JPH0615541A - Vibro-absorber for machine tool slideway used with direct-acting bearing - Google Patents
Vibro-absorber for machine tool slideway used with direct-acting bearingInfo
- Publication number
- JPH0615541A JPH0615541A JP19785792A JP19785792A JPH0615541A JP H0615541 A JPH0615541 A JP H0615541A JP 19785792 A JP19785792 A JP 19785792A JP 19785792 A JP19785792 A JP 19785792A JP H0615541 A JPH0615541 A JP H0615541A
- Authority
- JP
- Japan
- Prior art keywords
- machine tool
- acting bearing
- direct
- sliding
- grinding
- 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.)
- Pending
Links
Landscapes
- Machine Tool Units (AREA)
- Bearings For Parts Moving Linearly (AREA)
Abstract
Description
【0001】[0001]
【産業上の利用分野】本発明は、直動軸受を用いた工作
機械滑り面の振動吸収装置に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibration absorbing device for a machine tool sliding surface using a linear motion bearing.
【0002】[0002]
【従来の技術】従来の単なる“平ー平”摺動面の構造
は、図1に示すようにスライドベース1aと移動テーブ
ル2aの案内面にシム(調整板)10をはさみ、摺動間
隙Sに数μm〜数10μmのすきまを設けて作動させる
構造であるため、NC(数値制御)により1μm単位の
直進指令を出しても“すきま量”の範囲で蛇行送りB
し、目的の送り方向Cの動きが一定せず、とくにテーブ
ル上面Aにワークがセットされ、切削あるいは研削荷重
がかかると、方向性が定まらず高精度加工に必要な1μ
m〜2μmの定量送りができなくなり、同時2軸制御に
おける円弧切削や研削精度に影響を及ぼし、真円度など
に高精度が得られなかった。なお8aはボールねじ、9
aはサーボモータである。2. Description of the Related Art As shown in FIG. 1, a conventional mere "flat-flat" sliding surface structure is such that a shim (adjustment plate) 10 is inserted between guide surfaces of a slide base 1a and a moving table 2a to form a sliding gap S. Since the structure is designed to operate with a clearance of several μm to several tens of μm, even if a straight line command is issued in 1 μm units by NC (numerical control), the meandering feed is within the range of “clearance amount” B
However, if the target movement in the feed direction C is not constant and the work is set on the table upper surface A and a cutting or grinding load is applied, the directionality is not fixed and 1 μ required for high precision machining.
Since it became impossible to feed a fixed amount of m to 2 μm, it affected circular arc cutting and grinding accuracy in the simultaneous biaxial control, and high accuracy such as roundness could not be obtained. 8a is a ball screw, 9
a is a servo motor.
【0003】このため追従性向上策として、図3のよう
にスライドベース1aと移動テーブル2aとの間に予圧
を与えた直動軸受3aを採用することにより図1の摺動
間隙Sのすきまがなくなり、また摩擦係数が“V−平”
または“平−平”の場合、潤滑良好な状態で通常0.1
〜0.05であるのに対し0.03と小さくなってNC
の指令数値に忠実かつ正確に目的の送り方向Cに移動で
きるようになった。即ち工作機械の滑り面に直動軸受を
利用できるようになると、追従性がよくなり、加工精度
が向上する。Therefore, as a measure for improving the followability, by adopting the linear motion bearing 3a in which a preload is applied between the slide base 1a and the moving table 2a as shown in FIG. 3, the clearance of the sliding gap S in FIG. And the coefficient of friction is "V-flat"
Or, in the case of "flat-flat", it is usually 0.1 with good lubrication.
~ 0.05, but decreased to 0.03 NC
It became possible to move in the target feed direction C faithfully and accurately according to the command value of. That is, if the linear bearing can be used for the sliding surface of the machine tool, the followability is improved and the machining accuracy is improved.
