JP2008307642A - Vibration isolating tool and its manufacturing method - Google Patents

Vibration isolating tool and its manufacturing method Download PDF

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JP2008307642A
JP2008307642A JP2007157764A JP2007157764A JP2008307642A JP 2008307642 A JP2008307642 A JP 2008307642A JP 2007157764 A JP2007157764 A JP 2007157764A JP 2007157764 A JP2007157764 A JP 2007157764A JP 2008307642 A JP2008307642 A JP 2008307642A
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vibration
tool
dynamic
vibration absorber
absorber
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Koji Uchiumi
幸治 内海
Masayuki Kyoi
正之 京井
Hideaki Onozuka
英明 小野塚
Tomu Kato
吐夢 加藤
Yasuo Miyashita
靖生 宮下
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Hitachi Plant Technologies Ltd
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Hitachi Plant Technologies Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a vibration isolating tool capable of shortening optimum adjustment time of a dynamic damper as the dynamic damper capable of obtaining large vibration isolation effects without optimizing the damper every time vibration characteristics of a tool body vary even if the characteristics vary, and its manufacturing method. <P>SOLUTION: The dynamic damper comprising a spindle 25 and low elasticity rubbers 24 fixed to both ends of the spindle 25 is supported by the rubber 24 inside a cavity 7 of a cover 1. A dynamic damper structure is provided, which can attain stable self-excited vibration suppression effects without a large increase/decrease in the effects of the damper even if the vibration characteristics of the tool body vary. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、特に圧縮機インペラの羽根部形状を切削加工する際に有効な防振工具及びその製造方法に関する。 The present invention relates to an anti-vibration tool particularly effective for cutting a blade shape of a compressor impeller and a manufacturing method thereof.

エンドミルなどの防振工具を用いた切削加工による、深穴や深溝の切削加工において、深穴の奥面や深溝の側面の切削加工を行うためには、工具の突き出し長さが長い、長尺な防振工具を用いて被削材を切削する必要がある。しかし、工具の突き出し長さが長いと、工具剛性が低くなってしまい、切削加工中に工具に作用する切削力に対する工具剛性の不足から、工具の自励振動が発生し、加工面粗さの悪化や、工具欠損が生じ易くなる。このため、長尺工具を用いた切削加工では、工具自励振動を発生させないように、切込み量や送り速度といった加工諸元を低く設定せざるを得ないため、加工能率が低くなってしまう問題がある。
このような問題を引き起こす工具自励振動を抑制する手段として、従来、種々の抑制方法が提案されている。例えば特開2002-233903（特許文献１）に記すように、工具外周部に超硬素材からなる棒を固着させる方法や、特開2002-233911（特許文献２）に記すように、工具本体の外周部に超硬素材、セラミックなどの硬質材料を溶射する方法によって、工具剛性を高め、自励振動を抑制する方法がある。加えて工具本体の素材を一般的に用いられている鋼素材から超硬素材に変更し、剛性を高めた工具も市販されている。 In cutting of deep holes and deep grooves by cutting using vibration-proof tools such as end mills, in order to cut deep holes and side surfaces of deep grooves, long tool protrusion lengths are required. It is necessary to cut the work material using a proper vibration isolating tool. However, if the protrusion length of the tool is long, the tool stiffness will be low, and the tool will not be sufficiently strong against the cutting force acting on the tool during the cutting process. Deterioration and tool loss are likely to occur. For this reason, in cutting using a long tool, it is necessary to set processing parameters such as the cutting depth and feed rate low so as not to generate tool self-excited vibration, and therefore the processing efficiency is lowered. There is.
Conventionally, various suppression methods have been proposed as means for suppressing tool self-excited vibration that causes such problems. For example, as described in Japanese Patent Laid-Open No. 2002-233903 (Patent Document 1), a method of fixing a rod made of a carbide material to the outer periphery of the tool, or as described in Japanese Patent Laid-Open No. 2002-233911 (Patent Document 2), There is a method of increasing tool rigidity and suppressing self-excited vibration by a method of spraying a hard material such as a carbide material or ceramic on the outer peripheral portion. In addition, tools with increased rigidity by changing the material of the tool body from a commonly used steel material to a carbide material are also commercially available.

この一例として、図１に工具の剛性を高めた場合の工具周波数応答の一例を示す。超硬素材といった硬質材料のヤング率は鋼の２倍程度を有しており、剛性は最大で２倍まで向上するため、一般に使用される鋼製工具の振動波形５０は、波形６０になり、振動の最大振幅が抑制される。   As an example of this, FIG. 1 shows an example of the tool frequency response when the rigidity of the tool is increased. The Young's modulus of a hard material such as a cemented carbide material has about twice that of steel, and the rigidity is improved up to twice, so that the vibration waveform 50 of a generally used steel tool becomes a waveform 60, The maximum amplitude of vibration is suppressed.

別の方法として、例えば特開2003-62735（特許文献３）や特開2006-305674（特許文献４）のように、工具内部に質量、バネ、減衰からなる動吸振器を内蔵する方法がある。この方法は、工具内部に内蔵された動吸振器を構成する、質量とバネにより決まる動吸振器の固有振動数を、動吸振器を内蔵させる工具本体の固有振動数に合わせて最適調整することで、動吸振器が工具本体（カバー）の振動の位相と逆位相で振動し、工具本体の振動を相殺することができる。加えて、動吸振器の錘を支持している減衰は、錘の振動を粘弾性体が受けて粘弾性体が歪み、振動エネルギーを熱エネルギーに変換し散逸することで、振動が収まるまでの時間を早めることができる。   As another method, for example, there is a method of incorporating a dynamic vibration absorber made up of mass, spring, and damping inside the tool, as disclosed in JP 2003-62735 (Patent Document 3) and JP 2006-305674 (Patent Document 4). . In this method, the natural frequency of the dynamic vibration absorber, which is determined by the mass and the spring, constituting the dynamic vibration absorber built in the tool is optimally adjusted according to the natural frequency of the tool body in which the dynamic vibration absorber is built. Thus, the dynamic vibration absorber vibrates in the opposite phase to the vibration phase of the tool body (cover), and the vibration of the tool body can be canceled out. In addition, the damping that supports the weight of the dynamic vibration absorber is that the viscoelastic body receives the vibration of the weight, the viscoelastic body is distorted, and the vibration energy is converted into heat energy and dissipated until the vibration is settled. You can speed up the time.

