JP5498220B2 - Angle head - Google Patents

Angle head Download PDF

Info

Publication number
JP5498220B2
JP5498220B2 JP2010073824A JP2010073824A JP5498220B2 JP 5498220 B2 JP5498220 B2 JP 5498220B2 JP 2010073824 A JP2010073824 A JP 2010073824A JP 2010073824 A JP2010073824 A JP 2010073824A JP 5498220 B2 JP5498220 B2 JP 5498220B2
Authority
JP
Japan
Prior art keywords
drill
gear
shaft
head
bevel gear
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
JP2010073824A
Other languages
Japanese (ja)
Other versions
JP2011206852A (en
Inventor
宗之 河瀬
雄二 橋本
正人 佐々木
功一 高橋
慶高 小磯
春機 溝口
秋雄 武和
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kubota Corp
MST Corp
Original Assignee
Kubota Corp
MST Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kubota Corp, MST Corp filed Critical Kubota Corp
Priority to JP2010073824A priority Critical patent/JP5498220B2/en
Publication of JP2011206852A publication Critical patent/JP2011206852A/en
Application granted granted Critical
Publication of JP5498220B2 publication Critical patent/JP5498220B2/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Landscapes

  • Jigs For Machine Tools (AREA)

Description

本発明は、ヘッド本体の出力軸から動力伝達されて出力軸の軸芯に直交するドリル軸芯まわりに駆動されるドリル駆動軸を備えたアングルヘッドに関する。   The present invention relates to an angle head provided with a drill drive shaft that is driven around a drill axis that is transmitted from an output shaft of a head body and is orthogonal to the axis of the output shaft.

上記したアングルヘッドは、工作機械に装着されたヘッド本体の先端部に設けられている。工作機械側には回転駆動される出力軸が設けてある。アングルヘッドは、この回転駆動力を装置の先端側で直交する方向に変換し、例えば、狭い孔の内部で、装置先端部の挿入方向に対して直角方向に各種の孔を加工するものである。
従来、このような加工を行なう装置として、例えば、以下に示すものがあった。
The angle head described above is provided at the tip of the head body mounted on the machine tool. An output shaft that is rotationally driven is provided on the machine tool side. The angle head converts this rotational driving force into a direction orthogonal to the front end side of the device, and for example, processes various holes in a direction perpendicular to the insertion direction of the front end of the device inside a narrow hole. .
Conventionally, as an apparatus for performing such processing, for example, there has been the following.

例えば、特許文献1には、簡単容易に回転工具の刃先方向の角度を変更できるアングルヘッドが開示されている。この技術では、回転不能な工作機械本体にアングルヘッドの非回転支承部材3を接続し、工作機械の回転可能な主軸2に、前記非回転支承部材3に回転可能に支持された回転軸1を接続してある。切削工具はヘッド本体に支持され、前記回転軸から動力を伝達されて回転駆動する。ヘッド本体は、非回転支承部材に相対回転自在、且つ、所定の相対回転位置で位置固定可能に構成してある。本装置は、このように切削工具の向きを任意に変更し設定することで、孔あけ加工の利便性を向上させようとするものである。   For example, Patent Document 1 discloses an angle head that can easily and easily change the angle in the blade edge direction of a rotary tool. In this technique, a non-rotating bearing member 3 of an angle head is connected to a machine tool body that cannot rotate, and a rotating shaft 1 that is rotatably supported by the non-rotating bearing member 3 is attached to a rotatable main shaft 2 of the machine tool. Connected. The cutting tool is supported by the head body, and is rotated by being transmitted with power from the rotating shaft. The head main body is configured to be rotatable relative to the non-rotating support member and to be fixed at a predetermined relative rotational position. This device is intended to improve the convenience of drilling by arbitrarily changing and setting the direction of the cutting tool in this way.

この従来技術では、回転工具の取り付けを以下の要領で行なう。即ち、ヘッド本体の内部に回転軸の軸線に対して90度の角度で回転可能なアングル軸を設けてあり、このアングル軸に傘歯車を介して回転軸からの回転駆動が連動連結される。ドリル等の切削具はこのアングル軸に取り付けられ、その際にはチャックが用いられる。このチャックは、アングル軸に対して切削具の側に設けられ、明細書中には詳細な構成が記載されていないが、切削具に外挿しつつアングル軸に螺着されるものと思われる。これにより切削具をアングル軸に押圧し、摩擦力などによって切削具の固定を行なう。   In this prior art, the rotating tool is attached in the following manner. That is, an angle shaft capable of rotating at an angle of 90 degrees with respect to the axis of the rotary shaft is provided inside the head main body, and the rotational drive from the rotary shaft is linked to the angle shaft via a bevel gear. A cutting tool such as a drill is attached to the angle shaft, and a chuck is used at that time. This chuck is provided on the side of the cutting tool with respect to the angle shaft, and although a detailed configuration is not described in the specification, it is considered that the chuck is screwed to the angle shaft while being extrapolated to the cutting tool. As a result, the cutting tool is pressed against the angle shaft, and the cutting tool is fixed by frictional force or the like.

特開2002−103154号公報Japanese Patent Laid-Open No. 2002-103154

しかしながら、上記従来の切削具の固定方法では、ドリルの側にチャック部材が位置するから、ドリル側の空間を広く確保することができない。よって、ドリルの穿孔深さが短くなったり、ヘッド本体の先端部を挿入可能な孔のサイズが制限されるなど、作業性に欠けるものとなる。
また、本件公報の図面には、キャップ状と判断されるチャック部材が示されている。しかし、このような部材を用いて切削具を強固に保持しようとすると、切削具を押圧する際にチャック部材の蓋部分が変形する可能性がある。そのため、キャップ部材に十分な剛性を持たせる必要が生じるなどチャック部材の全体サイズが過大となる恐れが生じる。このように、従来のアングルヘッドでは、極小空間における穿孔作業性が低下するなど未だ改善の余地があった。
However, in the conventional method for fixing a cutting tool, since the chuck member is positioned on the drill side, a wide space on the drill side cannot be secured. Therefore, the drilling depth of the drill is shortened, and the size of the hole into which the tip of the head main body can be inserted is limited, resulting in poor workability.
In addition, the drawing of this publication shows a chuck member that is determined to have a cap shape. However, if the cutting tool is to be held firmly using such a member, the lid portion of the chuck member may be deformed when the cutting tool is pressed. For this reason, the entire size of the chuck member may become excessive, for example, the cap member needs to have sufficient rigidity. As described above, the conventional angle head still has room for improvement, such as a decrease in drilling workability in a minimal space.

本発明の目的は、ドリルを強固に保持することができ、且つ、ヘッド先端部をコンパクトに構成したアングルヘッドを提供することにある。   An object of the present invention is to provide an angle head that can hold a drill firmly and that has a compact head tip.

本第1発明のアングルヘッドに係る特徴構成は、工作機械に装着されるヘッド本体と、出力軸芯の周りに回転可能に前記ヘッド本体に設けられた出力軸と、ドリルが装着され、前記出力軸芯に直交するドリル軸芯の周りに回転するドリル駆動軸と、前記出力軸の回転を前記ドリル駆動軸に伝達する回転連動機構とを備え、前記ドリルの一方に、ネジ部が形成されたテーパシャンク部を備えると共に、前記ドリル駆動軸に、前記回転連動機構からの回転が伝達されるドリル駆動ギヤと、前記テーパシャンク部を挿入可能なテーパ状のドリル取付孔と、当該ドリル取付孔の底部に位置する貫通孔とが設けてあり、前記ドリルを締結する連結ネジを、前記貫通孔を介して前記テーパシャンク部のネジ部に螺合可能に構成し
前記回転連動機構が、
前記出力軸と一体に回転する入力ベベルギヤと、前記入力ベベルギヤに噛合しつつ前記出力軸芯に直交するベベルギヤ軸芯の周りに回転するベベルギヤ部、及び、当該ベベルギヤ部と同軸芯状に一体回転する平ギヤ部を有する回転伝動体と、前記平ギヤ部に噛合して前記ベベルギヤ軸芯と平行な入力ギヤ軸芯の周りに回転する入力平ギヤと、前記ベベルギヤ軸芯と平行な出力ギヤ軸芯の周りに回転する出力平ギヤと、前記入力平ギヤと前記出力平ギヤとを連動させ、前記ベベルギヤ軸芯と平行な伝動ギヤ軸芯まわりに回転する伝動平ギヤとを有し、
前記ベベルギヤ軸芯と、前記入力ギヤ軸芯と、前記伝動ギヤ軸芯と、前記出力ギヤ軸芯と、前記ドリル軸芯とを、前記出力軸芯に平行な直線に沿って並設し、
前記ベベルギヤ部を、前記平ギヤ部に対して前記出力軸が位置する側とは反対側に配置してある点にある。
The characteristic configuration of the angle head according to the first aspect of the present invention is that a head main body mounted on a machine tool, an output shaft provided on the head main body so as to be rotatable around an output shaft core, a drill is mounted, and the output A drill drive shaft that rotates around a drill shaft orthogonal to the shaft core, and a rotation interlocking mechanism that transmits the rotation of the output shaft to the drill drive shaft, and a screw portion is formed on one of the drills A taper shank portion, a drill drive gear for transmitting rotation from the rotation interlocking mechanism to the drill drive shaft, a tapered drill attachment hole into which the taper shank portion can be inserted, and A through hole located at the bottom, and a connecting screw for fastening the drill is configured to be screwable with the threaded portion of the tapered shank through the through hole ,
The rotation interlocking mechanism is
An input bevel gear that rotates integrally with the output shaft, a bevel gear portion that meshes with the input bevel gear and that rotates around a bevel gear shaft that is orthogonal to the output shaft core, and that rotates integrally with the bevel gear portion coaxially. A rotary transmission having a spur gear, an input spur gear meshing with the spur gear and rotating about an input gear shaft parallel to the bevel gear shaft, and an output gear shaft parallel to the bevel gear shaft An output spur gear that rotates around the transmission gear, and a transmission spur gear that rotates around the transmission gear shaft parallel to the bevel gear shaft core by interlocking the input spur gear and the output spur gear.
The bevel gear shaft core, the input gear shaft core, the transmission gear shaft core, the output gear shaft core, and the drill shaft core are juxtaposed along a straight line parallel to the output shaft core,
The bevel gear portion is arranged on the side opposite to the side where the output shaft is located with respect to the flat gear portion .

