JPH0431812B2 - - Google Patents
Info
- Publication number
- JPH0431812B2 JPH0431812B2 JP60035182A JP3518285A JPH0431812B2 JP H0431812 B2 JPH0431812 B2 JP H0431812B2 JP 60035182 A JP60035182 A JP 60035182A JP 3518285 A JP3518285 A JP 3518285A JP H0431812 B2 JPH0431812 B2 JP H0431812B2
- Authority
- JP
- Japan
- Prior art keywords
- tool
- conical
- tightening
- hole
- fitting hole
- 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.)
- Expired - Lifetime
Links
- 230000004323 axial length Effects 0.000 claims description 10
- 238000005452 bending Methods 0.000 description 8
- 239000002826 coolant Substances 0.000 description 8
- 238000005553 drilling Methods 0.000 description 5
- 238000003754 machining Methods 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 238000003780 insertion Methods 0.000 description 2
- 230000037431 insertion Effects 0.000 description 2
- 238000003801 milling Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 244000145845 chattering Species 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 239000012809 cooling fluid Substances 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23B—TURNING; BORING
- B23B31/00—Chucks; Expansion mandrels; Adaptations thereof for remote control
- B23B31/02—Chucks
- B23B31/10—Chucks characterised by the retaining or gripping devices or their immediate operating means
- B23B31/107—Retention by laterally-acting detents, e.g. pins, screws, wedges; Retention by loose elements, e.g. balls
- B23B31/1075—Retention by screws
- B23B31/1077—Retention by screws acting on a floating pin
Description
【発明の詳細な説明】
この発明は、工具ホルダのテーパシヤンクを受
入れる切頭円錐状受孔が形成され、この受孔の周
縁を囲む環状端面を有する工作機械の工具取付装
置に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a tool mounting device for a machine tool in which a truncated conical receiving hole for receiving a taper shank of a tool holder is formed and an annular end surface surrounding the periphery of the receiving hole.
スピンドルヘツド（DIN2079）と、工具ホル
ダのテーパシヤンク（DIN2080）との間で最も
頻繁に使用される結合構造が、今日の高出力工作
機械の全加工力を工具へ問題なく伝達するのに最
早や適していないことが判明している。
DIN2080にもとづくISOテーパ50を例にとると、
テーパ部の最大直径が約70mmであるのに対して、
テーパシヤンクを受入れるスピンドルの外径は
128mmである。したがつて、工具に作用する横方
向力のすべてが、工具機械の工具スピンドルに比
較して薄いテーパシヤンクによつてスピンドルへ
伝達されなければならない。このような構成で
は、切頭円錐状受孔内でテーパシヤンクがゆるむ
ことがないので、スピンドル内に設けられ、テー
パシヤンクを受孔内へ引込む保持手段によつて、
極めて高いレベルの保持力を発生させる必要があ
る。自動工具交換機能付工作機械すなわちマシニ
ングセンタの場合、工具交換動作を行なう際、上
記保持手段によつてテーパシヤンクをゆるめるこ
とができなければならない。そのため、ダイアフ
ラム形ばね作動式締付爪がしばしば使用される。
ダイアフラム形ばねが負荷から解放されると、こ
れらの爪が、テーパシヤンクの端部の頭付ボルト
の頭部背後へ接近し、残余の力でもつてテーパシ
ヤンクを受孔内へ引込む。この動作が終ると、ダ
イアフラム形ばねのバイアスレベルが極めて高く
ても、引込力は相当減少して、スピンドルからか
なり突出している工具に作用する半径方向の大き
な切削力により、テーパシヤンクはスピンドル内
の受孔中で一時的にゆるめられることになる。し
かし、このときチヤターリングが発生するという
欠点がある。さらにテーパシヤンクの最大直径は
スピンドルの外径よりかなり小さい工具ホルダの
曲げ強さはそれが締めつけられていないときの最
小直径で決まるから、工具ホルダの曲げ強さはテ
ーパシヤンクの最大直径のみに依存する。 The most frequently used coupling structure between the spindle head (DIN 2079) and the taper shank of the tool holder (DIN 2080) is no longer suitable for problem-free transmission of the full machining forces of today's high-power machine tools to the tool. It turns out that it is not.
Taking ISO taper 50 based on DIN2080 as an example,
While the maximum diameter of the tapered part is approximately 70mm,
The outer diameter of the spindle that accepts the taper shank is
It is 128mm. All lateral forces acting on the tool must therefore be transmitted to the spindle by means of a tapered shank, which is thin compared to the tool spindle of the tool machine. In such an arrangement, the taper shank does not loosen within the truncated conical receiving hole, so that the retaining means provided in the spindle for drawing the tapered shank into the receiving hole.
It is necessary to generate an extremely high level of holding force. In the case of a machine tool with an automatic tool change function, that is, a machining center, the holding means must be able to loosen the taper shank during a tool change operation. For this reason, diaphragm-type spring-actuated clamping pawls are often used.
When the diaphragm spring is unloaded, these pawls approach the end of the taper shank behind the head of the headed bolt and with residual force pull the taper shank into the receiving hole. At the end of this action, even at very high bias levels in the diaphragm spring, the retraction force is considerably reduced and the taper shank is forced into its receptacle in the spindle due to the large radial cutting forces acting on the tool, which protrudes significantly from the spindle. It will be temporarily loosened in the hole. However, there is a drawback that chattering occurs at this time. Further, the maximum diameter of the taper shank is significantly smaller than the outer diameter of the spindle, and since the bending strength of the tool holder is determined by its minimum diameter when it is untightened, the bending strength of the tool holder depends only on the maximum diameter of the taper shank.
