駆動されて、ロッド４が退入する。
【００３８】
以上説明したワークサポート１によれば、次のような効果が得られる。
１）第１、第２のテーパー面３０ｃ，６ａ間の隙間３４に装着された複数のローラ部材３２を転動させつつコレット部材５を径縮小側へ弾性変形させてロッド４をロックするので、第１、第２テーパー面３０ｃ，６ａ間の摩擦を低減して第１油圧シリンダ７の駆動力を効率よくコレット部材５に伝達させることができ、ワークサポート１を小型化することも可能になる。
【００３９】
また、複数のボールを用いて第１、第２テーパー面３０ｃ，６ａ間の摩擦を低減する場合に比べて、複数のローラ部材３２とコレット部材５との接触面積は大きくなるので、線接触の状態でローラ部材３２からコレット部材５に力が伝達され、コレット部材５に局所的に大きな力が作用せず、長期間に亙ってワークサポート１を繰り返し使用しても第１、第２テーパー面３０ｃ，６ａに圧痕がつきにくく、耐久性に優れる。
【００４０】
さらに、各ローラ部材３２は、コレット部材５及び筒状体６の正五角形の内外周面の夫々一面を形成する２組の第１、第２テーパー面３０ｃ，６ａの間に装着されるため、比較的長さの長いローラ部材３２を装着することができ、ローラ部材３２の数を少なくできるし、ローラ部材３２の組付けも容易になる。
【００４１】
２）筒状体６が、第１油圧シリンダ７の筒状ピストン部材４０に内嵌されており、筒状体６と筒状ピストン部材４０が別部材に構成されているため、筒状体６に複数の第２テーパー面６ａで多角形内周面を形成することが容易になる。
３）筒状体６の下端側部分に、前記複数のローラ部材３２を下端側から受け止めるローラ受け部材３３を設けたので、第１油圧シリンダ７により筒状体６をコレット部材５に対して下方へ駆動したとき、複数のローラ部材３２が第１、第２テーパー面３０ｃ，６ａ間の隙間３４を転動しつつ第１、第２テーパー面３０ｃ，６ａに確実に係合するため、第１油圧シリンダ７の駆動力をコレット部材５に効率よく伝達することができる。
【００４２】
４）コレット分割体３０に、複数のローラ部材３２のコレット部材５に対する周方向の位置を規制する位置規制部３０ｄが設けられているので、第１、第２テーパー面３０ｃ，６ａ間の隙間３４において、ローラ部材３２が周方向に移動することなく軸心方向に転動できるため、第１油圧シリンダ７の駆動力をコレット部材５に効率よく伝達することができる。
【００４３】
次に、前記実施形態に種々の変更を加えた変更形態について説明する。但し、前記実施形態と同じ構成のものについては、前記実施形態と同じ符号を付して適宜その説明を省略する。
１］筒状体６と筒状ピストン部材４０とを一体形成してもよく、この場合には、ワークサポート１の部品数を減らすことができる。
２］第１、第２テーパー面３０ｃ，６ａの数は５つに限るものではなく、コレット部材５の外周面と筒状体６の内周面を、五角形以外の他の多角形の外周面及び内周面に形成してもよい。
【００４４】
３］図１０、図１１に示すように、コレット部材５に位置規制部３０ｄを設ける代わりに、複数のローラ部材３２のコレット部材５に対する周方向の位置を規制する複数の位置規制部材７０を設けてもよい。各位置規制部材７０は、２つのローラ部材３２の間に配設された円筒分割体状の規制部７０ａと、この規制部７０ａの下端に一体的に設けられた基部７０ｂとを有する。これら複数の位置規制部材７０により、ローラ部材３２の周方向の位置が規制されて、第１、第２テーパー面３０ｃ，６ａ間の隙間３４において、ローラ部材３２が周方向に移動することなく軸心方向に転動できるため、第１油圧シリンダ７の駆動力をコレット部材５に効率よく伝達することができる。
【００４５】
４］前記実施形態とは逆に、以下に説明するワークサポート１Ｂのように、コレット部材１５５の複数の第１テーパー面１８１ａが下端側程径縮小側へテーパー化した多角形外周面を形成し、筒状体１５６の複数の第２テーパー面１５６ａが下端側程径縮小側へテーパー化した多角形内周面を形成するようにしてもよい。
【００４６】
図１２〜図１４に示すように、ワークサポート１Ｂは、本体ハウジング１５３と、この本体ハウジング１５３に上下方向に相対移動可能に装着された出力部材としてのロッド１５４（軸部材に相当する）と、ロッド１５４に外嵌され径縮小側に弾性変形可能なコレット部材１５５と、本体ハウジング１５３内に配設されてコレット部材１５５にロッド１５４の軸心方向へ移動自在に外嵌された筒状体１５６と、この筒状体１５６をコレット部材１５５に対して相対的に上方へ駆動する第１油圧シリンダ１５７（第１の駆動手段）と、筒状体１５６をコレット部材１５５に対して相対的に上方へ駆動するコイルバネ１５８（第２の駆動手段）と、ロッド１５４を上方へ進出駆動する第２油圧シリンダ１５９などを有する。
【００４７】
本体ハウジング１５３は、上部本体１６０と下部本体１６１を有し、上部本体１６０の上端側部分には、径方向内側へ突出する環状突出部１６２が形成され、この環状突出部の内側に、ロッド１５４をコレット部材１５５を介して挿通する為の挿通孔１６３が形成されている。さらに、本体ハウジング１５３の内部において環状突出部１６２の下側には、収容穴１６４と、この収容穴１６４に連なる第１油圧シリンダ１５７のシリンダ穴１６５が形成されている。
【００４８】
ロッド１５４は、コレット部材１５５を介して本体ハウジング１５３の挿通孔１６３に挿通されている。このロッド１５４の内部には、前記実施形態と同様に、バネ収容穴１７０が形成されている。そして、このバネ収容穴１７０には、ロッド１５４を上方へ付勢するコイルバネ１７１と、このコイルバネ１７１を下方から受けるバネ受け部材１７２とが配設されており、バネ受け部材１７２は、第２油圧シリンダ１５９のピストン部材１９５に連結された連結ロッド１７３により下方から支持されている。
【００４９】
コレット部材１５５は、径方向外側に水平に突出する突出部１８０と、この突出部１８０から下方へ延び且つ周方向に並ぶ複数（例えば、１０個）のコレット分割体１８１とを一体形成したものである。突出部１８０は、上部本体１６０の上端部に内嵌螺合され且つ環状突出部１６２に係合しており、突出部１８０の径方向内側部分にはダストシール１８２が装着されている。複数のコレット分割体１８１の上端部は上部本体１６０の挿通孔１６３に挿通されている。一方、複数のコレット分割体１８１の下側略２／３の部分の外周部には、夫々第１テーパー面１８１ａが形成されている。そして、これら複数の第１テーパー面１８１ａにより、コレット部材１５５に下端側程径縮小側へテーパー化した略正五角形の外周面が形成されている。
【００５０】
筒状体１５６は、複数のコレット分割体１８１に上下方向（ロッド１５４の軸心方向）へ移動自在に外嵌され且つ本体ハウジング１５３の収容穴１６４に摺動自在に装着されている。この筒状体１５６は、下端側程径縮小側へテーパー化した略正五角形の内周面を形成すると共に複数の第１テーパー面１８１ａとの間に所定の隙間１８４を形成する複数の第２テーパー面１５６ａを有する。
【００５１】
前記実施形態と同様に、複数組の第１、第２のテーパー面１８１ａ，１５６ａ間の隙間１８４には、複数（例えば、各々の隙間１８４に５つ）のローラ部材１８５が夫々ロッド１５４の軸心方向へ転動可能に装着されている。ところで、図１２、図１４に示すように、筒状体１５６の上端部には、径方向内側（ロッド１５４の軸心側）へ突出する突出部１５６ｂが設けられており、この突出部１５６ｂにより、複数のローラ部材１８５がそれ以上筒状体１５６に対して上方へ移動しないようになっている。さらに、複数のローラ部材１８５は、筒状体１５６の下側のローラ受け部材１８６により下方から受け止められ、このローラ受け部材１８６はコイルバネ１８７により上方へ付勢されている。
【００５２】
第１油圧シリンダ１５７は、上部本体１６０に形成されたシリンダ穴１６５と、このシリンダ穴１６５に摺動自在に装着されたピストン部材１９０と、このピストン部材１９０を上方へ駆動する駆動力を発生させる油室１９１などを備えている。ピストン部材１９０は、下部本体１６１の筒部１６１ａに摺動自在に外嵌され、ピストン部材１９０の上端は、筒状体１５６の下端に当接している。そして、このピストン部材１９０の下側には、油室１９１が形成されている。
【００５３】
筒状体１５６を下方へ付勢するコイルバネ１５８は、上部本体１６０の環状突出部１６２と筒状体１５６の上端との間に配設されている。
第２油圧シリンダ１５９は、ピストン部材１９５と、このピストン部材１９５を上方へ駆動する駆動力を発生させる油室１９６などを備え、前記実施形態と略同様の構成を有するためその説明を省略する。尚、この第２油圧シリンダ１５９の油室１９６は、第１油圧シリンダ１５７の油室１９１と油路１９７を介して連通している。
【００５４】
次に、このワークサポート１Ｂの作用について説明する。
図１２に示すように、ロッド１５４が最大限退入している状態から、第２油圧シリンダ１５９の油室１９６に油圧を供給すると、油室１９６に発生した駆動力によりピストン部材１９５が上方へ駆動される。すると、ピストン部材１９５に連結ロッド１７３を介して連結されたバネ受け部材１７２も上方へ駆動されるため、ロッド１５４が上方へ進出する。
【００５５】
同時に、油室１９６から、油路１９７を介して第１油圧シリンダ１５７の油室１９１にも油圧が供給され、油室１９１に発生した第１油圧シリンダ１５７の駆動力により筒状体１５６が上方へ駆動される。このとき、コレット部材１５５の第１テーパー面１８１ａと筒状体１５６の第２テーパー面１５６ａとの間の隙間１８４において、複数のローラ部材１８５が軸心方向に転動しつつ第１、第２テーパー面１８１ａ，１５６ａに夫々係合するため、第１、第２テーパー面１８１ａ，１５６ａ間の摩擦が低減されて、第１油圧シリンダ１５７の駆動力がコレット部材１５５に効率よく伝達され、コレット部材１５５が径縮小側に弾性変形する。そして、コレット部材１５５によりロッド１５４の下半部が確実に把持され、ロッド１５４が進出した状態でロックされて、図１４に示すように、ワーク２がロッド１５４により下方から支持される。
【００５６】
逆に、図１４に示すように、ロッド１５４が進出位置でロックされている状態から、第１油圧シリンダ１５７の油室１９１の油圧を排出していくと、筒状体１５６がコイルバネ１５８の付勢力により下方へ駆動される。すると、コレット部材１５５に径縮小側へ弾性変形させる力が作用しなくなり、ロッド１５４のロック状態が解除されて、コイルバネ１５８の付勢力によりロッド１５４が下方へ駆動されて、ロッド１５４が退入する。
【００５７】
このワークサポート１Ｂによれば、前記実施形態と略同様の効果が得られる。
即ち、第１、第２のテーパー面１８１ａ，１５６ａ間の隙間１８４に装着された複数のローラ部材１８５を転動させつつコレット部材１５５を径縮小側へ弾性変形させてロッド１５４をロックするので、第１、第２テーパー面１８１ａ，１５６ａ間の摩擦を低減して第１油圧シリンダ１５７の駆動力を効率よくコレット部材１５５に伝達させることができ、ワークサポート１Ｂを小型化することも可能になる。
【００５８】
また、複数のボールを用いて第１、第２テーパー面１８１ａ，１５６ａ間の摩擦を低減する場合に比べて、複数のローラ部材１８５とコレット部材１５５との接触面積は大きくなるので、線接触の状態でローラ部材１８５からコレット部材１５５に力が伝達され、コレット部材１５５に局所的に大きな力が作用せず、長期間に亙ってワークサポート１Ｂを繰り返し使用しても第１、第２テーパー面１８１ａ，１５６ａに圧痕がつきにくく、耐久性に優れる。
