JP2587778Y2 - Impact tool - Google Patents
Impact toolInfo
- Publication number
- JP2587778Y2 JP2587778Y2 JP1993052620U JP5262093U JP2587778Y2 JP 2587778 Y2 JP2587778 Y2 JP 2587778Y2 JP 1993052620 U JP1993052620 U JP 1993052620U JP 5262093 U JP5262093 U JP 5262093U JP 2587778 Y2 JP2587778 Y2 JP 2587778Y2
- Authority
- JP
- Japan
- Prior art keywords
- cylinder
- pressure receiving
- piston
- hole
- receiving portion
- 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
Landscapes
- Percussive Tools And Related Accessories (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本考案は、圧縮空気を利用してタ
ガネで金属又は石材等の表面を、はつり又は研削する衝
撃工具に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an impact tool for grinding or grinding a surface of a metal or a stone with a rag using compressed air.
【０００２】[0002]
【従来の技術】従来、コンプレッサから送気される圧縮
空気により作動する衝撃工具は、シリンダ内を勢いよく
往復動するピストンによってタガネの後端を打撃し、そ
の衝撃によってタガネの先端部分を金属や石材等の被加
工面に衝突させて、はつりまたは研削作業を行ってい
る。しかし、打撃と被加工面からの反作用による反動と
によって該衝撃工具を保持する作業者の手に強い衝撃が
伝わるため、疲労が激しくて長時間連続して作業を行う
ことが困難であった。そのため、この種の衝撃工具にあ
っては衝撃や振動を吸収する種々の緩衝装置を具えてい
る。2. Description of the Related Art Conventionally, an impact tool operated by compressed air sent from a compressor hits the rear end of a spring with a piston that reciprocates vigorously in a cylinder, and the shock causes the tip of the spring to be made of metal or metal. Hanging or grinding work is performed by colliding with a work surface such as a stone material. However, since a strong impact is transmitted to the operator's hand holding the impact tool by the impact and the reaction due to the reaction from the surface to be processed, it is difficult to work continuously for a long time due to severe fatigue. Therefore, this type of impact tool is provided with various shock absorbers for absorbing impact and vibration.
【０００３】たとえば、実開昭５８−１６０７２５号公
報に記載されている衝撃工具は、圧縮空気を動力源とす
るものであり、衝撃を吸収する装置としてはばねが開示
されている。このようなばねによる緩衝装置は、該ばね
の強度によって衝撃吸収機能と振動吸収機能とが決まっ
てしまうため、圧縮空気の圧力の強弱や振動数及び衝撃
力等に適合したばねを選択して取付ける必要がある。For example, an impact tool described in Japanese Utility Model Application Laid-Open No. 58-160725 uses compressed air as a power source, and a spring is disclosed as a device for absorbing impact. In such a shock absorber using a spring, the shock absorbing function and the vibration absorbing function are determined by the strength of the spring. Therefore, a spring suitable for the strength of the compressed air, the frequency, the impact force, and the like is selected and attached. There is a need.
【０００４】[0004]
【考案が解決しようとする課題】従来、ばね等の緩衝装
置は、強い衝撃を受けた場合に互いに密着して弾力性を
失って該衝撃が直接工具に伝わり、該衝撃が大きな振動
となって工具を保持している作業者の手に伝達するが、
この衝撃は工具の破損または作業性を悪くすると共に、
工具の緩衝装置に用いるばねを取付ける構造が複雑にな
って重量が重くなってしまう等の問題点を有している。
本考案は、ピストンの往復動による打撃によって発生す
る衝撃や被加工面に衝突した際の反作用を、ばねを使用
することなく圧縮空気を利用して該衝撃を緩和吸収する
ことを目的とするものである。Conventionally, shock absorbers such as springs, when subjected to a strong shock, come into close contact with each other and lose elasticity, and the shock is directly transmitted to the tool, and the shock becomes a large vibration. To the hand of the worker holding the tool,
This impact not only damages the tool or deteriorates the workability, but also
There is a problem that the structure for mounting the spring used for the shock absorber of the tool becomes complicated and the weight becomes heavy.