このように、動吸振器を内蔵した前記防振工具は、前記動吸振器の固有振動数の調整と、減衰による振動エネルギーの散逸により、工具の振動を効果的に抑制する方法である。   Thus, the anti-vibration tool incorporating the dynamic vibration absorber is a method of effectively suppressing the vibration of the tool by adjusting the natural frequency of the dynamic vibration absorber and dissipating vibration energy due to the damping.

この方法を用いた前記動吸振器を構成する部材として、質量は密度７８００ｋｇ/ｍ3以上の高密度材料であり、例えばヘビーメタル（密度１８０００ｋｇ/ｍ３）などが用いられ、減衰はヤング率１００ＫＰａ以下、引っ張り強度１〜１００ＫＰa、伸び２００〜４００％の粘弾性体や、粘性流体（例えばシリコーンオイル）が用いられ、バネは機構に応じて金属やゴムを含む弾性体が用いられている。 As a member constituting the dynamic vibration absorber using this method, the mass is a high-density material having a density of 7800 kg / m 3 or more, for example, heavy metal (density 18000 kg / m 3 ) is used, and the attenuation is Young's modulus of 100 KPa. Hereinafter, a viscoelastic body having a tensile strength of 1 to 100 KPa and an elongation of 200 to 400% or a viscous fluid (for example, silicone oil) is used, and an elastic body including metal or rubber is used for the spring according to the mechanism.

図２に上記動吸振器を内蔵した防振工具の質点系振動モデルを示す。このモデルは、工具の持つ質量ｍ１，バネ定数ｋ１、減衰比ζ１と，動吸振器の錘質量ｍ２，バネ定数ｋ２、減衰比ζ２から構成されており、工具に加振力ｆが作用したときの、工具本体の振動振幅ｘ１を計算できるモデルである。   FIG. 2 shows a mass system vibration model of a vibration isolating tool incorporating the dynamic vibration absorber. This model is composed of the mass m1 of the tool, the spring constant k1, the damping ratio ζ1, the mass d2 of the dynamic vibration absorber, the spring constant k2, and the damping ratio ζ2, and when the excitation force f acts on the tool. This is a model that can calculate the vibration amplitude x1 of the tool body.

動吸振器を効果的に使用するためには，動吸振器の固有振動数を決定する因子であるバネ定数ｋ２と、動吸振器の減衰比ζ２を工具本体の振動特性ｍ１、ｋ１、に合わせて最適な値に設定する必要がある。動吸振器の最適設計値は、工具本体の質量m1と動吸振器の錘錘質量ｍ２の比である、質量比μが決まれば以下の式（１）、（２）により求められる。   In order to use the dynamic vibration absorber effectively, the spring constant k2 which is a factor for determining the natural frequency of the dynamic vibration absorber and the damping ratio ζ2 of the dynamic vibration absorber are matched with the vibration characteristics m1 and k1 of the tool body. Therefore, it is necessary to set the optimal value. The optimum design value of the dynamic vibration absorber can be obtained by the following formulas (1) and (2) when the mass ratio μ, which is the ratio of the mass m1 of the tool body to the mass f2 of the dynamic vibration absorber, is determined.

Figure 2008307642
Figure 2008307642

Figure 2008307642
ここで，ω１は工具本体の固有振動数，ω２は動吸振器の固有振動数である。従来の防振工具は、使用する工具本体の振動特性ｍ１、ｋ１を実験的または解析的に見積り，これを設計の入力値として式（１）（２）に代入し、工具本体に内蔵する動吸振器のバネ定数ｋ２と、減衰比ζ２の設定値を決定し、前記設定値になるように、動吸振器のバネ、減衰の調整作業を行い動吸振器の最適化を行うことが可能である。
Figure 2008307642
 Here, ω1 is the natural frequency of the tool body, and ω2 is the natural frequency of the dynamic vibration absorber. In the conventional anti-vibration tool, the vibration characteristics m1 and k1 of the tool body to be used are estimated experimentally or analytically, and this is substituted into equations (1) and (2) as design input values, and the built-in motion in the tool body. It is possible to determine the set value of the spring constant k2 of the vibration absorber and the damping ratio ζ2, and to adjust the dynamic vibration absorber by adjusting the spring and damping of the dynamic vibration absorber so that the set value is obtained. is there.

図３は，カバー１に質量２１・バネ２２・減衰２３からなる動吸振器２aを内蔵した従来の防振工具３aを、コレットチャックＡと、別の種類のコレットチャックＢを介して、それぞれを工作機械４に取り付けて支持する使用形態の一例を示している。   FIG. 3 shows a conventional anti-vibration tool 3a in which a cover 1 includes a dynamic vibration absorber 2a composed of a mass 21, a spring 22 and a damping 23, with a collet chuck A and another type of collet chuck B, respectively. An example of a usage pattern that is attached to and supported by the machine tool 4 is shown.