【００５９】
５］図１５に示すように、長い軸状に形成されたワーク等の軸部材８４をその途中部において固定する軸部材ロック用のロック装置８０に本発明を適用することもできる。このロック装置８０の本体ハウジング８３は上部本体９０と下部本体９１とを有し、上部本体９０及び下部本体９１には、夫々軸部材８４を挿通する為の挿通孔９２，９３が形成されている。軸部材８４が挿通孔９２，９３に挿通されて軸部材８４が本体ハウジング８３に貫通状に装着された状態では、軸部材８４には、径縮小側に弾性変形可能なコレット部材５が外嵌されている。さらに、本体ハウジング８３内にはこのコレット部材５に軸心方向へ移動自在に外嵌された筒状体６も配設されている。
【００６０】
これらコレット部材５及び筒状体６は、図８、図９に示される前記実施形態のものと略同じ構成を有するものである。即ち、コレット部材５には、略正五角形の外周面を形成する５つの第１テーパー面３０ｃが設けられ、筒状体６には、略正五角形の内周面を形成する５つの第２テーパー面６ａが設けられている。そして、各組の第１、第２テーパー面３０ｃ，６ａ間の隙間３４には、軸部材８４の軸心方向へ転動可能な複数（例えば、５つ）のローラ部材３２が装着されている。
【００６１】
さらに、このロック装置８０には、コレット部材５を下方へ駆動する油圧シリンダ８７も設けられている。この油圧シリンダ８７は、本体ハウジング８３のシリンダ穴９４に摺動自在に配設され且つ筒状体に外嵌された筒状ピストン部材４０と、筒状ピストン部材４０を下方へ駆動する駆動力を発生させる環状油室４１とを有する。環状油室４１は、油路９５、環状隙間９６を介して外部の油圧供給源（図示略）と接続されている。さらに、コレット部材５を上方へ駆動するコイルバネ８８も設けられている。
【００６２】
油圧シリンダ８７の環状油室４１に油圧が供給されると、この環状油室４１に発生した駆動力により筒状ピストン部材４０が下方へ駆動され、筒状ピストン部材４０と共に筒状体６もコイルバネ８８の付勢力に抗して下方へ移動する。このとき、コレット部材５の第１テーパー面３０ｃと筒状体６の第２テーパー面６ａとの間の隙間３４において、複数のローラ部材３２が軸心方向に転動しつつ第１、第２テーパー面３０ｃ，６ａに夫々係合し、第１、第２テーパー面３０ｃ，６ａ間の摩擦が低減されるため、油圧シリンダ８７の駆動力がコレット部材５に効率よく伝達され、コレット部材５が径縮小側に弾性変形する。そして、コレット部材５により軸部材４が確実に把持されてロックされる。
【００６３】
６］その他、機械加工用の工具を主軸等に固定する工具固定装置や、軸状のワークを固定するクランプ装置など、種々の軸部材をロックするロック装置に本発明を適用できるのは言うまでもない。
【００６４】
次に、本発明の別実施形態について説明する。この別実施形態は、筒状のワーク等の筒部材をロックする筒部材ロック用のロック装置に本発明を適用した一例である。
図１６、図１７に示すように、ロック装置１００は、筒状に形成されたワーク等の筒部材１０４に内嵌される本体ハウジング１０３と、筒部材１０４に内嵌され径拡大側に弾性変形可能なコレット部材１０５と、本体ハウジング１０３内に配設されてコレット部材１０５に軸心方向へ移動可能に内嵌されたピストン部材１０６と、ピストン部材１０６をコレット部材１０５に対して相対的に上方へ駆動する油圧シリンダ１０７と、ピストン部材１０６をコレット部材１０５に対して相対的に下方へ駆動するコイルバネ１０８とを有し、このロック装置１００は、本体ハウジング１０３に外嵌される筒部材１０４を本体ハウジング１０３に対してロック解除可能にロックする。
【００６５】
本体ハウジング１０３は、上部本体１１０と、この上部本体１１０の下端部に固定された下部本体１１１とを備えている。上部本体１１０は、上側の鍔部１１０ａとこの鍔部１１０ａから下方へ延びる軸部１１０ｂを有し、この軸部１１０ｂの下端部に下部本体１１１が外嵌されて、ボルト１１２により上部本体１１０に下部本体１１１が固定されている。下部本体１１１の上半部には筒部１１１ａが形成され、この筒部１１１ａの内側に油圧シリンダ１０７のシリンダ穴１１３が形成されている。尚、上部本体１１０の鍔部１１０ａの外径と下部本体１１１の外径は同径に形成されている。
【００６６】
図１６〜図１８に示すように、コレット部材１０５は、上部本体１１０の鍔部１１０ａと下部本体１１１の筒部１１１ａとの間に装着され、これら鍔部１１０ａと筒部１１１ａにより、コレット部材１０５は上下方向に移動しないように規制されている。このコレット部材１０５の外径は、上部本体１１０の鍔部１１０ａ及び下部本体１１１の外径と略同径に形成されており、筒部材１０４は本体ハウジング１０３と同じく筒部材１０４に内嵌される。
【００６７】
コレット部材１０５は、周方向に並ぶ複数（例えば、１０個）のコレット分割体１２０を有し、複数のコレット分割体１２０の間には夫々複数のスリット１２０ａが形成され、これら複数のスリット１２０ａによりコレット部材１０５は径拡大側に弾性変形可能に構成されている。複数のコレット分割体１２０の下端部には、夫々径方向内側へ突出する突出部１２０ｂが形成され、さらに、複数のコレット分割体１２０の内面部には、夫々第１テーパー面１２０ｃが形成されている。そして、図１８に示すように、コレット部材１０５の上半部の内周面は、径の変化しない略正五角形の内周面に形成され、コレット部材１０５の下半部の内周面には、複数の第１テーパー面１２０ｃにより上端側程径縮小側へテーパー化した略正五角形の外周面が形成されている。
【００６８】
ピストン部材１０６は、上部本体１１０の軸部１１０ａの上下方向途中部に摺動自在に外嵌され、さらに、ピストン部材１０６の上側略２／３の部分は、複数のコレット分割体１２０に軸心方向（上下方向）に移動自在に内嵌されている。図１６、図１７、図１９に示すように、このピストン部材１０６は、上端側程径縮小側へテーパー化した略正五角形の外周面を形成すると共に複数の第１テーパー面１２０ｃとの間に所定の隙間１２４を形成する複数（例えば、５つ）の第２テーパー面１０６ａを有する。ピストン部材１０６の上端部には、内側へ突出する環状突出部１０６ｂが形成され、さらに、ピストン部材１０６の上端部の軸心側部分には、コイルバネ１０８を下方から受ける環状のバネ受け部１０６ｃも形成されている。
【００６９】
ところで、複数組の第１、第２テーパー面１２０ｃ，１０６ａ間の隙間１２４には、複数（例えば、各々の隙間１２４に６つ）のローラ部材１２５が夫々筒部材１０４の軸心方向へ転動可能に装着されている。そして、後述の油圧シリンダ１０７によりピストン部材１０６が上方へ駆動されたときには、これら複数のローラ部材１２５を介してコレット部材１０５に油圧シリンダ１０７の駆動力が作用し、コレット部材１０５が径拡大側へ弾性変形するように構成されている。これら複数のローラ部材１２５は、コレット部材１０５の突出部１２０ｂにより下方から受け止められ、さらに、複数のローラ部材１２５はピストン部材１０６の環状突出部１０６ｂにより上方へそれ以上転動しないように規制されている。
【００７０】
油圧シリンダ１０７は、下部本体１１１に形成されたシリンダ穴１１３と、上部本体１１０の軸部１１０ａに摺動自在に外嵌され且つシリンダ穴１１３に摺動自在に内嵌された環状ピストン部材１２６と、この環状ピストン部材１２６の下側に形成され環状ピストン部材１２６を上方へ駆動する環状油室１２７などを備えている。環状ピストン部材１２６の上端はピストン部材１０６の下端に当接しており、ピストン部材１０６と環状ピストン部材１２６は一体的に上方へ移動可能に構成されている。環状油室１２７は、下部本体１１１に形成された油圧供給口１２８及び油路１２９を介して外部の油圧供給源（図示略）と接続され、環状油室１２７に油圧を給排可能である。
【００７１】
ピストン部材１０６を下方へ付勢するコイルバネ１０８は、上部本体１１０とピストン部材１０６の間に形成されたバネ収容室１３０に配設されており、このコイルバネ１０８は、上部本体１１０の鍔部１１０ａの下面と下部本体１１１のバネ受け部１０６ｃに夫々当接している。そして、油圧シリンダ１０７の環状油室１２７から油圧が排出されて油圧シリンダ１０７の駆動力が低下したときには、コイルバネ１０８は油圧シリンダ１０７の駆動力に抗してピストン部材１０６を下方へ駆動する。
【００７２】
次に、ロック装置１００の作用及び効果について説明する。
図１６に示すように、本体ハウジング１０３に筒部材１０４を外嵌させてから、油圧シリンダ１０７の環状油室１２７に油圧を供給すると、環状油室１２７に発生した駆動力により環状ピストン部材１２６がコイルバネ１０８の付勢力に抗して上方へ駆動される。すると、図１７に示すように、ピストン部材１０６も環状ピストン部材１２６と共に上方へ駆動される。
【００７３】
このとき、コレット部材１０５の第１テーパー面１２０ｃとピストン部材１０６の第２テーパー面１０６ａとの間の隙間１２４において、複数のローラ部材１２５が軸心方向に転動しつつ第１、第２テーパー面１２０ｃ，１０６ａに夫々係合するため、第１、第２テーパー面１２０ｃ，１０６ａ間の摩擦が低減されて、油圧シリンダ１０７の駆動力がコレット部材１０５に効率よく伝達され、コレット部材１０５が径拡大側に弾性変形する。そして、複数のコレット分割体１２０が筒部材１０４の内周面に密着して、筒部材１０４がロックされる。
【００７４】
逆に、図１７に示すように、筒部材１０４がロックされている状態から、環状油室１２７の油圧を排出していくと、ピストン部材１０６及び環状ピストン部材１２６がコイルバネ１０８の付勢力により下方へ駆動される。すると、コレット部材１０５に径拡大側へ弾性変形させる力が作用しなくなり、筒部材１０４のロック状態が解除される。
【００７５】
このロック装置１００によれば、複数のローラ部材１２５とコレット部材１０５との接触面積は大きくなるので、コレット部材１０５に局所的に大きな力が作用せず、長期間に亙ってロック装置１００を繰り返し使用しても第１、第２テーパー面１２０ｃ，１０６ａに圧痕がつきにくく、耐久性に優れる。その他、前記実施形態と略同様の効果が得られる。
【００７６】
【発明の効果】請求項１の発明によれば、第１、第２のテーパー面間の隙間に装着された複数のローラ部材を転動させつつコレット部材を径縮小側へ弾性変形させて軸部材をロックするので、第１、第２のテーパー面間の摩擦を低減して第１の駆動手段の駆動力を効率よくコレット部材に伝達させることができ、ロック装置を小型化することも可能になる。また、複数のローラ部材とコレット部材との接触面積が比較的大きくなり、線接触の状態でローラ部材からコレット部材に力が伝達されるため、コレット部材に局所的に大きな力が作用せず、長期間に亙ってロック装置を使用しても第１、第２のテーパー面に圧痕がつきにくくなるため、耐久性に優れる。
【００７７】
さらに、複数の第１のテーパー面によりコレット部材に多角形外周面が形成され、複数の第２のテーパー面により筒状体に多角形内周面が形成されており、各ローラ部材がコレット部材及び筒状体の多角形内外周面の夫々一面を構成する第１、第２テーパー面間の隙間に装着されるため、比較的長さの長いローラ部材を装着することができ、ローラ部材の数を少なくできるし、ローラ部材の組付けも容易になる。
【００７８】
請求項２の発明によれば、第１、第２の駆動手段の少なくとも一方が、本体ハウジング内に配設された流体圧シリンダを有するので、流体圧シリンダにより筒状体をコレット部材に対して相対的に一端側又は他端側へ駆動して、軸部材を確実にロック状態又はロック解除状態にすることができる。