【0004】また、従来、高精度を必要とする研削盤で
は、滑らかな摺動を得るために、“V−平”構造を採用
せざるを得なかったが、直動軸受を利用することにより
高度な技能を要する“きさげ作業”が不要となり、製作
コストの低減につながる。Conventionally, in a grinding machine which requires high precision, a "V-flat" structure has been obliged to be adopted in order to obtain smooth sliding. However, by using a linear motion bearing, This eliminates the need for "scraping", which requires a high level of skill, leading to a reduction in manufacturing costs.
【0005】[0005]
【発明が解決しようとする課題】しかし、直動軸受はボ
ールの場合は点接触、ローラーの場合は線接触で減衰能
力が低いことによる微振動が発生し、高精度を必要とす
る研削ならびに精密旋削には使用できなかった。However, a linear bearing has point contact in the case of a ball and line contact in the case of a roller, which causes minute vibrations due to its low damping capacity, which requires high precision in grinding and precision. It could not be used for turning.
【0006】また切削または研削加工時に発生する振動
と、回転駆動部より発生する振動とが共振しやすくなる
ため、重切削時や断続切削時には“たたき現象”によっ
て刃具を損傷させ、剛性が低いと判断されている。研削
では、砥石が高速で回転し“たたき現象”によりチャタ
ーマークがみられ、重研削では目的どおりの切り込みが
出来ないとされている。Further, since the vibration generated during cutting or grinding and the vibration generated by the rotary drive portion are likely to resonate with each other, during heavy cutting or intermittent cutting, the "knocking phenomenon" damages the cutting tool, resulting in low rigidity. It has been judged. In grinding, the grindstone rotates at high speed and chatter marks are seen due to the "tapping phenomenon", and it is said that heavy grinding does not allow the desired cutting.
【0007】[0007]
【課題を解決するための手段】本発明は上記課題を解決
するためになされたものであって、その要旨とするとこ
ろは、直動軸受を用いた両側ガイドレールの中間におけ
るスライドベースと移動テーブルとの間に介在された摺
動部の摺動面に潤滑性樹脂を設けて弾性体が構成され、
潤滑性樹脂を介して下向き方向に計算された予圧を与え
ることにより直動軸受が発生する微振動を吸収抑制させ
るようにしたことを特徴とする直動軸受を用いた工作機
械滑り面の振動吸収装置である。SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and its gist is to provide a slide base and a moving table in the middle of both guide rails using a linear motion bearing. An elastic body is formed by providing a lubricating resin on the sliding surface of the sliding portion interposed between
Absorption of vibrations on machine tool sliding surfaces using linear bearings is characterized by absorbing and suppressing minute vibrations generated by linear bearings by applying a pre-computed downward pressure via a lubricating resin. It is a device.
【0008】次に本発明を以下実施例について図4,5
を参照しながら詳しく説明する。Next, the present invention will be described with reference to the following embodiments with reference to FIGS.
Will be described in detail with reference to.