また公知の穿孔工具（ドイツ特許第3108439号）
によると、工具のヘツド部は、工具ホルダ内の円
筒状嵌合孔に係入する円筒状スピゴツト部を有す
る。円筒状嵌合孔の領域で、工具ホルダは半径方
向反対側に延在する２個の雌ねじ部を有し、各雌
ねじ部には円錐状凹部が形成された締付ねじがね
じ込まれる。スピゴツト部の横孔内に半径方向に
移動自在な締付ピンが設けられる。この締付ピン
の各端部に円錐状突起が形成され、これら突起が
締付ねじの円錐状凹部と協働する。雌ねじ部の軸
線と横孔の軸線とは以下のような配置関係にあ
る。すなわち、一方の締付ねじが締付けつけらる
と、この締付ねじが締付ピンに作用して、スピゴ
ツト部を囲む環状面を工具ホルダの端面へ押し付
ける。この結合構造によれば、取付精度、交換精
度が向上し、高レベルのトルクを伝達でき、極め
て高い曲げ強さを有する結合構造が穿孔工具の部
品間で得られる。しかしながら、公知の穿孔工具
では、工具ホルダ自身がテーパシヤンクを有し、
このシヤンクによつて工作機械の工具スピンドル
に嵌入されるので、工具ホルダが工作機械工具ス
ピンドルへ結合するに際し先に述べたような問題
が発生する。 Also known drilling tool (German patent no. 3108439)
According to U.S. Pat. In the area of the cylindrical fitting hole, the tool holder has two radially oppositely extending internal threads, into each of which a tightening screw formed with a conical recess is screwed. A radially movable clamping pin is provided in the lateral hole of the spigot. A conical projection is formed at each end of the clamping pin, which projections cooperate with a conical recess of the clamping screw. The axis of the female threaded portion and the axis of the horizontal hole have the following arrangement relationship. That is, when one of the tightening screws is tightened, this tightening screw acts on the tightening pin and presses the annular surface surrounding the spigot portion against the end surface of the tool holder. According to this joint structure, mounting accuracy and replacement accuracy are improved, a high level of torque can be transmitted, and a joint structure having extremely high bending strength can be obtained between the parts of the drilling tool. However, in known drilling tools, the tool holder itself has a taper shank,
The shank is inserted into the tool spindle of the machine tool, so that the problems mentioned above occur when the tool holder is connected to the tool spindle of the machine tool.
この発明は上記のような従来の装置の問題を解
決するものであり、工作機械の工具スピンドルと
工具ホルダとの間の結合の曲げ抵抗力を高め、高
レベルのトルク伝達を可能とし、必要に応じて従
来のテーパシヤンクを具備した工具ホルダのスピ
ンドルヘツドの嵌入をも可能にした取付装置を提
供する。 This invention solves the problems of conventional devices as described above by increasing the bending resistance of the connection between the tool spindle and tool holder of a machine tool, allowing high levels of torque transmission, and providing the required Accordingly, there is provided a mounting device which also allows the insertion of a spindle head of a tool holder equipped with a conventional taper shank.
この発明によると、切頭円錐状受孔の領域にお
いて、スピンドルヘツドは第１工具のテーパシヤ
ンクに換えて円筒状スピゴツト部を有する第２工
具ホルダの円筒状スピゴツト部を受入れる円筒状
嵌合孔を有し、この嵌合孔の直径が切頭円錐状受
孔の最大直径より若干小さく、かつ端面から測つ
た嵌合孔の端部まで軸方向長さが切頭円錐状受孔
の端部までの軸方向長さより短かく、円筒状嵌合
孔の領域において、スピンドルヘツドは半径方向
反対向きに延びる２個の雌ねじ部を有し、各雌ね
じ部には円錐状突起または円錐状凹部が形成され
た締付けねじが螺合し、スピゴツト部の横孔には
締付ピンが半径方向に移動自在に設けられ、この
締付ピンの各端部に円錐状凹部または円錐状突起
が形成され、該凹部および突起はそれぞれ締付ね
じの円錐状突起または円錐状凹部と協働し、雌ね
じの軸の端面からの距離は横孔の軸が工具ホルダ
の環状面からの距離よりも若干大きくて、締付ね
じの一方を締付けると、この締付ねじは締付ピン
に作用して環状面と端面とを互いに近づける方向
へ押圧する。 According to the invention, in the area of the truncated conical receiving hole, the spindle head has a cylindrical receiving hole for receiving the cylindrical spigot part of the second tool holder, which has a cylindrical spigot part instead of the tapered shank of the first tool. However, the diameter of this fitting hole is slightly smaller than the maximum diameter of the truncated conical receiving hole, and the axial length measured from the end face to the end of the truncated conical receiving hole is the same as that of the truncated conical receiving hole. Shorter than the axial length, in the region of the cylindrical fitting hole, the spindle head has two internally threaded sections extending in radially opposite directions, each internally threaded section being formed with a conical projection or a conical recess. A tightening screw is screwed into the spigot portion, and a tightening pin is provided in the horizontal hole of the spigot section so as to be movable in the radial direction.A conical recess or a conical protrusion is formed at each end of the tightening pin, and a conical recess or a conical protrusion is formed at each end of the tightening pin. The protrusions cooperate with conical protrusions or conical recesses of the tightening screw, respectively, and the distance from the end face of the shaft of the internal thread is slightly larger than the distance of the axis of the transverse hole from the annular surface of the tool holder, When one of the two is tightened, the tightening screw acts on the tightening pin and presses the annular surface and the end surface toward each other.