【００７９】
請求項３の発明によれば、第１の駆動手段が流体圧シリンダを有し、この流体圧シリンダは、本体ハウジング内に摺動自在に配設され且つ筒状体に外嵌された筒状ピストン部材を有するので、流体圧シリンダの筒状ピストン部材を他端側へ移動させることで、筒状体も筒状ピストン部材と共に他端側へ移動させて、複数のローラ部材を介してコレット部材を径縮小側へ弾性変形させることができる。また、筒状体と筒状ピストン部材とを別部材とすることで、筒状体に複数の第２のテーパー面で多角形内周面を形成することが容易になる。
【００８０】
請求項４の発明によれば、第２の駆動手段が流体圧シリンダの駆動力に抗して筒状体を一端側へ駆動する圧縮バネ部材を有するので、この圧縮バネ部材により第１の駆動手段の流体圧シリンダの駆動力に抗して筒状体を一端側へ駆動して、軸部材のロック状態を解除することができる。
【００８１】
請求項５の発明によれば、筒状体の他端側部分に、前記複数のローラ部材を他端側から受け止めるローラ受け部材を設けたので、第１の駆動手段により筒状体をコレット部材に対して他端側へ駆動したときには、複数のローラ部材が第１、第２のテーパー面間の隙間を転動しつつこれら第１、第２のテーパー面に確実に係合するため、第１の駆動手段の駆動力をコレット部材に効率よく伝達することができる。
【００８２】
請求項６の発明によれば、複数のローラ部材のコレット部材に対する周方向の位置を規制する位置規制部を設けたので、第１、第２のテーパー面間の隙間において、ローラ部材が周方向に移動することなく軸心方向に転動できるため、第１の駆動手段の駆動力をコレット部材に効率よく伝達することができる。
請求項７の発明によれば、請求項１の発明と略同様の効果が得られるため、その説明を省略する。
【００８３】
請求項８の発明によれば、第１、第２のテーパー面間の隙間に装着された複数のローラ部材を転動させつつコレット部材を径拡大側へ弾性変形させて筒部材をロックするので、第１、第２のテーパー面間の摩擦を低減して第１の駆動手段の駆動力を効率よくコレット部材に伝達させることができ、ロック装置を小型化することも可能になる。また、複数のローラ部材とコレット部材との接触面積が比較的大きくなるので、コレット部材に局所的に大きな力が作用せず、長期間に亙ってロック装置を使用しても第１、第２のテーパー面に圧痕がつきにくくなるため、耐久性に優れる。
【００８４】
さらに、複数の第１のテーパー面によりコレット部材に多角形内周面が形成され、複数の第２のテーパー面によりピストン部材に多角形外周面が形成されており、各ローラ部材がコレット部材及びピストン部材の多角形内外周面の夫々一面を構成する第１、第２テーパー面間の隙間に装着されるため、比較的長さの長いローラ部材を装着することができ、ローラ部材の数を少なくできるし、ローラ部材の組付けも容易になる。
【図面の簡単な説明】
【図１】本発明の実施形態に係るワークサポート及び周辺装置の構成図である。
【図２】ワークサポートの正面図である。
【図３】ワークサポートの平面図である。
【図４】ロッド退入状態におけるワークサポートのＩＶ−ＩＶ線断面図である。
【図５】ワーク支持状態におけるワークサポートの図４相当図である。
【図６】図４のＶＩ−ＶＩ線断面図である。
【図７】図４のＶＩＩ−ＶＩＩ線断面図である。
【図８】コレット部材及びローラ部材の斜視図である。
【図９】筒状体の斜視図である。
【図１０】変更形態の図７相当図である。
【図１１】位置規制部材の斜視図である。
【図１２】変更形態の図４相当図である。
【図１３】図１２のＸＩＩＩ−ＸＩＩＩ線断面図である。
【図１４】変更形態の図５相当図である。
【図１５】変更形態の図４相当図である。
【図１６】別実施形態の図４相当図である。
【図１７】別実施形態の図５相当図である。
【図１８】別実施形態のコレット部材の下方から見た斜視図である。
【図１９】別実施形態のピストン部材及びローラ部材の斜視図である。
【符号の説明】
１，１Ａ，１Ｂワークサポート
３本体ハウジング
４ロッド
５コレット部材
６筒状体
６ａ第２テーパー面
７第１油圧シリンダ
８コイルバネ
９第２油圧シリンダ
１２挿通孔
３０ｃ第１テーパー面
３０ｄ位置規制部
３２ローラ部材
３３ローラ受け部材
３４隙間
４０筒状ピストン部材
７０位置規制部材
８０ロック装置
８３本体ハウジング
８４軸部材
８７油圧シリンダ
８８コイルバネ
１００ロック装置
１０３本体ハウジング
１０４筒部材
１０５コレット部材
１０６ピストン部材
１０６ａ第２テーパー面
１０７油圧シリンダ
１０８コイルバネ
１２０ｃ第１テーパー面
１２４隙間
１２５ローラ部材
１５３本体ハウジング
１５４ロッド
１５５コレット部材
１５６筒状体
１５６ａ第２テーパー面
１５７第１油圧シリンダ
１５８コイルバネ
１５９第２油圧シリンダ
１８１ａ第１テーパー面
１８４隙間
１８５ローラ部材[0001]
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a locking device for locking a shaft member and a locking device for locking a cylindrical member, and more particularly to a locking device capable of efficiently locking a shaft member and a cylindrical member and having excellent durability.
[0002]
2. Description of the Related Art Conventionally, a work support which supports a work from below by a rod which is locked to a main body housing so as to be unable to advance and retreat, a clamp device for fixing a shaft-like or cylindrical work, and the like, are fitted or fitted in a main body housing. Various types of lock devices have been proposed as lock devices for locking a shaft member or a tubular member to be externally fitted to a predetermined position with respect to the main body housing. Among them, a sleeve or a sleeve externally fitted to the shaft member has been proposed. There is one configured to lock a shaft member by elastically deforming a collet or the like toward a diameter reducing side.
[0003]
For example, in the collet-type clamp device described in Patent Literature 1, a collet is externally fitted to a rod inserted into a main body housing, and a tapered outer peripheral surface of the collet and a taper of a piston member opposed to the tapered outer peripheral surface. A plurality of balls are interposed in the annular taper gap formed between the peripheral surface and the peripheral surface in the circumferential direction and the axial direction. When the piston member is driven downward, a force acts on a plurality of balls from the tapered inner peripheral surface of the piston member, and the plurality of balls are pressed against the tapered outer peripheral surface of the collet while rolling, and Is elastically deformed toward the diameter reduction side to lock the rod.
[0004]
On the other hand, in the chuck device described in Patent Literature 2, the chuck body provided on the tip end side of the tool holder has a circular tapered outer surface with a circular cross section opposed to the tapered hole, and is externally fitted to the tool. The press-fit body in the form of a collet is mounted. Here, a plurality of sets of square grooves are formed in the taper hole of the chuck body and the tapered outer peripheral surface of the press-fitting body in a circumferential direction, and a plurality of rollers are provided in a gap formed by the plurality of sets of square grooves. They are mounted side by side. When the tightening ring is operated to move the press-fit body in the axial direction, the plurality of rollers engage with the tapered hole of the chuck body and the tapered outer peripheral surface of the press-fit body, respectively, and the press-fit body is inserted through the plurality of rollers. Is elastically deformed toward the reduced diameter side, and the tool is locked.