本構成のように、ドリル駆動軸にドリルのテーパシャンク部を取り付け、駆動軸の反対側から連結ネジによってドリルを引き付ける構成であれば、ドリルの錐部側に従来のチャック部材等を設ける必要がない。よって、錐部側の空間がより広く確保でき、狭い作業領域においても深い孔加工を行なうことができる。
固定に用いる連結ネジは、テーパシャンク部に設けたネジ部に螺合し、ドリル駆動軸の底部に形成した貫通孔を介してテーパシャンク部を引張固定する。テーパシャンク部をドリル取付孔に押し付けて固定する場合には、ドリルを錐部の側からドリル駆動軸の側に押し付ける方法も採り得る。ただし、その場合には、ドリルの外形よりも広いチャック部材をドリル駆動軸に外嵌しなければならないなど、締結手段そのもののサイズが大きくなる。しかし、本構成のごとく、ドリルをドリル駆動軸の側に裏側から引っ張る方法であれば、例えば、ドリルの外径よりも小径のネジなどを用いて連結ネジを構成することも容易である。よって、本構成であれば、締結手段そのもののサイズをコンパクトにすることができ、先端部の細いアングルヘッドを提供することができる。
If the drill shank is attached to the drill drive shaft and the drill is pulled by the connecting screw from the opposite side of the drive shaft as in this configuration, a conventional chuck member or the like must be provided on the drill cone side. Absent. Therefore, a wider space on the cone portion side can be secured, and deep drilling can be performed even in a narrow work area.
Connecting screw used for fixing the screwed into a screw portion provided in the tapered shank portion, a tensile fixes the taper shank portion via a through hole formed in the bottom of the drill drive shaft. When the taper shank portion is pressed and fixed to the drill mounting hole, a method of pressing the drill from the cone portion side to the drill drive shaft side can also be adopted. However, in that case, the size of the fastening means itself becomes large, for example, a chuck member wider than the outer shape of the drill must be fitted on the drill drive shaft. However, as in this configuration, if the drill is pulled from the back side to the drill drive shaft side, for example, it is easy to configure the connecting screw using a screw having a diameter smaller than the outer diameter of the drill. Therefore, with this configuration, the size of the fastening means itself can be made compact, and an angle head with a thin tip can be provided.

本構成のごとく、複数の平ギヤを並設することで、回転連動機構を収容するケースのサイズを小さく構成することができる。平ギヤを用いて動力を伝達す場合、当該平ギヤに作用するモーメントは平ギヤの半径により変化する。この半径はドリルに求められる回転トルクや、出力軸が入力し得るトルク、平ギヤを構成する材質等に基づいて決定される。このため、平ギヤの全体のサイズは小さくするにも一定の制限がある。ただし、平ギヤの全体の形状は、歯の平面方向においては所定の広さを必要とするが、軸芯方向のサイズを決定するにはある程度の自由度が存在する。
そこで、本構成のごとく、平ギヤの軸芯方向を出力軸芯に対して直行させ、複数の平ギヤを並設することとすれば、当該並設方向に垂直な断面視において、平ギヤの径方向の長さについてはそれ程縮小できないものの、回転軸の長さは短縮化が容易である。このように、本構成であれば、回転連動機構を収容するケースの一方の厚み、即ち、ドリルの回転軸に沿う方向の長さを短縮してケースのコンパクト化が可能となり、より狭い場所での穿孔作業が容易となる。
Like this structure, the size of the case which accommodates a rotation interlocking | linkage mechanism can be comprised small by arranging several flat gears in parallel. When power is transmitted using a spur gear, the moment acting on the spur gear varies depending on the radius of the spur gear. This radius is determined based on the rotational torque required for the drill, the torque that can be input by the output shaft, the material constituting the spur gear, and the like. For this reason, there is a certain limitation even if the overall size of the spur gear is reduced. However, the overall shape of the spur gear requires a predetermined width in the tooth plane direction, but there is a certain degree of freedom in determining the size in the axial direction.
Therefore, as in the present configuration, if the axial center direction of the flat gear is made perpendicular to the output shaft core, and a plurality of flat gears are arranged side by side, in the cross-sectional view perpendicular to the parallel arrangement direction, Although the length in the radial direction cannot be reduced so much, the length of the rotating shaft can be easily shortened. Thus, with this configuration, the thickness of one of the cases accommodating the rotation interlocking mechanism, that is, the length in the direction along the rotation axis of the drill can be shortened, and the case can be made compact. Drilling work becomes easier.

また、本構成の装置では、各平ギヤの回転軸芯が出力軸芯に平行な直線に沿って並設してあるから、これら輪列の幅を最小に留めることができる。さらに、本構成であれば、同じ平ギヤを並べる際に、各回転軸芯を千鳥に配置するものに比べて出力軸からドリルまでの距離を最も長く確保することができる。よって、底の深い作業スペースに対しても対応し易いアングルヘッドを提供することができる。   Further, in the apparatus of this configuration, the rotation shaft cores of the respective flat gears are arranged side by side along a straight line parallel to the output shaft core, so that the width of these wheel trains can be kept to a minimum. Furthermore, with this configuration, when arranging the same spur gears, it is possible to ensure the longest distance from the output shaft to the drill as compared with a configuration in which the rotation shaft cores are arranged in a staggered manner. Therefore, it is possible to provide an angle head that can easily cope with a deep working space.

本構成のごとく、回転伝動体を構成するのに、出力軸の入力ベベルギヤに噛合するベベルギヤ部に対して、このベベルギヤ部に一体的に取り付ける平ギヤ部を出力軸の側に設けることで、当該平ギヤ部に連接される他の平ギヤ部が前記出力軸に近い位置に並設されることになる。このため、アングルヘッドの先端部全体が出力軸芯に近い位置に形成されることとなり、アングルヘッド全体の径方向のサイズを小さくすることができる。
さらに、本構成であれば、べべルギヤ部は入力べべルギヤから駆動力を受け取る必要があるため、平ギヤ部の外径は、入力べべルギヤとの干渉を避けるために必然的にベベルギヤ部の外径よりも小さくなる。アングルヘッドの外形サイズを考えたとき、ドリルの回転軸芯に直角な幅方向のサイズは、この大きなベベルギヤ部の直径に左右される。よって、当該装置を極力小さい孔に挿入するためには、このべべルギヤ部は、装置先端部のうち、ドリルの回転軸芯に沿う方向の中央位置に近付けるのが好ましい。ただし、ドリルの錐部は所定の長さを有するから、ベベルギヤ部を設ける位置は制限される。ベベルギヤ部を装置の中央に位置させるためには、ドリルの側に近付ける方が有利である。よって、本構成のごとく、外径の小さい平ギヤ部をベベルギヤ部に対して出力軸の側に設けることで、アングルヘッドの先端部の形状をよりコンパクトに構成することができる。
As in this configuration, in order to configure the rotary transmission body, a flat gear portion that is integrally attached to the bevel gear portion is provided on the output shaft side with respect to the bevel gear portion that meshes with the input bevel gear of the output shaft. The other spur gear portion connected to the spur gear portion is juxtaposed at a position close to the output shaft. For this reason, the entire tip of the angle head is formed at a position close to the output shaft core, and the radial size of the entire angle head can be reduced.
Furthermore, with this configuration, the bevel gear portion needs to receive driving force from the input bevel gear, so the outer diameter of the flat gear portion is inevitably outside of the bevel gear portion to avoid interference with the input bevel gear. It becomes smaller than the diameter. When considering the outer size of the angle head, the size in the width direction perpendicular to the axis of rotation of the drill depends on the diameter of the large bevel gear portion. Therefore, in order to insert the device into a hole as small as possible, it is preferable that the bevel gear portion is close to the center position in the direction along the rotation axis of the drill in the tip portion of the device. However, since the cone portion of the drill has a predetermined length, the position where the bevel gear portion is provided is limited. In order to position the bevel gear portion at the center of the apparatus, it is advantageous to approach the side of the drill. Therefore, as in this configuration, by providing the flat gear portion having a small outer diameter on the output shaft side with respect to the bevel gear portion, the shape of the tip portion of the angle head can be configured more compactly.

本第発明のアングルヘッドに係る特徴構成は、前記回転連動機構と前記ドリル駆動ギヤとを収容するヘッド部ケースの先端部を形成する表面のうち、前記ドリルの突出位置を含む平面が、当該平面に対して前記ヘッド部ケースの基端側に隣接する表面よりも引退した段差部となっている点にある。 The characteristic configuration according to the angle head of the second aspect of the present invention is that the plane including the protruding position of the drill among the surfaces forming the tip portion of the head case that houses the rotation interlocking mechanism and the drill drive gear is It is in the point which becomes a level difference part which retreated from the surface adjacent to the base end side of the head part case to a plane.