この使用形態において，まず、コレットチャックＡに防振工具３aを取り付ける場合、コレットチャックＡの剛性が工作機械４の持つ剛性と比較し大幅に低下するため、カバー１を十分に固定支持する条件とはならず、カバー１の振動特性にコレットチャックＡの振動特性が影響を及ぼす。従来の防振工具３aは、常に同じコレットチャックＡを使用する場合であれば、この使用形態におけるカバー１の振動特性ｍ１，ｋ１から、式（１）（２）を用いて動吸振器２aの振動特性ｋ２、ζ２を最適値に設定し、大きな振動抑制効果が得られる。   In this mode of use, first, when attaching the vibration isolating tool 3a to the collet chuck A, the rigidity of the collet chuck A is significantly lower than the rigidity of the machine tool 4, so that the cover 1 is sufficiently fixed and supported. In other words, the vibration characteristics of the collet chuck A affect the vibration characteristics of the cover 1. If the conventional anti-vibration tool 3a always uses the same collet chuck A, from the vibration characteristics m1 and k1 of the cover 1 in this usage pattern, the dynamic vibration absorber 2a is expressed by using equations (1) and (2). The vibration characteristics k2 and ζ2 are set to optimum values, and a large vibration suppression effect can be obtained.

図４に、式（１）（２）を用いて動吸振器のバネ定数ｋ２、減衰ζ２を最適化した場合の、錘質量ｍ２，バネ定数ｋ２、減衰ζ２から構成される従来の動吸振器２aを内蔵した防振工具３aの周波数応答の一例を示す。   FIG. 4 shows a conventional dynamic vibration absorber composed of weight mass m2, spring constant k2 and damping ζ2 when the spring constant k2 and damping ζ2 of the dynamic vibration absorber are optimized using the equations (1) and (2). An example of the frequency response of the anti-vibration tool 3a incorporating 2a is shown.

例えばカバー１がｍ１＝０．２５ｋｇ、ｋ１＝３．０ｅ6Ｎ／ｍ、ζ１＝０．０１の振動特性を持つ場合、動吸振器２ａの質量をｍ２＝０．１ｋｇとすると、質量比μ＝０．４であるたのめ，式（１）（２）より動吸振器２aの最適なバネ定数と減衰比の設定値は、ｋ２＝６．１ｅ6Ｎ／ｍ、ζ１＝０．２３となる。 For example, when the cover 1 has vibration characteristics of m1 = 0.25 kg, k1 = 3.0e 6 N / m, and ζ1 = 0.01, if the mass of the dynamic vibration absorber 2a is m2 = 0.1 kg, the mass ratio μ Therefore, the optimal spring constant and damping ratio setting values of the dynamic vibration absorber 2a are k2 = 6.1e 6 N / m and ζ1 = 0.23 from Equations (1) and (2). .

この結果を用いて動吸振器２aの振動特性k２、ζ２を最適化すると、前記動吸振器２aを内蔵した防振工具３aの振動波形は６１となり、従来防振工具３aは動吸振器２aを前記設定値に調整しておけば，動吸振器２aを内蔵していないカバー１のみの工具の振動波形５１の最大振幅を大幅に抑制可能である。   When the vibration characteristics k2 and ζ2 of the dynamic vibration absorber 2a are optimized using this result, the vibration waveform of the vibration isolation tool 3a incorporating the dynamic vibration absorber 2a is 61, and the conventional vibration isolation tool 3a has the dynamic vibration absorber 2a. By adjusting to the set value, the maximum amplitude of the vibration waveform 51 of the tool having only the cover 1 that does not include the dynamic vibration absorber 2a can be significantly suppressed.

特開2002-233903号公報JP 2002-233903 A 特開2002-233911号公報Japanese Patent Laid-Open No. 2002-233911 特開2003-62735号公報JP 2003-62735 A 特開2006-305674号公報JP 2006-305674 JP

しかし、上記特許文献１や特許文献２の場合、超硬素材の材料費は、鋼の数倍高いため、工具の製造コストに対する自励振動抑制効果が小さい場合や、ヤング率の向上倍率と同等の自励振動抑制効果が得られず、所望の効果が得られない場合があるという課題がある。 However, in the case of Patent Document 1 and Patent Document 2 described above, the material cost of the carbide material is several times higher than that of steel, so that the self-excited vibration suppressing effect on the tool manufacturing cost is small, or the Young's modulus improvement magnification is equivalent. The self-excited vibration suppressing effect cannot be obtained, and there is a problem that a desired effect may not be obtained.

また、特許文献３や特許文献４の場合、前記使用形態では、工具の突き出し長さＬｔや、工具径φＤ、または加工方法に応じて、使用するコレットチャックＡを、例えばコレットチャックＢに変更して使用するのが一般的である。   Further, in the case of Patent Document 3 and Patent Document 4, in the above-described usage mode, the collet chuck A to be used is changed to, for example, the collet chuck B according to the tool protrusion length Lt, the tool diameter φD, or the processing method. Is generally used.

この一例を図３に合わせて示す。同図に示すように、コレットチャックＡに合わせて最適化された前記動吸振器２aを内蔵する前記防振工具３aをコレットチャックＢに取付けた場合、動吸振器２aを内蔵していないカバー１の波形５１は波形５２に変わり、これに伴い、防振工具３aの振動波形は、波形６１から波形６２のように変化し、波形５２の最大振幅を効果的に抑制できなくなる。   An example of this is shown in FIG. As shown in the figure, when the vibration isolator 3a including the dynamic vibration absorber 2a optimized for the collet chuck A is attached to the collet chuck B, the cover 1 does not include the dynamic vibration absorber 2a. The waveform 51 changes to the waveform 52, and accordingly, the vibration waveform of the anti-vibration tool 3a changes from the waveform 61 to the waveform 62, and the maximum amplitude of the waveform 52 cannot be effectively suppressed.

以上述べたように、工具を固定するために用いるコレットチャックにより、工具本体の振動特性が変化する図４の使用形態では、従来の質量・バネ・減衰からなる動吸振器では工具本体の振動特性の変化に柔軟に対応できず工具自励振動の抑制効果が著しく減少してしまい、製品加工時の加工能率が低下する課題があった。   As described above, the vibration characteristics of the tool body change due to the collet chuck used to fix the tool. In the usage configuration of FIG. As a result, the effect of suppressing the tool self-excited vibration is remarkably reduced, and the machining efficiency at the time of product machining is reduced.