【0009】[0009]
【実施例】先ず直動軸受(リニアウエイ)3を用いた2
本のガイドレール4の中間に、ボールねじ8を挾んで切
込台上面の移動テーブル2を支える形で、移動テーブル
2にL字型の2本のサブスライドレール5を固定し、ス
ライドベース1に固定した2本のプレート6を組み合わ
せた構造の摺動部Rを設ける。そこでその摺動部Rの摺
動面に潤滑性樹脂7を介在して弾性体を構成する。そし
てプレート6により下向き矢印方向イに計算された予圧
を与えることによって直動軸受3が発生する微振動を吸
収,抑制させるようにしたことを特徴としている。また
摺動部Rの摺動面には高粘度の潤滑油を強制的に供給し
て効果を高めているため、特に切込み移動テーブルに採
用した場合、剛性が高まり高精度研削が可能となる。な
お図中、9はサーボモータである。また上記の潤滑性樹
脂7としては例えば商品名ターカイトまたはルーロンな
どの摺動材(エンジニアリング・プラスチック)が使用
される。[First Embodiment] First, 2 using a linear motion bearing (linear way) 3
In the middle of the guide rail 4 of the book, two L-shaped sub-slide rails 5 are fixed to the moving table 2 so as to support the moving table 2 on the upper surface of the cutting table by sandwiching the ball screw 8 and sliding base 1 A sliding part R having a structure in which two plates 6 fixed to each other are combined is provided. Therefore, an elastic body is formed by interposing a lubricating resin 7 on the sliding surface of the sliding portion R. The plate 6 is adapted to absorb and suppress the minute vibration generated by the linear motion bearing 3 by applying a calculated preload in the downward arrow direction a. Further, since a high-viscosity lubricating oil is forcibly supplied to the sliding surface of the sliding portion R to enhance the effect, rigidity is increased and high precision grinding is possible especially when the sliding table is adopted as a cutting movement table. In the figure, 9 is a servo motor. As the above-mentioned lubricating resin 7, for example, a sliding material (engineering plastic) such as trade name Turkete or Lulon is used.
【0010】[0010]
【発明の効果】次に本発明の効果を実施例を挙げて説明
する。図6においては、CNC内面研削盤(大成機械製
GRI−1000N2)の切込台Hの摺動面(滑り面)
に直動軸受(リニアウエイ)を用いているが、これに本
発明の振動吸収装置を組み込んだ場合の発生振動と、同
装置を取り外した場合の発生振動とを切込台H上の測定
位置Pにおいて測定してみて、表1の結果を得た。ちな
みに機械静止時の外部(工場環境)振動は、最大0.8
μmまである。Next, the effects of the present invention will be described with reference to examples. In FIG. 6, a sliding surface (sliding surface) of the cutting table H of the CNC inner surface grinding machine (GRI-1000N2 manufactured by Taisei Machinery Co., Ltd.)
A linear motion bearing is used in the above, but the generated vibration when the vibration absorbing device of the present invention is incorporated therein and the generated vibration when the device is removed are measured positions on the cutting table H. When measured at P, the results shown in Table 1 were obtained. By the way, the maximum external (factory environment) vibration when the machine is stationary is 0.8.
There is up to μm.
【0011】[0011]
【表1】 [Table 1]
【0012】上記の測定結果から、サブミクロンの加工
精度(とくに面粗さ、及び同時2軸制御によるテーパー
研削面の真直度)が要求される内面研削盤の摺動部への
同装置の採用の効用は十分に認められる。また切込台上
の振動は、機械の動的精度に影響するが、とくに砥石ス
ピンドルを介して砥石に振動を伝播し、砥石のワークへ
の当たりが一定せず加工寸法精度のバラツキ、真円度、
ビビリマーク、チャターマークの発生など面性状に悪影
響を及ぼすが、本発明の使用によりこれらの問題を解
消、加工精度が向上した。From the above measurement results, adoption of the same device for the sliding portion of the inner surface grinding machine, which requires submicron processing accuracy (particularly surface roughness and straightness of tapered ground surface by simultaneous two-axis control) The utility of is fully recognized. The vibration on the cutting table affects the dynamic accuracy of the machine, but in particular, the vibration propagates to the grindstone through the grindstone spindle, and the contact of the grindstone with the work is not constant, resulting in variations in machining dimensional accuracy and a perfect circle. Every time,
Although the surface properties such as chatter marks and chatter marks are adversely affected, use of the present invention solves these problems and improves processing accuracy.
【図1】従来技術の説明図である。FIG. 1 is an explanatory diagram of a conventional technique.
【図2】従来技術の説明図である。FIG. 2 is an explanatory diagram of a conventional technique.
【図3】従来技術の説明図である。FIG. 3 is an explanatory diagram of a conventional technique.
【図4】本発明装置の正面図である。FIG. 4 is a front view of the device of the present invention.
