JPH09250457A - Air compressor - Google Patents
Air compressorInfo
- Publication number
- JPH09250457A JPH09250457A JP5517196A JP5517196A JPH09250457A JP H09250457 A JPH09250457 A JP H09250457A JP 5517196 A JP5517196 A JP 5517196A JP 5517196 A JP5517196 A JP 5517196A JP H09250457 A JPH09250457 A JP H09250457A
- Authority
- JP
- Japan
- Prior art keywords
- weight
- air
- compressor
- air tank
- vibration
- 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.)
- Granted
Links
Landscapes
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】この発明は、エアコンプレッ
サに関するものであり、特に、振動を低下させて低騒音
化したエアコンプレッサに関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air compressor, and more particularly to an air compressor which has reduced vibration and noise.
【０００２】[0002]
【発明が解決しようとする課題】可搬型エアコンプレッ
サは、コンプレッサユニットと空気タンクとが一体的に
結合され、モータあるいはエンジンによって駆動される
コンプレッサユニットから吐出される高圧空気は空気タ
ンクに蓄えられる。In a portable air compressor, a compressor unit and an air tank are integrally connected, and high pressure air discharged from a compressor unit driven by a motor or an engine is stored in the air tank.
【０００３】空気工具等に用いられるエアコンプレッサ
は、一般的にレシプロ形コンプレッサユニットが搭載さ
れているが、特に、吐出量が大きいコンプレッサユニッ
トほど振動と騒音が大きく、低騒音化が要望されてい
る。そこで、低騒音のエアコンプレッサを提供するため
に解決すべき技術的課題が生じてくるのであり、本発明
は上記課題を解決することを目的とする。An air compressor used for a pneumatic tool or the like is generally equipped with a reciprocating compressor unit. Particularly, a compressor unit having a larger discharge amount has a larger vibration and noise, and a lower noise is demanded. . Therefore, a technical problem to be solved in order to provide an air compressor with low noise occurs, and an object of the present invention is to solve the above problem.
【０００４】[0004]
【課題を解決するための手段】この発明は、上記目的を
達成するために提案するものであり、空気タンクと、前
記空気タンク内へ空気を圧縮充填するコンプレッサユニ
ットとを結合したエアコンプレッサにおいて、レールま
たはガイドへ錘を走行自在に装着し、前記錘の走行方向
の前後両側にバネあるいは磁石の組合せ等による弾発手
段を介装して前記錘を前記レールまたはガイドの走行範
囲の中間位置に安定させた動吸振器を前記空気タンク内
に装置し、前記動吸振器の共振周波数を前記コンプレッ
サユニットの発生する振動の基本周波数とほぼ等しく設
定したことを特徴とするエアコンプレッサを提供するも
のである。DISCLOSURE OF THE INVENTION The present invention is proposed in order to achieve the above object, and is an air compressor in which an air tank and a compressor unit for compressing and filling air into the air tank are combined, A weight is attached to a rail or a guide so that the weight can travel freely, and an elastic means such as a combination of springs or magnets is provided on both front and rear sides of the weight in the traveling direction to move the weight to an intermediate position in the traveling range of the rail or the guide. A stabilized dynamic vibration reducer is installed in the air tank, and a resonance frequency of the dynamic vibration reducer is set to be substantially equal to a fundamental frequency of vibration generated by the compressor unit. is there.