さらに、従来防振工具を用いて振動抑制効果を得るためには、使用するチャック毎に再度最適調整が必要となり、調整にともなう作業時間の延長により、全体の製造コストが高くなってしまう課題があった。   Furthermore, in order to obtain the vibration suppression effect using the conventional vibration isolating tool, it is necessary to make the optimum adjustment again for each chuck to be used, and there is a problem that the whole manufacturing cost increases due to the extension of the working time accompanying the adjustment. there were.

本発明の目的は、上記課題を解決し、工具本体の振動特性が変化しても、前記振動特性の変化ごとに、動吸振器の最適化をおこなうことなく、大きな振動抑制効果が得られる動吸振器を内蔵した防振工具及びその製造方法を提供することにある。   The object of the present invention is to solve the above-mentioned problems, and even if the vibration characteristic of the tool body changes, a dynamic vibration suppressing effect can be obtained without optimizing the dynamic vibration absorber for each change of the vibration characteristic. An object of the present invention is to provide an anti-vibration tool incorporating a vibration absorber and a method for manufacturing the same.

本発明は、上記課題を解決する手段として、工具本体に内蔵する動吸振器構造にランチェスタダンパ方式を採用することで、工具本体の振動特性が変化しても動吸振器の自励振動抑制効果が大幅に増減せず、安定した自励振動抑制効果が得られることを特徴とする動吸振器構造を有している防振工具である。   As a means for solving the above-mentioned problems, the present invention employs a lanchester damper system in a dynamic vibration absorber structure built in a tool body, thereby suppressing self-excited vibration of the dynamic vibration absorber even if the vibration characteristics of the tool body change. The anti-vibration tool has a dynamic vibration absorber structure characterized in that a stable self-excited vibration suppressing effect can be obtained without greatly increasing or decreasing the effect.

本発明によれば、加工面精度の低下や工具欠損の原因となる工具自励振動を抑制し、加工能率を向上するために、工具内部に中空部を設け、振動特性の変化ごとに動吸振器の調整を行うことなく大きな振動抑制効果が得られる動吸振器を備えることにより、工具本体の振動特性が変化しても、動吸振器の自励振動抑制効果が大幅に増減せず、安定した自励振動抑制効果が得られ、動吸振器の最適調整時間を削減することができる。 According to the present invention, in order to suppress tool self-excited vibration, which causes a decrease in machining surface accuracy and tool breakage, and to improve machining efficiency, a hollow portion is provided inside the tool, and dynamic vibration absorption is performed for each change in vibration characteristics. By providing a dynamic vibration absorber that can obtain a large vibration suppression effect without adjusting the vibration device, even if the vibration characteristics of the tool body change, the dynamic vibration absorber's self-excited vibration suppression effect does not increase or decrease significantly and is stable. The self-excited vibration suppressing effect can be obtained, and the optimum adjustment time of the dynamic vibration absorber can be reduced.

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

まず、本実施例の動吸振器の特徴と、防振工具の構造を述べる。図５は、本実施例のランチェスタダンパ方式を採用した動吸振器を質点系振動モデルで表したものである。このダンパは図２のバネ定数ｋ２をｋ２<<ｋ１とすることで，錘質量ｍ２を減衰比ζ２のみで支えている振動モデルとなる。このダンパ方式は、制振対象（カバー１）の振動特性ｍ１、ｋ１が変化しても、動吸振器を最適調整することなく、大きな振動抑制効果が得られることを特徴としている。   First, the characteristics of the dynamic vibration absorber of the present embodiment and the structure of the vibration isolating tool will be described. FIG. 5 shows a dynamic vibration absorber adopting the Lanchester damper system of the present embodiment in a mass system vibration model. This damper becomes a vibration model in which the mass m2 is supported only by the damping ratio ζ2 by setting the spring constant k2 of FIG. 2 to k2 << k1. This damper system is characterized in that even if the vibration characteristics m1 and k1 of the vibration suppression target (cover 1) change, a large vibration suppression effect can be obtained without optimal adjustment of the dynamic vibration absorber.

図６は上記ダンパ方式を有する本実施例の防振工具の構造を示したものである。本実施例の防振工具３bに内蔵されている動吸振器２bは、両端に凹形状を有する錘２５と、前記錘２５の両端に設けられた凹形状に合う、凸形状を有する低弾性ゴム２４のような粘弾性体から構成されており、低弾性ゴム２４と錘２５の中心軸が一致する構造となっている。
錘２５はカバー１の軸方向に設けられた中空部に低弾性ゴム２４により支持された構造を有する防振工具であり、錘２５側面と中空部７の側面の間には、クリアランスＣが設けられている。 FIG. 6 shows the structure of the vibration isolating tool of the present embodiment having the damper system. The dynamic vibration absorber 2b built in the vibration isolating tool 3b of the present embodiment includes a weight 25 having a concave shape at both ends, and a low elastic rubber having a convex shape that matches the concave shape provided at both ends of the weight 25. The low-elasticity rubber 24 and the weight 25 have the same center axis.
The weight 25 is a vibration isolating tool having a structure supported by a low elastic rubber 24 in a hollow portion provided in the axial direction of the cover 1, and a clearance C is provided between the side surface of the weight 25 and the side surface of the hollow portion 7. It has been.

さらに、前記動吸振器２bは、カッター５とカバー１を連結するための固定具６により、工具中空部内に固定されており、固定具６を取り外すことで、内部の動吸振器２bを容易に取り出せる構造となっているため、防振工具３bの製造段階で、錘２５の長さＬ１と、低弾性ゴムの厚さＬ２をカバー１の振動特性に合わせて調整することが容易な構造となっている。   Further, the dynamic vibration absorber 2b is fixed in the tool hollow portion by a fixing tool 6 for connecting the cutter 5 and the cover 1, and the internal dynamic vibration absorber 2b can be easily removed by removing the fixing tool 6. Since the structure can be taken out, it is easy to adjust the length L1 of the weight 25 and the thickness L2 of the low elastic rubber according to the vibration characteristics of the cover 1 in the manufacturing stage of the vibration isolator 3b. ing.