The purpose of the present invention is to absorb and absorb the impact generated by the impact of the reciprocating motion of the piston and the reaction when it collides with the work surface by using compressed air without using a spring. It is.
【０００５】[0005]
【課題を解決するための手段】本考案は、ハウジングの
内部にピストンを内蔵したシリンダを摺動自在に設け、
該シリンダには流体圧力を受けて前方へ押圧する第１の
受圧部と、前記ピストンが後方へ押圧されると同時に該
シリンダを前方へ押圧する第４の受圧部とを設け、さら
に、前記シリンダには該シリンダを後方へ押圧する第２
及び第３の受圧部と、前記ピストンが前方へ押圧される
と同時に該シリンダを後方へ押圧する第５の受圧部とを
設けた構成を、上記課題を解決するための手段とする。
さらに、前記シリンダに設けた第１の受圧部と第４の受
圧部との面積の和が、前記第２の受圧部と第３の受圧部
との面積の和よりも大きく且つ該第２及び第３の受圧部
の面積と第５の受圧部との面積の和よりも小さく設定し
たことを特徴とするものである。According to the present invention, a cylinder having a built-in piston is slidably provided in a housing.
The cylinder is provided with a first pressure receiving portion that presses forward by receiving a fluid pressure, and a fourth pressure receiving portion that presses the cylinder forward while the piston is pressed rearward. The second presses the cylinder backward.
A configuration for providing the third pressure-receiving portion and a fifth pressure-receiving portion that presses the cylinder rearward while the piston is pressed forward at the same time as means for solving the above problem.
Further, the sum of the areas of the first pressure receiving section and the fourth pressure receiving section provided in the cylinder is larger than the sum of the areas of the second pressure receiving section and the third pressure receiving section, and It is characterized in that it is set smaller than the sum of the area of the third pressure receiving portion and the area of the fifth pressure receiving portion.
【０００６】[0006]
【作用】ハウジング内にシリンダとピストンを同一軸線
上に前後動可能に収容し、該シリンダの後端面に設けた
第１の受圧部と、シリンダ前部内面に設けた第４の受圧
部との面積の和と、シリンダ外部前面に設けた第３及び
第２の受圧部の面積との和より小さく、また、前記第２
および第３の受圧部の面積の和と、前記シリンダのシリ
ンダ室後端の第５の受圧部の面積との和より大きく設定
して、該シリンダ内に収容したピストンを流体圧力によ
り前進し、他方、ハウジング内に前後動可能に収容した
シリンダの前側及び後側の受圧部と、ピストンの前部及
び後部の受圧部との面積の差を利用し、タガネの後端を
ピストンで叩打した後、反作用により後退する該ピスト
ンと同じように該流体圧力により前後動する該シリンダ
を該ピストンと反対方向への前後動運動を繰り返すこと
により、衝撃力を相殺し振動や衝撃を吸収して衝撃を小
さくする。A cylinder and a piston are accommodated in a housing so as to be movable back and forth on the same axis, and a first pressure receiving portion provided on a rear end surface of the cylinder and a fourth pressure receiving portion provided on a front inner surface of the cylinder. Smaller than the sum of the area and the area of the third and second pressure receiving portions provided on the outer front surface of the cylinder;
And the sum of the area of the third pressure receiving section and the area of the fifth pressure receiving section at the rear end of the cylinder chamber of the cylinder is set to be larger than the piston, and the piston accommodated in the cylinder is advanced by the fluid pressure, On the other hand, using the difference in area between the front and rear pressure receiving parts of the cylinder housed in the housing so as to be able to move back and forth, and using the difference in the area of the front and rear pressure receiving parts of the piston, after striking the rear end of the spring with the piston The cylinder, which moves back and forth by the fluid pressure in the same manner as the piston which retreats by the reaction, repeats the forward and backward movement in the opposite direction to the piston, thereby canceling the impact force and absorbing the vibration and shock to absorb the shock. Make it smaller.