【図5】本発明装置の平面図である。FIG. 5 is a plan view of the device of the present invention.
【図6】本発明実施例の説明図である。FIG. 6 is an explanatory diagram of an example of the present invention.
【符号の説明】 1 1a スライドベース 2 2a 移動テーブル 3 3a 直動軸受 4 ガイドレール 5 サブスライドレール 6 プレート 7 潤滑性樹脂 8 8a ボールねじ 9 9a サーボモーター 10 シム A テーブル上面 B 蛇行送り C 目的の送り方向 H 切込台 P 測定位置 R 摺動部 S 摺動間隙 イ 矢印方向[Explanation of symbols] 1 1a Slide base 2 2a Moving table 3 3a Linear motion bearing 4 Guide rail 5 Sub slide rail 6 Plate 7 Lubricating resin 8 8a Ball screw 9 9a Servo motor 10 Shim A Table top surface B Meandering feed C Purpose Feeding direction H Cutting table P Measuring position R Sliding part S Sliding gap b Arrow direction
Claims (1)
イドベースと移動テーブルとの間に介在された摺動部の
摺動面に潤滑性樹脂を設けて弾性体が構成され潤滑性樹
脂を介して下向き方向に計算された予圧を与えることに
より直動軸受が発生する微振動を吸収抑制させるように
したことを特徴とする直動軸受を用いた工作機械滑り面
の振動吸収装置。Lubricating resin is provided on the sliding surface of the sliding part interposed between the slide base and the moving table in the middle of the guide rails on both sides using the linear motion bearing, and the elastic body is configured to face downward through the lubricating resin. A vibration absorbing device for a machine tool sliding surface using a linear motion bearing, characterized by absorbing and suppressing minute vibrations generated by the linear motion bearing by applying a preload calculated in the direction.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP19785792A JPH0615541A (en) | 1992-07-01 | 1992-07-01 | Vibro-absorber for machine tool slideway used with direct-acting bearing |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP19785792A JPH0615541A (en) | 1992-07-01 | 1992-07-01 | Vibro-absorber for machine tool slideway used with direct-acting bearing |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH0615541A true JPH0615541A (en) | 1994-01-25 |
Family
ID=16381490
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP19785792A Pending JPH0615541A (en) | 1992-07-01 | 1992-07-01 | Vibro-absorber for machine tool slideway used with direct-acting bearing |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0615541A (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR101008079B1 (en) * | 2008-07-30 | 2011-01-13 | 김기태 | Transfer table for servo thomson press |
JP2011251629A (en) * | 2010-06-02 | 2011-12-15 | Mitsubishi Electric Corp | Movable platform fence |
JP6113874B1 (en) * | 2016-02-10 | 2017-04-12 | 株式会社東海理化電機製作所 | Buckle device |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0245497B2 (en) * | 1982-05-19 | 1990-10-09 | Inoue Japax Res |
-
1992
- 1992-07-01 JP JP19785792A patent/JPH0615541A/en active Pending
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0245497B2 (en) * | 1982-05-19 | 1990-10-09 | Inoue Japax Res |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR101008079B1 (en) * | 2008-07-30 | 2011-01-13 | 김기태 | Transfer table for servo thomson press |
JP2011251629A (en) * | 2010-06-02 | 2011-12-15 | Mitsubishi Electric Corp | Movable platform fence |
JP6113874B1 (en) * | 2016-02-10 | 2017-04-12 | 株式会社東海理化電機製作所 | Buckle device |
JP2017140943A (en) * | 2016-02-10 | 2017-08-17 | 株式会社東海理化電機製作所 | Buckle device |
CN107054284A (en) * | 2016-02-10 | 2017-08-18 | 株式会社东海理化电机制作所 | Locking ring device |
CN107054284B (en) * | 2016-02-10 | 2019-03-12 | 株式会社东海理化电机制作所 | Locking ring device |
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