【０００５】[0005]
【発明の実施の形態】以下、この発明の実施の一形態を
図に従って詳述する。図１はエアコンプレッサ１を示
し、電動形のコンプレッサユニット２に空気タンク３が
結合されている。コンプレッサユニット２は、モータ４
の回転軸５に取り付けた偏心軸６と、シリンダ７に挿入
されたピストン８とをコネクティングロッド９にて連結
した往復動形コンプレッサであり、シリンダ７の頂部に
設けた吐出弁１０を介して空気タンク３内へ圧縮空気を
吐出する。また、モータ４の偏心軸６には回転系の質量
バランスをとるためのバランスウェイト１１が取付けら
れている。尚、１２は電源コード、１３は電源プラグで
ある。BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of the present invention will be described in detail below with reference to the drawings. FIG. 1 shows an air compressor 1 in which an air tank 3 is connected to an electric compressor unit 2. The compressor unit 2 has a motor 4
Is a reciprocating compressor in which an eccentric shaft 6 attached to a rotary shaft 5 of a cylinder 7 and a piston 8 inserted in a cylinder 7 are connected by a connecting rod 9, and an air is discharged through a discharge valve 10 provided at the top of the cylinder 7. Compressed air is discharged into the tank 3. A balance weight 11 for balancing the mass of the rotating system is attached to the eccentric shaft 6 of the motor 4. Reference numeral 12 is a power cord, and 13 is a power plug.
【０００６】空気タンク３には、空気圧レギュレータ１
４を介して圧力空気を取出せるカプラ１５と、無制御圧
力空気を直接取出せるカプラ１６の２系統の空気取出し
口が設けられている。空気タンク３内には動吸振器２１
が収納され、空気タンク３の内壁に固定されている。The air tank 3 includes an air pressure regulator 1
There are provided two systems of air outlets, namely, a coupler 15 for taking out the pressured air through 4 and a coupler 16 for directly taking out the uncontrolled pressured air. A dynamic vibration absorber 21 is installed in the air tank 3.
Are stored and fixed to the inner wall of the air tank 3.
【０００７】図２は動吸振器２１を示し、ガイドシャフ
ト２２に錘２３がスライド自在に装着され、錘２３の両
面とガイドシャフト２２の両側端板２４，２５とにそれ
ぞれ圧縮コイルバネ２６，２７が介装されている。錘２
３は両側から圧縮コイルバネ２６，２７に押圧され、両
側の圧縮コイルバネ２６，２７の弾発力が均衡するガイ
ドシャフト２２の中間位置に安定している。FIG. 2 shows a dynamic vibration absorber 21 in which a weight 23 is slidably mounted on a guide shaft 22, and compression coil springs 26 and 27 are provided on both surfaces of the weight 23 and both end plates 24 and 25 of the guide shaft 22, respectively. It is installed. Weight 2
3 is pressed by the compression coil springs 26 and 27 from both sides, and is stable at an intermediate position of the guide shaft 22 where the elastic forces of the compression coil springs 26 and 27 on both sides are balanced.
【０００８】錘２３の質量ｍ0 と圧縮コイルバネ２６，
２７のバネ定数ｋ0 とによって決定される動吸振器２１
の共振周波数ｆ0 は次式で表されれる。 １／２π√（ｋ0 ／ｍ0 ）＝ｆ0 （Ｈｚ） ここでは、コンプレッサユニット２のモータ４の回転数
が、例えば、１４４０ｒｐｍ＝２４Ｈｚであるとする
と、錘２３の質量ｍ0 ＝１ｋｇ、バネ定数ｋ0 ＝２．３
ｋｇｆとしてｆ0 ≒２４Ｈｚとし、共振周波数ｆ0 をコ
ンプレッサユニット２の基本振動周波数と等しく設定し
てある。The mass m 0 of the weight 23 and the compression coil spring 26,
Dynamic vibration absorber 21 determined by the spring constant k 0 of 27
The resonance frequency f 0 of is expressed by the following equation. 1 / 2π√ (k 0 / m 0 ) = f 0 (Hz) Here, if the rotation speed of the motor 4 of the compressor unit 2 is, for example, 1440 rpm = 24 Hz, the mass m 0 of the weight 23 is 1 kg, Spring constant k 0 = 2.3
The resonance frequency f 0 is set equal to the fundamental vibration frequency of the compressor unit 2, with f 0 ≈24 Hz as kgf.