上記構造を有する本実施例の防振工具３ｂでは、切削加工中にカッター５が受ける切削力による工具自励振動が、固定具６、カバー１、低弾性ゴム２４を介して錘２５に伝わることで、錘２５がカバー１の振動と位相差をもって軸方向と垂直な平面内で振動し、低弾性ゴム２４がカバー１の軸方向と垂直な平面内で歪むことで、振動エネルギーを熱エネルギーに変換し散逸して振動を抑制するものである。このため、錘２５は十分に振動できるクリアランスＣが必要となる。本実施例ではクリアランスＣが０．５ｍｍ以上あることが好ましく、本実施例ではクリアランスＣを１．０ｍｍとしている。   In the vibration isolating tool 3b of the present embodiment having the above-described structure, the tool self-excited vibration due to the cutting force received by the cutter 5 during cutting is transmitted to the weight 25 via the fixture 6, the cover 1, and the low elastic rubber 24. Thus, the weight 25 vibrates in a plane perpendicular to the axial direction with a phase difference from the vibration of the cover 1, and the low elastic rubber 24 is distorted in a plane perpendicular to the axial direction of the cover 1. It transforms and dissipates to suppress vibration. Therefore, the weight 25 needs a clearance C that can sufficiently vibrate. In this embodiment, the clearance C is preferably 0.5 mm or more. In this embodiment, the clearance C is 1.0 mm.

次に、上記構造を有する本実施例の防振工具に用いる素材について説明する。
本実施例の動吸振器に用いる低弾性ゴム２４は、硬さがＪＩＳＫ６２５３に準じた試験で３０〜６０（タイプＡ）、伸びが５００〜９００％、静的せん断弾性率が０．３〜０．８ＭＰａ、反発弾性が２〜１３％のものが適しており、さらに好ましい低弾性ゴムとしては、内外ゴム株式会社製「ハネナイト」ＧＰ-３５Ｌ、ＧＰ-６０Ｌ、ＣＰ-４０Ｓ、ＣＰ−５５Ｓ、ＡＰ-３０、ＡＰ−５０、ＧＰ-４０ＨＢ、ＧＰ-５０Ｖが本実施例の実施形態に適している。この中で本実施例では、ＧＰ-３５Ｌが用いられている。
また、錘２５には、超硬材料、タングステン、銅-タングステン合金などの密度１３０００〜１９０００ｋｇ/ｍ3の高比重合金が適している。この中で本実施例では、銅-タングステン合金（密度１４０００ｋｇ/ｍ3）を用いている。 Next, the material used for the vibration isolating tool of the present embodiment having the above structure will be described.
The low elastic rubber 24 used in the dynamic vibration absorber of this example has a hardness of 30 to 60 (type A) according to JISK6253, an elongation of 500 to 900%, and a static shear modulus of 0.3 to 0. .8 MPa, rebound resilience of 2 to 13% is suitable, and more preferable low-elasticity rubbers include “Hanenite” GP-35L, GP-60L, CP-40S, CP-55S, AP manufactured by Inner and Outer Rubber Co., Ltd. -30, AP-50, GP-40HB, GP-50V are suitable for the embodiment of this example. Among these, GP-35L is used in the present embodiment.
For the weight 25, high specific polymerized gold having a density of 13,000 to 19000 kg / m 3 such as a super hard material, tungsten, or a copper-tungsten alloy is suitable. Among these, in this example, a copper-tungsten alloy (density 14000 kg / m 3 ) is used.

以上の構造、素材を用いた防振工具３ｂの工具自励振動の抑制効果を図７に示す。同図は動吸振器２bを内蔵した本実施例の防振工具３bを用いて、図５のコレットチャックＡと３２にそれぞれ取り付けた場合の、防振工具の振動抑制効果を周波数応答で示した一例である。コレットチャックＡを用いて、動吸振器を内蔵しないカバー１のみを支持した場合の振動波形５１が、本実施例の動吸振器２bを内蔵させることで、波形６３へと変化し、振動の最大振幅が抑制される。   FIG. 7 shows the suppression effect of the tool self-excited vibration of the vibration-proof tool 3b using the above structure and material. The figure shows the vibration suppression effect of the vibration isolating tool in terms of frequency response when the vibration isolating tool 3b of the present embodiment incorporating the dynamic vibration absorber 2b is attached to the collet chucks A and 32 in FIG. It is an example. When the collet chuck A is used to support only the cover 1 that does not include the dynamic vibration absorber, the vibration waveform 51 changes to the waveform 63 by incorporating the dynamic vibration absorber 2b of this embodiment, and the maximum vibration is obtained. Amplitude is suppressed.

また、コレットチャックＡをコレットチャックＢに変更した場合における、動吸振器を内蔵しないカバー１のみの振動波形５２は、本実施例の動吸振器２bを内蔵させることで、波形６４へと変化し、上記コレットチャックＡの振動抑制効果を持続できていることが分かる。
以上述べたように、本実施例の防振工具３ｂは、カバー１の振動特性の変化に柔軟に対応でき、且つ、カバー１の振動特性の変化ごとに、動吸振器２ｂを最適化しなくても、大きな工具の自励振動抑制効果が得られることが特徴である。 Further, when the collet chuck A is changed to the collet chuck B, the vibration waveform 52 of only the cover 1 that does not include the dynamic vibration absorber is changed to the waveform 64 by incorporating the dynamic vibration absorber 2b of this embodiment. It can be seen that the vibration suppressing effect of the collet chuck A can be maintained.
As described above, the vibration isolator 3b according to the present embodiment can flexibly cope with the change in the vibration characteristics of the cover 1 and does not optimize the dynamic vibration absorber 2b for each change in the vibration characteristics of the cover 1. In addition, it is characterized in that a self-excited vibration suppressing effect of a large tool can be obtained.

