JP5314940B2

JP5314940B2 - Rotating tool clutch device

Info

Publication number: JP5314940B2
Application number: JP2008151734A
Authority: JP
Inventors: 博樹中島; 宏志栗林; 金子　　豊
Original assignee: 株式会社アルプスツール
Priority date: 2008-06-10
Filing date: 2008-06-10
Publication date: 2013-10-16
Anticipated expiration: 2028-06-10
Also published as: JP2009297795A

Abstract

<P>PROBLEM TO BE SOLVED: To reduce vibration caused by a clutch device of a rotary tool. <P>SOLUTION: The clutch device of the rotary tool includes a tenon shape projection 8 on either of a driving shaft 5 of a machine tool or a transmission shaft 4 of the rotary tool 3a, and a groove 7 in which the projection is fitted on the other shaft. Spring sections 19a, 19b are formed by thinning and forming an insertion hole 19 on either or both of the projection side or/and a groove side, and the spring sections are elastically deformed in a roughly perpendicular direction to the fitting surfaces when fitting the projection in the groove. This eliminates a gap between the driving shaft and the transmission shaft, thus preventing vibration, noise, and the like. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、旋盤等に使用される回転工具のクラッチ装置に関する。 The present invention relates to a clutch device for a rotary tool used in a lathe or the like.

図２１に示すように、旋盤のターレット１には刃物２を保持した回転工具３が複数個取り付けられる。各回転工具３の伝動軸４はターレット１の中心部に向かって突出し、ターレット１の中心部には回転工具３の伝動軸４に動力を伝達する駆動軸５が設けられる。回転工具３の伝動軸４は旋盤本体側の駆動軸５にクラッチ装置６を介して動力的に係脱可能である。 As shown in FIG. 21, a plurality of rotating tools 3 holding a cutter 2 are attached to a turret 1 of a lathe. The transmission shaft 4 of each rotary tool 3 protrudes toward the center of the turret 1, and a drive shaft 5 that transmits power to the transmission shaft 4 of the rotary tool 3 is provided at the center of the turret 1. The transmission shaft 4 of the rotary tool 3 can be engaged and disengaged dynamically with a drive shaft 5 on the lathe body side via a clutch device 6.

このクラッチ装置６は、図２１に示すように、旋盤の駆動軸５の先端に形成された溝７と、回転工具３における伝動軸４の先端に形成されたほぞ状の突起８とを有し、ターレット１が旋回して所望の回転工具３の突起８が駆動軸５の溝７に嵌まり込むことにより、この回転工具３が駆動軸５に動力的に連結される。駆動軸５の回転は溝７と突起８との係合により伝動軸４に伝達され、かさ歯車９ａ，９ｂ等の伝動機構を介して刃物２に伝達される。この刃物２の回転により図示しないワークに所定の加工が行われる。他の刃物を使用する場合は、駆動軸５が停止状態になったところでターレット１が旋回し、前回の回転工具３における突起８が駆動軸５の溝７から離脱し、次回の回転工具における突起８が駆動軸５の溝７内に嵌まり込み、この回転工具が駆動軸５に動力的に連結される。そして、溝７と突起８との係合により駆動軸５の回転が伝動軸４に伝達され、かさ歯車９ａ，９ｂ等の伝動機構を介して刃物２に伝達される。この刃物２によりワークに対し他の加工が行われる。 As shown in FIG. 21, the clutch device 6 has a groove 7 formed at the tip of the drive shaft 5 of the lathe and a tenon-like protrusion 8 formed at the tip of the transmission shaft 4 in the rotary tool 3. When the turret 1 turns and the projection 8 of the desired rotary tool 3 fits into the groove 7 of the drive shaft 5, the rotary tool 3 is motively connected to the drive shaft 5. The rotation of the drive shaft 5 is transmitted to the transmission shaft 4 by the engagement between the groove 7 and the protrusion 8, and is transmitted to the blade 2 through a transmission mechanism such as bevel gears 9a and 9b. Predetermined processing is performed on the workpiece (not shown) by the rotation of the blade 2. When using another blade, the turret 1 turns when the drive shaft 5 is stopped, and the projection 8 on the previous rotary tool 3 separates from the groove 7 on the drive shaft 5, and the projection on the next rotary tool. 8 is fitted in the groove 7 of the drive shaft 5, and the rotary tool is motively connected to the drive shaft 5. Then, the rotation of the drive shaft 5 is transmitted to the transmission shaft 4 by the engagement of the groove 7 and the protrusion 8, and is transmitted to the blade 2 through a transmission mechanism such as bevel gears 9a and 9b. The cutting tool 2 performs other processing on the workpiece.

図２１に示すように、クラッチ装置における溝７と突起８との間には両者の係合、離脱を円滑に行うため隙間δが形成される。ところが、この隙間δの存在のため、工作中振動が発生する場合がある。また、かさ歯車９ａ，９ｂのバックラッシとクラッチ装置６の隙間δによる二重の振動でさらに大きな振動が発生する場合がある。この振動は騒音、発熱、磨耗、加工精度の低下の原因となる。 As shown in FIG. 21, a gap δ is formed between the groove 7 and the protrusion 8 in the clutch device in order to smoothly engage and disengage them. However, due to the presence of this gap δ, vibration during machining may occur. Further, there may be a case where a larger vibration is generated by the double vibration caused by the backlash of the bevel gears 9 a and 9 b and the gap δ of the clutch device 6. This vibration causes noise, heat generation, wear, and deterioration of processing accuracy.

従来、このような不具合を解消するために、クラッチ装置における溝７と突起８との間の隙間にゴム等の弾性体を介在させることが試みられている（例えば、特許文献１参照。）。 Conventionally, in order to solve such a problem, an attempt has been made to interpose an elastic body such as rubber in a gap between the groove 7 and the protrusion 8 in the clutch device (see, for example, Patent Document 1).

特開２００６−７４０１号公報JP 2006-7401 A

ところが、ゴム等の弾性体は損傷を受けやすく、磨耗しやすく、取り付け箇所から脱落しやすく、また、耐油性に欠けるという問題がある。また、ターレットが旋回する際に、ターレットの環状溝内を伝動軸の突起がスライドするが、そのとき突起に取り付けられたゴム等の弾性体と環状溝との間に摩擦力が生じやすく、突起が環状溝内を円滑にスライドし難いという問題がある。さらに、ゴムは加工精度が低く寸法精度が良くないので、突起と溝との間の隙間を埋めるための寸法管理が難しいという問題がある。さらに、ゴム等の弾性体を別途用意しなければならないので、部品点数が増え、組み付け工数が増えるという問題がある。 However, there are problems that elastic bodies such as rubber are easily damaged, are easily worn out, easily fall off from the mounting location, and lack oil resistance. Also, when the turret turns, the transmission shaft projection slides in the annular groove of the turret. At that time, a frictional force is easily generated between the elastic body such as rubber attached to the projection and the annular groove. However, there is a problem that it is difficult to smoothly slide in the annular groove. Further, since rubber has low processing accuracy and poor dimensional accuracy, there is a problem that it is difficult to manage the size to fill the gap between the protrusion and the groove. Furthermore, since an elastic body such as rubber has to be prepared separately, there is a problem that the number of parts increases and the number of assembling steps increases.