【０００９】一般に知られているように、動吸振器２１
は、ガイドシャフト方向の加速度がゼロのときに、錘２
３はガイドシャフト２２の中央位置で静止しており、加
速度が加わると錘２３がガイドシャフト２２に沿って相
対的に移動を開始する。そして、コンプレッサユニット
２の作動時に発生する振動によって空気タンク３ととも
に錘２３が振動し、共振周波数ｆ0 ≒２４Ｈｚのときに
空気タンク３と錘２３の振動位相が１８０度ずれ且つ、
錘２３の振幅も最大になる。このとき、錘２３の慣性力
が圧縮コイルバネ２６，２７、ガイドシャフト２２を介
して空気タンク３に作用し、エアコンプレッサ１全体の
慣性を低減させて振幅を抑制する。さらに、コンプレッ
サユニット２の基本振動周波数＝２４Ｈｚの振動が減衰
することにより、高次高調波振動（４８Ｈｚ，７２Ｈ
ｚ，‥‥）も減衰する。As is generally known, the dynamic vibration absorber 21
Is the weight 2 when the acceleration in the guide shaft direction is zero.
3 is stationary at the central position of the guide shaft 22, and the weight 23 starts to move relatively along the guide shaft 22 when acceleration is applied. Then, the weight 23 vibrates together with the air tank 3 due to the vibration generated during the operation of the compressor unit 2, and the vibration phase of the air tank 3 and the weight 23 deviates by 180 degrees when the resonance frequency f 0 ≈24 Hz,
The amplitude of the weight 23 also becomes maximum. At this time, the inertial force of the weight 23 acts on the air tank 3 via the compression coil springs 26 and 27 and the guide shaft 22 to reduce the inertia of the entire air compressor 1 and suppress the amplitude. Furthermore, the vibration of the fundamental vibration frequency of the compressor unit 2 = 24 Hz is attenuated, so that high-order harmonic vibration (48 Hz, 72 H) is generated.
z, ...) also decays.
【００１０】なお、動吸振器は、金属バネを用いたもの
以外に種々の形式ものが応用でき、図３に示すように、
ガイドシャフト３１に可動磁石３２をスライド自在に装
着し、ガイドシャフト３１の両端に固定磁石３３，３４
を装着して、可動磁石３２のＮ極と固定磁石３３のＮ極
を対向させ、可動磁石３２のＳ極と固定磁石３４のＮ極
を対向させて磁力線の反発力によって可動磁石３２をガ
イドシャフト３１の中間位置に安定させた磁石形動吸振
器３５を用いてもよい。As the dynamic vibration reducer, various types other than the one using a metal spring can be applied, and as shown in FIG.
A movable magnet 32 is slidably attached to the guide shaft 31, and fixed magnets 33, 34 are attached to both ends of the guide shaft 31.
And the N pole of the movable magnet 32 and the N pole of the fixed magnet 33 face each other, and the S pole of the movable magnet 32 and the N pole of the fixed magnet 34 face each other so that the movable magnet 32 is guided by the repulsive force of the magnetic force lines. The magnet type dynamic vibration reducer 35 stabilized at the intermediate position of 31 may be used.
【００１１】動吸振器の設置方向は、一般的に振動発生
源であるピストン８の往復方向に錘の振動方向を合致さ
せると効果が上がるが、これに限定せず、エアコンプレ
ッサの振動方向や振幅を分析して最も効果的な設置位置
並びに方向を決定するべきである。また、複数の動吸振
器を直交姿勢で設置すると、多方向の振動に対する制振
効果がより一層向上する。The installation direction of the dynamic vibration absorber is generally effective if the vibration direction of the weight is matched with the reciprocating direction of the piston 8 which is the vibration source, but the invention is not limited to this. The amplitude should be analyzed to determine the most effective installation location and orientation. Further, when a plurality of dynamic vibration absorbers are installed in an orthogonal posture, the vibration damping effect against vibrations in multiple directions is further improved.
【００１２】尚、この発明は上記の実施形態に限定する
ものではなく、この発明の技術的範囲内において種々の
改変が可能であり、この発明がそれらの改変されたもの
に及ぶことは当然である。The present invention is not limited to the above-mentioned embodiments, and various modifications can be made within the technical scope of the present invention, and it goes without saying that the present invention extends to those modifications. is there.