【０００７】[0007]
【実施例】本考案を実施例の図面に基づいて説明する
と、図１において、１は衝撃工具で、バルブ本体２に給
気孔３と排気孔７を別個に設け、該給気孔３に連続して
設けた弁室４内に開閉弁５を装着し、該開閉弁の上部に
設けた弁杆５ａをバルブ本体２の外部に突出させてあ
る。この開閉弁５を操作する開閉レバ−９は、前記バル
ブ本体２の後部にピン１０で枢動可能に軸支され、該給
気孔３の前部にパッキン１１を介して該バルブ本体２と
筒状のハウジング１３とはビス（図示せず）で固定され
ている。１１ａは前記給気孔３に連通するようにパッキ
ン１１に設けた第１開口、１１ｂは前記排気孔７に連通
するようにパッキン１１に設けた第２開口である。DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described with reference to the drawings of the embodiment. In FIG. 1, reference numeral 1 denotes an impact tool, in which a valve body 2 is provided with an air supply hole 3 and an exhaust hole 7 separately, An opening / closing valve 5 is mounted in the valve chamber 4 provided in this manner, and a valve rod 5 a provided above the opening / closing valve is projected outside the valve body 2. An opening / closing lever 9 for operating the opening / closing valve 5 is pivotally supported by a pin 10 at a rear portion of the valve body 2, and is connected to the valve body 2 via a packing 11 at a front portion of the air supply hole 3. The housing 13 is fixed with screws (not shown). 11a is a first opening provided in the packing 11 so as to communicate with the air supply hole 3, and 11b is a second opening provided in the packing 11 so as to communicate with the exhaust hole 7.
【０００８】このハウジング１３は、先端内部に形成し
た支持孔１４の内端に段部１５を設け、該段部１５を介
してハウジング内に大径室１６を形成し、該大径室１６
と略平行に軸線方向に通孔１７を設け、さらに、該通孔
１７の両端部分には該ハウジングの直径方向に第１、２
導通孔１８ａ、１８ｂを夫々形成して前記大径室１６に
連通している。１９は前記ハウジング１３の内部に設け
た大径室１６の後端に固定するガイド部で、このガイド
部１９の中心には軸線方向に大径な案内孔２０を形成
し、後部には直径方向に前記ハウジング１３の第１導通
孔１８ａと連通する第１孔２１を、また、支持部１９の
周縁部分の軸線方向には前記バルブ本体２に設けた排気
孔７に連通する第２孔２２を設けてある。The housing 13 has a step portion 15 at the inner end of a support hole 14 formed at the front end thereof, and a large-diameter chamber 16 is formed in the housing through the step portion 15.
A through hole 17 is provided in the axial direction substantially in parallel with the first through hole.
Conducting holes 18a and 18b are formed respectively and communicate with the large diameter chamber 16. Reference numeral 19 denotes a guide portion fixed to the rear end of the large-diameter chamber 16 provided inside the housing 13. A guide hole 20 having a large diameter is formed in the center of the guide portion 19 in the axial direction. A first hole 21 communicating with the first conduction hole 18 a of the housing 13, and a second hole 22 communicating with the exhaust hole 7 provided in the valve body 2 in the axial direction of the peripheral portion of the support portion 19. It is provided.
【０００９】２４は、前記ハウジング１３の先端に設け
た支持孔１４に前後動可能に軸承させたシリンダで、そ
の先端内部に設けた取付孔２５の内端からやや大径の案
内室２６を設け、該案内室２６の後部には環状段部２７
を介してやや大径なシリンダ室２８を連続して形成して
ある。このシリンダ２４の中間部外周に設けた大径胴部
２９の前側には第１段部３０と第２段部３１とを夫々形
成し、該大径胴部２９の後方に設けた段部３２を介して
小径部３２ａを設け、該大径胴部２９を前記ハウジング
の大径室１６内に前後動可能に収容してある。Reference numeral 24 denotes a cylinder which is rotatably supported in a support hole 14 provided at the front end of the housing 13 so as to be able to move back and forth. An annular step 27 is provided at the rear of the guide chamber 26.