この発明は、このために工作機械のスピンドル
ヘツド内に切頭円錐状受孔と、円筒状嵌合孔とを
設けることによつて、従来のテーパシヤンクを具
備した第１工具ホルダまたは円筒状スピゴツト部
と、その中に半径方向に移動自在に設けた締付ピ
ンとを具備した第２工具ホルダをスピンドルへ選
択的に嵌入させるようにしたものである。工具の
使用者はテーパシヤンクを具備した従来の第１工
具ホルダを継続して用いて回転または曲げモーメ
ントがそれ程大きくない作業を行うことができ
る。さらに使用者は、円筒状スピゴツト部により
スピンドルヘツドの円筒状嵌合孔内に直接受入れ
られる第２工具ホルダも選択的に使用することも
できる。この工具ホルダを用いれば、スピンドル
ヘツドと工具ホルダとの間に曲げに強くかつ高ト
ルクの伝達が可能な結合が得られる。すなわち、
締付ねじの軸と締付クランプピンの軸との間の軸
方向ずれのために、有効な軸方向力成分により締
付ねじは軸方向にも動かされ、大きなバイアス力
でもつて工具ホルダの環状面をスピンドルヘツド
の端面へ押圧する。環状面と端面とが互いに強く
合体するので、これらの面での摩擦係合を介して
トルクの大部分が伝達される。トルクの残りの部
分は締付ねじと締付ピンとにより伝達される。ま
た、環状面が端面に確実に係着するとき、工具に
作用する横方向の力が、これらの面によつてスピ
ンドルの比較的大きな直径部分へ伝達されること
も重要である。これにより工具スピンドルと工具
ホルダとの間の結合が曲げに対し非常に強くな
る。すなわち加工時における工具の振動が少な
く、工作機械のパワーの工具への伝達が良好に行
なわれ、さらに工具に対する片持梁りの長さも増
大できる。そして切削効率が高まり、加工時間が
短縮される。他の利点として、締付動作に関係す
ると共に、頻繁な工具交換により疲労する可能性
のあるすべての素子、すなわち締付ねじまたは締
付ピンを簡単に交換できることがあげられる。 For this purpose, the present invention provides a truncated conical receiving hole and a cylindrical fitting hole in the spindle head of the machine tool, so that the first tool holder or cylindrical spigot portion with a conventional taper shank is provided. A second tool holder, which includes a second tool holder and a fastening pin movably provided in the radial direction, is selectively inserted into the spindle. The tool user can continue to use the conventional first tool holder with the tapered shank to perform operations where rotational or bending moments are not too large. Additionally, the user may also optionally use a second tool holder which is received directly into the cylindrical fitting hole of the spindle head by means of a cylindrical spigot portion. This tool holder provides a connection between the spindle head and the tool holder that is resistant to bending and capable of transmitting high torque. That is,
Due to the axial misalignment between the axis of the clamping screw and the axis of the clamping clamp pin, the effective axial force component causes the clamping screw to move axially as well, and even with a large bias force, the annular shape of the tool holder Press the face against the end face of the spindle head. Since the annular surface and the end surface fit strongly together, most of the torque is transmitted through the frictional engagement on these surfaces. The remainder of the torque is transmitted by the clamping screw and clamping pin. It is also important that when the annular surfaces securely engage the end surfaces, the lateral forces acting on the tool are transmitted by these surfaces to the relatively large diameter section of the spindle. This makes the connection between the tool spindle and the tool holder very strong against bending. That is, the vibration of the tool during machining is reduced, the power of the machine tool is well transmitted to the tool, and the length of the cantilever beam relative to the tool can be increased. This increases cutting efficiency and reduces machining time. Another advantage is that all elements involved in the clamping operation and which can become fatigued due to frequent tool changes, ie clamping screws or clamping pins, can be easily replaced.
以下に実施例によりこの発明を詳細に説明す
る。 The present invention will be explained in detail with reference to Examples below.
工作機械の工具スピンドル１は主軸台２内に回
転自在に取付けられている。スピンドル１のヘツ
ド１ａに切頭円錐状受孔３ａ，３ｂが形成されて
いる。受孔３ａ，３ｂはDIN2079または対応す
るISO規格に相当する形状のものである。受孔３
ａの周縁は、スピンドルの軸Ａに対して直角に延
びる平坦な環状端面４で囲まれている。 A tool spindle 1 of a machine tool is rotatably mounted in a headstock 2. The head 1a of the spindle 1 has frusto-conical receiving holes 3a, 3b formed therein. The receiving holes 3a, 3b have a shape corresponding to DIN2079 or a corresponding ISO standard. Receiving hole 3
The periphery of a is surrounded by a flat annular end face 4 extending at right angles to the axis A of the spindle.
受孔３ａ，３ｂの領域において、スピンドルヘ
ツド１ａはこれらと同心の円筒状嵌合孔５を有す
る。嵌合孔５の直径Ｄは受孔３ａ，３ｂの最大直
径Ｄ１より若干小さい。端面４から測つて、嵌合
孔５の端部までの長さＬは、受孔３ｂの端部まで
の軸方向長さＬ１より短かい。 In the region of the receiving holes 3a, 3b, the spindle head 1a has a cylindrical receiving hole 5 concentric therewith. The diameter D of the fitting hole 5 is slightly smaller than the maximum diameter D1 of the receiving holes 3a and 3b. The length L from the end surface 4 to the end of the fitting hole 5 is shorter than the axial length L1 to the end of the receiving hole 3b.
嵌合孔５の直径Ｄの選択に際しては、端面４と
嵌合孔５の先端との間に軸方向で充分な長さがあ
り、かつ第３図に示す第１工具ホルダ２０のテー
パシヤンク６を確実に支持するのに適した部分３
ａが形成されるようにしなければならない。嵌合
孔５の直径Ｄは受孔３ａの最大直径Ｄ１の約４〜
10％、好ましくは約6.5％だけ小さいとよいこと
が判明している。ISO−50によるテーパの場合に
は、受孔３ａの最大直径Ｄ１は69.85mmである。
嵌合孔５の直径を65.5mmに選択したとすると、受
孔３ａの軸方向長さは約14.9mmである。テーパシ
ヤンク６の前端を適切に支持するには、これだけ
の長さがあれば充分である。 When selecting the diameter D of the fitting hole 5, make sure that there is a sufficient length in the axial direction between the end surface 4 and the tip of the fitting hole 5, and that the taper shank 6 of the first tool holder 20 shown in FIG. Part 3 suitable for reliable support
a must be formed. The diameter D of the fitting hole 5 is about 4 to the maximum diameter D1 of the receiving hole 3a.