また、本実施例の防振工具３bは、図６の錘２５と低弾性ゴム２４において、予め用意された錘２５の長さＬ1が異なる複数の錘と、低弾性ゴム２４の厚さＬ２が異なる複数の低弾性ゴムとの組み合わせの中から、中空部の長さＬと一致するように、錘２５と低弾性ゴム２４の組み合わせを一つ選択し、制振ゴム２４の厚さＬ２を変えることで、動吸振器２bの減衰比ζ２を最適な値に設定することが可能である。最適化を行う際は、工具本体の質量ｍ１と動吸振器の錘質量ｍ２の比である、質量比μを用いて、下記の式（３）の減衰比になるよう、低弾性ゴムの厚さＬ２を調整すれば容易に最適化が可能である構造を有していることを特徴とした防振工具構造である。   Further, in the vibration isolator 3b of the present embodiment, a plurality of weights having different lengths L1 of the weight 25 prepared in advance and a thickness L2 of the low elastic rubber 24 in the weight 25 and the low elastic rubber 24 of FIG. One combination of the weight 25 and the low elastic rubber 24 is selected from a combination of a plurality of different low elastic rubbers so as to match the length L of the hollow portion, and the thickness L2 of the damping rubber 24 is changed. Thus, the damping ratio ζ2 of the dynamic vibration absorber 2b can be set to an optimum value. When optimizing, the thickness of the low elastic rubber is adjusted so that the damping ratio of the following formula (3) is obtained by using the mass ratio μ, which is the ratio of the mass m1 of the tool body and the mass m2 of the dynamic vibration absorber. The anti-vibration tool structure has a structure that can be easily optimized by adjusting the length L2.

Figure 2008307642
上述の方法を用いた本実施例の防振工具３ｂのカバー１は、工具材料としてＳＣＭ４４０（降伏強度４１０ＧＰa）を用いられている。工具径φＤ＝１２〜８０ｍｍにおいてＬｔ/Ｄが１０以下であれば、降伏強度を満足するように中空部７を設計することが可能である。しかし、Ｌｔ/Ｄが７．５以下で工具径が１２ｍｍより小さくなると、中空部７を設ける際に降伏強度を満足できなくなり、これ以上小さな工具径で防振工具を製造できなくなる。
Figure 2008307642
 The cover 1 of the vibration isolating tool 3b of the present embodiment using the above-described method uses SCM440 (yield strength 410 GPa) as a tool material. If the tool diameter φD is 12 to 80 mm and Lt / D is 10 or less, the hollow portion 7 can be designed so as to satisfy the yield strength. However, if Lt / D is 7.5 or less and the tool diameter is smaller than 12 mm, the yield strength cannot be satisfied when the hollow portion 7 is provided, and the vibration-proof tool cannot be manufactured with a tool diameter smaller than this.

これに対し、本実施例ではφ１２ｍｍ以下でＬｔ/Ｄが１０以下となる防振工具を製作するために、カバー１の材料をＳＣＭ４４０から、降伏強度１０００ＧＰa以上となる超硬材料を用いて製造してもよい。また、上記材質の変更は、工具径φＤ＝１６〜８０ｍｍにおいてＬｔ/Ｄが１０以上となる防振工具を製作するために、カバー１に超硬材料（降伏強度１０００ＧＰa以上となる、ＪＩＳ規格の分類Ｅ２、Ｅ３、Ｅ４、Ｅ５、Ｖ１０、Ｖ２０、Ｖ３０、Ｖ４０、Ｖ５０、Ｖ６０に属する材質）を用いてもよい。   On the other hand, in this embodiment, in order to manufacture a vibration isolating tool having φ12 mm or less and Lt / D of 10 or less, the material of the cover 1 is manufactured from SCM440 using a super hard material having a yield strength of 1000 GPa or more. May be. In addition, the change of the material is made of a cemented carbide material (with a yield strength of 1000 GPa or more, with a yield strength of 1000 GPa or more) in order to produce an anti-vibration tool having an Lt / D of 10 or more at a tool diameter φD = 16-80 mm Materials belonging to the classifications E2, E3, E4, E5, V10, V20, V30, V40, V50, and V60) may be used.

本実施例の防振工具を用いることで、例えば長尺工具による圧縮機用インペラの羽根形成のための切削加工がの加工能率を向上することができる。以下、圧縮機用インペラの羽根切削加工における、本実施例の効果について述べる。   By using the vibration isolating tool of the present embodiment, for example, the cutting efficiency for forming the blades of the impeller for the compressor using a long tool can be improved. Hereinafter, effects of the present embodiment in blade cutting of the compressor impeller will be described.

一般に、圧縮機用インペラは製造コストの増加を抑制するため、鍛造やプレスによって形成した羽根を軸に溶接することで製造されていた。インペラ性能を向上させるためには、羽根枚数を増やし、羽根の形状を、羽根高さが高い複雑な曲面を持つ３次元形状にする必要がある。しかし、従来の鍛造もしくはプレスによる羽根の形成だけでは、形状精度が悪いため、インペラの性能を向上させることが困難である。性能を向上させるためには、バルク材である鍛造素材から切削工具を用いて、羽根形状を切削加工て形成する方法が望ましい。   In general, a compressor impeller has been manufactured by welding a blade formed by forging or pressing to a shaft in order to suppress an increase in manufacturing cost. In order to improve the impeller performance, it is necessary to increase the number of blades and make the blade shape into a three-dimensional shape having a complicated curved surface with a high blade height. However, it is difficult to improve the performance of the impeller simply by forming blades by conventional forging or pressing because the shape accuracy is poor. In order to improve the performance, a method of forming a blade shape from a forged material that is a bulk material by using a cutting tool is desirable.