本構成であれば、ドリルによる穿孔深さをより大きく確保することができる。ドリルの基端部には大径のボス部が存在したり、ドリルを装着するドリル駆動軸にはドリル取付け用の工具を係合させる部位を設ける場合がある。本構成のごとく、ヘッド部ケースの平面のうち、ドリル基端部周辺の平面をヘッド部ケースの最前面から引退させることで、当該段差を上記ボス部等の配置スペースに利用することができる。ドリルの穿孔深さは、ヘッド部ケースの最前面から突出したドリルの長さによって既定されることが多いから、上記構成を備えることで、ドリルの有効長さを最も大きく確保することができる。   If it is this structure, the drilling depth by a drill can be ensured more largely. There is a case where a boss portion having a large diameter exists at the base end portion of the drill, or a portion for engaging a tool for attaching a drill is provided on a drill drive shaft on which the drill is mounted. As in this configuration, by retreating the plane around the drill base end portion of the plane of the head portion case from the forefront of the head portion case, the step can be used as an arrangement space for the boss portion and the like. Since the drilling depth of the drill is often determined by the length of the drill protruding from the forefront of the head part case, the effective length of the drill can be maximized by providing the above configuration.

本第発明のアングルヘッドに係る特徴構成は、前記段差部と、当該段差部に対して前記ヘッド部ケースの基端側に隣接する表面との境界位置に、前記ドリルから飛散した切り粉を前記ドリルから離間する方向に飛散させる傾斜面を形成した点にある。 The characteristic configuration according to the angle head of the third aspect of the invention is characterized in that chips scattered from the drill are disposed at a boundary position between the step portion and a surface adjacent to the base end side of the head portion case with respect to the step portion. In the point which formed the inclined surface scattered in the direction away from the said drill.

本構成によると、ドリル駆動軸から飛散した切り粉が、段差部におけるケース外側面の傾斜面によってドリル駆動軸から離れる方向に飛散する。よって、ドリル駆動軸から飛散した切り粉が再度ドリル駆動軸に付着して切削の障害となることがなく、穿孔作業を効率的に行なえるアングルヘッドを得ることができる。   According to this configuration, the chips scattered from the drill drive shaft are scattered in a direction away from the drill drive shaft by the inclined surface of the case outer surface at the stepped portion. Therefore, it is possible to obtain an angle head capable of efficiently performing a drilling operation without causing chips scattered from the drill drive shaft to adhere to the drill drive shaft again and obstruct cutting.

アングルヘッドの全体を示す正面図である。It is a front view which shows the whole angle head. アングルヘッドの先端部を示す斜視図である。It is a perspective view which shows the front-end | tip part of an angle head. アングルヘッドの先端部を示す側面図である。It is a side view which shows the front-end | tip part of an angle head. アングルヘッドの先端部を示す底面図である。It is a bottom view which shows the front-end | tip part of an angle head. アングルヘッドの縦断正面図および平ギヤの配列を示す説明図である。It is explanatory drawing which shows the vertical front view of an angle head, and the arrangement | sequence of a flat gear. 連結手段の構成を示す説明図である。It is explanatory drawing which shows the structure of a connection means. 第1の別実施形態に係るヘッド部を示す縦断正面図である。It is a vertical front view which shows the head part which concerns on 1st another embodiment. 第2の別実施形態に係るヘッド部を示す縦断正面図である。It is a vertical front view which shows the head part which concerns on 2nd another embodiment. ケースの先端部を示す横断平面図である。It is a cross-sectional top view which shows the front-end | tip part of a case . ドリルの取外し治具を示す説明図である。It is explanatory drawing which shows the removal jig | tool of a drill .

以下、本発明の実施の形態を図面に基づいて説明する。   Hereinafter, embodiments of the present invention will be described with reference to the drawings.

図1は、本発明の実施例に係るアングルヘッドの全体を示す正面図である。本アングルヘッドは、ヘッド本体枠1、及びヘッド本体枠1に回転自在に支持された回転軸2を有したヘッド本体Aと、ヘッド本体枠1に基端部が連結されたヘッド部ケース10、及びヘッド部ケース10の先端部に回転自在に支持されたドリル駆動軸20を有したヘッド部Bとを備えて構成してある。   FIG. 1 is a front view showing an entire angle head according to an embodiment of the present invention. This angle head includes a head main body frame 1, a head main body A having a rotation shaft 2 rotatably supported by the head main body frame 1, a head portion case 10 having a base end connected to the head main body frame 1, And a head part B having a drill drive shaft 20 rotatably supported at the tip of the head part case 10.

このアングルヘッドは、ヘッド本体Aで図外の工作機械に装着される。ドリル駆動軸20が工作機械からヘッド本体Aを介して伝達される動力によって回転駆動され、ドリル駆動軸20に取付けられたドリル30が回転駆動される。ヘッド部ケース10の先端側が、工作機械による操作によって加工対象物の孔内に挿入され、加工対象物の内壁に穿孔する本装置は、例えば、パワーステアリング装置の油圧機器を構成するケーシング等の加工に用いる。   This angle head is mounted on a machine tool (not shown) by the head body A. The drill drive shaft 20 is rotationally driven by the power transmitted from the machine tool via the head body A, and the drill 30 attached to the drill drive shaft 20 is rotationally driven. The apparatus in which the tip end side of the head case 10 is inserted into the hole of the workpiece by operation with a machine tool and drilled in the inner wall of the workpiece, for example, processing of a casing or the like constituting the hydraulic equipment of the power steering device Used for.

(ヘッド本体)
ヘッド本体Aは、回転軸2のヘッド本体枠1に支持される側とは反対側の端側に設けられたテーパ軸部2aと、ヘッド本体枠1に回転軸2と平行に配置して設けられた位置決めピン3とを備えている。ヘッド本体Aは、テーパ軸部2aが工作機械の主軸(図示せず)に連結され、位置決めピン3が工作機械の位置決めブロック(図示せず)に装着されることにより、アングルヘッドを工作機械に対して所定の連結状態で連結して工作機械によるアングルヘッドの駆動及び操作を可能にする。
(Head body)
The head main body A is provided with a taper shaft portion 2 a provided on an end side of the rotary shaft 2 opposite to the side supported by the head main body frame 1, and the head main body frame 1 arranged in parallel with the rotary shaft 2. The positioning pin 3 is provided. In the head body A, the taper shaft portion 2a is connected to the main shaft (not shown) of the machine tool, and the positioning pin 3 is attached to the positioning block (not shown) of the machine tool, whereby the angle head is attached to the machine tool. On the other hand, the angle head is driven and operated by the machine tool by being connected in a predetermined connection state.

図5に示すように、ヘッド本体Aは、ヘッド本体枠1に対して回転軸2のテーパ軸部2aが位置する側とは反対側に位置する箇所に設けられた出力軸4を備えている。出力軸4の先端側がヘッド部ケース10の基端部の内側に配置されるとともにドリル駆動軸20に連動されている。出力軸4は、工作機械からの駆動力によって出力軸芯4aまわりに回転駆動され、ドリル駆動軸20に動力を伝達する。出力軸4の出力軸芯4aは、回転軸2の回転軸芯と一致するように構成してある。   As shown in FIG. 5, the head main body A includes an output shaft 4 provided at a position on the opposite side of the head main body frame 1 from the side where the tapered shaft portion 2 a of the rotation shaft 2 is located. . The distal end side of the output shaft 4 is disposed inside the proximal end portion of the head portion case 10 and is interlocked with the drill drive shaft 20. The output shaft 4 is rotationally driven around the output shaft core 4 a by the driving force from the machine tool, and transmits power to the drill drive shaft 20. The output shaft core 4 a of the output shaft 4 is configured to coincide with the rotational shaft core of the rotating shaft 2.

(ヘッド部)
図2(a),(b)は、ヘッド部Bの先端部を示す斜視図である。図5は、ヘッド部Bを示す縦断正面図である。これらの図に示すように、ドリル駆動軸20は、出力軸4の出力軸芯4aと直交するドリル軸芯20a周りに回転する。ドリル駆動軸20にはドリル取付け孔21(図6参照)が開口形成してある。ドリル取付け孔21の開口側端部にはドリル30を装着する際に工具を係止する工具係止面20bを設けてある。ドリル駆動軸20は、工具係止面20bがヘッド部ケース10の表面から突出する状態に設けてある。
(Head)
2A and 2B are perspective views showing the tip of the head part B. FIG. FIG. 5 is a longitudinal front view showing the head part B. FIG. As shown in these drawings, the drill drive shaft 20 rotates around a drill axis 20 a orthogonal to the output axis 4 a of the output shaft 4. A drill mounting hole 21 (see FIG. 6) is formed in the drill drive shaft 20. A tool locking surface 20b for locking the tool when the drill 30 is mounted is provided at the opening side end of the drill mounting hole 21. The drill drive shaft 20 is provided in a state in which the tool locking surface 20 b protrudes from the surface of the head part case 10.

図5に示すように、ヘッド部Bは、主にヘッド部ケース10で構成される。ヘッド部ケース10には、出力軸4の入力ベベルギヤ41に連結された伝動装置40を内装してある。この伝動装置40は、出力軸4からの駆動力をドリル駆動軸20に伝達する。ドリル駆動軸20は保持したドリル30をドリル軸芯20a周りに回転駆動する。   As shown in FIG. 5, the head part B is mainly composed of a head part case 10. The head case 10 is internally provided with a transmission device 40 connected to the input bevel gear 41 of the output shaft 4. The transmission device 40 transmits the driving force from the output shaft 4 to the drill driving shaft 20. The drill drive shaft 20 rotationally drives the held drill 30 around the drill axis 20a.