It has been found that it is better to be smaller by 10%, preferably about 6.5%. In the case of taper according to ISO-50, the maximum diameter D1 of the receiving hole 3a is 69.85 mm.
If the diameter of the fitting hole 5 is selected to be 65.5 mm, the axial length of the receiving hole 3a is approximately 14.9 mm. This length is sufficient to properly support the front end of the tapered shank 6.
テーパシヤンク６の後端も受孔３ｂで支持され
ている嵌合孔５は受孔の全長Ｌ１に亘つて延びて
いない。端面４から測つて、嵌合孔５の端部まで
の軸方向長さＬは受孔３ｂの端部までの軸方向長
さＬ１の約1/2〜2/3にする必要がある。これによ
り、テーパシヤンク６の後端を充分に支持できる
受孔３ｂが形成される。 The fitting hole 5, whose rear end of the taper shank 6 is also supported by the receiving hole 3b, does not extend over the entire length L1 of the receiving hole. The axial length L from the end surface 4 to the end of the fitting hole 5 needs to be approximately 1/2 to 2/3 of the axial length L1 to the end of the receiving hole 3b. Thereby, a receiving hole 3b is formed that can sufficiently support the rear end of the taper shank 6.
さらに嵌合孔５の領域において、スピンドルヘ
ツド１ａには半径方向反対側に延びる２個の雌ね
じ部７，８が形成され、各雌ねじ部７，８に締付
ねじ９，１０が半径方向からねじ込まれる。締付
ねじ９は円錐状突起９ａを有し、締付ねじ１０は
切頭円錐状凹部１０ａを有する。雌ねじ部７，８
の軸線Ａ１は端面４からａ１だけ離間している。 Furthermore, in the region of the fitting hole 5, the spindle head 1a is formed with two internally threaded portions 7, 8 extending radially oppositely, into each female threaded portion 7, 8 a tightening screw 9, 10 is screwed from the radial direction. It will be done. The clamping screw 9 has a conical projection 9a, and the clamping screw 10 has a truncated conical recess 10a. Female thread parts 7, 8
The axis A1 of is spaced apart from the end face 4 by a1.
工具ホルダ１１の円筒状スピゴツト部１２が極
めて僅かなすきまを介して（実際は殆んどすきま
がない）嵌合孔５に嵌入される。この工具ホルダ
１１の自由端１１ａには例えば穿孔ヘツド、内側
丸削り工具、ミーリング工具、リーマまたはブロ
ーチその他のような工具が装着される。これらの
工具は工具ホルダ１１へ固定されるか、交換可能
に取付けられる。また中間部材を介して接続して
もよい。 The cylindrical spigot portion 12 of the tool holder 11 is fitted into the fitting hole 5 with an extremely small gap (actually, there is almost no gap). The free end 11a of this tool holder 11 is fitted with tools, such as, for example, a drilling head, an internal turning tool, a milling tool, a reamer or a broach, or the like. These tools are fixed to the tool holder 11 or are replaceably attached. Alternatively, they may be connected via an intermediate member.
スピゴツト部１２に形成した横孔１３に、円筒
状締付ピン１４を半径方向に変位自在に取付け
る。締付ピン１４の一端には円錐状突起１４ａが
形成され、この突起で切頭円錐状凹部に１０ａに
係合する。他端には切頭円錐状凹部１４ｂが形成
され、ここに円錐状突起部９ａが係合する。横孔
１３の軸線Ａ２の距離ａ２は前述の距離ａ１より
若干小さい。 A cylindrical tightening pin 14 is attached to a horizontal hole 13 formed in the spigot portion 12 so as to be freely displaceable in the radial direction. A conical projection 14a is formed at one end of the clamping pin 14 and engages with the frusto-conical recess 10a. A truncated conical recess 14b is formed at the other end, into which the conical protrusion 9a engages. The distance a2 between the axis A2 of the horizontal hole 13 is slightly smaller than the aforementioned distance a1.
工具ホルダ１１を冷媒供給リングで囲んでもよ
い。工具ホルダ１１が回転ホルダの場合、冷媒供
給リングは静止して配置される。この冷媒供給リ
ングを介して、工具ホルダの軸方向孔１５ａへ供
給された冷却流体は工具の切刃へ導びかれる。 The tool holder 11 may be surrounded by a coolant supply ring. If the tool holder 11 is a rotating holder, the coolant supply ring is arranged stationary. Via this coolant supply ring, the cooling fluid supplied to the axial hole 15a of the tool holder is guided to the cutting edge of the tool.
工具を交換するには、締付ねじの前端の円錐状
突起９ａが嵌合孔５から離脱するまで締付ねじ９
を緩めるだけでよい。これに伴い、締付ピン１４
の円錐状端部１４ａが円錐状凹部１０ａから離脱
するまで締付ピン１４を横孔１３内で移動できる
ので、工具ホルダ１１を左方向へ動かしてスピン
ドルヘツド１ａからはずすことができる。 To replace the tool, tighten the tightening screw 9 until the conical protrusion 9a at the front end of the tightening screw separates from the fitting hole 5.
All you have to do is loosen it. Along with this, the tightening pin 14
The clamping pin 14 can be moved in the horizontal hole 13 until the conical end 14a of the tool holder 14 is disengaged from the conical recess 10a, so that the tool holder 11 can be moved to the left and removed from the spindle head 1a.