従って、本発明は上記問題点を解決する手段を提供することを目的とする。 Accordingly, an object of the present invention is to provide means for solving the above-mentioned problems.

上記課題を解決するため、本発明は次のような構成を採用する。 In order to solve the above problems, the present invention employs the following configuration.

すなわち、請求項１に係る発明は、工作機械の駆動軸（５）と回転工具（３ａ，３ｂ）の伝動軸（４）とのいずれか一方にほぞ状の突起（８）を有し、他方に上記突起（８）が係脱可能に嵌まり込む溝（７）を有した回転工具のクラッチ装置において、上記溝（７）が上記駆動軸（５）又は上記伝動軸（４）を横断するように形成されることによって上記駆動軸側（５）又は上記伝動軸（４）側にバネ部（１９ａ，１９ｂ）が形成され、上記突起（８）と上記溝（７）との係合時にそれらの係合面（７ａ，７ｂ，８ａ，８ｂ）に対し略垂直方向に上記バネ部（１９ａ，１９ｂ）が弾性変形するようにし、上記溝（７）の幅より太い貫通孔（１９）が溝底に沿って上記駆動軸（５）又は上記伝動軸（４）を横断するように形成されたことを特徴とする。 In other words, the invention according to claim 1 has a tenon-like projection (8) on one of the drive shaft (5) of the machine tool and the transmission shaft (4) of the rotary tool (3a, 3b). In the clutch device of the rotary tool having a groove (7) into which the protrusion (8) is detachably fitted, the groove (7) crosses the drive shaft (5) or the transmission shaft (4). As a result, spring portions (19a, 19b) are formed on the drive shaft side (5) or the transmission shaft (4) side, and when the projection (8) and the groove (7) are engaged. The spring portions (19a, 19b) are elastically deformed in a direction substantially perpendicular to the engaging surfaces (7a, 7b, 8a, 8b), and a through hole (19) thicker than the width of the groove (7) is formed. characterized in that along the groove bottom is formed so as to cross the drive shaft (5) or the transmission shaft (4) To.

また、請求項２に記載されるように、請求項１に記載の回転工具のクラッチ装置において、上記突起（８）が上記係合面（８ａ，８ｂ）に平行に延びるすり割り（２０）で除肉されることによって、上記突起（８）側にバネ部（２０ａ，２０ｂ）が形成されたものとすることができる。 Further, as described in claim 2 , in the clutch device for a rotary tool according to claim 1, the protrusion (8) is a slot (20) extending in parallel with the engagement surface (8a, 8b). By removing the thickness, the spring portions (20a, 20b) can be formed on the protrusion (8) side.

また、請求項３に記載されるように、請求項１に記載の回転工具のクラッチ装置において、上記突起（８）の係合面（８ａ，８ｂ）に凸状湾曲面が形成され、上記駆動軸（５）又は上記伝動軸（４）の軸心に平行に上記凸状湾曲面を掠めるように伸びる縦穴（２１）によって上記突起（８）が除肉されることにより、上記突起（８）側にバネ部（２１ａ，２１ｂ）が形成されたものとすることができる。 According to a third aspect of the present invention, in the rotary tool clutch device according to the first aspect, a convex curved surface is formed on the engagement surface (8a, 8b) of the protrusion (8), and the driving is performed. The protrusion (8) is thinned by the vertical hole (21) extending so as to give up the convex curved surface in parallel to the axis of the shaft (5) or the transmission shaft (4), thereby the protrusion (8). Spring portions (21a, 21b) may be formed on the side.

また、請求項４に記載されるように、請求項１に記載の回転工具のクラッチ装置において、上記突起（８）の両端近傍における両係合面（８ａ，８ｂ）に凸状湾曲面が形成され、上記駆動軸（５）又は上記伝動軸（４）の軸心に平行に上記凸状湾曲面を掠めるように伸びる縦穴（２３）によって上記突起（８）の両端が除肉され、上記駆動軸（５）又は上記伝動軸（４）の軸心に垂直に上記縦穴（２３）を横断するように伸びる横すり割り（２４）によって上記突起（８）の両端が除肉されることにより、上記突起（８）の両端にバネ部（２２）が形成されたものとすることができる。 According to a fourth aspect of the present invention, in the clutch device for a rotary tool according to the first aspect, convex curved surfaces are formed on both engaging surfaces (8a, 8b) in the vicinity of both ends of the protrusion (8). Both ends of the protrusion (8) are thinned by vertical holes (23) extending so as to give up the convex curved surface parallel to the axis of the drive shaft (5) or the transmission shaft (4), and the drive Both ends of the protrusion (8) are thinned by a horizontal slit (24) extending so as to cross the vertical hole (23) perpendicular to the axis of the shaft (5) or the transmission shaft (4), Spring portions (22) may be formed at both ends of the protrusion (8).

また、請求項５に記載されるように、請求項４に記載の回転工具のクラッチ装置において、上記縦穴（２３）と上記横すり割り（２４）とで上記突起（８）の両端に形成されたリング部が縦すり割り（２５）によって除肉されることにより、上記突起（８）の両端にバネ部（２２）が形成されたものとすることができる。 According to a fifth aspect of the present invention, in the clutch device for a rotary tool according to the fourth aspect , the vertical hole (23) and the horizontal slit (24) are formed at both ends of the protrusion (8). Since the ring portion is thinned by the vertical slit (25), the spring portions (22) can be formed at both ends of the protrusion (8).