[0005]
[Patent Document 1] JP-A-10-146733 (page 3-5, FIG. 1-8)
[Patent Document 2] International Publication No. 95/07161 pamphlet (pages 7-8, FIGS. 11-13)
[0006]
In the clamp device described in Patent Document 1, a plurality of balls are pressed against the tapered outer peripheral surface of the collet when the rod is locked. The contact area is fairly small, and force is transmitted from the ball to the tapered outer peripheral surface in almost point contact. Then, since a large force locally acts on the tapered outer peripheral surface of the collet from the ball, an indentation of the ball is made on the tapered outer peripheral surface as the clamp device is repeatedly used. In such a case, a sufficient force is transmitted from the piston member to the collet, and the rod cannot be reliably locked, which is disadvantageous in terms of durability.
[0007]
On the other hand, in the chuck device described in Patent Literature 2, since a roller is interposed between the tapered hole of the chuck body and the tapered outer peripheral surface of the press-fitting body, a plurality of balls are provided as in Patent Literature 1. The contact area between the roller and the outer peripheral surface of the taper is larger than in the case where the roller is interposed, and since a force is transmitted from the roller to the outer peripheral surface of the taper in a line contact state, a relatively large force acts locally on the outer peripheral surface of the taper. No longer. However, since the tapered hole of the chuck body and the tapered outer peripheral surface of the press-fitting body are formed on the inner peripheral surface and the outer peripheral surface, respectively, having a circular cross section, only a roller having a short length is provided between the tapered hole and the tapered outer peripheral surface. Cannot be installed. Therefore, it is necessary to mount a number of rollers side by side in the circumferential direction, which is disadvantageous in terms of manufacturing cost and assembly.
SUMMARY OF THE INVENTION An object of the present invention is to provide a highly durable locking device that can securely apply a force to a shaft member and a cylindrical member to securely lock the shaft member and the cylindrical member.
[0008]
According to a first aspect of the present invention, there is provided a locking device for locking a shaft member, wherein the shaft member inserted through an insertion hole formed in the main body housing is releasably locked to the main body housing. A collet member that has a plurality of first tapered surfaces that form a polygonal outer peripheral surface that is externally fitted to the shaft member and that tapers toward the diameter reducing side toward one end, and is elastically deformable toward the diameter reducing side; The collet member has a polygonal inner peripheral surface which is fitted to the collet member so as to be movable in the axial direction, and is tapered toward the diameter decreasing side toward one end, and a predetermined gap is formed between the collet member and the plurality of first tapered surfaces. A cylindrical body having a plurality of second tapered surfaces, and a plurality of roller members mounted in gaps between the plurality of sets of the first and second tapered surfaces so as to be rollable in the axial direction of the shaft member. , The cylindrical body as a collet member A first driving means for driving the cylindrical body relatively to the other end side, and a second driving means for driving the cylindrical body relatively to the one end side with respect to the collet member; When the cylindrical body is driven to the other end by the driving means, the collet member is elastically deformed toward the diameter reducing side via a plurality of roller members.
[0009]
This lock device locks a shaft member such as a rod of a work support or a clamp device or a workpiece provided for machining to be inserted into an insertion hole of a main body housing so as to be unlockable to the main body housing. . A collet member is externally fitted to the shaft member, and a cylindrical body is externally fitted to the collet member so as to be movable in the axial direction. The collet member is provided with a plurality of first tapered surfaces that form a polygonal outer peripheral surface that tapers to a diameter decreasing side toward one end, and the cylindrical body tapers to a diameter decreasing side toward one end. A plurality of second tapered surfaces forming the polygon inner peripheral surface are provided.
[0010]
Here, when the cylindrical body is driven to the other end side relative to the collet member by the first driving means, the plurality of roller members roll while rolling in the gap between the first and second tapered surfaces. The collet member is engaged with the first and second tapered surfaces, is pressed toward the diameter reducing side via the plurality of roller members, and is elastically deformed, whereby the shaft member is locked by the collet member. Conversely, when the cylindrical member is driven to the one end side relative to the collet member by the second driving means from the locked state of the shaft member, no force acts on the collet member, and the elastic deformation is released. Also, the locked state of the shaft member is released.
[0011]
According to a second aspect of the present invention, in the locking device for locking a shaft member, at least one of the first and second driving means has a fluid pressure cylinder disposed in a main body housing. It is assumed that. Therefore, the cylindrical body is driven toward the one end or the other end relative to the collet member by the fluid pressure cylinder.
[0012]
According to a third aspect of the present invention, in the locking device for locking a shaft member according to the second aspect of the present invention, the first driving means has a hydraulic cylinder, and the hydraulic cylinder is slidably disposed in the main body housing. And a cylindrical piston member externally fitted to the cylindrical body. When the cylindrical piston member of the fluid pressure cylinder moves to the other end side in the main body housing, the cylindrical body also moves to the other end side together with the cylindrical piston member, and the collet member is reduced in diameter through a plurality of roller members. It will be elastically deformed to the side.
[0013]
According to a fourth aspect of the present invention, there is provided a locking device for locking a shaft member according to the third aspect of the present invention, wherein the second driving means drives the cylindrical body to one end side against a driving force of a fluid pressure cylinder. It is characterized by having. Therefore, when the cylindrical body is driven to one end side against the driving force of the fluid pressure cylinder of the first driving means by the compression spring member, no force acts on the collet member and the locked state of the shaft member is released. You.
[0014]
The lock device for locking a shaft member according to claim 5 is the invention according to claims 1 to 4, wherein a roller receiving member that receives the plurality of roller members from the other end side is provided at the other end portion of the tubular body. It is characterized by the following. When the cylindrical body is driven to the other end side with respect to the collet member by the first driving means, the plurality of roller members rolls in the gap between the first and second tapered surfaces while rotating between the first and second tapered surfaces. And the driving force of the first driving means is efficiently transmitted to the collet member.
[0015]
According to a sixth aspect of the present invention, in the locking device for locking a shaft member according to the first to fifth aspects, a position regulating portion for regulating a circumferential position of the plurality of roller members with respect to the collet member is provided. It is. Accordingly, in the gap between the first and second tapered surfaces, the roller member rolls only in the axial direction without moving in the circumferential direction, so that the driving force of the first driving means is efficiently transmitted to the collet member. Is done.
[0016]
According to a seventh aspect of the present invention, there is provided a locking device for locking a shaft member, comprising: a main body housing; and a shaft member mounted on the main body housing so as to be relatively movable in an axial direction thereof. In a locking device for locking, the locking device has a plurality of first tapered surfaces which are fitted to the shaft member and form a polygonal outer peripheral surface which is tapered toward a diameter decreasing side toward one end side, and are elastically deformable toward the diameter decreasing side. A predetermined inner space is formed between the collet member and a plurality of first tapered surfaces which form a polygonal inner peripheral surface which is fitted to the collet member so as to be movable in the axial direction and which is tapered toward the diameter reducing side toward one end. And a plurality of cylindrical bodies having a plurality of second tapered surfaces forming a gap between the first and second sets of first and second tapered surfaces so as to be rollable in the axial direction of the shaft member. Roller member and the cylindrical body A first driving unit that drives the cylindrical member toward the other end relative to the collet member; and a second driving unit that drives the cylindrical body toward the one end relative to the collet member. When the cylindrical body is driven to the other end by the first driving means, the collet member is elastically deformed to the diameter reducing side via a plurality of roller members.
[0017]
The locking device for locking the shaft member locks the shaft member which is relatively movable in the axial direction with respect to the main body housing so as to be unlockable to the main body housing. Therefore, the description is omitted.
[0018]
The lock device for locking a cylindrical member according to claim 8, wherein the lock member locks the cylindrical member externally fitted to the main body housing to the main body housing so as to be unlockable. A collet member having a plurality of first tapered surfaces forming a tapered polygonal inner peripheral surface and capable of being elastically deformed toward the enlarged diameter side; a collet member fitted inside the collet member so as to be movable in the axial direction; A piston member having a plurality of second tapered surfaces forming a polygonal outer peripheral surface tapered to a diameter decreasing side toward one end side and forming a predetermined gap between the plurality of first tapered surfaces; A plurality of roller members rotatably mounted in the gap between the first and second tapered surfaces in the axial direction of the cylindrical member, and the piston member is driven to one end side relative to the collet member. First drive to A step and second driving means for driving the piston member toward the other end relative to the collet member, wherein when the first driving means drives the piston member toward the one end, a plurality of The present invention is characterized in that the collet member is elastically deformed toward the enlarged diameter side via a roller member.
[0019]
This locking device locks a tubular member, such as a cylindrical work, which is fitted to the main body housing, to the main body housing so as to be unlockable. A collet member is externally fitted to the cylindrical member, and a piston member is internally fitted to the collet member so as to be movable in the axial direction. The collet member is provided with a plurality of first tapered surfaces that form a polygonal inner peripheral surface that tapers to a diameter decreasing side toward one end, and the piston member tapers to a diameter decreasing side toward one end. A plurality of second tapered surfaces forming a polygonal outer peripheral surface are provided.
[0020]
Here, when the piston member is driven toward the one end side relative to the collet member by the first driving means, the plurality of roller members roll while rolling in the gap between the first and second tapered surfaces. The collet member is engaged with the second tapered surface, is pressed toward the diameter-enlargement side via the plurality of roller members, and is elastically deformed, so that the cylindrical member is locked by the collet member. Conversely, when the cylindrical member is driven toward the other end relative to the collet member by the second driving means from the locked state of the cylindrical member, no force acts on the collet member and the elastic deformation is released. Then, the locked state of the tubular member is also released.
[0021]
Embodiments of the present invention will be described. This embodiment is an example in which the present invention is applied to a work support that supports a workpiece to be machined from below and prevents elastic deformation and vibration of the workpiece. The vertical direction in FIGS. 1 and 2 will be described below as the vertical direction.
[0022]
As shown in FIGS. 1 to 5, the work support 1 includes a main body housing 3, a rod 4 (corresponding to a shaft member) as an output member inserted into an insertion hole 12 formed in the main body housing 3, A collet member 5 externally fitted to the rod 4 and elastically deformable to a reduced diameter side; a cylindrical body 6 disposed in the main body housing 3 and externally fitted to the collet member 5 so as to be movable in the axial direction; A first hydraulic cylinder 7 for driving the cylindrical body 6 relatively downward with respect to the collet member 5, a coil spring 8 (compression spring member) for driving the cylindrical body 6 relatively upward with respect to the collet member 5, And a second hydraulic cylinder 9 for driving the rod 4 to advance upward. Then, when machining the work 2, as shown in FIG. 1, the rods 4 of the plurality of work supports 1 are brought into contact with the work 2 from below to support the work 2.
[0023]
As shown in FIGS. 2 to 5, the main body housing 3 includes a substantially cylindrical upper main body 10 and a substantially cylindrical lower main body 11 fitted in a lower half portion of the upper main body 10. An insertion hole 12 for inserting the rod 4 is formed in an upper end portion of the upper body 10, and a cylinder hole of the first hydraulic cylinder 7 connected to a lower end of the insertion hole 12 is formed inside the upper body 10. 13 are also formed. At the upper end of the insertion hole 12, a dust seal 14 for preventing dust, cutting chips and the like from entering the main body housing 3 is mounted.