次に他の工具の工具ホルダ１１を嵌合すれば、
スピゴツト部１２が嵌合孔５に係合する。受孔３
ａの直径Ｄ１は嵌合孔５の直径Ｄよりも外側へ増
大しているので、受孔３ａはスピゴツト部１２の
挿入動作を容易にしている。しかして締付ねじ９
が半径方向内方へ向つてねじ部７へねじ込まれる
と、円錐状突起９ａが締付ピン１４を半径方向へ
移動するので、締付ピン１４の円錐状突起１４ａ
が締付ねじ１０の凹部１０ａに再び係合する。締
付ねじ９の半径方向に有効な締付力が締付ねじ１
０に等しく大きさの反対方向の反作用力を発生す
る。軸線Ａ１，Ａ２が軸方向で互いにずれている
から、２個の締付ねじ９，１０のそれぞれが等し
い大きさの軸方向力成分を発生する。したがつ
て、締付ねじ９の突起の円錐角が90°の場合、こ
の締付ねじの締付力により全体の締付力が倍増さ
れると共に、工具ホルダ１１の環状面１６が端面
４へ押圧される。この時の押圧力は半径方向の締
付力の２倍である。第１図から明らかなように、
環状面１６の外径は端面４の外径に等しくスピン
ドルヘツド１ａの直径にほぼ対応する。したがつ
て、工具ホルダ１１は、これらの面１６，４を介
し極めて広い範囲でスピンドルヘツド１ａにより
支持される。このようにして、曲げに対して強く
かつがたつきが殆んどない結合が２個の部材間に
得られる。かかる構成例はこの発明の重要な特徴
をなす。 Next, if the tool holder 11 of another tool is fitted,
The spigot portion 12 engages with the fitting hole 5. Receiving hole 3
Since the diameter D1 of the receiving hole 3a is larger outwardly than the diameter D of the fitting hole 5, the receiving hole 3a facilitates the insertion operation of the spigot portion 12. However, the tightening screw 9
is screwed radially inward into the threaded portion 7, the conical protrusion 9a moves the tightening pin 14 in the radial direction, so that the conical protrusion 14a of the tightening pin 14
re-engages with the recess 10a of the tightening screw 10. The effective tightening force in the radial direction of the tightening screw 9 is the tightening force of the tightening screw 1.
Generates a reaction force in the opposite direction of magnitude equal to zero. Since the axes A1 and A2 are offset from each other in the axial direction, each of the two tightening screws 9 and 10 generates an axial force component of equal magnitude. Therefore, when the cone angle of the protrusion of the tightening screw 9 is 90°, the tightening force of this tightening screw doubles the overall tightening force, and the annular surface 16 of the tool holder 11 moves toward the end surface 4. Pressed. The pressing force at this time is twice the radial tightening force. As is clear from Figure 1,
The outer diameter of the annular surface 16 is equal to the outer diameter of the end face 4 and approximately corresponds to the diameter of the spindle head 1a. The tool holder 11 is therefore supported by the spindle head 1a over a very wide area via these surfaces 16, 4. In this way, a bending-resistant and virtually rattling-free bond is obtained between the two parts. Such a configuration example constitutes an important feature of the present invention.
円錐状突起９ａを有する締付ねじ９、円錐状凹
部１０ａを有する締付ねじ１０、および一端に円
錐状突起１４ａを備え、他端に円錐状凹部１４ｂ
を設けて、ねじ９，１０に対応する締付ピン１４
を使用することは、実際上特に有利であることが
判明している。しかしながら、この構成の変形例
として、両締付ねじにそれぞれ円錐状凹部を形成
し、締付ピンの両端にそれぞれ対応する突起を形
成してもよい。逆に両締付ねじに円錐状突起を形
成し、締付ピンの両端に円錐状凹部を形成しても
よい。 A tightening screw 9 having a conical projection 9a, a tightening screw 10 having a conical recess 10a, and a conical projection 14a at one end and a conical recess 14b at the other end.
A tightening pin 14 corresponding to the screws 9 and 10 is provided.
It has been found to be particularly advantageous in practice to use However, as a modification of this configuration, conical recesses may be formed in both tightening screws, and corresponding protrusions may be formed at both ends of the tightening pin. Conversely, conical protrusions may be formed on both tightening screws, and conical recesses may be formed on both ends of the tightening pin.
次に第２図の他の実施例について説明する。受
孔３ａ，３ｂおよび嵌合孔５を有するスピンドル
ヘツド１ａは、第１図の実施例のものと全く同一
である。スピンドルヘツド１ａに対向する工具ホ
ルダ１１′の端部も工具ホルダ１１のそれと同一
構造なので、第１図と同じ符号を付して説明を省
略する。しかしこの実施例では、工具ホルダ１
１′の前端部に嵌合孔１７と、この嵌合孔１７の
範囲で半径方向反対向きの２個の雌ねじ部１８，
１９とが形成される。そして締付ねじ９，１０に
対応する締付ねじが雌ねじ部１８，１９にねじ込
まれる。嵌合孔１７の直径Ｄ２を選択するに際し
ては、ドイツ特許第3108439号に示したミーリン
グ工具、内側丸削り工具または穿孔ヘツドのスピ
ゴツト部（図示せず）が嵌合孔１７に係着するこ
と、または工具と工具ホルダの間に挿入される可
能性のある中間部材のスピゴツト部が嵌合孔１７
に係着すること等の要件を満足するようにする。
工具ホルダ１１′は、前述のドイツ特許第3108439
号による工具とこの発明による工具スピンドルと
の間で、いわばアダプタの働きをするので、結合
寸法もそれに見合うように定められる。工具ホル
ダ１１′は冷媒供給リング１５を具備しているの
で、１個の同一工具ホルダ１１′と１個の同一冷
媒供給リングを用いることによつて、切刃に対応
する内部冷媒供給形の種々の工具を結合できると
いう利点がある。 Next, another embodiment shown in FIG. 2 will be described. The spindle head 1a with the receiving holes 3a, 3b and the fitting hole 5 is exactly the same as that of the embodiment of FIG. The end of the tool holder 11' facing the spindle head 1a also has the same structure as that of the tool holder 11, so the same reference numerals as in FIG. 1 will be given and the explanation will be omitted. However, in this embodiment, the tool holder 1
1' has a fitting hole 17 at the front end thereof, and two internally threaded portions 18 facing radially oppositely within the fitting hole 17.