(伝動装置)
図5に示すように、伝動装置40は、出力軸4に連結された入力ベベルギヤ41を備える他、当該入力ベベルギヤ41の回転をドリル30に伝える回転連動機構を備えている。特に、図5のものは回転連動機構として、入力ベベルギヤ41にベベルギヤ部42aが噛合った回転伝動体42と、この回転伝動体42の平ギヤ部42bに噛合った入力平ギヤ51を有したギヤ連動機構50を備えており、このギヤ連動機構50が備える出力平ギヤ52に噛合ったドリル駆動ギヤ22とを備えて構成してある。
入力ベベルギヤ41は、ヘッド本体Aの出力軸4に一体回転自在に連結されており、出力軸芯4aまわりに回転する。
(Transmission device)
As shown in FIG. 5, the transmission device 40 includes an input bevel gear 41 coupled to the output shaft 4 and a rotation interlocking mechanism that transmits the rotation of the input bevel gear 41 to the drill 30. In particular, the one shown in FIG. 5 has a rotation transmission mechanism 42 in which a bevel gear portion 42a is engaged with an input bevel gear 41 and an input flat gear 51 in engagement with a flat gear portion 42b of the rotation transmission member 42 as a rotation interlocking mechanism. The gear interlocking mechanism 50 is provided, and the drill driving gear 22 meshed with the output spur gear 52 included in the gear interlocking mechanism 50 is provided.
The input bevel gear 41 is connected to the output shaft 4 of the head main body A so as to be integrally rotatable, and rotates around the output shaft core 4a.

回転伝動体42は、入力ベベルギヤ41に噛合うベベルギヤ部42aと、ギヤ連動機構50の入力平ギヤ51に噛合う平ギヤ部42bと、ベベルギヤ部42a及び平ギヤ部42bを支持する一本の回転支軸42cとを備えて構成してある。ベベルギヤ部42a及び平ギヤ部42bは、回転支軸42cに一体回転自在に連結されており、出力軸4の出力軸芯4aと直交する回転支軸42cの軸芯で成るベベルギヤ軸芯42d周りに一体回転する。   The rotation transmission body 42 is a single rotation that supports the bevel gear portion 42a that meshes with the input bevel gear 41, the flat gear portion 42b that meshes with the input flat gear 51 of the gear interlocking mechanism 50, and the bevel gear portion 42a and the flat gear portion 42b. And a support shaft 42c. The bevel gear portion 42a and the flat gear portion 42b are connected to the rotation support shaft 42c so as to be rotatable integrally with each other, and around the bevel gear shaft core 42d formed by the shaft core of the rotation support shaft 42c orthogonal to the output shaft core 4a of the output shaft 4. Rotates together.

ギヤ連動機構50は、回転伝動体42の平ギヤ部42bに噛合う入力平ギヤ51と、ドリル駆動ギヤ22に噛合う出力平ギヤ52と、入力平ギヤ51と出力平ギヤ52の間に位置する伝動平ギヤ53を備えている。   The gear interlocking mechanism 50 is positioned between the input flat gear 51 that meshes with the flat gear portion 42 b of the rotary transmission 42, the output flat gear 52 that meshes with the drill drive gear 22, and the input flat gear 51 and the output flat gear 52. A transmission spur gear 53 is provided.

入力平ギヤ51は、支軸51aを介してヘッド部ケース10に回転自在に支持されており、ベベルギヤ軸芯42dと平行な支軸51aの軸芯で成る入力ギヤ軸芯51b周りに回転する。出力平ギヤ52は、支軸52aを介してヘッド部ケース10に回転自在に支持されており、ベベルギヤ軸芯42dと平行な支軸52aの軸芯で成る出力ギヤ軸芯52b周りに回転する。   The input spur gear 51 is rotatably supported by the head case 10 via a support shaft 51a, and rotates around an input gear shaft core 51b composed of a shaft shaft of a support shaft 51a parallel to the bevel gear shaft core 42d. The output spur gear 52 is rotatably supported by the head case 10 via a support shaft 52a, and rotates around an output gear shaft 52b that is a shaft of a support shaft 52a parallel to the bevel gear shaft core 42d.

伝動平ギヤ53は、支軸53aを介してヘッド部ケース10に回転自在に支持されており、ベベルギヤ軸芯42dと平行な支軸53aの軸芯で成る伝動ギヤ軸芯53b周りに回転する。伝動平ギヤ53は、入力平ギヤ51及び出力平ギヤ52に噛合っており、入力平ギヤ51と出力平ギヤ52を連動させる。   The transmission spur gear 53 is rotatably supported by the head case 10 via a support shaft 53a, and rotates around a transmission gear shaft core 53b formed of a shaft core of a support shaft 53a parallel to the bevel gear shaft core 42d. The transmission spur gear 53 meshes with the input spur gear 51 and the output spur gear 52, and interlocks the input spur gear 51 and the output spur gear 52.

ドリル駆動ギヤ22はドリル駆動軸20に一体回転可能に構成してあり、ドリル軸芯20a周りに回転する。当該ドリル駆動ギヤ22は、ドリル駆動軸20と単一の部材から削り出すなどして形成しても良いし、ドリル駆動軸20に対してギヤの部分を溶接しても良い。また、キー等を用いてドリル駆動軸20に固定するものであっても良い。   The drill drive gear 22 is configured to rotate integrally with the drill drive shaft 20 and rotates around the drill shaft core 20a. The drill drive gear 22 may be formed by cutting out from a single member with the drill drive shaft 20, or a gear portion may be welded to the drill drive shaft 20. Moreover, you may fix to the drill drive shaft 20 using a key etc.

したがって、伝動装置40は、入力ベベルギヤ41と回転伝動体42のベベルギヤ部42aとによって動力変換部43を構成し、出力軸4の出力軸芯4aまわりの駆動力を、動力変換部43によって出力軸芯4aと直交したベベルギヤ軸芯42dまわりの駆動力に変換する。変換後の駆動力は、平ギヤ部42bからギヤ連動機構50の入力平ギヤ51、伝動平ギヤ53及び出力平ギヤ52を介してドリル駆動ギヤ22に伝達される。これにより、出力軸4の出力軸芯4a周りの駆動力が、ドリル軸芯20a周りの駆動力に変換した状態でドリル駆動軸20に伝達される。   Therefore, in the transmission device 40, the input bevel gear 41 and the bevel gear portion 42a of the rotating transmission body 42 constitute a power conversion unit 43, and the driving force around the output shaft core 4a of the output shaft 4 is output by the power conversion unit 43 to the output shaft. The driving force is converted around the bevel gear shaft core 42d orthogonal to the core 4a. The converted driving force is transmitted from the spur gear portion 42b to the drill driving gear 22 via the input spur gear 51, the transmission spur gear 53, and the output spur gear 52 of the gear interlocking mechanism 50. Thereby, the driving force around the output shaft core 4a of the output shaft 4 is transmitted to the drill driving shaft 20 in a state where it is converted into the driving force around the drill shaft core 20a.

入力ベベルギヤ41、ベベルギヤ部42a、平ギヤ部42b、入力平ギヤ51、伝動平ギヤ53、出力平ギヤ52及びドリル駆動ギヤ22の各歯には、ガタ付き及び騒音の発生が少ない状態で噛合うように特殊樹脂コーテイングを施すとよい。例えば、ヘッド部ケース10に潤滑油を充満させるとともに油圧を加えることにより、各ギヤのバックラッシュによるガタ付きを抑制することができる。   The teeth of the input bevel gear 41, the bevel gear portion 42a, the flat gear portion 42b, the input flat gear 51, the transmission flat gear 53, the output flat gear 52, and the drill driving gear 22 are engaged with each other with little play and little noise. It is better to apply special resin coating. For example, the backlash of each gear due to backlash can be suppressed by filling the head case 10 with lubricating oil and applying hydraulic pressure.

図1,図5(a)に示すように、ヘッド部ケース10は、ヘッド本体枠1に連結されるとともに入力ベベルギヤ41を収容する入力ケース部12と、この入力ケース部12からヘッド本体Aが位置する側とは反対側に向けて延出した駆動ケース部13とを備えて構成してある。駆動ケース部13は、回転伝動体42、ギヤ連動機構50及びドリル駆動ギヤ22を収容するとともにドリル駆動軸20を支持する。   As shown in FIGS. 1 and 5A, the head case 10 is connected to the head body frame 1, and also includes an input case 12 that accommodates the input bevel gear 41, and the head body A from the input case 12. The driving case portion 13 extends toward the opposite side to the positioned side. The drive case portion 13 accommodates the rotary drive body 42, the gear interlocking mechanism 50, and the drill drive gear 22 and supports the drill drive shaft 20.

入力ケース部12は、入力ベベルギヤ41に対してヘッド本体枠1が位置する側とは反対側に出力軸4と直交する状態で位置する入力ケース壁12aを備えて構成してある。入力ケース壁12aは、これの内面側に設けられた出力軸支持部12bを備え、この出力軸支持部12bによってベアリング14を介して出力軸4の端部を支持する。   The input case portion 12 includes an input case wall 12a that is positioned in a state orthogonal to the output shaft 4 on the side opposite to the side on which the head main body frame 1 is positioned with respect to the input bevel gear 41. The input case wall 12 a includes an output shaft support portion 12 b provided on the inner surface side thereof, and supports the end portion of the output shaft 4 via the bearing 14 by the output shaft support portion 12 b.