[0024]
An upper end of the lower main body 11 is provided with a cylindrical portion 11 a protruding upward, and a cylinder hole 15 of the second hydraulic cylinder 9 is formed inside the lower main body 11. Further, a receiving portion 11b for receiving the coil spring 8 is formed in an upper end portion of the lower main body 11.
[0025]
The rod 4 has a substantially cylindrical rod body 4a and an output portion 4b screwed to the tip of the rod body 4a. The rod 4 is inserted into the insertion hole 12 so as to be able to move up and down with respect to the body housing 3. ing. A cylindrical hole 16 is formed at the lower end of the rod body 4a, and a spring housing hole 18 having a smaller diameter than the cylindrical hole 16 is formed in the rod body 4a so as to be continuous with the upper end of the cylindrical hole 16 with an intermediate wall portion 17 therebetween. Have been. A coil spring 19 that urges the rod 4 upward and a spring receiving member 20 that receives the coil spring 19 from below are provided in the spring receiving hole 18. The spring receiving member 20 is a piston of the second hydraulic cylinder 9. It is supported from below by a connecting rod 21 connected to the member 51 and penetrating through the communication hole of the intermediate wall portion 17. Here, the upper end of the connecting rod 21 is formed to be larger in diameter than the communicating hole, and when the spring receiving member 20 moves downward, the connecting rod 21 Is configured to be pushed down.
[0026]
As shown in FIGS. 4 to 8, the collet member 5 is externally fitted to the lower half of the rod body 4 a, and the lower end of the collet member 5 contacts the upper end of the lower main body 11. Is restricted from moving downward. The collet member 5 includes a plurality of (for example, 10) collet divided bodies 30 arranged in the circumferential direction and a base 31 integrally formed with the collet divided bodies 30. Each of the plurality of slits 30a is formed, and the collet member 5 is configured to be elastically deformable toward the diameter reduction side by the plurality of slits 30a. At the upper end of each of the plurality of collet divisions 30, a protruding portion 30b that protrudes radially outward is formed, and at the outer surface of the plurality of collet divisions 30, a first tapered surface 30c is formed, respectively. I have. As shown in FIGS. 7 and 8, the plurality of first tapered surfaces 30 c form a substantially regular pentagonal outer peripheral surface that is tapered toward the upper end side toward the diameter reduction side.
[0027]
As shown in FIGS. 4 to 9, the lower 2/3 portion of the cylindrical body 6 is fitted to the plurality of collet divided bodies 30 so as to be movable in the axial direction, and the cylindrical body 6 is It has a plurality of second tapered surfaces 6a that form a substantially regular pentagonal inner peripheral surface that tapers toward the diameter decreasing side toward the upper end and that forms a predetermined gap with the plurality of first tapered surfaces 30c.
That is, the inner peripheral surface of the upper half of the cylindrical body 6 is formed as a substantially regular pentagonal inner peripheral surface whose diameter does not change, while the inner peripheral surface of the lower half of the cylindrical body 6 has a plurality of It is formed on the inner surface of a substantially regular pentagon tapered toward the diameter reduction side toward the upper end by the two tapered surfaces 6a. Further, the outer peripheral surface of the cylindrical body 6 is formed in a cylindrical surface, and the cylindrical piston member 40 of the first hydraulic cylinder 7 is fitted on the cylindrical body 6.
[0028]
By the way, a plurality of (for example, five in each gap 34) roller members 32 roll in the axial direction of the rod 4 in the gap 34 between the plurality of sets of the first and second tapered surfaces 30c and 6a. Mounted as possible. When the cylindrical body 6 is driven downward by a first hydraulic cylinder 7 described later, the driving force of the first hydraulic cylinder 7 acts on the collet member 5 via the plurality of roller members 32, and the collet member 5 Are configured to be elastically deformed toward the diameter reduction side.
[0029]
Here, as shown in FIGS. 7 and 8, each of the roller members 32 includes two sets of first and second tapered surfaces 30 c which form one surface of the inner and outer peripheral surfaces of the regular pentagon of the collet member 5 and the cylindrical body 6. , 6a, the roller member 32 can be made sufficiently long. The plurality of roller members 32 are received from below by a roller receiving member 33 provided at a lower end portion of the tubular body 6, and the plurality of roller members 32 are further upwardly raised by the protruding portions 30 b of the collet member 5. It is regulated not to roll. As shown in FIGS. 6 to 8, a position regulating portion 30 d that regulates the circumferential position of the plurality of roller members 32 with respect to the collet member 5 is provided at the end of the collet split body 30 on the slit 30 a side in the radial direction. It is provided so as to protrude outward.
[0030]
The first hydraulic cylinder 7 has a cylinder hole 13 formed in the upper body 10, a cylindrical piston member 40 slidably fitted in the cylinder hole 13, and drives the cylindrical piston member 40 downward. An annular oil chamber 41 and the like are provided.
The cylindrical piston member 40 is formed integrally with a small-diameter cylindrical portion 40a at an upper end, a wall portion 40b extending circumferentially from a lower end of the small-diameter cylindrical portion 40a, and a large-diameter cylindrical portion 40c extending downward from the wall portion 40b. Things. The small-diameter cylindrical portion 40a is slidably fitted in the insertion hole 12 of the upper body 10, and a seal member 42 is mounted between the insertion hole 12 and the small-diameter cylindrical portion 40a. On the other hand, the large-diameter cylindrical portion 40c is slidably fitted in the cylinder hole 13, and the lower end of the large-diameter cylindrical portion 40c is inserted into an annular gap 43 formed between the upper main body 10 and the lower main body 11. The seal member 44 is also mounted between the lower main body 11 and the large-diameter cylindrical portion 40c.
[0031]
An annular oil chamber 41 is formed between the wall 40 b and the upper end of the cylinder hole 13, and a part of the hydraulic pressure supplied to the second hydraulic cylinder 9 described below is provided in the annular oil chamber 41. The oil supply can be supplied via an oil passage 45 in the main body 11, an annular gap 43, and an oil passage (not shown) formed between the cylinder hole 13 and the large-diameter cylindrical portion 40c.
[0032]
The second hydraulic cylinder 9 has a cylinder hole 15 formed in the lower main body 11, a piston member 51 slidably mounted in the cylinder hole 15, and an oil for generating a driving force for driving the piston member 51 upward. It has a chamber 52 and a coil spring 53 for urging the piston member 51 downward. The lower end of the connecting rod 21 is screwed to the upper half of the piston member 51, and the piston member 51 is connected to the rod 4 via the connecting rod 21 and the spring receiving member 20.
[0033]
An oil chamber 52 is formed below the piston member 51, and hydraulic pressure is supplied to and discharged from the oil chamber 52 with an external hydraulic pressure source (not shown). The oil chamber 52 communicates with the annular oil chamber 41 of the first hydraulic cylinder 7 via an oil passage 45, an annular gap 43, and an oil passage (not shown) between the cylinder hole 13 and the large-diameter cylindrical portion 40c. Communicating. The coil spring 53 is provided in a spring accommodating chamber 54 formed in the lower body 11, and the lower end of the coil spring 53 is in contact with the upper end of the piston member 51.
[0034]
A coil spring 8 for urging the cylindrical body 6 upward is disposed in a spring accommodating chamber 60 formed between the lower main body 11 and the cylindrical body 6. They are in contact with the spring receiving portions 11b of the main body 11, respectively. Therefore, the cylindrical body 6 is urged by the coil spring 8, and the upper end of the cylindrical body 6 abuts on the lower surface of the wall 40 b of the cylindrical piston member 40, and the cylindrical body 6 is integrated with the cylindrical piston member 40. Can be moved up and down. Then, when the hydraulic pressure is discharged from the annular oil chamber 41 of the first hydraulic cylinder 7 and the driving force of the first hydraulic cylinder 7 decreases, the coil spring 8 causes the cylindrical body 6 to resist the driving force of the first hydraulic cylinder 7. Is driven upward.
[0035]
Next, the operation of the work support 1 will be described.
As shown in FIG. 4, when the hydraulic pressure is supplied to the oil chamber 52 of the second hydraulic cylinder 9 from the state where the rod 4 is fully retracted, the driving force generated in the oil chamber 52 causes the piston member 51 to move the coil spring 53. Is driven upward against the urging force of Then, the spring receiving member 20 connected to the piston member 51 via the connecting rod 21 is also driven upward against the urging force of the coil spring 19, and the rod 4 advances upward.
[0036]
At the same time, oil pressure is also supplied from the oil chamber 52 to the annular oil chamber 41 of the first hydraulic cylinder 7 via the oil passage 45 and the annular gap 43, and the driving force of the first hydraulic cylinder generated in the annular oil chamber 41 The cylindrical piston member 40 is driven downward, and the cylindrical body 6 moves downward together with the cylindrical piston member 40 against the collet member 5 against the urging force of the coil spring 8. At this time, in the gap 34 between the first tapered surface 30c of the collet member 5 and the second tapered surface 6a of the cylindrical body 6, the first and second roller members 32 roll while moving in the axial direction. The engagement between the tapered surfaces 30c and 6a, respectively, reduces the friction between the first and second tapered surfaces 30c and 6a, and the driving force of the first hydraulic cylinder 7 is efficiently transmitted to the collet member 5, and the collet member 5 elastically deforms to the diameter reduction side. Then, the lower half of the rod 4 is securely gripped by the collet member 5 and locked in a state in which the rod 4 has advanced, and as shown in FIG. Supported by
[0037]
Conversely, as shown in FIG. 5, when the oil pressure in the oil chamber is discharged from the state in which the rod 4 is locked at the advanced position, the oil pressure is also discharged from the annular oil chamber 41 and the cylindrical body 6 and The cylindrical piston member 40 is driven upward by the urging force of the coil spring 8. Then, the force for elastically deforming the collet member 5 toward the diameter reducing side does not act, the locked state of the rod 4 is released, and the rod 4 is driven downward by the urging force of the coil spring 8 to retreat. .
[0038]
According to the work support 1 described above, the following effects can be obtained.
1) Since the collet member 5 is elastically deformed toward the diameter reducing side while rolling the plurality of roller members 32 mounted in the gap 34 between the first and second tapered surfaces 30c and 6a, the rod 4 is locked. The friction between the first and second tapered surfaces 30c and 6a can be reduced to efficiently transmit the driving force of the first hydraulic cylinder 7 to the collet member 5, and the work support 1 can be downsized. .