19 are formed. Then, tightening screws corresponding to the tightening screws 9 and 10 are screwed into the female threaded portions 18 and 19. When selecting the diameter D2 of the fitting hole 17, it is important to ensure that the spigot part (not shown) of the milling tool, inner rounding tool or drilling head shown in German Patent No. 3108439 engages in the fitting hole 17; Or, the spigot part of the intermediate member that may be inserted between the tool and the tool holder is inserted into the fitting hole 17.
Ensure that requirements such as being anchored to the vehicle are met.
The tool holder 11' is designed according to the aforementioned German patent no. 3108439.
Since the tool acts as an adapter between the tool according to No. 1 and the tool spindle according to the present invention, the dimensions of the connection are determined accordingly. Since the tool holder 11' is equipped with a coolant supply ring 15, by using one and the same tool holder 11' and one and the same coolant supply ring, various internal coolant supply types corresponding to the cutting blades can be used. It has the advantage of being able to combine two tools.
最後にこの発明によれば、DIN2080にもとづ
きテーパシヤンクを有する公知の工具ホルダ２０
を、第３図に示すようにこの発明の工作機械工具
スピンドルへ固着することができる。すなわち締
付ねじ９，１０を動かして、従来から用いられて
いる２個の半径方向反対向きのエントレインメン
ト部材２１を、端面部４に設けた対応の溝２２内
へ公知のように嵌着する。そして、工具ホルダ２
０のエントレインメントフランジ２０ａに設けた
溝２３内へエントレインメント部材２１が挿入さ
れる。次にテーパシヤンク内にねじ込まれた引張
棒２５、またはばね荷重締付けコレツト（図示せ
ず）によつてテーパシヤンク６を受孔３ａ，３ｂ
へ引込むと、このテーパシヤンク６は受孔３ａ，
３ｂで支持される。続いて、工具ホルダの周りに
同心状に配置された冷媒供給リング２６から冷媒
が供給される。 Finally, according to the invention, the known tool holder 20 with a tapered shank according to DIN 2080
can be secured to the machine tool tool spindle of the present invention as shown in FIG. That is, by moving the tightening screws 9, 10, two conventionally used radially opposite entrainment members 21 are fitted into corresponding grooves 22 provided in the end face 4 in a known manner. . And tool holder 2
The entrainment member 21 is inserted into the groove 23 provided in the entrainment flange 20a of No. 0. The taper shank 6 is then inserted into the receiving holes 3a, 3b by a tension rod 25 screwed into the taper shank or by a spring-loaded clamping collet (not shown).
When the taper shank 6 is pulled into the receiving hole 3a,
3b. Coolant is then supplied from a coolant supply ring 26 arranged concentrically around the tool holder.
工具ホルダ１１には、横孔とその中の締付ピン
とを具備し前方に突出した別のスピゴツト部を嵌
合孔１７の代りに設けてもよい。このような構造
の工具ホルダは、ドイツ特許第3108438号に示す
原理とは逆の運動の工具を受けるのに適してい
る。なぜならこのような工具はスピゴツト部の代
りに嵌合孔を有し、半径方向反対向きの２個の雌
ねじを具備しているからである。すでに述べたよ
うに、この種の工具は工具交換装置と組合せて使
用できる。 In place of the fitting hole 17, the tool holder 11 may be provided with another forwardly projecting spigot portion having a lateral hole and a tightening pin therein. A tool holder of such construction is suitable for receiving a tool with a movement opposite to the principle shown in DE 31 08 438. This is because such a tool has a fitting hole instead of a spigot and is provided with two radially opposed internal threads. As already mentioned, tools of this type can be used in combination with tool changers.
第１図は、この発明の第１実施例の部分断面
図、第２図は、この発明の第２実施例の部分断面
図、第３図は、前記両実施例の工具スピンドルに
従来の工具のテーパシヤンクを装着した状態を示
す部分断面図である。
１……工具スピンドル、１ａ……スピンドルヘ
ツド、２……主軸台、３ａ，３ｂ……切頭円錐状
受孔、４……環状端面、５……円筒状嵌合孔、６
……テーパシヤンク、７，８……雌ねじ部、９，
１０……締付ねじ、９ａ……円錐状突起、１０ａ
……円錐状凹部、１１，１１′……第２工具ホル
ダ、１２……円筒状スピゴツト部、１３……横
孔、１４……締付ピン、１４ａ……円錐状凹部、
１４ｂ……円錐状突起、１６……環状面、２０…
…第１工具ホルダ。
FIG. 1 is a partial sectional view of a first embodiment of the invention, FIG. 2 is a partial sectional view of a second embodiment of the invention, and FIG. FIG. 3 is a partial cross-sectional view showing a state in which the taper shank is attached. 1... Tool spindle, 1a... Spindle head, 2... Headstock, 3a, 3b... truncated conical receiving hole, 4... Annular end surface, 5... Cylindrical fitting hole, 6
... Taper shank, 7, 8 ... Female thread part, 9,
10...Tightening screw, 9a...Conical projection, 10a
... Conical recess, 11, 11' ... Second tool holder, 12 ... Cylindrical spigot part, 13 ... Horizontal hole, 14 ... Tightening pin, 14a ... Conical recess,
14b... Conical projection, 16... Annular surface, 20...
...First tool holder.