, A cylinder chamber 28 having a slightly larger diameter is formed continuously. A first step portion 30 and a second step portion 31 are formed on the front side of a large-diameter body portion 29 provided on the outer periphery of an intermediate portion of the cylinder 24, and a step portion 32 provided behind the large-diameter body portion 29. The large-diameter body portion 29 is accommodated in the large-diameter chamber 16 of the housing so as to be movable back and forth.
【００１０】この大径胴部２９の前部に設けた第１段部
３０と第２段部３１との間には、直径方向に第１通孔３
４を貫通して設け、また、段部３２のやや後方には第２
通孔３５を直径方向に貫通して設けてある。このシリン
ダ２４の先端側面に設けた収容孔３６内に、ボ−ル等か
らなる掛止部材３７を収容してある。ここで、シリンダ
２４の第１段部３０の前部環状平面を第３の受圧部Ｃと
し、第２段部３１の前部環状平面を第２の受圧部Ｂと
し、さらに、該シリンダ２４の内部前面に設けた環状段
部２７の環状平面を第４の受圧部Ｄと設定してある。A first through hole 3 is diametrically provided between a first step 30 and a second step 31 provided at the front of the large-diameter body 29.
4 and a second portion slightly behind the step portion 32.
A through hole 35 is provided to penetrate in the diameter direction. A retaining member 37 made of a ball or the like is accommodated in an accommodation hole 36 provided on the tip side surface of the cylinder 24. Here, the front annular surface of the first step portion 30 of the cylinder 24 is referred to as a third pressure receiving portion C, the front annular surface of the second step portion 31 is referred to as a second pressure receiving portion B, and An annular flat surface of the annular step portion 27 provided on the inner front surface is set as a fourth pressure receiving portion D.
【００１１】３８は、前方に設けた鍔部３９を連結ピン
４０でシリンダ２４の後端に固着して該シリンダ２４内
に設けたシリンダ室２８の後端を閉鎖した後部体で、該
後部体３８を前記ガイド部１９の案内孔２０内に前後動
可能に軸承させてある。この後部体３８の前部円形面を
第５の受圧部Ｅに設定し、また、前記ガイド部１９の案
内孔２０に前後動可能に軸承させた後部体３８の後端円
形面を第１の受圧部Ａと設定する。なお、このシリンダ
２４の後部に後部体３８を固着させることにより、該シ
リンダ２４の質量を増大させて後記するピストン４２と
該シリンダ２４との質量の調整を図っている。Reference numeral 38 denotes a rear body in which a flange 39 provided at the front is fixed to the rear end of the cylinder 24 with a connecting pin 40 and the rear end of the cylinder chamber 28 provided in the cylinder 24 is closed. 38 is supported in the guide hole 20 of the guide portion 19 so as to be able to move back and forth. The front circular surface of the rear body 38 is set to the fifth pressure receiving portion E, and the rear circular surface of the rear body 38 which is supported in the guide hole 20 of the guide portion 19 so as to be able to move back and forth is the first circular surface. Set as pressure receiving section A. By fixing the rear body 38 to the rear of the cylinder 24, the mass of the cylinder 24 is increased to adjust the mass of the piston 42 and the cylinder 24 described later.