[0039]
In addition, the contact area between the plurality of roller members 32 and the collet member 5 is larger than when the friction between the first and second tapered surfaces 30c and 6a is reduced by using a plurality of balls. In this state, a force is transmitted from the roller member 32 to the collet member 5, a large force does not locally act on the collet member 5, and even if the work support 1 is repeatedly used for a long period of time, the first and second tapers are provided. Indentations are not easily formed on the surfaces 30c and 6a, and the durability is excellent.
[0040]
Furthermore, since each roller member 32 is mounted between two sets of first and second tapered surfaces 30c and 6a that form one surface of each of the inner and outer peripheral surfaces of the regular pentagon of the collet member 5 and the cylindrical body 6, The roller member 32 having a relatively long length can be mounted, the number of the roller members 32 can be reduced, and the assembling of the roller member 32 becomes easy.
[0041]
2) Since the tubular body 6 is fitted inside the tubular piston member 40 of the first hydraulic cylinder 7, and the tubular body 6 and the tubular piston member 40 are configured as separate members, the tubular body 6 It is easy to form a polygon inner peripheral surface with a plurality of second tapered surfaces 6a.
3) Since the roller receiving member 33 for receiving the plurality of roller members 32 from the lower end side is provided at the lower end side portion of the cylindrical body 6, the cylindrical body 6 is moved downward with respect to the collet member 5 by the first hydraulic cylinder 7. When the roller member 32 is driven to the first direction, the plurality of roller members 32 are securely engaged with the first and second tapered surfaces 30c and 6a while rolling in the gap 34 between the first and second tapered surfaces 30c and 6a. The driving force of the hydraulic cylinder 7 can be efficiently transmitted to the collet member 5.
[0042]
4) Since the collet split body 30 is provided with the position regulating portion 30d for regulating the circumferential position of the plurality of roller members 32 with respect to the collet member 5, the gap 34 between the first and second tapered surfaces 30c and 6a is provided. Since the roller member 32 can roll in the axial direction without moving in the circumferential direction, the driving force of the first hydraulic cylinder 7 can be transmitted to the collet member 5 efficiently.
[0043]
Next, modified embodiments in which various modifications are made to the above-described embodiment will be described. However, the same components as those of the above-described embodiment are denoted by the same reference numerals as those of the above-described embodiment, and the description thereof will be appropriately omitted.
1] The tubular body 6 and the tubular piston member 40 may be formed integrally. In this case, the number of parts of the work support 1 can be reduced.
2] The number of the first and second tapered surfaces 30c and 6a is not limited to five, and the outer peripheral surface of the collet member 5 and the inner peripheral surface of the cylindrical body 6 may be formed by a polygonal outer peripheral surface other than a pentagon. And may be formed on the inner peripheral surface.
[0044]
3] As shown in FIGS. 10 and 11, instead of providing the collet member 5 with the position regulating portion 30d, a plurality of position regulating members 70 for regulating the circumferential positions of the plurality of roller members 32 with respect to the collet member 5 are provided. You may. Each position regulating member 70 has a cylindrical divided body-shaped regulating portion 70a provided between the two roller members 32, and a base 70b integrally provided at a lower end of the regulating portion 70a. The position of the roller member 32 in the circumferential direction is regulated by the plurality of position regulating members 70, and the roller member 32 is not moved in the circumferential direction in the gap 34 between the first and second tapered surfaces 30c and 6a. Since the rolling can be performed in the center direction, the driving force of the first hydraulic cylinder 7 can be efficiently transmitted to the collet member 5.
[0045]
4] Contrary to the above-described embodiment, as in a work support 1B described below, a plurality of first tapered surfaces 181a of the collet member 155 form a polygonal outer peripheral surface tapered to a diameter decreasing side toward a lower end side. Alternatively, the plurality of second tapered surfaces 156a of the cylindrical body 156 may form a polygonal inner peripheral surface that tapers toward the diameter decreasing side toward the lower end.
[0046]
As shown in FIGS. 12 to 14, the work support 1 </ b> B includes a main body housing 153, a rod 154 (corresponding to a shaft member) as an output member mounted on the main body housing 153 so as to be relatively movable in the vertical direction. A collet member 155 externally fitted to the rod 154 and elastically deformable to a reduced diameter side; and a cylindrical body 156 disposed inside the main body housing 153 and externally fitted to the collet member 155 so as to be movable in the axial direction of the rod 154. A first hydraulic cylinder 157 (first driving means) for driving the cylindrical body 156 relatively upward with respect to the collet member 155; And a second hydraulic cylinder 159 for driving the rod 154 to move upward.
[0047]
The main body housing 153 has an upper main body 160 and a lower main body 161. An annular protrusion 162 projecting radially inward is formed on an upper end portion of the upper main body 160, and a rod 154 is provided inside the circular protrusion. Is inserted through the collet member 155 to form an insertion hole 163. Further, a housing hole 164 and a cylinder hole 165 of the first hydraulic cylinder 157 connected to the housing hole 164 are formed below the annular protrusion 162 inside the main body housing 153.
[0048]
The rod 154 is inserted through the insertion hole 163 of the main body housing 153 via the collet member 155. Inside the rod 154, a spring accommodating hole 170 is formed as in the above embodiment. The spring receiving hole 170 is provided with a coil spring 171 for urging the rod 154 upward and a spring receiving member 172 for receiving the coil spring 171 from below. The spring receiving member 172 is provided with a second hydraulic pressure. It is supported from below by a connecting rod 173 connected to the piston member 195 of the cylinder 159.
[0049]
The collet member 155 is formed by integrally forming a protruding portion 180 that protrudes horizontally outward in the radial direction, and a plurality (for example, 10) of collet split bodies 181 extending downward from the protruding portion 180 and arranged in the circumferential direction. is there. The protruding portion 180 is screwed into the upper end of the upper main body 160 and is engaged with the annular protruding portion 162. A dust seal 182 is mounted on a radially inner portion of the protruding portion 180. The upper ends of the plurality of collet split bodies 181 are inserted into the insertion holes 163 of the upper main body 160. On the other hand, a first tapered surface 181a is formed on an outer peripheral portion of a lower approximately 2/3 portion of the plurality of collet divided bodies 181. The plurality of first tapered surfaces 181a form a substantially regular pentagonal outer peripheral surface of the collet member 155 that is tapered toward the diameter decreasing side toward the lower end side.
[0050]
The cylindrical body 156 is externally movably fitted to the plurality of collet divided bodies 181 in the vertical direction (axial direction of the rod 154), and is slidably mounted in the housing hole 164 of the main body housing 153. The cylindrical body 156 forms a substantially regular pentagonal inner peripheral surface that is tapered toward the diameter decreasing side toward the lower end side, and also forms a plurality of second gaps 184 between the plurality of first tapered surfaces 181a. It has a tapered surface 156a.
[0051]
Similarly to the above-described embodiment, a plurality of (for example, five in each gap 184) roller members 185 are provided in the gap 184 between the plurality of sets of the first and second tapered surfaces 181a and 156a, respectively. It is mounted so that it can roll in the direction of the center. As shown in FIGS. 12 and 14, a projection 156b is provided at the upper end of the cylindrical body 156 so as to project radially inward (toward the axis of the rod 154). The plurality of roller members 185 are prevented from moving upward with respect to the cylindrical body 156 any more. Further, the plurality of roller members 185 are received from below by a roller receiving member 186 below the tubular body 156, and the roller receiving member 186 is urged upward by a coil spring 187.
[0052]
The first hydraulic cylinder 157 generates a cylinder hole 165 formed in the upper body 160, a piston member 190 slidably mounted in the cylinder hole 165, and a driving force for driving the piston member 190 upward. An oil chamber 191 and the like are provided. The piston member 190 is slidably fitted to the cylindrical portion 161 a of the lower main body 161, and the upper end of the piston member 190 is in contact with the lower end of the cylindrical body 156. An oil chamber 191 is formed below the piston member 190.
[0053]
A coil spring 158 for urging the cylindrical body 156 downward is provided between the annular projecting portion 162 of the upper main body 160 and the upper end of the cylindrical body 156.
The second hydraulic cylinder 159 includes a piston member 195, an oil chamber 196 that generates a driving force for driving the piston member 195 upward, and the like. The oil chamber 196 of the second hydraulic cylinder 159 communicates with the oil chamber 191 of the first hydraulic cylinder 157 via an oil passage 197.
[0054]
Next, the operation of the work support 1B will be described.
As shown in FIG. 12, when the hydraulic pressure is supplied to the oil chamber 196 of the second hydraulic cylinder 159 from the state where the rod 154 is fully retracted, the piston member 195 is moved upward by the driving force generated in the oil chamber 196. Driven. Then, the spring receiving member 172 connected to the piston member 195 via the connecting rod 173 is also driven upward, so that the rod 154 advances upward.
[0055]
At the same time, oil pressure is also supplied from the oil chamber 196 to the oil chamber 191 of the first hydraulic cylinder 157 via the oil passage 197, and the cylindrical body 156 is moved upward by the driving force of the first hydraulic cylinder 157 generated in the oil chamber 191. Driven to At this time, in the gap 184 between the first tapered surface 181a of the collet member 155 and the second tapered surface 156a of the tubular body 156, the first and second roller members 185 roll in the axial direction while rotating. The engagement between the first and second tapered surfaces 181a and 156a reduces the friction between the first and second tapered surfaces 181a and 156a, and the driving force of the first hydraulic cylinder 157 is efficiently transmitted to the collet member 155. 155 is elastically deformed toward the diameter reduction side. Then, the lower half portion of the rod 154 is securely held by the collet member 155, and is locked in a state where the rod 154 is advanced, so that the work 2 is supported by the rod 154 from below as shown in FIG.
[0056]
Conversely, as shown in FIG. 14, when the oil pressure in the oil chamber 191 of the first hydraulic cylinder 157 is discharged from the state where the rod 154 is locked at the advanced position, the cylindrical body 156 is attached with the coil spring 158. It is driven downward by the force. Then, the force for elastically deforming the collet member 155 toward the diameter reducing side does not act, the locked state of the rod 154 is released, and the rod 154 is driven downward by the urging force of the coil spring 158, and the rod 154 is retracted. .
[0057]
According to the work support 1B, substantially the same effects as in the above embodiment can be obtained.
That is, since the collet member 155 is elastically deformed to the diameter reducing side while the plurality of roller members 185 mounted in the gap 184 between the first and second tapered surfaces 181a and 156a are rolled, the rod 154 is locked. The friction between the first and second tapered surfaces 181a and 156a can be reduced to efficiently transmit the driving force of the first hydraulic cylinder 157 to the collet member 155, and the work support 1B can be downsized. .