本発明によれば、工作機械の駆動軸（５）と回転工具（３ａ，３ｂ）の伝動軸（４）とのいずれか一方にほぞ状の突起（８）を有し、他方に上記突起（８）が係脱可能に嵌まり込む溝（７）を有した回転工具のクラッチ装置において、上記溝（７）が上記駆動軸（５）又は上記伝動軸（４）を横断するように形成されることによって上記駆動軸側（５）又は上記伝動軸（４）側にバネ部（１９ａ，１９ｂ）が形成され、上記突起（８）と上記溝（７）との係合時にそれらの係合面（７ａ，７ｂ，８ａ，８ｂ）に対し略垂直方向に上記バネ部（１９ａ，１９ｂ）が弾性変形するようにし、上記溝（７）の幅より太い貫通孔（１９）が溝底に沿って上記駆動軸（５）又は上記伝動軸（４）を横断するように形成されたことから、突起（８）と溝（７）との間の隙間を埋める手段として、従来のゴム等の弾性体を用いるのではなくて、突起（８）側と溝（７）側の金属等の構成材料を弾性体として利用することとなり、従って、摩擦力等の外力や油に対する耐久性に優れ、また、締め代（γ）の寸法管理も容易に行うことができるクラッチとすることができる。その結果、旋盤等の工作機械の駆動軸（５）の回転が回転工具（３ａ，３ｂ）の伝動軸（４）に滑らかに伝達され、振動、騒音、発熱、磨耗等が低減し、加工精度が向上する。また、ターレット（１）が旋回する際に、伝動軸（４）が円滑にスライドし、回転工具（３ａ，３ｂ）の移動が滑らかになるという利点がある。さらに、ゴム等の弾性体の部品を用意する必要がないので、部品点数が減り、組み付け工数が減るという利点がある。 According to the present invention, a tenon-like projection (8) is provided on one of the drive shaft (5) of the machine tool and the transmission shaft (4) of the rotary tool (3a, 3b), and the projection ( In the clutch device of the rotary tool having a groove (7) in which 8) is detachably fitted, the groove (7) is formed so as to cross the drive shaft (5) or the transmission shaft (4). As a result, spring portions (19a, 19b) are formed on the drive shaft side (5) or the transmission shaft (4) side, and when the projection (8) and the groove (7) are engaged, they are engaged. The spring portions (19a, 19b) are elastically deformed in a direction substantially perpendicular to the surfaces (7a, 7b, 8a, 8b), and a through hole (19) wider than the width of the groove (7) extends along the groove bottom. from what has been formed so as to cross the drive shaft (5) or the transmission shaft (4) Te, the projections (8) grooves ( Instead of using a conventional elastic body such as rubber as a means for filling the gap between the metal and the like, a constituent material such as a metal on the protrusion (8) side and the groove (7) side is used as the elastic body. Therefore, it is possible to provide a clutch that is excellent in durability against external force such as frictional force and oil, and that can easily manage the dimension of the fastening allowance (γ). As a result, the rotation of the drive shaft (5) of a machine tool such as a lathe is smoothly transmitted to the transmission shaft (4) of the rotary tools (3a, 3b), reducing vibration, noise, heat generation, wear, etc., and machining accuracy Will improve. Moreover, when a turret (1) turns, there exists an advantage that a transmission shaft (4) slides smoothly and the movement of a rotary tool (3a, 3b) becomes smooth. Further, since there is no need to prepare elastic parts such as rubber, there is an advantage that the number of parts is reduced and the number of assembling steps is reduced.

以下、図面を参照して発明を実施するための最良の形態について説明する。 The best mode for carrying out the invention will be described below with reference to the drawings.

＜実施の形態１＞
図１及び図２に示すように、工作機械である旋盤のターレット１の周壁部には、複数個の回転工具３ａ，３ｂが取り付けられている。ターレット１はその中心軸１０を中心にして旋回可能である。ターレット１の旋回に伴い周壁部上の所望の回転工具３ａ又は３ｂが図示しないワークに対して接近し又は離反する。ターレット１内にはその中心軸１０から周壁部に向かって駆動軸５が設けられ、旋盤の図示しない駆動源からの動力がこの駆動軸５に伝達される。また、ターレット１の中央部には旋盤本体側に固定されるガイドレール１１が環状に配置される。駆動軸５の終端がこのガイドレール１１の一部に形成された図１に示す切欠部１１ａ内に入り込んでいる。 <Embodiment 1>
As shown in FIGS. 1 and 2, a plurality of rotary tools 3a and 3b are attached to a peripheral wall portion of a turret 1 of a lathe that is a machine tool. The turret 1 can turn around its central axis 10. As the turret 1 turns, a desired rotary tool 3a or 3b on the peripheral wall approaches or separates from a workpiece (not shown). A drive shaft 5 is provided in the turret 1 from the central shaft 10 toward the peripheral wall portion, and power from a drive source (not shown) of the lathe is transmitted to the drive shaft 5. A guide rail 11 fixed to the lathe body side is annularly arranged at the center of the turret 1. The end of the drive shaft 5 enters a notch 11a formed in a part of the guide rail 11 shown in FIG.

回転工具３ａ，３ｂは、上記ターレット１に固定されるハウジング１２を備える。図１中、符号１３はハウジング１２をターレット１に固定するためのボルトを示す。ハウジング１２内には、図２に示すように、上記駆動軸５に動力的に連結可能な伝動軸４が各種ベアリング１４を介し回転自在に支持される。伝動軸４の始端はハウジング１２外に突出し、上記ガイドレール１１に向かって伸びる。伝動軸４の終端は伝動機構であるかさ歯車９ａ，９ｂを介して出力軸であるスピンドル１５に動力的に連結される。スピンドル１５は伝動軸４に直交する方向に配置され、ハウジング１２に対し各種ベアリング１６を介し回転自在に支持される。スピンドル１５にはコレットチャック１７が取り付けられ、コレットチャック１７に着脱自在に把持された刃物２がハウジング１２の側面から突出する。 The rotary tools 3 a and 3 b include a housing 12 that is fixed to the turret 1. In FIG. 1, reference numeral 13 denotes a bolt for fixing the housing 12 to the turret 1. As shown in FIG. 2, the transmission shaft 4 that can be connected to the drive shaft 5 is movably supported in the housing 12 via various bearings 14. The starting end of the transmission shaft 4 projects out of the housing 12 and extends toward the guide rail 11. The terminal end of the transmission shaft 4 is motively connected to a spindle 15 which is an output shaft via bevel gears 9a and 9b which are transmission mechanisms. The spindle 15 is disposed in a direction orthogonal to the transmission shaft 4 and is rotatably supported on the housing 12 via various bearings 16. A collet chuck 17 is attached to the spindle 15, and the blade 2 detachably held by the collet chuck 17 projects from the side surface of the housing 12.

なお、スピンドル１５を省略し、伝動軸４にコレットチャック１７、刃物２等を装着するようにしてもよい。 The spindle 15 may be omitted, and the collet chuck 17 and the blade 2 may be attached to the transmission shaft 4.

図１及び図２に示すように、旋盤側の駆動軸５に回転工具３ａ，３ｂの伝動軸４を動力的に接続したり切り離したりするためのクラッチ装置１８が設けられる。 As shown in FIGS. 1 and 2, a clutch device 18 is provided for connecting and disconnecting the transmission shaft 4 of the rotary tools 3a and 3b to and from the drive shaft 5 on the lathe side.

このクラッチ装置１８は、図４乃至図８に示すように、伝動軸４の始端に形成されたほぞ状の突起８と、駆動軸５の終端に形成された上記突起８が係脱可能に嵌まり込む溝７とを具備する。ほぞ状の突起８は伝動軸４の軸端にその直径方向に伸びる板片として形成される。また、溝７は駆動軸５の軸端にその直径方向に伸びるように形成される。 As shown in FIGS. 4 to 8, the clutch device 18 has a tenon-like projection 8 formed at the start end of the transmission shaft 4 and the projection 8 formed at the end of the drive shaft 5 detachably fitted. And a groove 7 to be fitted. The tenon-like projection 8 is formed at the shaft end of the transmission shaft 4 as a plate piece extending in the diameter direction. The groove 7 is formed at the shaft end of the drive shaft 5 so as to extend in the diameter direction.

図４乃至図８に示すように、ほぞ状の突起８には二つの平坦な係合面８ａ，８ｂが平行に形成され、溝７には突起８の係合面の８ａ，８ｂに対向する係合面７ａ，７ｂが形成される。 As shown in FIGS. 4 to 8, the tenon-like protrusion 8 is formed with two flat engaging surfaces 8 a and 8 b in parallel, and the groove 7 faces the engaging surfaces 8 a and 8 b of the protrusion 8. Engagement surfaces 7a and 7b are formed.