【００１２】４２はピストンで、後部外周面に設けた環
状の係止段部４３を介して胴部４４を形成してあり、該
係止段部４３の前部環状平面を第６の受圧部Ｆと設定し
てある。このピストン４２の略前部には直径方向に設け
た第３孔４５と直交して軸線方向に連通する第４孔４６
を開口し、前記シリンダ２４のシリンダ室２８内に前後
動可能に収容してある。４８はタガネで、該タガネの後
部には軸線方向に設けた長溝４９内に前記シリンダ２４
の先端部側面に設けたテ−パ−状の収容孔３６内に収容
した掛止部材３７を、該タガネ４８の長溝４９に係合さ
せて該タガネが回転しないよう一定範囲内で前後動可能
に支承してある。Reference numeral 42 denotes a piston, which has a body portion 44 formed through an annular locking step 43 provided on the rear outer peripheral surface, and a front annular flat surface of the locking step 43 is connected to a sixth pressure receiving portion. F is set. At a substantially front portion of the piston 42, a fourth hole 46 orthogonal to an axial direction and orthogonal to a third hole 45 provided in the diameter direction.
And is accommodated in the cylinder chamber 28 of the cylinder 24 so as to be movable back and forth. Reference numeral 48 designates a cylinder, and the cylinder 24 is provided in a long groove 49 provided in the axial direction at the rear of the cylinder.
The engaging member 37 accommodated in the tapered accommodating hole 36 provided on the side surface of the distal end portion is engaged with the long groove 49 of the slug 48 so that it can be moved back and forth within a certain range so that the slug does not rotate. It is supported.
【００１３】５０はハウジング１３及びシリンダ２４の
先端に取付けた保持筒で、内面に掛止部材３７が掛止す
る凹状溝５１を設け、この保持筒５０とハウジング１３
との間にコイルバネ５２を円周方向に弾発して取付け、
この保持筒５０を回転させることにより係止部材３７を
凹状溝５１に合致させてタガネ４８を脱着させることが
できる。なお、５３はコンプレッサ−等（図示せず）と
給気孔３とを連結するホ−ス、５４は工具本体２の一端
に装着させた排気ホ−スで、この排気ホ−スを利用して
騒音を防止している。５５はハウジング１３内に設けた
排気路で、前記第２通孔３５と第２孔２２とを連通し、
第２開口１１ｂを介して排気孔７に連通している。な
お、本実施例では駆動源に圧縮空気を用いた例について
説明したが、その他の流体圧力を利用することも可能で
ある。Reference numeral 50 denotes a holding cylinder mounted on the tip of the housing 13 and the cylinder 24. A concave groove 51 for engaging the locking member 37 is provided on the inner surface of the holding cylinder.
The coil spring 52 is resiliently attached in the circumferential direction between the
By rotating the holding cylinder 50, the locking member 37 is aligned with the concave groove 51, and the flap 48 can be detached. Reference numeral 53 denotes a hose for connecting a compressor or the like (not shown) to the air supply hole 3, and reference numeral 54 denotes an exhaust hose attached to one end of the tool main body 2, using this exhaust hose. Prevents noise. Reference numeral 55 denotes an exhaust passage provided in the housing 13, which communicates the second through hole 35 with the second hole 22.
It communicates with the exhaust hole 7 via the second opening 11b. In this embodiment, an example in which compressed air is used as the driving source has been described, but other fluid pressures can be used.
【００１４】ここで、物体を同じ圧力で移動させる場合
に、物体の質量が大きいと速度は遅く、質量が小さいと
速度が早くなることから、シリンダ２４とピストン４２
とを同じ周期で相反する方向に動作させ、ピストンの持
つ運動エネルギ−（数１）とシリンダの持つ運動エネル
ギ−（数２）が（数３）に示すように同じになるときに
制振される。Here, when the object is moved at the same pressure, the speed is slow if the mass of the object is large, and the speed is high if the mass is small.
Are operated in opposite directions at the same cycle, and when the kinetic energy of the piston (Equation 1) and the kinetic energy of the cylinder (Equation 2) become the same as shown in (Equation 3), vibration is suppressed. You.