駆動ケース部13は、平ギヤ部42b、入力平ギヤ51、伝動平ギヤ53、出力平ギヤ52及びドリル駆動ギヤ22に対して出力軸4が位置する側にベベルギヤ軸芯42d、入力ギヤ軸芯51b、伝動ギヤ軸芯53b、出力ギヤ軸芯52b及びドリル軸芯20aと直交する状態で位置する主ケース壁13aを備えて構成してある。主ケース壁13aは、これの内面側に平ギヤ部42b、入力平ギヤ51、伝動平ギヤ53、出力平ギヤ52及びドリル駆動ギヤ22に対応させて設けられた支持部13bを備えており、回転伝動体42の回転支軸42c、入力平ギヤ51の支軸51a、伝動平ギヤ53の支軸53a,出力平ギヤの支軸52a及びドリル駆動軸20を支持部13bによってベアリングを介して支持する。   The drive case portion 13 has a bevel gear shaft core 42d and an input gear shaft core on the side where the output shaft 4 is located with respect to the spur gear portion 42b, the input spur gear 51, the transmission spur gear 53, the output spur gear 52 and the drill drive gear 22. 51b, a transmission gear shaft core 53b, an output gear shaft core 52b, and a main case wall 13a positioned perpendicular to the drill shaft core 20a. The main case wall 13a includes a support portion 13b provided on the inner surface side thereof corresponding to the flat gear portion 42b, the input flat gear 51, the transmission flat gear 53, the output flat gear 52, and the drill drive gear 22, The rotation support shaft 42c of the rotary transmission 42, the support shaft 51a of the input flat gear 51, the support shaft 53a of the transmission flat gear 53, the support shaft 52a of the output flat gear, and the drill drive shaft 20 are supported by the support portion 13b via bearings. To do.

図5(b)に示すように、回転伝動体42のベベルギヤ軸芯42d、入力平ギヤ51の入力ギヤ軸芯51b、伝動平ギヤ53の伝動ギヤ軸芯53b、出力平ギヤ52の出力ギヤ軸芯52a及びドリル軸芯20aは、出力軸芯4aに平行な直線Lに直交する状態でその直線Lに沿って並ぶ状態に配置してある。これにより、ヘッド部ケース10における駆動ケース部13は、平ギヤ部42b、入力平ギヤ51、伝動平ギヤ53、出力平ギヤ52及びドリル駆動ギヤ22が並ぶ方向と直交する方向で、かつ平ギヤ部42b及び各平ギヤ51,53,52,22の径方向に沿う方向きでの大きさが比較的小さい形状になっている。
つまり、各平ギヤの回転軸芯が出力軸芯4aに平行な直線に沿って並設してあるから、これら輪列の幅を最小に留めることができる。さらに、本構成であれば、同じ形状の入力平ギヤ51を並べる際に、各回転軸芯を千鳥に配置するものに比べて出力軸4からドリル30までの距離を最も長く確保することができる。よって、底の深い作業スペースに対しても対応し易いアングルヘッドを提供することができる。
As shown in FIG. 5B, the bevel gear shaft core 42 d of the rotating transmission body 42, the input gear shaft core 51 b of the input flat gear 51, the transmission gear shaft core 53 b of the transmission flat gear 53, and the output gear shaft of the output flat gear 52. The core 52a and the drill shaft core 20a are arranged along the straight line L in a state orthogonal to the straight line L parallel to the output shaft core 4a. Accordingly, the drive case 13 in the head case 10 is formed in a direction perpendicular to the direction in which the flat gear portion 42b, the input flat gear 51, the transmission flat gear 53, the output flat gear 52, and the drill driving gear 22 are arranged, and the flat gear. The portion 42b and the flat gears 51, 53, 52, and 22 have a relatively small size in the direction along the radial direction.
In other words, since the rotation shaft cores of the respective flat gears are arranged in parallel along a straight line parallel to the output shaft core 4a, the width of these wheel trains can be minimized. Furthermore, with this configuration, when the input flat gears 51 having the same shape are arranged, it is possible to ensure the longest distance from the output shaft 4 to the drill 30 as compared to the case where the rotation shaft cores are arranged in a staggered manner. . Therefore, it is possible to provide an angle head that can easily cope with a deep working space.

回転伝動体42のベベルギヤ部42aと平ギヤ部42bとを、ベベルギヤ部42aが平ギヤ部52bに対して出力軸4が位置する側とは反対側に位置する状態で配置し、出力軸4を平ギヤ部42bに対してベベルギヤ軸芯42dに沿う方向で極力寄った箇所に位置させている。
本構成のごとく、回転伝動体42を構成するのに、出力軸4の入力ベベルギヤ41に噛合するベベルギヤ部42aに対して、このベベルギヤ部42aに一体的に取り付ける平ギヤ部52bを出力軸4の側に設けることで、当該平ギヤ部52bに連接される他の平ギヤが前記出力軸4に近い位置に並設されることになる。このため、アングルヘッドの先端部全体が出力軸芯に近い位置に形成されることとなり、アングルヘッド全体の径方向のサイズを小さくすることができる。
The bevel gear portion 42a and the flat gear portion 42b of the rotary transmission 42 are arranged in a state where the bevel gear portion 42a is located on the opposite side of the flat gear portion 52b from the side on which the output shaft 4 is located. The flat gear portion 42b is positioned at a position that is as close as possible in the direction along the bevel gear shaft core 42d.
As in this configuration, in order to configure the rotary transmission body 42, the flat gear portion 52 b that is integrally attached to the bevel gear portion 42 a is attached to the bevel gear portion 42 a that meshes with the input bevel gear 41 of the output shaft 4. By providing on the side, the other spur gear connected to the spur gear portion 52b is juxtaposed at a position close to the output shaft 4. For this reason, the entire tip of the angle head is formed at a position close to the output shaft core, and the radial size of the entire angle head can be reduced.

さらに、本構成であれば、べべルギヤ部42aは入力べべルギヤ41から駆動力を受け取る必要があるため、平ギヤ部52bの外径は、入力べべルギヤ41との干渉を避けるべく必然的にベベルギヤ部42aの外径よりも小さくなる。アングルヘッドの外形サイズを考えたとき、ドリル30の回転軸芯に直角な幅方向のサイズは、この大きなベベルギヤ部42aの直径に左右される。よって、当該装置を極力小さい孔に挿入するためには、このべべルギヤ部42aは、装置先端部のうち、ドリル30の回転軸芯に沿う方向のうち中央位置に近付けるのが好ましい。ただし、ドリル30の錐部32は所定の長さを有するから、べべルギヤ部42aを設ける位置は制限される。ベベルギヤ部42aを装置の中央に位置させるためには、ドリル30の側に近付ける方が有利である。よって、本構成のごとく、外径の小さい平ギヤ部52bをべべルギヤ部42aに対して出力軸4の側に設けることで、アングルヘッドの先端部の形状をよりコンパクトに構成することができる。   Further, in this configuration, since the bevel gear portion 42 a needs to receive a driving force from the input bevel gear 41, the outer diameter of the flat gear portion 52 b is inevitably in order to avoid interference with the input bevel gear 41. It becomes smaller than the outer diameter of the part 42a. When considering the outer size of the angle head, the size in the width direction perpendicular to the rotational axis of the drill 30 depends on the diameter of the large bevel gear portion 42a. Therefore, in order to insert the device into a hole as small as possible, it is preferable that the bevel gear portion 42a is close to the center position in the direction along the rotation axis of the drill 30 in the tip portion of the device. However, since the conical portion 32 of the drill 30 has a predetermined length, the position where the bevel gear portion 42a is provided is limited. In order to position the bevel gear portion 42a in the center of the apparatus, it is advantageous to bring it closer to the drill 30 side. Therefore, as in this configuration, by providing the flat gear portion 52b having a small outer diameter on the output shaft 4 side with respect to the bevel gear portion 42a, the shape of the tip portion of the angle head can be configured more compactly.

(段差部)
図2,図5に示すように、ヘッド部ケース10における駆動ケース部13のうちのドリル駆動軸20を設けてある先端部11と、この先端部11に対してヘッド本体Aが位置する側に偏位している基端側部15との間に段差部16を設けてある。段差部16は、駆動ケース部13における先端部11のドリル駆動軸20の端部が突出しているケース外側面11aを、駆動ケース部13における基端側部15の平ギヤ部42bに対してベベルギヤ部42aが位置する側のケース外側面15aに対して出力軸4が位置する側に偏位させてある。ドリル駆動軸20に取付けられたドリル30の基端側に位置する連結部31(図6参照)を基端側部15におけるケース外側面15aに対してケース内方側に極力寄った箇所に位置させる凹入部17を駆動ケース部13のドリル駆動軸20が突出する側の外面側に形成している。
(Step part)
As shown in FIGS. 2 and 5, the tip end portion 11 of the drive case portion 13 of the head portion case 10 provided with the drill drive shaft 20 and the head body A on the side where the head body A is located. A step portion 16 is provided between the proximal end side portion 15 that is displaced. The stepped portion 16 has a bevel gear with respect to the flat gear portion 42b of the base end side portion 15 of the drive case portion 13 on the case outer surface 11a from which the end portion of the drill drive shaft 20 of the distal end portion 11 of the drive case portion 13 projects. The output shaft 4 is deviated to the side where the output shaft 4 is located with respect to the case outer surface 15a on the side where the portion 42a is located. The connecting portion 31 (see FIG. 6) located on the base end side of the drill 30 attached to the drill drive shaft 20 is located at a position that is as close as possible to the case inner side with respect to the case outer surface 15a in the base end side portion 15. The recessed portion 17 to be formed is formed on the outer surface side of the drive case portion 13 from which the drill drive shaft 20 protrudes.

図2,図3に示すように、段差部16におけるケース外側面16aは、一対の傾斜反射面16b,16bを備えた傾斜面に構成してある。   As shown in FIGS. 2 and 3, the case outer surface 16 a in the step portion 16 is configured as an inclined surface having a pair of inclined reflecting surfaces 16 b and 16 b.