図１及び図３に示すように、全回転工具３ａ，３ｂにおける伝動軸４の突起８は上記ターレット１内のガイドレール１１の環状溝１１ｂ内に嵌まり込んでいる。このためターレット１が旋回する際、伝動軸４の突起８は常に一定の姿勢を保って移動する。一方、駆動
軸５は回転を停止する際、その溝７が上記ガイドレール１１内の伝動軸４の突起８に合致しうる向きになるよう制御される。駆動軸５が停止し、ターレット１が旋回すると、全回転工具３ａ，３ｂの伝動軸４がガイドレール１１の環状溝１１ｂ内をスライドし、図１及び図２に示すように、所望の回転工具３ａが駆動軸５の終端に到達したところで、この回転工具３ａの突起８が駆動軸５の溝７内に嵌まり込む。 As shown in FIGS. 1 and 3, the projection 8 of the transmission shaft 4 in all the rotary tools 3 a and 3 b is fitted in the annular groove 11 b of the guide rail 11 in the turret 1. For this reason, when the turret 1 turns, the protrusion 8 of the transmission shaft 4 always moves in a constant posture. On the other hand, when the rotation of the drive shaft 5 is stopped, the groove 7 is controlled so that the groove 7 can be aligned with the projection 8 of the transmission shaft 4 in the guide rail 11. When the drive shaft 5 stops and the turret 1 turns, the transmission shaft 4 of all the rotary tools 3a, 3b slides in the annular groove 11b of the guide rail 11, and as shown in FIGS. When 3 a reaches the end of the drive shaft 5, the protrusion 8 of the rotary tool 3 a is fitted into the groove 7 of the drive shaft 5.

図２１に示したように、クラッチ装置６における溝７と突起８との間には両者の係合、離脱を円滑に行うため隙間δが形成され、この隙間δの存在のため工作中振動が発生する場合があるが、これを防止するためこの実施の形態１のクラッチ装置１８では、図４、図５及び図６に示すように、上記溝７側に除肉によってバネ部１９ａ，１９ｂが形成され、上記突起８と上記溝７との係合時にそれらの係合面８ａ，８ｂに対し図５中、矢印ａで示す方向にこのバネ部１９ａ，１９ｂが弾性変形するようになっている。 As shown in FIG. 21, a gap δ is formed between the groove 7 and the protrusion 8 in the clutch device 6 in order to smoothly engage and disengage the both. In order to prevent this, in the clutch device 18 according to the first embodiment, as shown in FIGS. 4, 5 and 6, the spring portions 19a and 19b are formed on the groove 7 side by thinning. When the projection 8 and the groove 7 are engaged, the spring portions 19a and 19b are elastically deformed in the direction indicated by the arrow a in FIG. .

上記除肉は上記溝７の幅より太い貫通孔１９が溝７の底を抉るように駆動軸５を横断することによって行われる。これにより、上記溝７側すなわち駆動軸５の終端に二片の板バネ状のバネ部１９ａ，１９ｂが形成される。 The thinning is performed by traversing the drive shaft 5 so that a through hole 19 wider than the width of the groove 7 covers the bottom of the groove 7. As a result, two pieces of leaf springs 19a and 19b are formed on the groove 7 side, that is, at the end of the drive shaft 5.

また、図５に示すように、突起８はその幅すなわち二つの平坦な係合面８ａ，８ｂ間の距離がＷ＋γとなるように形成され、溝７の幅すなわち二つの平坦な係合面７ａ，７ｂ間の距離はＷとなるように形成される。このγが突起と溝との間の締め代となる。駆動軸５と伝動軸４は各々棒状の金属材料で構成され、溝７や突起８は金属材料を切削加工等することにより切り出され、それらの係合面７ａ，７ｂ，８ａ，８ｂは高度の寸法精度で平滑に仕上げられる。 Further, as shown in FIG. 5, the protrusion 8 is formed so that the width thereof, that is, the distance between the two flat engaging surfaces 8a and 8b is W + γ, and the width of the groove 7, that is, the two flat engaging surfaces 7a. , 7b is formed to be W. This γ becomes a fastening allowance between the protrusion and the groove. The drive shaft 5 and the transmission shaft 4 are each made of a rod-like metal material, and the grooves 7 and the protrusions 8 are cut out by cutting the metal material, and their engaging surfaces 7a, 7b, 8a, 8b are highly sophisticated. Smooth finish with dimensional accuracy.

さらに、図６及び図７に示すように、突起８と溝７との係脱方向における各係合面７ａ，７ｂ，８ａ，８ｂの端縁には、両者の係合を容易にするためのガイド面７ｃ，８ｃが面取り等によって形成される。 Further, as shown in FIGS. 6 and 7, the end edges of the engagement surfaces 7a, 7b, 8a, 8b in the engagement / disengagement direction of the protrusion 8 and the groove 7 are for facilitating the engagement between the two. Guide surfaces 7c and 8c are formed by chamfering or the like.

これにより、図４に示すように伝動軸４の突起８はガイド面７ｃ，８ｃの案内によって駆動軸５の溝７内に円滑に入り込み、また、入り込みながら駆動軸５のバネ部１９ａ，１９ｂを押し広げる。その結果、バネ部１９ａ，１９ｂの弾性力によって溝７の係合面７ａ，７ｂが突起８の係合面８ａ，８ｂに接触し、従来生じていた隙間δが解消される。 As a result, as shown in FIG. 4, the projection 8 of the transmission shaft 4 smoothly enters the groove 7 of the drive shaft 5 by the guide surfaces 7c and 8c, and the spring portions 19a and 19b of the drive shaft 5 are inserted while entering. Push out. As a result, the engaging surfaces 7a and 7b of the groove 7 come into contact with the engaging surfaces 8a and 8b of the protrusion 8 by the elastic force of the spring portions 19a and 19b, and the gap δ that has been generated conventionally is eliminated.

次に、上記構成のクラッチ装置の作用について説明する。 Next, the operation of the clutch device configured as described above will be described.

図１及び図２に示すように、加工に使用する回転工具３ａの伝動軸４の突起８が駆動軸５の溝７内に嵌まり込み、他の回転工具３ｂにおける伝動軸４の突起８はターレット１内のガイドレール１１の環状溝１１ｂ内に嵌まり込んでいる。 As shown in FIGS. 1 and 2, the projection 8 of the transmission shaft 4 of the rotary tool 3a used for machining fits into the groove 7 of the drive shaft 5, and the projection 8 of the transmission shaft 4 of the other rotary tool 3b is The guide rail 11 in the turret 1 is fitted in the annular groove 11 b.

所定の加工が終了すると、駆動軸５及び伝動軸４が回転を停止する。その際、両軸５，４の溝７と突起８はガイドレール１１の切欠部１１ａ内において環状溝１１ｂに合致する向きで停止する。 When the predetermined machining is completed, the drive shaft 5 and the transmission shaft 4 stop rotating. At that time, the grooves 7 and the protrusions 8 of the shafts 5 and 4 are stopped in a direction matching the annular groove 11b in the notch portion 11a of the guide rail 11.