しかし、上述のように、羽根が羽根高さの高い３次元形状になっているため、切削加工に必要となる工具は小径で長尺な工具を用いる必要があるが、工具の持つ剛性が低くなり、工具の自励振動が発生しやすくなるため、切削加工による諸望の羽根の形状精度を得られない場合や、工具の刃先が欠損してしまい切削を続行することが不可能な状況になり易くなる。このため、小径で長尺な工具を用いた羽根の切削加工の加工能率を向上させることが非常に困難であった。   However, as described above, since the blade has a three-dimensional shape with a high blade height, it is necessary to use a long tool with a small diameter as a tool necessary for cutting, but the rigidity of the tool is low. Therefore, it is easy to generate self-excited vibrations of the tool, and it is impossible to obtain the desired blade shape accuracy by cutting, or the cutting edge of the tool is lost and cutting cannot be continued. It becomes easy to become. For this reason, it has been very difficult to improve the processing efficiency of blade cutting using a long tool with a small diameter.

この問題は、従来の防振工具を適用することで改善することが可能であるが、圧縮機用インペラの羽根切削加工では、使用するコレットチャックが複数あるため、工具の支持条件が多数存在する。一方、従来防振工具は、上述したように、個々のコレットチャックで決まる、工具の支持条件に合わせて内蔵している動吸振器のバネ定数や減衰比を、最適化しなければ諸望の自励振動抑制効果が得られない。   This problem can be improved by applying a conventional vibration isolating tool. However, in blade cutting of an impeller for a compressor, since there are a plurality of collet chucks to be used, there are many support conditions for the tool. . On the other hand, as described above, the conventional anti-vibration tool has a self-desired self unless it optimizes the spring constant and damping ratio of the built-in dynamic vibration absorber according to the support condition of the tool, which is determined by each collet chuck. The excitation vibration suppression effect cannot be obtained.

しかし、最適化により諸望の抑制効果を得るためには、防振工具の調整に時間を要し、切削加工の遅延を招き、製造コストが高くなってしまうため、加工能率が向上しても、製造全体のコスト削減効果は小さくなってしまう可能性がある。このため、従来防振工具を用いた加工能率向上が困難であった。   However, it takes time to adjust the anti-vibration tool in order to obtain the effect of suppressing various desires by optimization, resulting in a delay in cutting and an increase in manufacturing cost. The cost reduction effect of the entire manufacturing may be reduced. For this reason, it has been difficult to improve machining efficiency using a conventional vibration-proof tool.

本実施例は、多数のコレットチャックにより決まる工具の支持部条件に対して、振動抑制効果が大幅に変化しないため、支持部条件毎の調整作業が不要となり、調整にともなう切削加工の遅延を削減できる。   In this example, the vibration suppression effect does not change significantly with respect to the tool support conditions determined by a large number of collet chucks. Therefore, adjustment work for each support condition is not necessary, and cutting delays associated with adjustment are reduced. it can.

図８は、本実施例の防振工具３ｂを回転数Ｓで回転させながらツールパス８に沿って移動させ、鍛造素材１００から切削加工にて羽根１０１を形成し、圧縮機用インペラを製造する手法を示した一例である。   In FIG. 8, the anti-vibration tool 3b of the present embodiment is moved along the tool path 8 while rotating at the rotational speed S, and blades 101 are formed by cutting from the forging material 100 to manufacture a compressor impeller. It is an example showing a technique.

同図の加工で使用する工具が例えば４種類ある場合、すべての工具を従来防振工具にすると、調整に半日/本かかるため、すべてを調整するのに約２日かかる。一方、本実施例の防振工具は調整が要らないため、従来防振工具の調整にかける２日間で圧縮機用インペラを１台生産することができ、一月あたり１２台生産しているとすると、１３台生産できるようになり、生産効率を１０％向上できる。   If there are, for example, four types of tools used in the machining shown in the figure, if all the tools are conventional anti-vibration tools, the adjustment takes half a day / piece, so it takes about two days to adjust all. On the other hand, since the anti-vibration tool of the present embodiment does not require adjustment, it is possible to produce one compressor impeller in two days for the adjustment of the conventional anti-vibration tool, and produce 12 units per month. Then, 13 units can be produced, and the production efficiency can be improved by 10%.

従来用いられている工具自励振動の抑制方法の一例を示した図である。It is the figure which showed an example of the suppression method of the tool self-excited vibration used conventionally. 従来用いられている防振工具を質点系振動モデルで示した図である。It is the figure which showed the vibration isolator tool used conventionally by the mass system vibration model. 工具を異なるコレットチャックを介して工作機械に取り付ける際の模式図である。It is a schematic diagram at the time of attaching a tool to a machine tool via a different collet chuck. 従来防振工具を異なるコレットチャックを介して工作機械に取り付けた際の、工具自励振動抑制効果を示した図である。It is the figure which showed the tool self-excited vibration suppression effect at the time of attaching a conventional vibration isolating tool to a machine tool via a different collet chuck. 本実施例の動吸振器を質点系振動モデルで表した図である。It is the figure which represented the dynamic vibration absorber of the present Example by the mass system vibration model. 本実施例の実施形態になる工具内部にランチェスタダンパを内蔵した防振工具を示した図である。It is the figure which showed the vibration proof tool which incorporated the Lanchester damper in the inside of the tool which becomes embodiment of a present Example. 本実施例による動吸振器を内蔵した振工具を、異なるコレットチャックを介して工作機械に取り付けた際の、工具自励振動抑制効果を示した図である。It is the figure which showed the tool self-excited vibration suppression effect at the time of attaching the vibration tool incorporating the dynamic vibration absorber by a present Example to a machine tool via a different collet chuck. 本実施例の防振工具による圧縮機用インペラの羽根切削加工を示す図である。It is a figure which shows the blade cutting process of the impeller for compressors with the vibration isolator of a present Example.