段差部16におけるケース外側面16aは、ドリル駆動軸22及びドリル駆動軸22に取付けられたドリル30から飛散して一方の傾斜反射面16bに当った切り粉を、一方の傾斜反射面16bの反射及び傾斜の作用によってドリル駆動軸22及びドリル30から離れる方向F1(図3参照)に反射させる。ケース外側面16aは、ドリル駆動軸22及びドリル駆動軸22に取付けられたドリル30から飛散して他方の傾斜反射面16bに当った切り粉を、他方の傾斜反射面16bの反射及び傾斜の作用によってドリル駆動軸22及びドリル30から離れる方向F2(図3参照)に反射させる。
したがって、段差部16におけるケース外側面16aは、ドリル駆動軸20やドリル30から飛散した切り粉がドリル駆動軸20やドリル30に落下して付着することを防止する。
The case outer surface 16a in the stepped portion 16 reflects the cutting powder scattered from the drill driving shaft 22 and the drill 30 attached to the drill driving shaft 22 and hitting one inclined reflecting surface 16b on one inclined reflecting surface 16b. And it reflects in the direction F1 (refer FIG. 3) which leaves | separates from the drill drive shaft 22 and the drill 30 by the effect | action of inclination. The outer surface 16a of the case scatters chips from the drill driving shaft 22 and the drill 30 attached to the drill driving shaft 22 and hits the other inclined reflecting surface 16b, and reflects and tilts the other inclined reflecting surface 16b. Is reflected in a direction F2 (see FIG. 3) away from the drill drive shaft 22 and the drill 30.
Therefore, the case outer surface 16a in the step portion 16 prevents the chips scattered from the drill drive shaft 20 and the drill 30 from dropping and adhering to the drill drive shaft 20 and the drill 30.

図2,図4に示すように、ヘッド部ケース10における駆動ケース部13のドリル駆動軸20が突出する側とは反対側に位置する両角部に、面取り部18をドリル駆動軸22が位置する先端部11とギヤ連動機構50が位置する基端側部15とにわたって設けてある。両角部の面取り部18は、加工対象物の穴径が小さい場合、駆動ケース部13のドリル30に対して背後に位置する角部が加工対象物の穴Hの内壁に当たることを回避してヘッド部Bの先端側を穴Hに挿入し易くする。   As shown in FIGS. 2 and 4, the chamfered portion 18 and the drill drive shaft 22 are located at both corners of the drive case 13 in the head case 10 that are opposite to the side from which the drill drive shaft 20 protrudes. It is provided over the distal end portion 11 and the proximal end side portion 15 where the gear interlocking mechanism 50 is located. When the hole diameter of the workpiece is small, the chamfered portions 18 at both corners avoid the corner portion located behind the drill 30 of the drive case 13 from hitting the inner wall of the hole H of the workpiece. The tip side of the part B is easily inserted into the hole H.

図2,図4に示すように、ヘッド部ケース10における駆動ケース部13のドリル駆動軸20が突出する側に位置する両角部に、ドリル30による穴あけが進んだ場合の駆動ケース部13の加工対象物の穴内壁に対する当接を回避する面取り部18aを設けてある。   As shown in FIGS. 2 and 4, machining of the drive case 13 when drilling with a drill 30 has advanced in both corners of the drive case 13 in the head case 10 located on the side where the drill drive shaft 20 protrudes. A chamfer 18a is provided to avoid contact of the object with the inner wall of the hole.

図2,図5に示すように、ヘッド部ケース10における先端部11のドリル駆動軸20が突出する側とは反対側のケース外側面15bに、先端部11の放熱面積を拡大する凹入部19を、ドリル駆動軸20のための支持部13bの背後に位置させて設けてある。したがって、ドリル駆動軸20の回転及びドリル30の穴あけに起因するヘッド部ケース10における先端部11の温度上昇を効果的に抑制することができる。   As shown in FIGS. 2 and 5, a recessed portion 19 that enlarges the heat radiation area of the tip end portion 11 is formed on the case outer surface 15 b of the head portion case 10 on the side opposite to the side from which the drill drive shaft 20 protrudes. Is located behind the support portion 13b for the drill drive shaft 20. Therefore, the temperature rise of the front end portion 11 in the head portion case 10 due to the rotation of the drill drive shaft 20 and the drilling of the drill 30 can be effectively suppressed.

図6(a)は、ドリル30をドリル駆動軸20に取付ける連結手段60のドリル30が外された状態を示す断面図である。図6(b)は、連結手段60のドリル30が取付けられた状態を示す断面図である。これらの図に示すように、連結手段60は、ドリル駆動軸20に設けられたドリル取付け孔21及び連結ネジ61と、ドリル30の基部に設けられた連結部31とを備えて構成してある。   FIG. 6A is a cross-sectional view showing a state in which the drill 30 of the connecting means 60 for attaching the drill 30 to the drill drive shaft 20 is removed. FIG. 6B is a cross-sectional view showing a state where the drill 30 of the connecting means 60 is attached. As shown in these drawings, the connecting means 60 includes a drill mounting hole 21 and a connecting screw 61 provided in the drill drive shaft 20, and a connecting portion 31 provided at the base of the drill 30. .

ドリル取付け孔21は、ドリル駆動軸20のヘッド部ケース10の外部に突出する端面20bと、ドリル駆動軸20の内部に設定された奥端とにわたって、奥側ほど内径が小なる奥細り状態に形成して設けられている。   The drill mounting hole 21 is in a narrowed state in which the inner diameter becomes smaller toward the back side over the end surface 20b of the drill driving shaft 20 protruding outside the head case 10 and the back end set inside the drill driving shaft 20. It is formed and provided.

ドリル30の連結部31はテーパシャンクに形成してある。つまり、ドリル30の錐部32に連結している側とは反対側に位置する先端31aがドリル駆動軸20のドリル取付け孔21に挿入する方向での先端になり、かつこの先端側ほど外径が小になる先細り状態に形成されている。連結部31のうちドリル30の側の端部は、ドリル30の外径よりも太く形成しておくのが望ましい。これにより、ドリル30の把持力を高めることができる。また、連結部31のもう一方の端部の外径は先細に構成する。これにより、連結部31の面積をできるだけ広く確保しつつ、ドリル取付け孔21と連結部31との締結、取外し時に、両者のくさび効果が適度に発揮されるように構成する。
ドリル30の連結部31の端部にはネジ部34としてメネジ孔33を設けてある。メネジ孔33は、連結部31のドリル取付け孔21に挿入する方向での先端31aに開口している。尚、当該メネジ孔33の代わりにオネジを突出形成させるものであっても良い。
The connecting portion 31 of the drill 30 is formed in a taper shank. That is, the tip 31a located on the side opposite to the side connected to the conical portion 32 of the drill 30 is the tip in the direction of insertion into the drill mounting hole 21 of the drill drive shaft 20, and the outer diameter of the tip is closer to the tip. The taper is formed in a tapered state in which becomes smaller. The end of the connecting portion 31 on the drill 30 side is preferably formed thicker than the outer diameter of the drill 30. Thereby, the gripping force of the drill 30 can be increased. Further, the outer diameter of the other end of the connecting portion 31 is tapered. Thereby, while ensuring the area of the connection part 31 as wide as possible, it is comprised so that the wedge effect of both may be exhibited moderately at the time of the fastening of the drill attachment hole 21 and the connection part 31, and removal.
A female screw hole 33 is provided as a screw part 34 at the end of the connecting part 31 of the drill 30. The female screw hole 33 opens at the tip 31a in the direction of insertion into the drill mounting hole 21 of the connecting portion 31. In place of the female screw hole 33, a male screw may be protruded.

連結ネジ61は、ネジ部62がドリル取付け孔21に位置し、操作部63がドリル駆動軸20のドリル取付け孔21が位置する側とは反対側の端部に設けられた操作孔23に位置する状態でドリル駆動軸20に回転自在に支持されている。尚、当該連結ネジ61は、必ずしも図6に示すようなオネジである必要はなく、連結部31において上記メネジ孔33の代わりにオネジが突出形成される場合には、それに適合するメネジで構成することもできる。   The connecting screw 61 has a screw portion 62 positioned in the drill mounting hole 21 and an operation portion 63 positioned in the operation hole 23 provided at the end of the drill drive shaft 20 opposite to the side where the drill mounting hole 21 is positioned. In this state, the drill drive shaft 20 is rotatably supported. The connecting screw 61 does not necessarily have to be a male screw as shown in FIG. 6. If a male screw protrudes from the connecting portion 31 instead of the female screw hole 33, the connecting screw 61 is configured with a female screw that matches the male screw. You can also.

図6(b)に示すように、ドリル30の連結部31がドリル駆動軸20のドリル取付け孔21に挿入され、連結部31のメネジ孔33の開口に連結ネジ61のネジ軸部61の先端が係入すると、連結ネジ61の操作部63が正回転方向に回転操作されることにより、操作部63の操作孔23の奥側に位置する端部が操作孔23の底面に当接し、メネジ孔33に螺合して回転するネジ軸部62が操作孔23の底面を反力点にして連結部31をドリル取付け孔21の奥側に引き寄せ操作する。このとき、ドリル駆動軸20の開口端部に形成した工具係止面20bをレンチ等で保持しつつ、連結ネジ61を締結する。連結部31の外周面がドリル取付け孔21の内周面に圧接されると、連結手段60は、連結作用状態になり、連結部31をドリル駆動軸20に摩擦で連結させてドリル30をドリル駆動軸20に一体回転自在に連結する。   As shown in FIG. 6B, the connecting portion 31 of the drill 30 is inserted into the drill mounting hole 21 of the drill drive shaft 20, and the tip of the screw shaft portion 61 of the connecting screw 61 is inserted into the female screw hole 33 of the connecting portion 31. When the operating portion 63 of the connecting screw 61 is rotated in the forward rotation direction, the end portion of the operating portion 63 located on the far side of the operating hole 23 comes into contact with the bottom surface of the operating hole 23, and the female screw is engaged. The screw shaft portion 62 that rotates by being screwed into the hole 33 pulls the connecting portion 31 toward the back side of the drill mounting hole 21 with the bottom surface of the operation hole 23 as a reaction point. At this time, the connecting screw 61 is fastened while holding the tool locking surface 20b formed at the opening end of the drill drive shaft 20 with a wrench or the like. When the outer peripheral surface of the connecting portion 31 is brought into pressure contact with the inner peripheral surface of the drill mounting hole 21, the connecting means 60 enters a connecting state, and the connecting portion 31 is connected to the drill drive shaft 20 by friction to drill the drill 30. The drive shaft 20 is connected to the drive shaft 20 so as to freely rotate.