ターレット１が旋回を開始し、前回の加工に携わった回転工具３ａにおける伝動軸４の突起８が駆動軸５の溝７から離脱してガイドレール１１の環状溝１１ｂ内に嵌まり込む。また、次回の加工に携わる回転工具３ｂの伝動軸４の突起８がガイドレール１１の環状溝１１ｂ内をスライドし、この環状溝１１ｂから離脱して駆動軸５の溝７内に嵌まり込むと、ターレット１が停止する。 The turret 1 starts to turn, and the projection 8 of the transmission shaft 4 in the rotary tool 3a engaged in the previous machining is detached from the groove 7 of the drive shaft 5 and fitted into the annular groove 11b of the guide rail 11. Further, when the projection 8 of the transmission shaft 4 of the rotary tool 3b engaged in the next machining slides in the annular groove 11b of the guide rail 11 and is detached from the annular groove 11b and fitted into the groove 7 of the drive shaft 5. The turret 1 stops.

ターレット１の旋回によって、図４に示すように、回転工具３ｂの伝動軸４の突起８が駆動軸５の溝７内に入り込もうとすると、駆動軸５のバネ部１９ａ，１９ｂが上記締め代γ分だけ弾性的に拡開し、その溝７の係合面７ａ，７ｂが突起８の係合面８ａ，８ｂに接触する。突起８が溝７内に完全に入り込むと、両者の係合面８ａ，８ｂ，７ａ，７ｂ同士が接触し、駆動軸５に対し回転工具３ｂの伝動軸４が動力的に連結されることになる。 When the projection 8 of the transmission shaft 4 of the rotary tool 3b tries to enter the groove 7 of the drive shaft 5 by turning the turret 1 as shown in FIG. The engagement surface 7a, 7b of the groove 7 comes into contact with the engagement surface 8a, 8b of the protrusion 8. When the protrusion 8 completely enters the groove 7, the engagement surfaces 8 a, 8 b, 7 a, 7 b come into contact with each other, and the transmission shaft 4 of the rotary tool 3 b is dynamically connected to the drive shaft 5. Become.

その後、駆動軸５が回転すると、動力がクラッチ装置１８、伝動軸４、かさ歯車９ａ，９ｂ、スピンドル１５を介し刃物２に伝達され、刃物２が図示しないワークに対して所望の加工を行う。 Thereafter, when the drive shaft 5 rotates, power is transmitted to the blade 2 through the clutch device 18, the transmission shaft 4, the bevel gears 9a and 9b, and the spindle 15, and the blade 2 performs desired machining on a workpiece (not shown).

駆動軸５と伝動軸４の回転中、溝７の係合面７ａ，７ｂが突起８の係合面８ａ，８ｂにバネ部１９ａ，１９ｂの弾性変形による弾性力によって接触していることから、駆動軸５の回転が回転工具３ｂの伝動軸４に滑らかに伝達される。その結果、回転工具等の振動、騒音等が低減し、加工精度が向上する。 Since the engagement surfaces 7a and 7b of the groove 7 are in contact with the engagement surfaces 8a and 8b of the protrusion 8 by elastic force due to elastic deformation of the spring portions 19a and 19b during rotation of the drive shaft 5 and the transmission shaft 4, The rotation of the drive shaft 5 is smoothly transmitted to the transmission shaft 4 of the rotary tool 3b. As a result, vibration, noise, etc. of the rotary tool are reduced, and machining accuracy is improved.

＜実施の形態２＞
図９乃至図１２に示すように、この実施の形態２のクラッチ装置１８において、伝動軸４側に突起８が形成され、駆動軸５側に溝７が形成されるが、突起８がその係合面８ａ，８ｂに平行に延びるすり割り２０で除肉されることによって、突起８側にバネ部２０ａ，２０ｂが形成される。 <Embodiment 2>
As shown in FIGS. 9 to 12, in the clutch device 18 according to the second embodiment, the protrusion 8 is formed on the transmission shaft 4 side and the groove 7 is formed on the drive shaft 5 side. Spring parts 20a and 20b are formed on the projection 8 side by being thinned by a slit 20 extending parallel to the mating surfaces 8a and 8b.

ターレット１の旋回によって、図９に示すように、回転工具３ｂの駆動軸５の溝７内に伝動軸４の突起８が入り込もうとすると、突起８側のバネ部２０ａ，２０ｂが図１０に示した締め代γ分だけ矢印ｂの方向に弾性的に縮小して、溝７の係合面７ａ，７ｂが突起８の係合面８ａ，８ｂに接触する。突起８が溝７内に完全に入り込むと、両者の係合面８ａ，８ｂ，７ａ，７ｂ同士が接触し、駆動軸５に対し回転工具３ｂの伝動軸４が動力的に連結されることになる。 If the projection 8 of the transmission shaft 4 enters the groove 7 of the drive shaft 5 of the rotary tool 3b by turning the turret 1, the spring portions 20a and 20b on the projection 8 side are shown in FIG. The engagement surfaces 7a and 7b of the groove 7 are brought into contact with the engagement surfaces 8a and 8b of the protrusion 8 by elastic reduction in the direction of the arrow b by the tightening allowance γ. When the protrusion 8 completely enters the groove 7, the engagement surfaces 8 a, 8 b, 7 a, 7 b come into contact with each other, and the transmission shaft 4 of the rotary tool 3 b is dynamically connected to the drive shaft 5. Become.

その後、駆動軸５が回転すると、実施の形態１の場合と同様にして、動力がクラッチ装置１８、伝動軸４、かさ歯車９ａ，９ｂ、スピンドル１５を介し刃物２に伝達され、刃物２が図示しないワークに対して所望の加工を行う。 Thereafter, when the drive shaft 5 rotates, the power is transmitted to the blade 2 through the clutch device 18, the transmission shaft 4, the bevel gears 9a and 9b, and the spindle 15 in the same manner as in the first embodiment, and the blade 2 is illustrated. The desired machining is performed on the workpiece that does not.

駆動軸５と伝動軸４の回転中、溝７の係合面７ａ，７ｂに突起８の係合面８ａ，８ｂがバネ部２０ａ，２０ｂの弾性変形による弾性力によって接触していることから、駆動軸５の回転が回転工具３ｂの伝動軸４に滑らかに伝達される。その結果、振動、騒音等が低減し、加工精度が向上する。 During the rotation of the drive shaft 5 and the transmission shaft 4, the engagement surfaces 8 a and 8 b of the protrusion 8 are in contact with the engagement surfaces 7 a and 7 b of the groove 7 by the elastic force due to the elastic deformation of the spring portions 20 a and 20 b. The rotation of the drive shaft 5 is smoothly transmitted to the transmission shaft 4 of the rotary tool 3b. As a result, vibration, noise, etc. are reduced, and machining accuracy is improved.

その他、この実施の形態２において実施の形態１と同じ部分には同一の符号を付して示し、詳細な説明を省略する。 In addition, in this Embodiment 2, the same part as Embodiment 1 is attached | subjected and shown, and detailed description is abbreviate | omitted.