符号の説明Explanation of symbols

1…工具本体、2a…従来の動吸振器、2b…本実施例による動吸振器、21…質量、22…バネ、23…減衰、24…低弾性ゴム、25…錘、3a…従来防振工具、3b…本実施例の防振工具、4…工作機械、5…カッター、6…固定具、7…中空部、8…ツールパス、100…鍛造素材、101…羽根。 DESCRIPTION OF SYMBOLS 1 ... Tool body, 2a ... Conventional dynamic vibration absorber, 2b ... Dynamic vibration absorber by a present Example, 21 ... Mass, 22 ... Spring, 23 ... Damping, 24 ... Low elastic rubber, 25 ... Weight, 3a ... Conventional vibration isolation Tool, 3b ... vibration isolating tool of this embodiment, 4 ... machine tool, 5 ... cutter, 6 ... fixture, 7 ... hollow part, 8 ... tool path, 100 ... forging material, 101 ... blade.

Claims (8)

本体内部の軸方向に設けられた中空部に、錘と粘弾性体から構成される動吸振器を、前記粘弾性体により支持する構造を備え、前記本体の軸方向に垂直な平面内における振動に対して、前記動吸振器が相対移動可能であることを特徴とする防振工具。 A hollow portion provided in the axial direction inside the main body has a structure in which a dynamic vibration absorber made up of a weight and a viscoelastic body is supported by the viscoelastic body, and vibrations in a plane perpendicular to the axial direction of the main body On the other hand, the vibration isolator is movable relative to the vibration isolator. 請求項１に記載の防振工具において、前記粘弾性体が、低弾性ゴムであることを特徴とする防振工具。 The anti-vibration tool according to claim 1, wherein the viscoelastic body is a low-elasticity rubber. 請求項２に記載の防振工具において、前記低弾性ゴムの硬さが、ＪＩＳＫ６２５３に準じた試験で３０〜６０（タイプＡ）、伸びが５００〜９００％、静的せん断弾性率が０．３〜０．８ＭＰａ、反発弾性が２〜１３％であることを特徴とする防振工具。 The anti-vibration tool according to claim 2, wherein the hardness of the low-elasticity rubber is 30 to 60 (type A) according to JISK6253, the elongation is 500 to 900%, and the static shear modulus is 0.3. An anti-vibration tool characterized by having a rebound resilience of ˜0.8 MPa and a resilience of 2 to 13%. 請求項１に記載の防振工具において、前記錘が、超硬材料、タングステン、銅-タングステン合金などの密度１３０００〜１９０００ｋｇ/ｍ3の高比重合金であることを特徴とする防振工具。 The anti-vibration tool according to claim 1, wherein the weight is a high specific-polymerization gold having a density of 13,000 to 19000 kg / m 3 such as a super hard material, tungsten, or a copper-tungsten alloy. 請求項１に記載の防振工具において、前記錘の側面と前記中空部の側面の間に、０．５ｍｍ以上のクリアランスＣを設けたことを特徴とする防振工具。 The anti-vibration tool according to claim 1, wherein a clearance C of 0.5 mm or more is provided between a side surface of the weight and a side surface of the hollow portion. 請求項１に記載の防振工具において、前記動吸振器は、カッターとカバーを連結するための固定具により、前記中空部内に固定されており、前記固定具を取り外すことで、内部の前記動吸振器を取り出せる構造であることを特徴とする防振工具。 The anti-vibration tool according to claim 1, wherein the dynamic vibration absorber is fixed in the hollow portion by a fixture for connecting a cutter and a cover, and the internal vibration is removed by removing the fixture. An anti-vibration tool characterized by having a structure capable of removing a vibration absorber. 本体内部の軸方向に設けられた中空部に、錘と粘弾性体から構成される動吸振器を備えた防振工具の製造方法であって、長さが異なる複数の錘と、厚さが異なる複数の粘弾性体との組み合わせの中から、前記中空部の長さと一致するように、前記錘と前記粘弾性体の組み合わせを一つ選択し、前記粘弾性体の厚さを変えることで、前記動吸振器の減衰比を設定することを特徴とする防振工具の製造方法。 A method of manufacturing an anti-vibration tool comprising a dynamic vibration absorber made up of a weight and a viscoelastic body in a hollow portion provided in the axial direction inside the main body, wherein a plurality of weights having different lengths and thicknesses By selecting one combination of the weight and the viscoelastic body from the combination with different viscoelastic bodies so as to match the length of the hollow portion, and changing the thickness of the viscoelastic body A method for manufacturing a vibration isolating tool, wherein a damping ratio of the dynamic vibration absorber is set. 請求項７に記載の防振工具の製造方法において、前記防振工具本体の質量と前記動吸振器の錘質量の比である質量比を用いて、前記粘弾性体の厚さを調整することを特徴とする防振工具の製造方法。 The method of manufacturing a vibration isolating tool according to claim 7, wherein the thickness of the viscoelastic body is adjusted using a mass ratio that is a ratio of a mass of the vibration isolating tool body and a mass of the dynamic vibration absorber. The manufacturing method of the vibration isolator characterized by these.
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CN102848002A (en) * 2011-07-01 2013-01-02 钴碳化钨硬质合金公司 Rotary cutting tool with vibration damping device
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Publication number Priority date Publication date Assignee Title
JP2011011276A (en) * 2009-07-01 2011-01-20 Hitachi Plant Technologies Ltd Vibration-proof tool
CN102848002A (en) * 2011-07-01 2013-01-02 钴碳化钨硬质合金公司 Rotary cutting tool with vibration damping device
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CN114025901A (en) * 2019-07-01 2022-02-08 山特维克科洛曼特公司 Metal cutting tool comprising a vibration damping member
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