ドリル30をドリル駆動軸20から取り外す場合には、連結ネジ61を反時計方向に数回転だけ回し、連結ネジ61の頭部をドリル取付け孔21の端部から離間させる。この状態で、図10に示すドリルの取外し治具80をヘッドの先端部に位置決めし保持する。当該取外し治具80の前側プレート81に形成した係止溝82を、ドリル駆動軸20の工具係止面20bに係合させ、後側プレート83に螺合させた押出しネジ84を連結ネジ61の端部に近接させる。この状態で、押出しネジ84をねじ込んでゆき、連結ネジ61を介してテーパシャンク部31をドリル駆動軸20から離間させる。この後、ドリル30を回転させて連結ネジ61から離脱させる。
連結ネジ61には、抜止め用のストッパー64を設けてある。よって、ドリル30が装着されていない状態でも、連結ネジ61がドリル取付け孔21から脱落することはない。
When removing the drill 30 from the drill drive shaft 20, the connecting screw 61 is rotated several times counterclockwise, and the head of the connecting screw 61 is separated from the end of the drill mounting hole 21. In this state, the drill removing jig 80 shown in FIG. 10 is positioned and held at the tip of the head. The locking groove 82 formed in the front plate 81 of the removal jig 80 is engaged with the tool locking surface 20 b of the drill drive shaft 20, and the extrusion screw 84 screwed into the rear plate 83 is connected to the connection screw 61. Close to the edge. In this state, the extrusion screw 84 is screwed in, and the taper shank portion 31 is separated from the drill drive shaft 20 via the connection screw 61. Thereafter, the drill 30 is rotated and detached from the connection screw 61.
The connecting screw 61 is provided with a stopper 64 for preventing the removal. Therefore, even if the drill 30 is not attached, the connecting screw 61 does not fall out of the drill mounting hole 21.

〔別実施形態〕
図7は、第1の別実施形態に係るヘッド部Bを示す縦断正面図である。このヘッド部Bでは、回転伝動体42を構成するベベルギヤ部42aのうち入力ベベルギヤ41に噛合う輪体部42aRをボス部42aTに対して出力軸4が位置する側とは反対側に偏位させて形成する。併せて、平ギヤ部42bのうちギヤ連動機構50の入力平ギヤ51に噛合う輪体部42bRを、ボス部42bTに対して出力軸4が位置する側とは反対側に偏位させ、ベベルギヤ部42aのボス部42aTに外嵌させてある。
[Another embodiment]
FIG. 7 is a longitudinal sectional front view showing the head part B according to the first alternative embodiment. In the head portion B, the ring body portion 42aR that meshes with the input bevel gear 41 in the bevel gear portion 42a that constitutes the rotary transmission body 42 is displaced to the side opposite to the side where the output shaft 4 is located with respect to the boss portion 42aT. Form. At the same time, the ring body portion 42bR meshing with the input flat gear 51 of the gear interlocking mechanism 50 in the flat gear portion 42b is displaced to the side opposite to the side where the output shaft 4 is located with respect to the boss portion 42bT, and the bevel gear The boss portion 42aT of the portion 42a is externally fitted.

本構成であれば、ベベルギヤ部42aを支持するベアリングを、ボス部42aTの凹部に入り込ませた状態に設けることができる。このため、当該ベアリングも出力軸4の側に移動する。よって、ヘッド部ケース10の表面のうちドリル30が突出する側の平面をより引退させることができ、ヘッド部ケース10をさらに細く構成することができる。   If it is this structure, the bearing which supports the bevel gear part 42a can be provided in the state which entered the recessed part of the boss | hub part 42aT. For this reason, the bearing also moves to the output shaft 4 side. Therefore, the plane on the side from which the drill 30 projects out of the surface of the head part case 10 can be retreated, and the head part case 10 can be configured to be thinner.

図8は、第2の別実施形態に係るヘッド部Bを示す縦断正面図である。このヘッド部Bでは、ドリル駆動軸20に設けたドリル駆動ギヤ22の外縁部をドリル30の側に張り出させ、ドリル駆動ギヤ22に凹入部73を形成してある。この凹入部73にドリル駆動軸20の支持部72を進入させた状態に設けてある。   FIG. 8 is a longitudinal front view showing a head portion B according to a second alternative embodiment. In the head portion B, the outer edge portion of the drill drive gear 22 provided on the drill drive shaft 20 is projected to the drill 30 side, and a recess 73 is formed in the drill drive gear 22. The support part 72 of the drill drive shaft 20 is provided in the recessed part 73.

これにより、当該ヘッド部Bでは、ドリル駆動軸20の端部が突出している部位のケース外側面11aが、駆動ケース部13の基端側に形成されたケース外側面15aに対して大きく引退した形状となる。このように変位量Dを大きく確保する結果、ケース外側面11aからのドリル30の突出長さは同じにしつつも、ケース外側面15aからのドリル30の突出長さを小さくすることができる。よって、加工する対象品の作業空間の内部にヘッド部Bを挿入し易くなる。ケース外側面11aからのドリル30の突出長さは変わらないから、作業空間の底部の形状によっては、ドリル30の長さを有効に利用した孔部を穿孔することができる。   Thereby, in the said head part B, the case outer surface 11a of the site | part from which the edge part of the drill drive shaft 20 protrudes largely retracted with respect to the case outer surface 15a formed in the base end side of the drive case part 13. It becomes a shape. As a result of ensuring a large amount of displacement D in this way, it is possible to reduce the protruding length of the drill 30 from the case outer surface 15a while keeping the protruding length of the drill 30 from the case outer surface 11a the same. Therefore, it becomes easy to insert the head part B into the work space of the target product to be processed. Since the protruding length of the drill 30 from the case outer surface 11a does not change, a hole that effectively uses the length of the drill 30 can be drilled depending on the shape of the bottom of the work space.

は、第の別実施形態に係るヘッド部ケース10の先端部を示す横断平面図である。当該ヘッド部ケース10では、ドリル駆動軸20を支持する二つのベアリングのうち、ドリル30とは異なる側に設けたベアリング74の外径D1を、ドリル30の側に設けたベアリング75の外径D2よりも小さく構成してある。 FIG. 9 is a cross-sectional plan view showing the tip of the head case 10 according to the third alternative embodiment. In the head case 10, the outer diameter D1 of the bearing 74 provided on the side different from the drill 30 out of the two bearings supporting the drill drive shaft 20 is the outer diameter D2 of the bearing 75 provided on the drill 30 side. It is configured smaller.

この結果、ヘッド部ケースの先端部11のうちドリル30とは反対側の両角部に大きな面取り部18を設けることができる。よって、加工対象物の孔の内径がより小さい場合でも、ヘッド部ケースの先端部11を容易に挿入することができる。   As a result, large chamfered portions 18 can be provided at both corners on the opposite side of the tip 30 of the head portion case from the drill 30. Therefore, even when the inner diameter of the hole of the workpiece is smaller, the tip portion 11 of the head case can be easily inserted.

〔別実施例〕
(1)上述した実施例では、一枚の伝動平ギヤ53を備えてギヤ連動機構50を構成した例を示したが、これに替え、二枚以上の伝動平ギヤ53を備えて構成したギヤ連動機構を採用して実施してもよい。この場合も、本発明の目的を達成することができる。
[Another Example]
(1) In the above-described embodiment, an example in which the gear interlocking mechanism 50 is configured by including one transmission flat gear 53 is shown. However, instead of this, a gear that is configured by including two or more transmission flat gears 53 is provided. An interlocking mechanism may be adopted for implementation. Also in this case, the object of the present invention can be achieved.

本発明は、加工対象物の穴内壁に穴内から穴あけを行なう機械加工に使用するアングルヘッドに限らず、加工対象物の外面側から穴あけを行う機械加工に使用するアングルヘッドにも利用することができる。   The present invention is not limited to an angle head used for machining in which a hole is drilled in a hole inner wall of a workpiece from the inside of the hole, but can also be used for an angle head used for machining in which a hole is drilled from the outer surface side of the workpiece. it can.