＜実施の形態３＞
図１３乃至図１５に示すように、この実施の形態３におけるクラッチ装置１８において、伝動軸４側に突起８が形成され、駆動軸５側に溝７が形成されるが、突起８の両端の係合面８ａ，８ｂにそれぞれ凸状湾曲面が形成され、伝動軸４の軸心に平行に伸びる縦穴２１が、凸状湾曲面を掠めるように突起８の両端にそれぞれ穿設されることにより、突起８の両端にバネ部２１ａ，２１ｂが形成される。 <Embodiment 3>
As shown in FIGS. 13 to 15, in the clutch device 18 according to the third embodiment, the protrusion 8 is formed on the transmission shaft 4 side and the groove 7 is formed on the drive shaft 5 side. A convex curved surface is formed on each of the engaging surfaces 8a and 8b, and vertical holes 21 extending parallel to the axis of the transmission shaft 4 are formed at both ends of the protrusion 8 so as to give up the convex curved surface. The spring portions 21 a and 21 b are formed at both ends of the protrusion 8.

より具体的には、突起８の両端近傍において両係合面８ａ，８ｂに跨るように凸状湾曲面が形成される。突起８の両端には凸状湾曲面が略円筒形になって現れ、一つの縦穴２１が一方の凸状湾曲面と一方の係合面８ａとの間に薄肉部が形成されるように穿設され、もう一つの縦穴２１が他方の凸状湾曲面と他方の係合面８ｂとの間に薄肉部が形成されるように穿設される。このように縦穴２１，２１により突起８から除肉されることによって、図１５に示すように、各係合面８ａ，８ｂに薄肉のバネ部２１ａ，２１ｂが形成される。このバネ部２１ａ，２１ｂを挟む係合面８ａ，８ｂ間の距離は、溝７の幅がＷであるのに対しＷ＋γとされる。バネ部２１ａ，２１ｂは締め代γ分程度弾性的に圧縮可能である。 More specifically, a convex curved surface is formed so as to straddle both engaging surfaces 8a and 8b in the vicinity of both ends of the protrusion 8. At both ends of the protrusion 8, convex curved surfaces appear in a substantially cylindrical shape, and one vertical hole 21 is drilled so that a thin portion is formed between one convex curved surface and one engaging surface 8 a. Another vertical hole 21 is formed so that a thin portion is formed between the other convex curved surface and the other engagement surface 8b. Thus, by thinning from the protrusion 8 by the vertical holes 21 and 21, thin spring portions 21a and 21b are formed on the engaging surfaces 8a and 8b, respectively, as shown in FIG. The distance between the engagement surfaces 8a and 8b sandwiching the spring portions 21a and 21b is W + γ while the width of the groove 7 is W. The spring portions 21a and 21b can be elastically compressed by an amount of interference γ.

ターレット１の旋回によって、図１３に示すように、回転工具３ｂの駆動軸５の溝７内に伝動軸４の突起８が入り込もうとすると、突起８側のバネ部２１ａ，２１ｂが図１５に示した締め代γ分だけ弾性的に圧縮され、溝７の係合面７ａ，７ｂが突起８の係合面８ａ，８ｂに接触する。突起８が溝７内に完全に入り込むと、両者の係合面７ａ，７ｂ，８ａ，８ｂ同士が接触し、駆動軸５に対し回転工具３ｂの伝動軸４が動力的に連結されることになる。 When the projection 8 of the transmission shaft 4 tries to enter the groove 7 of the drive shaft 5 of the rotary tool 3b by turning the turret 1, the spring portions 21a and 21b on the projection 8 side are shown in FIG. The engagement surface 7a, 7b of the groove 7 comes into contact with the engagement surface 8a, 8b of the protrusion 8 by being elastically compressed by the tightening allowance γ. When the protrusion 8 completely enters the groove 7, the engaging surfaces 7 a, 7 b, 8 a, and 8 b come into contact with each other, and the transmission shaft 4 of the rotary tool 3 b is dynamically connected to the drive shaft 5. Become.

駆動軸５と伝動軸４の回転中、溝７の係合面７ａ，７ｂに突起８の係合面８ａ，８ｂがバネ部２１ａ，２１ｂの弾性変形による弾性力によって接触していることから、駆動軸５の回転が回転工具３ｂの伝動軸４に滑らかに伝達される。その結果、振動、騒音等が低減し、加工精度が向上する。 During the rotation of the drive shaft 5 and the transmission shaft 4, the engaging surfaces 8a and 8b of the protrusion 8 are in contact with the engaging surfaces 7a and 7b of the groove 7 by the elastic force due to the elastic deformation of the spring portions 21a and 21b. The rotation of the drive shaft 5 is smoothly transmitted to the transmission shaft 4 of the rotary tool 3b. As a result, vibration, noise, etc. are reduced, and machining accuracy is improved.

その他、この実施の形態３において実施の形態１，２と同じ部分には同一の符号を付して示し、詳細な説明を省略する。 In the third embodiment, the same parts as those in the first and second embodiments are denoted by the same reference numerals, and detailed description thereof is omitted.

＜実施の形態４＞
図１６乃至図１８に示すように、この実施の形態４のクラッチ装置１８において、伝動軸４側に突起８が形成され、駆動軸５側に溝７が形成されるが、突起８の両端の両係合面８ａ，８ｂ上であって突起８の先端側に各々バネ部２２が形成される。 <Embodiment 4>
As shown in FIGS. 16 to 18, in the clutch device 18 according to the fourth embodiment, the protrusion 8 is formed on the transmission shaft 4 side and the groove 7 is formed on the drive shaft 5 side. A spring portion 22 is formed on each of the engaging surfaces 8a and 8b on the tip end side of the protrusion 8 respectively.

より具体的には、図１６（Ｂ）に示すように、突起８の両端近傍における両係合面８ａ，８ｂに凸状湾曲面が形成され、伝動軸４の軸心に平行に伸びる縦穴２３が、凸状湾曲面を掠めるように突起８の両端にそれぞれ穿設され、伝動軸４の軸心に垂直な横すり割り２４が縦穴２３を横断するように突起８の両端に穿設される。さらに、縦穴２３と横すり割り２４とで突起８の両端に切り出されたリング部分が縦すり割り２５によって分断される。図１６（Ｂ）中、符号２３ａ，２４ａ，２５ａは、それぞれ縦穴２３、横すり割り２４、縦すり割り２５による除肉部分を示す。 More specifically, as shown in FIG. 16 (B), convex curved surfaces are formed on both engaging surfaces 8 a and 8 b in the vicinity of both ends of the protrusion 8, and the vertical hole 23 extends parallel to the axis of the transmission shaft 4. However, a slit 24 perpendicular to the axis of the transmission shaft 4 is drilled at both ends of the projection 8 so as to cross the vertical hole 23 so as to give up the convex curved surface. . Further, the ring portion cut out at both ends of the protrusion 8 by the vertical hole 23 and the horizontal slot 24 is divided by the vertical slot 25. In FIG. 16B, reference numerals 23 a, 24 a, and 25 a indicate thinned portions by the vertical hole 23, the horizontal slot 24, and the vertical slot 25, respectively.