【００１３】[0013]
【発明の効果】以上説明したように、本発明のエアコン
プレッサは、コンプレッサユニットが発生する振動を動
吸振器を用いて制振するので、振動並びに騒音が著しく
低下し、作業環境の改善に効果を発揮する。また、動吸
振器を空気タンク内に収容したので、運搬や取扱いに支
障をきたすことがなく、動吸振器の破損も防止できる。
また、動吸振器に埃や異物が付着することもなく、特
に、磁石形動吸振器を用いる場合に問題となる磁石が砂
鉄や鉄粉を吸着することによる作動不良の発生が防止さ
れて長期間安定した動作が期待できる。As described above, in the air compressor of the present invention, the vibration generated by the compressor unit is damped by using the dynamic vibration reducer, so that the vibration and noise are remarkably reduced and the working environment is improved. Exert. Further, since the dynamic vibration reducer is housed in the air tank, it does not hinder transportation and handling, and damage to the dynamic vibration reducer can be prevented.
In addition, dust and foreign matter do not adhere to the dynamic vibration reducer, and in particular, when a magnet type dynamic vibration reducer is used, it is possible to prevent malfunctions due to adsorption of sand iron or iron powder by the magnet, which can prevent long operation. You can expect stable operation for a certain period.
【図１】本発明の実施形態を示し、エアコンプレッサの
一部切欠正面図である。FIG. 1 is a partially cutaway front view of an air compressor according to an embodiment of the present invention.
【図２】コイルバネ形動吸振器の正面図。FIG. 2 is a front view of a coil spring type dynamic vibration reducer.
【図３】磁石形動吸振器の正面図。FIG. 3 is a front view of a magnet type dynamic vibration reducer.
１ エアコンプレッサ ２ コンプレッサユニット ３ 空気タンク ２１ 動吸振器 ２２ ガイドシャフト ２３ 錘 ２４，２５ 端板 ２６，２７ 圧縮コイルバネ ３１ ガイドシャフト ３２ 可動磁石 ３３，３４ 固定磁石 ３５ 磁石形動吸振器 1 Air Compressor 2 Compressor Unit 3 Air Tank 21 Dynamic Vibration Absorber 22 Guide Shaft 23 Weight 24, 25 End Plate 26, 27 Compression Coil Spring 31 Guide Shaft 32 Movable Magnet 33, 34 Fixed Magnet 35 Magnet Dynamic Vibration Absorber
Claims (1)
を圧縮充填するコンプレッサユニットとを結合したエア
コンプレッサにおいて、レールまたはガイドへ錘を走行
自在に装着し、前記錘の走行方向の前後両側にバネある
いは磁石の組合せ等による弾発手段を介装して前記錘を
前記レールまたはガイドの走行範囲の中間位置に安定さ
せた動吸振器を前記空気タンク内に装置し、前記動吸振
器の共振周波数を前記コンプレッサユニットの発生する
振動の基本周波数とほぼ等しく設定したことを特徴とす
るエアコンプレッサ。1. An air compressor comprising an air tank and a compressor unit for compressing and filling air into the air tank, wherein a weight is movably mounted on a rail or a guide, and the weight is mounted on both front and rear sides of the weight in the traveling direction. A dynamic vibration absorber that stabilizes the weight at an intermediate position of the travel range of the rail or guide by interposing an elastic means such as a combination of springs or magnets is installed in the air tank to resonate the dynamic vibration absorber. An air compressor having a frequency set to be substantially equal to a fundamental frequency of vibration generated by the compressor unit.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP05517196A JP3180657B2 (en) | 1996-03-12 | 1996-03-12 | Air compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP05517196A JP3180657B2 (en) | 1996-03-12 | 1996-03-12 | Air compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH09250457A true JPH09250457A (en) | 1997-09-22 |
| JP3180657B2 JP3180657B2 (en) | 2001-06-25 |
Family
ID=12991290