4 出力軸
4a 出力軸芯
10 ヘッド部ケース
11 ヘッド部ケースの先端部
11a 先端部のケース外側面
15 ヘッド部ケースの基端側部
15a 基端側部のケース外側面
16 段差部
16a 段差部のケース外側面
20 ドリル駆動軸
20a ドリル軸芯
21 ドリル取付け孔
22 ドリル駆動ギヤ
42 回転伝動体
42a ベベルギヤ部
42b 平ギヤ部
42d ベベルギヤ軸芯
50 ギヤ連動機構
51 入力平ギヤ
51b 入力ギヤ軸芯
52 出力平ギヤ
52b 出力ギヤ軸芯
53 伝動平ギヤ
53b 伝動ギヤ軸芯
60 連結手段
61 連結ネジ
A ヘッド本体
B ヘッド部
L 直線
4 Output shaft 4a Output shaft core 10 Head portion case 11 Head portion case distal end portion 11a Tip portion case outer surface 15 Head portion case base end side portion 15a Base end side case outer surface 16 Step portion 16a Step portion Case outer surface 20 Drill drive shaft 20a Drill shaft core 21 Drill mounting hole 22 Drill drive gear 42 Rotating transmission element 42a Bevel gear portion 42b Flat gear portion 42d Bevel gear shaft core 50 Gear interlocking mechanism 51 Input flat gear 51b Input gear shaft core 52 Output flat Gear 52b Output gear shaft 53 Transmission spur gear 53b Transmission gear shaft 60 Connection means 61 Connection screw A Head body B Head portion L Straight line

Claims (3)

工作機械に装着されるヘッド本体と、
出力軸芯の周りに回転可能に前記ヘッド本体に設けられた出力軸と、
ドリルが装着され、前記出力軸芯に直交するドリル軸芯の周りに回転するドリル駆動軸と、
前記出力軸の回転を前記ドリル駆動軸に伝達する回転連動機構とを備え、
前記ドリルの一方に、ネジ部が形成されたテーパシャンク部を備えると共に、
前記ドリル駆動軸に、前記回転連動機構からの回転が伝達されるドリル駆動ギヤと、前記テーパシャンク部を挿入可能なテーパ状のドリル取付孔と、当該ドリル取付孔の底部に位置する貫通孔とが設けてあり、
前記ドリルを締結する連結ネジを、前記貫通孔を介して前記テーパシャンク部のネジ部に螺合可能に構成し
前記回転連動機構が、
前記出力軸と一体に回転する入力ベベルギヤと、
前記入力ベベルギヤに噛合しつつ前記出力軸芯に直交するベベルギヤ軸芯の周りに回転するベベルギヤ部、及び、当該ベベルギヤ部と同軸芯状に一体回転する平ギヤ部を有する回転伝動体と、
前記平ギヤ部に噛合して前記ベベルギヤ軸芯と平行な入力ギヤ軸芯の周りに回転する入力平ギヤと、
前記ベベルギヤ軸芯と平行な出力ギヤ軸芯の周りに回転する出力平ギヤと、
前記入力平ギヤと前記出力平ギヤとを連動させ、前記ベベルギヤ軸芯と平行な伝動ギヤ軸芯まわりに回転する伝動平ギヤとを有し、
前記ベベルギヤ軸芯と、前記入力ギヤ軸芯と、前記伝動ギヤ軸芯と、前記出力ギヤ軸芯と、前記ドリル軸芯とを、前記出力軸芯に平行な直線に沿って並設し、
前記ベベルギヤ部を、前記平ギヤ部に対して前記出力軸が位置する側とは反対側に配置してあるアングルヘッド。
A head body mounted on a machine tool;
An output shaft provided in the head body so as to be rotatable around an output shaft core;
A drill drive shaft mounted with a drill and rotating about a drill axis perpendicular to the output axis;
A rotation interlocking mechanism that transmits the rotation of the output shaft to the drill drive shaft,
One of the drills is provided with a taper shank portion in which a screw portion is formed,
A drill driving gear for transmitting rotation from the rotation interlocking mechanism to the drill driving shaft; a tapered drill mounting hole into which the tapered shank portion can be inserted; and a through hole located at the bottom of the drill mounting hole; Is provided,
The connecting screw for fastening the drill is configured to be screwable with the threaded portion of the tapered shank portion through the through hole ,
The rotation interlocking mechanism is
An input bevel gear that rotates integrally with the output shaft;
A rotation transmission body having a bevel gear portion rotating around a bevel gear shaft orthogonal to the output shaft core while meshing with the input bevel gear, and a flat gear portion rotating integrally with the bevel gear portion coaxially;
An input spur gear that meshes with the spur gear portion and rotates about an input gear shaft core parallel to the bevel gear shaft core;
An output spur gear that rotates about an output gear axis parallel to the bevel gear axis;
A transmission spur gear that interlocks the input spur gear and the output spur gear and rotates about a transmission gear shaft core parallel to the bevel gear shaft core;
The bevel gear shaft core, the input gear shaft core, the transmission gear shaft core, the output gear shaft core, and the drill shaft core are juxtaposed along a straight line parallel to the output shaft core,
The angle head which has arrange | positioned the said bevel gear part on the opposite side to the side in which the said output shaft is located with respect to the said flat gear part .
前記回転連動機構と前記ドリル駆動ギヤとを収容するヘッド部ケースの先端部を形成する表面のうち、前記ドリルの突出位置を含む平面が、当該平面に対して前記ヘッド部ケースの基端側に隣接する表面よりも引退した段差部となっている請求項1に記載のアングルヘッド。 Of the surface forming the distal end portion of the head portion case that houses the rotation interlocking mechanism and the drill drive gear, the plane including the protruding position of the drill is on the proximal end side of the head portion case with respect to the plane. angle head according to claim 1 that has a step portion retired than adjacent surfaces. 前記段差部と、当該段差部に対して前記ヘッド部ケースの基端側に隣接する表面との境界位置に、前記ドリルから飛散した切り粉を前記ドリルから離間する方向に飛散させる傾斜面を形成してある請求項2に記載のアングルヘッド。 At the boundary position between the stepped portion and the surface adjacent to the base end side of the head case with respect to the stepped portion, an inclined surface is formed that scatters chips scattered from the drill in a direction away from the drill. The angle head according to claim 2.
JP2010073824A 2010-03-26 2010-03-26 Angle head Active JP5498220B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2010073824A JP5498220B2 (en) 2010-03-26 2010-03-26 Angle head

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2010073824A JP5498220B2 (en) 2010-03-26 2010-03-26 Angle head

Publications (2)

Publication Number Publication Date
JP2011206852A JP2011206852A (en) 2011-10-20
JP5498220B2 true JP5498220B2 (en) 2014-05-21

Family

ID=44938527

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2010073824A Active JP5498220B2 (en) 2010-03-26 2010-03-26 Angle head

Country Status (1)

Country Link
JP (1) JP5498220B2 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015174199A (en) * 2014-03-17 2015-10-05 東芝機械株式会社 Off-set tool attachment and machine tool
KR101528912B1 (en) * 2014-08-18 2015-06-16 신재춘 Horizontal type changing apparatus of vertical type machining center
KR101520267B1 (en) * 2014-11-14 2015-05-15 (주)신태양 Caliper housing Processing Method
CN108098425B (en) * 2018-01-30 2024-05-03 南京信息职业技术学院 Radial drilling equipment for inner wall of cylinder body type deep hole
CN108356752A (en) * 2018-05-08 2018-08-03 广州隆控机电设备有限公司 A kind of fastener for bolt
CN114247913A (en) * 2020-09-22 2022-03-29 上海电气电站设备有限公司 Manual lateral drilling device

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58169910U (en) * 1982-05-10 1983-11-12 壽工業株式会社 Machine tool attachment drop prevention device
JPS5942810U (en) * 1982-09-14 1984-03-21 油谷重工株式会社 drilling device
JPS60150926A (en) * 1984-01-17 1985-08-08 Sanko Tokushu Kinzoku Kogyo Kk Non-standard angle head for boring
JPS63147244U (en) * 1987-03-19 1988-09-28

Also Published As

Publication number Publication date
JP2011206852A (en) 2011-10-20

Similar Documents

Publication Publication Date Title
JP5498220B2 (en) Angle head
JP4747282B2 (en) Insert removable drill
JP4672604B2 (en) Machining depth adjustment device for rotary tools
JP5011366B2 (en) Tool holder and method for assembling the tool holder
JP5873670B2 (en) Angle head type tool holder
JP5575876B2 (en) Fastening chuck
US9682453B2 (en) Tool changer for machine tool
KR101022592B1 (en) Structure of multi-spindle head for a machine tool
JP4948844B2 (en) Rotating tool turret
TWI395625B (en) Rotating tool loading and unloading device and the rotating tool
JP5728316B2 (en) Multi-axis machine tool
JP2013158883A (en) Gear machining cutter
JP3146237U (en) Rotating tool mounting shaft and rotating tool equipped with the mounting shaft
KR20020001560A (en) Turning Machining Tool
JP4689360B2 (en) Drill holder
JP2004130423A (en) Angle head
JP2007160472A5 (en)
JP2010274342A (en) Cutting tool
JP2006129611A (en) Machine tool
JP5961577B2 (en) Tool holder and machine tool
JP2007160472A (en) Cutting method and device of spectacle hole
JP2008055576A (en) Rotary tool turret
JP4420834B2 (en) Connection structure of rotating shaft
JP5345460B2 (en) U-axis drive structure of machine tool
JP2812884B2 (en) Hole processing equipment

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20120411

A711 Notification of change in applicant

Free format text: JAPANESE INTERMEDIATE CODE: A712

Effective date: 20120411

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A821

Effective date: 20120411

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20130718

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20130725

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20130918

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20140206

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20140307

R150 Certificate of patent or registration of utility model

Ref document number: 5498220

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

S111 Request for change of ownership or part of ownership

Free format text: JAPANESE INTERMEDIATE CODE: R313117

S531 Written request for registration of change of domicile

Free format text: JAPANESE INTERMEDIATE CODE: R313531

S533 Written request for registration of change of name

Free format text: JAPANESE INTERMEDIATE CODE: R313533

R350 Written notification of registration of transfer

Free format text: JAPANESE INTERMEDIATE CODE: R350

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250