これらの縦穴２３、横すり割り２４及び縦すり割り２５によって突起８が除肉されることにより、図１７に示すように、突起８の両端上部に各係合面８ａ，８ｂ側に突出する薄肉のバネ部２２が形成される。このバネ部２２を挟む係合面８ａ，８ｂ間の距離は溝７の幅がＷであるのに対しＷ＋γとされる。バネ部２２は締め代γ分程度弾性的に圧縮可能である。 When the projection 8 is thinned by the vertical hole 23, the horizontal slot 24, and the vertical slot 25, as shown in FIG. 17, the thin wall projecting toward the engaging surfaces 8a and 8b at the upper ends of both ends of the projection 8 is provided. The spring portion 22 is formed. The distance between the engagement surfaces 8a and 8b sandwiching the spring portion 22 is W + γ while the width of the groove 7 is W. The spring portion 22 can be elastically compressed by an amount of fastening margin γ.

なお、上記縦穴２３と横すり割り２４とで突起８の両端に切り出されたリング部分に対する上記縦すり割り２５の形成は省略してもよく、リング形のままバネ部として機能させることも可能である。 In addition, the formation of the vertical slit 25 for the ring portion cut out at both ends of the projection 8 by the vertical hole 23 and the horizontal slot 24 may be omitted, and it is possible to function as a spring portion while maintaining the ring shape. is there.

ターレット１の旋回によって、図１６（Ａ）に示すように、回転工具３ｂの駆動軸５の溝７内に伝動軸４の突起８が入り込もうとすると、突起８側のバネ部２２が図１７に示した締め代γ分だけ弾性的に圧縮され、溝７の係合面７ａ，７ｂに突起８の係合面８ａ，８ｂが接触する。突起８が溝７内に完全に入り込むと、両者の係合面７ａ，７ｂ，８ａ，８ｂ同士が接触し、駆動軸５に対し回転工具３ｂの伝動軸４が動力的に連結されることになる。 When the projection 8 of the transmission shaft 4 tries to enter the groove 7 of the drive shaft 5 of the rotary tool 3b by turning the turret 1, as shown in FIG. The engagement surface 8a and 8b of the projection 8 are brought into contact with the engagement surfaces 7a and 7b of the groove 7 by being elastically compressed by the shown fastening allowance γ. When the protrusion 8 completely enters the groove 7, the engaging surfaces 7 a, 7 b, 8 a, and 8 b come into contact with each other, and the transmission shaft 4 of the rotary tool 3 b is dynamically connected to the drive shaft 5. Become.

その後、駆動軸５が回転すると、実施の形態１の場合と同様に、動力がクラッチ装置１８、伝動軸４、かさ歯車９ａ，９ｂ、スピンドル１５を介し刃物２に伝達され、刃物２が図示しないワークに対して所望の加工を行う。 Thereafter, when the drive shaft 5 rotates, the power is transmitted to the blade 2 through the clutch device 18, the transmission shaft 4, the bevel gears 9a and 9b, and the spindle 15 as in the first embodiment, and the blade 2 is not shown. Perform desired machining on the workpiece.

駆動軸５と伝動軸４の回転中、溝７の係合面７ａ，７ｂに突起８のバネ部２２が弾性変形による弾性力によって接触していることから、駆動軸５の回転が回転工具３ｂの伝動軸４に滑らかに伝達される。その結果、振動、騒音等が低減し、加工精度が向上する。 While the drive shaft 5 and the transmission shaft 4 are rotating, the spring portion 22 of the protrusion 8 is in contact with the engaging surfaces 7a and 7b of the groove 7 by elastic force due to elastic deformation, so that the rotation of the drive shaft 5 is rotated by the rotary tool 3b. The transmission shaft 4 is smoothly transmitted. As a result, vibration, noise, etc. are reduced, and machining accuracy is improved.

その他、この実施の形態４において実施の形態１〜３と同じ部分には同一の符号を付して示し、詳細な説明を省略する。 In the fourth embodiment, the same parts as those in the first to third embodiments are denoted by the same reference numerals, and detailed description thereof is omitted.

＜実施の形態５＞
図１９乃至図２０に示すように、この実施の形態５におけるクラッチ装置においても、駆動軸５側に溝７が形成され、伝動軸４側に突起８が形成される。 <Embodiment 5>
As shown in FIGS. 19 to 20, also in the clutch device according to the fifth embodiment, the groove 7 is formed on the drive shaft 5 side, and the protrusion 8 is formed on the transmission shaft 4 side.

しかし、この実施の形態５では、実施の形態２と同様にして、突起８の係合面８ａ，８ｂに平行に延びるすり割り２６によって突起８から除肉されることにより、突起８にバネ部２６ａ，２６ｂが形成され、さらに、実施の形態１と同様にして、駆動軸５の溝７側にも、二片のバネ部１９ａ，１９ｂが形成される。 However, in the fifth embodiment, in the same manner as in the second embodiment, the protrusions 8 are removed from the protrusions 8 by the slits 26 extending in parallel with the engaging surfaces 8a and 8b of the protrusions 8, so that the spring portions are formed on the protrusions 8. 26a and 26b are formed, and two pieces of spring portions 19a and 19b are also formed on the groove 7 side of the drive shaft 5 as in the first embodiment.

突起８と溝７との係合時に、それらの係合面８ａ，８ｂ，７ａ，７ｂに対し図１９中、矢印ａ，ｂで示す略垂直方向に、バネ部１９ａ，１９ｂ，２６ａ，２６ｂが各々弾性変形することになる。 When the protrusion 8 and the groove 7 are engaged, the spring portions 19a, 19b, 26a, 26b are arranged in a substantially vertical direction indicated by arrows a, b in FIG. 19 with respect to the engaging surfaces 8a, 8b, 7a, 7b. Each will be elastically deformed.

ターレット１の旋回によって、回転工具３ｂの駆動軸５の溝７内に伝動軸４の突起８が入り込もうとすると、突起８側のバネ部２６ａ，２６ｂが図１９に示した締め代γの一部だけ弾性的に圧縮され、また、溝側のバネ部１９ａ，１９ｂも締め代γの残部だけ弾性的に拡開し、溝７の係合面７ａ，７ｂが突起８の係合面８ａ，８ｂに接触する。突起８が溝７内に完全に入り込むと、両者の係合面７ａ，７ｂ，８ａ，８ｂ同士が接触し、駆動軸５に対し回転工具３ｂの伝動軸４が動力的に連結されることになる。 When the projection 8 of the transmission shaft 4 tries to enter the groove 7 of the drive shaft 5 of the rotary tool 3b by turning the turret 1, the spring portions 26a and 26b on the projection 8 side are part of the tightening margin γ shown in FIG. The groove-side spring portions 19a and 19b are also elastically expanded only by the remaining portion of the interference γ, and the engagement surfaces 7a and 7b of the groove 7 are engaged with the engagement surfaces 8a and 8b of the protrusion 8. To touch. When the protrusion 8 completely enters the groove 7, the engaging surfaces 7 a, 7 b, 8 a, and 8 b come into contact with each other, and the transmission shaft 4 of the rotary tool 3 b is dynamically connected to the drive shaft 5. Become.