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP05517196A Expired - Fee Related JP3180657B2 (en) | 1996-03-12 | 1996-03-12 | Air compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3180657B2 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1450472A1 (en) * | 2002-10-16 | 2004-08-25 | Matsushita Refrigeration Company | Linear motor and liner compressor using the same |
| WO2004081379A3 (en) * | 2003-03-11 | 2005-01-06 | Lg Electronics Inc | Reciprocating compressor having vibration attenuating supporting unit |
| CN103775312A (en) * | 2014-01-21 | 2014-05-07 | 南通市红星空压机配件制造有限公司 | Air compressor device |
| US8851229B2 (en) | 2011-09-13 | 2014-10-07 | Black & Decker Inc. | Tank dampening device |
| US9890774B2 (en) | 2011-09-13 | 2018-02-13 | Black & Decker Inc. | Compressor intake muffler and filter |
| US11111913B2 (en) | 2015-10-07 | 2021-09-07 | Black & Decker Inc. | Oil lubricated compressor |
-
1996
- 1996-03-12 JP JP05517196A patent/JP3180657B2/en not_active Expired - Fee Related
Cited By (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1450472A1 (en) * | 2002-10-16 | 2004-08-25 | Matsushita Refrigeration Company | Linear motor and liner compressor using the same |
| EP1450472A4 (en) * | 2002-10-16 | 2005-04-13 | Matsushita Refrigeration | Linear motor and liner compressor using the same |
| US7078832B2 (en) * | 2002-10-16 | 2006-07-18 | Matsushita Refrigeration Company | Linear motor, and linear compressor using the same |
| US7614856B2 (en) * | 2002-10-16 | 2009-11-10 | Panasonic Corporation | Linear motor, and linear compressor using the same |
| WO2004081379A3 (en) * | 2003-03-11 | 2005-01-06 | Lg Electronics Inc | Reciprocating compressor having vibration attenuating supporting unit |
| US10036375B2 (en) | 2011-09-13 | 2018-07-31 | Black & Decker Inc. | Compressor housing having sound control chambers |
| US9670920B2 (en) * | 2011-09-13 | 2017-06-06 | Black & Decker Inc. | Tank dampening device |
| US20150016953A1 (en) * | 2011-09-13 | 2015-01-15 | Black & Decker Inc. | Tank dampening device |
| US9181938B2 (en) * | 2011-09-13 | 2015-11-10 | Black & Decker Inc. | Tank dampening device |
| US20150330380A1 (en) * | 2011-09-13 | 2015-11-19 | Black & Decker Inc. | Tank dampening device |
| AU2012216746B2 (en) * | 2011-09-13 | 2016-01-07 | Black & Decker Inc | Tank dampening device |
| AU2012216660B2 (en) * | 2011-09-13 | 2016-10-13 | Black & Decker Inc | Tank dampening device |
| US8851229B2 (en) | 2011-09-13 | 2014-10-07 | Black & Decker Inc. | Tank dampening device |
| US9890774B2 (en) | 2011-09-13 | 2018-02-13 | Black & Decker Inc. | Compressor intake muffler and filter |
| US10012223B2 (en) | 2011-09-13 | 2018-07-03 | Black & Decker Inc. | Compressor housing having sound control chambers |
| US11788522B2 (en) | 2011-09-13 | 2023-10-17 | Black & Decker Inc. | Compressor intake muffler and filter |
| US10871153B2 (en) | 2011-09-13 | 2020-12-22 | Black & Decker Inc. | Method of reducing air compressor noise |
| US10982664B2 (en) | 2011-09-13 | 2021-04-20 | Black & Decker Inc. | Compressor intake muffler and filter |
| CN103775312A (en) * | 2014-01-21 | 2014-05-07 | 南通市红星空压机配件制造有限公司 | Air compressor device |
| US11111913B2 (en) | 2015-10-07 | 2021-09-07 | Black & Decker Inc. | Oil lubricated compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3180657B2 (en) | 2001-06-25 |
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