[0058]
Further, the contact area between the plurality of roller members 185 and the collet member 155 is larger than in the case where the friction between the first and second tapered surfaces 181a and 156a is reduced using a plurality of balls. In this state, a force is transmitted from the roller member 185 to the collet member 155, a large force is not locally applied to the collet member 155, and the first and second tapers are used even when the work support 1B is used repeatedly for a long period of time. Indentations are less likely to be formed on the surfaces 181a and 156a, and the durability is excellent.
[0059]
5] As shown in FIG. 15, the present invention can be applied to a lock device 80 for locking a shaft member 84 such as a workpiece formed in a long shaft shape at an intermediate portion thereof. The main body housing 83 of the lock device 80 has an upper main body 90 and a lower main body 91, and the upper main body 90 and the lower main body 91 are formed with insertion holes 92 and 93 for inserting the shaft member 84, respectively. . In a state where the shaft member 84 is inserted through the insertion holes 92 and 93 and the shaft member 84 is attached to the main body housing 83 in a penetrating manner, the collet member 5 that can be elastically deformed to the diameter reducing side is fitted to the shaft member 84. Have been. Further, a cylindrical body 6 fitted to the collet member 5 so as to be movable in the axial direction is also provided in the main body housing 83.
[0060]
The collet member 5 and the cylindrical body 6 have substantially the same configuration as that of the embodiment shown in FIGS. That is, the collet member 5 is provided with five first tapered surfaces 30c that form a substantially regular pentagonal outer peripheral surface, and the cylindrical body 6 is provided with five second tapered surfaces that form a substantially regular pentagonal inner peripheral surface. A surface 6a is provided. A plurality of (for example, five) roller members 32 that can roll in the axial direction of the shaft member 84 are mounted in the gaps 34 between the first and second tapered surfaces 30c and 6a of each set. .
[0061]
Further, the lock device 80 is also provided with a hydraulic cylinder 87 for driving the collet member 5 downward. The hydraulic cylinder 87 is provided slidably in a cylinder hole 94 of the main body housing 83 and has a cylindrical piston member 40 fitted outside the cylindrical body, and a driving force for driving the cylindrical piston member 40 downward. And an annular oil chamber 41 to be generated. The annular oil chamber 41 is connected to an external hydraulic pressure supply (not shown) via an oil passage 95 and an annular gap 96. Further, a coil spring 88 for driving the collet member 5 upward is also provided.
[0062]
When hydraulic pressure is supplied to the annular oil chamber 41 of the hydraulic cylinder 87, the cylindrical piston member 40 is driven downward by the driving force generated in the annular oil chamber 41, and the cylindrical body 6 is also coiled together with the cylindrical piston member 40. It moves downward against the urging force of 88. At this time, in the gap 34 between the first tapered surface 30c of the collet member 5 and the second tapered surface 6a of the cylindrical body 6, the first and second roller members 32 roll while moving in the axial direction. The engagement between the first and second tapered surfaces 30c and 6a reduces the friction between the first and second tapered surfaces 30c and 6a, so that the driving force of the hydraulic cylinder 87 is efficiently transmitted to the collet member 5, and the collet member 5 is It elastically deforms to the diameter reduction side. Then, the shaft member 4 is securely held and locked by the collet member 5.
[0063]
6] In addition, it goes without saying that the present invention can be applied to a lock device that locks various shaft members, such as a tool fixing device that fixes a tool for machining to a main shaft or the like, or a clamp device that fixes an axial work. .
[0064]
Next, another embodiment of the present invention will be described. This alternative embodiment is an example in which the present invention is applied to a lock device for locking a tubular member that locks a tubular member such as a cylindrical work.
As shown in FIGS. 16 and 17, the lock device 100 includes a main body housing 103 that is internally fitted into a cylindrical member 104 such as a cylindrical work, and a locking device 100 that is internally fitted into the cylindrical member 104 and elastically deforms toward the enlarged diameter side. A possible collet member 105, a piston member 106 disposed in the main body housing 103 and fitted inside the collet member 105 so as to be movable in the axial direction, and the piston member 106 is moved upward relative to the collet member 105. The lock device 100 has a hydraulic cylinder 107 that drives the piston member 106 downward and a coil spring 108 that drives the piston member 106 downward relative to the collet member 105. The lock is releasably locked to the main body housing 103.
[0065]
The main body housing 103 includes an upper main body 110 and a lower main body 111 fixed to a lower end of the upper main body 110. The upper body 110 has an upper flange 110a and a shaft 110b extending downward from the flange 110a. A lower body 111 is externally fitted to a lower end of the shaft 110b. The lower body 111 is fixed. A cylindrical portion 111a is formed in the upper half of the lower body 111, and a cylinder hole 113 of the hydraulic cylinder 107 is formed inside the cylindrical portion 111a. The outer diameter of the flange 110a of the upper main body 110 and the outer diameter of the lower main body 111 are formed to have the same diameter.
[0066]
As shown in FIGS. 16 to 18, the collet member 105 is mounted between the flange 110 a of the upper main body 110 and the cylindrical portion 111 a of the lower main body 111, and the collet member 105 is formed by the flange 110 a and the cylindrical portion 111 a. Are restricted from moving in the vertical direction. The outer diameter of the collet member 105 is formed to be substantially the same as the outer diameter of the flange 110a of the upper main body 110 and the outer diameter of the lower main body 111, and the tubular member 104 is fitted in the tubular member 104 like the main body housing 103. .
[0067]
The collet member 105 has a plurality of (for example, 10) collet divided bodies 120 arranged in the circumferential direction, and a plurality of slits 120a are formed between the plurality of collet divided bodies 120, respectively. The collet member 105 is configured to be elastically deformable toward the enlarged diameter side. At the lower ends of the plurality of collet divided bodies 120, projecting portions 120b projecting radially inward are formed, and at the inner surface of the plurality of collet divided bodies 120, first tapered surfaces 120c are formed, respectively. I have. Then, as shown in FIG. 18, the inner peripheral surface of the upper half of the collet member 105 is formed on the inner peripheral surface of a substantially regular pentagon whose diameter does not change, and the inner peripheral surface of the lower half of the collet member 105 has A plurality of first tapered surfaces 120c form a substantially regular pentagonal outer peripheral surface that is tapered toward the diameter reduction side toward the upper end.
[0068]
The piston member 106 is slidably fitted to a middle part in the vertical direction of the shaft portion 110a of the upper main body 110. Further, approximately two-thirds of the upper part of the piston member 106 It is fitted inside so as to be movable in the direction (vertical direction). As shown in FIG. 16, FIG. 17, and FIG. 19, the piston member 106 forms a substantially regular pentagonal outer peripheral surface that tapers toward the diameter decreasing side toward the upper end, and is formed between the plurality of first tapered surfaces 120c. It has a plurality (for example, five) of second tapered surfaces 106 a forming a predetermined gap 124. At the upper end of the piston member 106, an annular projecting portion 106b projecting inward is formed. Further, at an axial center portion of the upper end of the piston member 106, an annular spring receiving portion 106c that receives the coil spring 108 from below is also provided. Is formed.
[0069]
By the way, in the gap 124 between the plurality of sets of the first and second tapered surfaces 120c and 106a, a plurality of (for example, six in each of the gaps 124) roller members 125 roll in the axial direction of the cylindrical member 104, respectively. Mounted as possible. Then, when the piston member 106 is driven upward by the hydraulic cylinder 107 described later, the driving force of the hydraulic cylinder 107 acts on the collet member 105 via the plurality of roller members 125, and the collet member 105 is moved toward the diameter increasing side. It is configured to be elastically deformed. The plurality of roller members 125 are received from below by the protrusion 120b of the collet member 105, and the plurality of roller members 125 are regulated by the annular protrusion 106b of the piston member 106 so as not to roll upward any more. I have.
[0070]
The hydraulic cylinder 107 has a cylinder hole 113 formed in the lower body 111, an annular piston member 126 slidably fitted on the shaft portion 110 a of the upper body 110 and slidably fitted in the cylinder hole 113. And an annular oil chamber 127 formed below the annular piston member 126 to drive the annular piston member 126 upward. The upper end of the annular piston member 126 is in contact with the lower end of the piston member 106, and the piston member 106 and the annular piston member 126 are configured to be integrally movable upward. The annular oil chamber 127 is connected to an external oil pressure supply source (not shown) via a hydraulic pressure supply port 128 and an oil passage 129 formed in the lower main body 111, and can supply and discharge oil pressure to and from the annular oil chamber 127.
[0071]
A coil spring 108 for urging the piston member 106 downward is provided in a spring accommodating chamber 130 formed between the upper main body 110 and the piston member 106. The coil spring 108 is provided on a flange 110a of the upper main body 110. The lower surface is in contact with the spring receiving portion 106c of the lower body 111, respectively. Then, when the hydraulic pressure is discharged from the annular oil chamber 127 of the hydraulic cylinder 107 and the driving force of the hydraulic cylinder 107 decreases, the coil spring 108 drives the piston member 106 downward against the driving force of the hydraulic cylinder 107.
[0072]
Next, the operation and effects of the lock device 100 will be described.
As shown in FIG. 16, when the cylinder member 104 is externally fitted to the main body housing 103 and then hydraulic pressure is supplied to the annular oil chamber 127 of the hydraulic cylinder 107, the annular piston member 126 is driven by the driving force generated in the annular oil chamber 127. It is driven upward against the urging force of the coil spring 108. Then, as shown in FIG. 17, the piston member 106 is also driven upward together with the annular piston member 126.
[0073]
At this time, in the gap 124 between the first tapered surface 120c of the collet member 105 and the second tapered surface 106a of the piston member 106, the plurality of roller members 125 are rolled in the axial direction while the first and second tapered surfaces. Since the first and second tapered surfaces 120c and 106a are engaged with the surfaces 120c and 106a, respectively, the friction between the first and second tapered surfaces 120c and 106a is reduced, and the driving force of the hydraulic cylinder 107 is efficiently transmitted to the collet member 105. It elastically deforms to the enlarged side. Then, the plurality of collet divided bodies 120 come into close contact with the inner peripheral surface of the tubular member 104, and the tubular member 104 is locked.
[0074]
Conversely, as shown in FIG. 17, when the oil pressure in the annular oil chamber 127 is discharged from the state where the tubular member 104 is locked, the piston member 106 and the annular piston member 126 are moved downward by the urging force of the coil spring 108. Driven to Then, the force for elastically deforming the collet member 105 toward the diameter-enlarged side is not applied, and the locked state of the tubular member 104 is released.
[0075]
According to the lock device 100, since the contact area between the plurality of roller members 125 and the collet member 105 is large, a large force is not locally applied to the collet member 105, and the lock device 100 is operated for a long period of time. Even when used repeatedly, the first and second tapered surfaces 120c and 106a are less likely to have indentations, and are excellent in durability. In addition, substantially the same effects as in the above embodiment can be obtained.