Claims (1)
け入れる切頭円錐状受孔３ａ，３ｂが形成され、
受穴３ａの周囲を囲む環状端面４が設けられたス
ピンドルヘツド１ａを有する工具スピンドル１に
おいて、スピンドルヘツド１ａがテーパシヤンク
６に換えて円筒状スピゴツト部１２を有する第２
工具ホルダ１１，１１′のスピゴツト部１２を受
入れる円筒状嵌合孔５を有し、この嵌合孔５の直
径Ｄが受孔３ａの最大直径Ｄ１より若干小さく、
端面４から測つた嵌合孔５の端部までの軸方向長
さＬが受孔３ｂの端部の軸方向長さＬ１より短
く、嵌合孔５の領域においてスピンドルヘツド１
ａは、半径方向反対向きに延びる２個の雌ねじ部
７，８を有し、各雌ねじ部７，８に円錐状突起又
は円錐状凹部が形成された締付ねじ９，１０が嵌
合し、スピゴツト部１２の横孔１３には締付ピン
１４が半径方向に移動可能に設けられ、この締付
ピン１４の各端部には円錐状凹部又は円錐状突起
が形成され、この締付ピン１４の各円錐状凹部又
は円錐状突起は、それぞれこれに対応する締付ね
じ９，１０の円錐状突起又は円錐状凹部と協働
し、雌ねじ部７，８の軸線Ａ１の端面４からの距
離ａ１は、横軸１３の軸線Ａ２の工具ホルダ１
１，１１′の環状面１６からの距離ａ２よりも若
干大きくて、締付ねじ９，１０の一方を締付ける
と、この締付ねじ９，１０は締付ピン１４に作用
して環状面１６と端面とを互いに近づける方向に
押圧することを特徴とする工作機械の工具取付装
置。 ２ 嵌合孔５の直径Ｄが受孔３ａ，３ｂの最大直
径Ｄ１より約４〜10％、好ましくは約6.5％だけ
小さいことを特徴とする特許請求の範囲第１項記
載の工作機械の工具取付装置。 ３ 端面から測つた嵌合孔５の端部までの軸方向
長さＬが、受孔３ｂの端部までの軸方向長さＬ１
の約1/2〜2/3であることを特徴とする特許請求の
範囲第１項記載の工作機械の工具取付装置。 ４ 一方の締付ねじ１０が円錐状凹部１０ａを有
し、他方の締付ねじ９が円錐状突起９ａを有し、
これに対応して締付ピン１４の一端に円錐状突起
１４ａが、他端に円錐状凹部１４ｂが形成されて
いることを特徴とする特許請求の範囲第１項記載
の工作機械の工具取付装置。[Claims] 1. A truncated conical receiving hole 3a, 3b is formed for receiving the taper shank 6 of the first tool holder 20,
In a tool spindle 1 having a spindle head 1a provided with an annular end surface 4 surrounding a receiving hole 3a, the spindle head 1a has a second spigot portion 12 having a cylindrical spigot portion 12 instead of the tapered shank 6.
It has a cylindrical fitting hole 5 for receiving the spigot portion 12 of the tool holder 11, 11', and the diameter D of the fitting hole 5 is slightly smaller than the maximum diameter D1 of the receiving hole 3a.
The axial length L measured from the end face 4 to the end of the fitting hole 5 is shorter than the axial length L1 of the end of the receiving hole 3b, and the spindle head 1 is located in the area of the fitting hole 5.
a has two internally threaded parts 7, 8 extending in opposite directions in the radial direction, and tightening screws 9, 10 each having a conical protrusion or a conical recess are fitted into each internally threaded part 7, 8; A clamping pin 14 is provided in the horizontal hole 13 of the spigot portion 12 so as to be movable in the radial direction, and a conical recess or a conical protrusion is formed at each end of the clamping pin 14. Each of the conical recesses or conical projections cooperates with the corresponding conical projection or conical recess of the tightening screws 9, 10, and the distance a1 from the end surface 4 of the axis A1 of the internally threaded portions 7, 8 is the tool holder 1 on the axis A2 of the horizontal axis 13
1, 11' from the annular surface 16, and when one of the tightening screws 9, 10 is tightened, this tightening screw 9, 10 acts on the tightening pin 14 and is connected to the annular surface 16. A tool mounting device for a machine tool, characterized in that it presses end faces in a direction that brings them closer to each other. 2. The machine tool tool according to claim 1, wherein the diameter D of the fitting hole 5 is smaller than the maximum diameter D1 of the receiving holes 3a, 3b by about 4 to 10%, preferably about 6.5%. Mounting device. 3 The axial length L from the end surface to the end of the fitting hole 5 is the axial length L1 to the end of the receiving hole 3b.
2. The tool mounting device for a machine tool according to claim 1, wherein the tool mounting device is about 1/2 to 2/3 of . 4 One tightening screw 10 has a conical recess 10a, the other tightening screw 9 has a conical protrusion 9a,
Correspondingly, a conical protrusion 14a is formed at one end of the tightening pin 14, and a conical recess 14b is formed at the other end. .