駆動軸５と伝動軸４の回転中、溝７の係合面７ａ，７ｂに突起８の係合面８ａ，８ｂが、バネ部８ａ，８ｂ，１９ａ，１９ｂの弾性変形による弾性力によって接触していることから、駆動軸５の回転が回転工具３ｂの伝動軸４に滑らかに伝達される。その結果、振動、騒音等が低減し、加工精度が向上する。 During the rotation of the drive shaft 5 and the transmission shaft 4, the engagement surfaces 8a and 8b of the protrusion 8 are brought into contact with the engagement surfaces 7a and 7b of the groove 7 by the elastic force due to the elastic deformation of the spring portions 8a, 8b, 19a and 19b. Therefore, the rotation of the drive shaft 5 is smoothly transmitted to the transmission shaft 4 of the rotary tool 3b. As a result, vibration, noise, etc. are reduced, and machining accuracy is improved.

その他、この実施の形態５において実施の形態１〜４と同じ部分には同一の符号を付して示し、詳細な説明を省略する。 In the fifth embodiment, the same parts as those in the first to fourth embodiments are denoted by the same reference numerals, and detailed description thereof is omitted.

なお、本発明は上記実施の形態１〜５に限定されるものではなく、本発明の要旨の範囲内において種々変更可能である。例えば、実施の形態１〜５では、突起が伝動軸側に設けられ、溝が駆動軸側に設けられるが、溝を伝動軸側に設け、突起を駆動軸側に設けるようにすることも可能である。 In addition, this invention is not limited to the said Embodiment 1-5, A various change is possible within the range of the summary of this invention. For example, in the first to fifth embodiments, the protrusion is provided on the transmission shaft side and the groove is provided on the drive shaft side. However, the groove may be provided on the transmission shaft side and the protrusion may be provided on the drive shaft side. It is.

本発明の実施の形態１に係るクラッチ装置を備えた旋盤の要部を示す立面図である。It is an elevation view which shows the principal part of the lathe provided with the clutch apparatus which concerns on Embodiment 1 of this invention. 図１中、ＩＩ−ＩＩ線矢視断面図である。FIG. 2 is a cross-sectional view taken along line II-II in FIG. 図１中、ＩＩＩ−ＩＩＩ線矢視断面図である。FIG. 3 is a cross-sectional view taken along line III-III in FIG. 1. 図２中、ＩＶ部分の斜視図である。FIG. 4 is a perspective view of a portion IV in FIG. 2. 図４中、クラッチ装置の突起と溝とを分離して示す正面図である。FIG. 5 is a front view showing a protrusion and a groove of the clutch device separately in FIG. 4. 駆動軸の先端の平面図である。It is a top view of the front-end | tip of a drive shaft. 伝動軸の先端の平面図である。It is a top view of the front-end | tip of a transmission shaft. 伝動軸の先端の正面図である。It is a front view of the front-end | tip of a transmission shaft. 本発明の実施の形態２に係るクラッチ装置を示す斜視図である。It is a perspective view which shows the clutch apparatus which concerns on Embodiment 2 of this invention. クラッチ装置の突起と溝とを分離して示す正面図である。It is a front view which isolate | separates and shows the protrusion and groove | channel of a clutch apparatus. 伝動軸の先端の平面図である。It is a top view of the front-end | tip of a transmission shaft. 駆動軸の先端の平面図である。It is a top view of the front-end | tip of a drive shaft. 本発明の実施の形態３に係るクラッチ装置を示す斜視図である。It is a perspective view which shows the clutch apparatus which concerns on Embodiment 3 of this invention. クラッチ装置の突起と溝とを分離して示す正面図である。It is a front view which isolate | separates and shows the protrusion and groove | channel of a clutch apparatus. 伝動軸の先端の平面図である。It is a top view of the front-end | tip of a transmission shaft. （Ａ）は本発明の実施の形態４に係るクラッチ装置を示す斜視図、（Ｂ）はバネ部の形成過程を示す斜視図である。(A) is a perspective view which shows the clutch apparatus which concerns on Embodiment 4 of this invention, (B) is a perspective view which shows the formation process of a spring part. クラッチ装置の突起と溝とを分離して示す正面図である。It is a front view which isolate | separates and shows the protrusion and groove | channel of a clutch apparatus. 伝動軸の先端の平面図である。It is a top view of the front-end | tip of a transmission shaft. 本発明の実施の形態５に係るクラッチ装置の突起と溝とを分離して示す正面図である。It is a front view which isolate | separates and shows the protrusion and groove | channel of the clutch apparatus which concern on Embodiment 5 of this invention. 伝動軸の先端の平面図である。It is a top view of the front-end | tip of a transmission shaft. 従来のクラッチ装置を示す立面図である。It is an elevational view showing a conventional clutch device.

Explanation of symbols

３ａ，３ｂ…回転工具
４…伝動軸
５…駆動軸
７…溝
７ａ，７ｂ，８ａ，８ｂ…係合面
８…突起
１８…クラッチ装置
１９…貫通孔
１９ａ，１９ｂ，２０ａ，２０ｂ，２１ａ，２１ｂ，２２，２６ａ，２６ｂ…バネ部
２０，２６…すり割り
２１，２３…縦穴
２４…横すり割り
２５…縦すり割り 3a, 3b ... rotating tool 4 ... transmission shaft 5 ... drive shaft 7 ... groove 7a, 7b, 8a, 8b ... engagement surface 8 ... projection 18 ... clutch device 19 ... through hole 19a, 19b, 20a, 20b, 21a, 21b , 22, 26a, 26b ... Spring part 20, 26 ... Slot 21, 23 ... Vertical hole 24 ... Horizontal slot 25 ... Vertical slot

Claims

In the rotary tool clutch device having a tenon-like projection on one of the drive shaft of the machine tool and the transmission shaft of the rotary tool, and a groove into which the projection is removably fitted, the groove Is formed so as to cross the drive shaft or the transmission shaft, so that a spring portion is formed on the drive shaft side or the transmission shaft side, and on the engagement surface when the protrusion and the groove are engaged. The rotation is characterized in that the spring portion is elastically deformed in a substantially vertical direction, and a through hole thicker than the width of the groove is formed to cross the drive shaft or the transmission shaft along the groove bottom. Tool clutch device.

2. The rotation device according to claim 1, wherein a spring portion is formed on the protrusion side when the protrusion is thinned by a slit extending in parallel with the engagement surface. Tool clutch device.

The clutch device for a rotary tool according to claim 1, wherein a convex curved surface is formed on the engagement surface of the protrusion, and the convex curved surface is given up parallel to the axis of the drive shaft or the transmission shaft. A clutch device for a rotary tool, characterized in that a spring portion is formed on the protrusion side by removing the protrusion by an elongated vertical hole.

The clutch device for a rotary tool according to claim 1, wherein convex curved surfaces are formed on both engaging surfaces in the vicinity of both ends of the projection, and the convex curved surface is parallel to the axis of the drive shaft or the transmission shaft. Both ends of the protrusion are thinned by vertical holes extending so as to give up, and both ends of the protrusion are thinned by a horizontal slit extending so as to cross the vertical hole perpendicular to the axis of the drive shaft or the transmission shaft. Thus, the rotary tool clutch device is characterized in that spring portions are formed at both ends of the protrusion.

5. The clutch device for a rotary tool according to claim 4 , wherein a ring portion formed at both ends of the projection by the vertical hole and the horizontal slit is thinned by the vertical slit, whereby springs are provided at both ends of the projection. A clutch device for a rotary tool, characterized in that a portion is formed.