[0076]
According to the first aspect of the present invention, the plurality of roller members mounted in the gap between the first and second tapered surfaces are rolled, and the collet member is elastically deformed to the diameter reducing side while the shaft is rotated. Since the member is locked, the friction between the first and second tapered surfaces can be reduced and the driving force of the first driving means can be efficiently transmitted to the collet member, and the locking device can be downsized. become. Further, the contact area between the plurality of roller members and the collet member becomes relatively large, and a force is transmitted from the roller member to the collet member in a line contact state, so that a large force does not locally act on the collet member, Even if the lock device is used for a long period of time, the first and second tapered surfaces are less likely to have indentations, and thus have excellent durability.
[0077]
Further, a polygonal outer peripheral surface is formed on the collet member by the plurality of first tapered surfaces, and a polygonal inner peripheral surface is formed on the cylindrical body by the plurality of second tapered surfaces. And a roller member having a relatively long length can be mounted because the roller member is mounted in a gap between the first and second tapered surfaces that form one surface of the polygonal inner and outer peripheral surfaces of the cylindrical body. The number can be reduced, and the assembly of the roller members becomes easy.
[0078]
According to the second aspect of the present invention, at least one of the first and second driving means has a fluid pressure cylinder disposed in the main body housing, so that the cylindrical body is moved by the fluid pressure cylinder with respect to the collet member. By driving relatively to one end side or the other end side, the shaft member can be reliably brought into the locked state or the unlocked state.
[0079]
According to the third aspect of the present invention, the first driving means has a fluid pressure cylinder, and the fluid pressure cylinder is slidably disposed in the main body housing and fitted to the tubular body. Since the piston member is provided, by moving the cylindrical piston member of the fluid pressure cylinder to the other end, the cylindrical body is also moved to the other end together with the cylindrical piston member, and the collet member is moved through the plurality of roller members. Can be elastically deformed toward the diameter reduction side. Further, by forming the cylindrical body and the cylindrical piston member as separate members, it becomes easy to form a polygonal inner peripheral surface with a plurality of second tapered surfaces in the cylindrical body.
[0080]
According to the fourth aspect of the present invention, since the second driving means has the compression spring member for driving the cylindrical body to one end side against the driving force of the fluid pressure cylinder, the first drive is performed by the compression spring member. The locked state of the shaft member can be released by driving the cylindrical body to one end side against the driving force of the fluid pressure cylinder of the means.
[0081]
According to the invention of claim 5, since the roller receiving member for receiving the plurality of roller members from the other end side is provided at the other end side portion of the cylindrical body, the cylindrical body is colleted by the first drive means. When the roller member is driven to the other end side, the plurality of roller members roll into the gap between the first and second tapered surfaces and securely engage with the first and second tapered surfaces. The driving force of the first driving means can be efficiently transmitted to the collet member.
[0082]
According to the sixth aspect of the present invention, since the position regulating portion for regulating the circumferential position of the plurality of roller members with respect to the collet member is provided, the roller member is arranged in the circumferential direction in the gap between the first and second tapered surfaces. Since the roller can be rolled in the axial direction without moving, the driving force of the first driving means can be efficiently transmitted to the collet member.
According to the seventh aspect of the invention, substantially the same effects as those of the first aspect of the invention can be obtained, and the description thereof is omitted.
[0083]
According to the invention of claim 8, the cylindrical member is locked by elastically deforming the collet member toward the diameter increasing side while rolling the plurality of roller members mounted in the gap between the first and second tapered surfaces. The friction between the first and second tapered surfaces can be reduced, the driving force of the first driving means can be efficiently transmitted to the collet member, and the locking device can be downsized. Further, since the contact area between the plurality of roller members and the collet member is relatively large, a large force is not locally applied to the collet member, and even if the lock device is used for a long period of time, the first and second lock members are used. Indentations are less likely to be formed on the tapered surface of No. 2, resulting in excellent durability.
[0084]
Furthermore, a polygonal inner peripheral surface is formed on the collet member by the plurality of first tapered surfaces, and a polygonal outer peripheral surface is formed on the piston member by the plurality of second tapered surfaces. Since the piston member is mounted in the gap between the first and second tapered surfaces that form one surface of each of the polygon inner and outer peripheral surfaces, a relatively long roller member can be mounted, and the number of roller members can be reduced. It can be reduced, and the assembly of the roller member becomes easy.
[Brief description of the drawings]
FIG. 1 is a configuration diagram of a work support and peripheral devices according to an embodiment of the present invention.
FIG. 2 is a front view of a work support.
FIG. 3 is a plan view of a work support.
FIG. 4 is a sectional view taken along line IV-IV of the work support in a rod retracted state.
FIG. 5 is a diagram corresponding to FIG. 4 of a work support in a work supporting state.
FIG. 6 is a sectional view taken along line VI-VI of FIG. 4;
FIG. 7 is a sectional view taken along line VII-VII of FIG. 4;
FIG. 8 is a perspective view of a collet member and a roller member.
FIG. 9 is a perspective view of a tubular body.
FIG. 10 is a diagram corresponding to FIG. 7 of a modified embodiment.
FIG. 11 is a perspective view of a position regulating member.
FIG. 12 is a diagram corresponding to FIG. 4 of a modified embodiment.
FIG. 13 is a sectional view taken along line XIII-XIII in FIG. 12;
FIG. 14 is a diagram corresponding to FIG. 5 of a modified embodiment.
FIG. 15 is a diagram corresponding to FIG. 4 of a modified embodiment.
FIG. 16 is a diagram corresponding to FIG. 4 of another embodiment.
FIG. 17 is a diagram corresponding to FIG. 5 of another embodiment.
FIG. 18 is a perspective view of a collet member according to another embodiment as viewed from below.
FIG. 19 is a perspective view of a piston member and a roller member according to another embodiment.
[Explanation of symbols]
1,1A, 1B Work support
3 Body housing
4 rod
5 Collet material
6 cylindrical body
6a Second tapered surface
7 First hydraulic cylinder
8 coil spring
9 Second hydraulic cylinder
12 insertion hole
30c 1st taper surface
30d Position regulation unit
32 roller member
33 Roller receiving member
34 gap
40 cylindrical piston member
70 Position regulating member
80 Locking device
83 Body housing
84 Shaft member
87 hydraulic cylinder
88 coil spring
100 locking device
103 Body housing
104 tube member
105 collet member
106 Piston member
106a 2nd taper surface
107 hydraulic cylinder
108 coil spring
120c 1st taper surface
124 gap
125 Roller member
153 Body housing
154 rod
155 collet member
156 cylindrical body
156a 2nd taper surface
157 1st hydraulic cylinder
158 Coil spring
159 Second hydraulic cylinder
181a First tapered surface
184 gap
185 Roller member

Claims

A lock device that locks a shaft member inserted into an insertion hole formed in a main body housing so as to be unlockable to the main body housing,
A collet member externally fitted to the shaft member and having a plurality of first tapered surfaces forming a polygonal outer peripheral surface tapered toward the diameter reducing side toward one end side and elastically deformable toward the diameter reducing side;
The collet member has a polygonal inner peripheral surface which is fitted to the collet member so as to be movable in the axial direction, and is tapered toward the diameter decreasing side toward one end, and a predetermined gap is formed between the collet member and the plurality of first tapered surfaces. A cylindrical body having a plurality of second tapered surfaces,
A plurality of roller members rotatably mounted in a gap between the plurality of sets of first and second tapered surfaces in the axial direction of the shaft member;
First driving means for driving the cylindrical body toward the other end relative to the collet member;
Second driving means for driving the cylindrical body toward one end relative to the collet member,
When the cylindrical body is driven to the other end by the first driving means, the collet member is elastically deformed toward the diameter reducing side via a plurality of roller members, and the shaft member is locked. Locking device.

The locking device according to claim 1, wherein at least one of the first and second driving means includes a fluid pressure cylinder disposed in a main body housing.

The first driving means has a fluid pressure cylinder, and the fluid pressure cylinder has a cylindrical piston member slidably disposed in the main body housing and fitted to the cylindrical body. The locking device for locking a shaft member according to claim 2.

The lock device for locking a shaft member according to claim 3, wherein the second driving means includes a compression spring member that drives the cylindrical body to one end side against a driving force of a fluid pressure cylinder.

The lock for locking a shaft member according to any one of claims 1 to 4, wherein a roller receiving member that receives the plurality of roller members from the other end side is provided at the other end portion of the tubular body. apparatus.

The lock device for locking a shaft member according to any one of claims 1 to 5, further comprising a position regulating portion that regulates a circumferential position of the plurality of roller members with respect to the collet member.

A lock device that has a main body housing and a shaft member mounted on the main body housing so as to be relatively movable in the axial direction, and locks the shaft member to the main body housing so as to be unlockable.
A collet member externally fitted to the shaft member and having a plurality of first tapered surfaces forming a polygonal outer peripheral surface tapered toward the diameter reducing side toward one end side and elastically deformable toward the diameter reducing side;
The collet member has a polygonal inner peripheral surface which is fitted to the collet member so as to be movable in the axial direction, and is tapered toward the diameter decreasing side toward one end, and a predetermined gap is formed between the collet member and the plurality of first tapered surfaces. A cylindrical body having a plurality of second tapered surfaces,
A plurality of roller members rotatably mounted in a gap between the plurality of sets of first and second tapered surfaces in the axial direction of the shaft member;
First driving means for driving the cylindrical body toward the other end relative to the collet member;
Second driving means for driving the cylindrical body toward one end relative to the collet member,
When the cylindrical body is driven to the other end by the first driving means, the collet member is elastically deformed toward the diameter reducing side via a plurality of roller members, and the shaft member is locked. Locking device.

In a lock device for locking a tubular member externally fitted to a main body housing to a main body housing so as to be unlocked,
A collet member which has a plurality of first tapered surfaces forming a polygonal inner peripheral surface which is internally fitted into the cylindrical member and which is tapered toward the diameter reducing side toward one end side, and which is elastically deformable toward the diameter increasing side;
The collet member has a polygonal outer peripheral surface which is movably fitted in the axial direction and is tapered toward the diameter decreasing side toward one end, and a predetermined gap is formed between the collet member and the plurality of first tapered surfaces. A piston member having a plurality of second tapered surfaces;
A plurality of roller members rotatably mounted in the gap between the plurality of first and second tapered surfaces in the axial direction of the cylindrical member;
First driving means for driving the piston member toward one end relative to the collet member;
Second driving means for driving the piston member toward the other end relative to the collet member,
A lock device for locking a cylinder member, wherein the collet member is elastically deformed toward a diameter-enlarged side via a plurality of roller members when the piston member is driven to one end side by the first driving means. .