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE8405489.1 | 1984-02-23 | ||
| DE8405489U DE8405489U1 (en) | 1984-02-23 | 1984-02-23 | Machine tool spindle and matching tool holder |
| DE3406498A DE3406498C1 (en) | 1984-02-23 | 1984-02-23 | Machine tool spindle and matching tool holder |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60207736A JPS60207736A (en) | 1985-10-19 |
| JPH0431812B2 true JPH0431812B2 (en) | 1992-05-27 |
Family
ID=37781873
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60035182A Granted JPS60207736A (en) | 1984-02-23 | 1985-02-22 | Tool fixture for machine tool |
Country Status (7)
| Country | Link |
|---|---|
| JP (1) | JPS60207736A (en) |
| CH (1) | CH666213A5 (en) |
| DE (2) | DE3406498C1 (en) |
| FR (1) | FR2560094B1 (en) |
| GB (1) | GB2154481B (en) |
| IT (1) | IT1200389B (en) |
| SE (1) | SE459403B (en) |
Families Citing this family (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0193020B1 (en) * | 1985-03-01 | 1990-11-28 | Fried. Krupp Gesellschaft mit beschränkter Haftung | Tooling device with an exchangeable tool head |
| GB8506112D0 (en) * | 1985-03-08 | 1985-04-11 | Crawford Collets Ltd | Boring bars |
| DE3632045C1 (en) * | 1986-09-20 | 1987-11-26 | Otto Eckle | Device for connecting two tool parts |
| DE8631442U1 (en) * | 1986-11-25 | 1988-03-24 | Komet Stahlhalter- Und Werkzeugfabrik Robert Breuning Gmbh, 7122 Besigheim, De | |
| DE3708746C1 (en) * | 1987-03-18 | 1988-06-09 | Otto Eckle | Coupling arrangement for the torsionally rigid connection of parts to be connected |
| DE8715525U1 (en) * | 1987-11-24 | 1989-03-23 | Komet Stahlhalter- Und Werkzeugfabrik Robert Breuning Gmbh, 7122 Besigheim, De | |
| DE4024644A1 (en) * | 1989-09-09 | 1991-03-14 | Komet Stahlhalter Werkzeug | Detachable fixing of tool to spindle - involves specially shaped bolts fitting in slots in tool spigot |
| GB9105366D0 (en) * | 1991-03-13 | 1991-04-24 | Shefcut Tool And Engineering L | Metal cutting tooling system |
| DE4124152C2 (en) * | 1991-07-20 | 2001-02-08 | Sms Demag Ag | Form-locking shaft coupling that can be automatically engaged and disengaged |
| SG48949A1 (en) * | 1991-12-03 | 1998-05-18 | Komet Praezisionswerkzeuge | A tool coupling with a radially elastically expandable coupling sleeve and a shaft with a clamping body |
| JPH0680509U (en) * | 1993-04-26 | 1994-11-15 | 大昭和精機株式会社 | Side lock type tool chuck |
| WO1996002346A1 (en) * | 1994-07-20 | 1996-02-01 | Komet Präzisionswerkzeuge Robert Breuning Gmbh | Tool head with axially adjustable chuck |
| FR2754201B1 (en) * | 1996-10-04 | 1998-12-11 | E P B Emile Pfalzgraf | DEVICE FOR TIGHTENING HOLLOW CONE ATTACHMENTS |
| JP4063669B2 (en) * | 2000-12-22 | 2008-03-19 | コメート グループ ホールディング ゲーエムベーハー | Device for joining two members |
| DE202004011571U1 (en) * | 2004-07-16 | 2004-10-07 | Flam, Mirko | tool adapter |
| BRPI0615832A2 (en) * | 2005-09-13 | 2011-05-31 | Komet Group Holding Gmbh | detachable two-component coupling device |
| US8610501B2 (en) | 2009-11-16 | 2013-12-17 | Covidien Lp | Class resonant-H electrosurgical generators |
| DE102010039793A1 (en) * | 2010-03-02 | 2011-09-08 | Komet Group Gmbh | Device for connecting two components |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5851004A (en) * | 1981-03-06 | 1983-03-25 | コメツト・シユタルハルタ−−ウント・ベルクツオイクフアブリ−ク・ロバ−ト・ブロイニング・ゲゼルシヤフト・ミツト・ベシユレンクテル・ハフツング | Hollow tool |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2383212A (en) * | 1944-02-19 | 1945-08-21 | Walter B Pohle | Shank construction |
| FR1019411A (en) * | 1950-06-02 | 1953-01-21 | Deragne Freres | Further training in portable boring machines |
| CH484713A (en) * | 1968-01-12 | 1970-01-31 | Baechtold Fritz | Milling arbor |
-
1984
- 1984-02-23 DE DE3406498A patent/DE3406498C1/en not_active Expired
- 1984-02-23 DE DE8405489U patent/DE8405489U1/en not_active Expired
-
1985
- 1985-01-03 CH CH6/85A patent/CH666213A5/en not_active IP Right Cessation
- 1985-01-07 GB GB08500334A patent/GB2154481B/en not_active Expired
- 1985-02-20 FR FR8502466A patent/FR2560094B1/en not_active Expired
- 1985-02-22 JP JP60035182A patent/JPS60207736A/en active Granted
- 1985-02-22 IT IT19619/85A patent/IT1200389B/en active
- 1985-02-22 SE SE8500890A patent/SE459403B/en not_active IP Right Cessation
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5851004A (en) * | 1981-03-06 | 1983-03-25 | コメツト・シユタルハルタ−−ウント・ベルクツオイクフアブリ−ク・ロバ−ト・ブロイニング・ゲゼルシヤフト・ミツト・ベシユレンクテル・ハフツング | Hollow tool |
Also Published As
| Publication number | Publication date |
|---|---|
| GB8500334D0 (en) | 1985-02-13 |
| FR2560094A1 (en) | 1985-08-30 |
| GB2154481B (en) | 1987-04-08 |
| IT1200389B (en) | 1989-01-18 |
| DE3406498C1 (en) | 1984-10-25 |
| GB2154481A (en) | 1985-09-11 |
| SE8500890L (en) | 1985-08-24 |
| DE8405489U1 (en) | 1985-06-20 |
| FR2560094B1 (en) | 1988-10-14 |
| SE8500890D0 (en) | 1985-02-22 |
| JPS60207736A (en) | 1985-10-19 |
| SE459403B (en) | 1989-07-03 |
| IT8519619A0 (en) | 1985-02-22 |
| CH666213A5 (en) | 1988-07-15 |
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