【００１５】[0015]
【数１】 (Equation 1)
【００１６】[0016]
【数２】 シリンダの持つ運動エネルギー＝１／２ＭｃＶｃ２ （Ｍｃ：シリンダ重量、Ｖｃ：シリンダの速度）## EQU00002 ## Kinetic energy of the cylinder = 1/2 McVc2 (Mc: cylinder weight, Vc: cylinder speed)
【００１７】[0017]
【数３】 (Equation 3)
【００１８】ピストンの持つ運動エネルギ−（数１）と
シリンダの持つ運動エネルギ−（数２）とを（数３）に
示すように等しくさせるには、ピストン４２のストロ−
ク長をＬｐ、シリンダ２４のストロ−ク長をＬｃとした
時に（数４）の関係となり、ｔ（時間）が同じ周期とい
うことにより（数５）となる。In order to make the kinetic energy of the piston (Equation 1) equal to the kinetic energy of the cylinder (Equation 2) as shown in (Equation 3), the stroke of the piston 42 is
When the stroke length is Lp and the stroke length of the cylinder 24 is Lc, the relationship becomes (Equation 4). Since t (time) has the same cycle, it becomes (Equation 5).
【００１９】[0019]
【数４】 (Equation 4)
【００２０】[0020]
【数５】 (Equation 5)
【００２１】よって、ピストン４２及びシリンダ２４の
重量に対するそれぞれのストロ−ク長Ｌｐを、第１〜６
の受圧部Ａ、Ｂ、Ｃ、Ｄ、Ｅ、Ｆで設定したことによ
り、ピストン４２とシリンダ２４のエネルギ−が同じと
なり、制振されるものである。Accordingly, the respective stroke lengths Lp with respect to the weights of the piston 42 and the cylinder 24 are defined as the first to sixth strokes.
By setting the pressure receiving portions A, B, C, D, E, and F, the energy of the piston 42 and the energy of the cylinder 24 become the same, and the vibration is suppressed.
【００２２】次に、本実施例の作用について説明する
と、図２において、開閉レバ−９を操作してハウジング
１３から突出している開閉弁５を押し下げると、給気孔
３の弁室４が開口し、コンプレッサ−（図示せず）から
送気される圧縮空気は、ホ−ス５３を通って給気孔３に
連通したパッキン１１の第１開口１１ａ内に進入し、ガ
イド部１９の案内孔２０に案内される後部体３８の第１
の受圧部Ａに作用してシリンダ２４を前進させる。それ
と同時に、第１孔２１から第１導通孔１８ａへと進入
し、更に、通孔１７から第２導通孔１８ｂを通ってハウ
ジングの大径室１６とピストン２４との間に進入し、シ
リンダ２４の第１通孔３４を通って内部に設けたシリン
ダ室２８に収容したピストン４２の第３孔４５を経て第
４孔４６に流入するが、ピストン４２の後部側は密閉さ
れていて圧縮空気の逃げ部がないためシリンダ室２８内
で該圧縮空気が膨張し、ピストンを図２の矢印Ｘ方向に
動作する力が作用する。Next, the operation of the present embodiment will be described. Referring to FIG. 2, when the on-off lever 9 is operated to push down the on-off valve 5 protruding from the housing 13, the valve chamber 4 of the air supply hole 3 is opened. Compressed air sent from a compressor (not shown) enters the first opening 11 a of the packing 11 communicating with the air supply hole 3 through the hose 53 and enters the guide hole 20 of the guide portion 19. The first of the guided rear body 38
And the cylinder 24 is advanced. At the same time, it enters from the first hole 21 to the first conduction hole 18a, further enters from the through hole 17 through the second conduction hole 18b between the large-diameter chamber 16 of the housing and the piston 24, and Flows into the fourth hole 46 through the third hole 45 of the piston 42 housed in the cylinder chamber 28 provided therein through the first through hole 34, but the rear side of the piston 42 is closed and compressed air is discharged. Since there is no escape portion, the compressed air expands in the cylinder chamber 28, and a force acts on the piston in the direction of arrow X in FIG.
【００２３】このシリンダ２４を図２の矢印Ｘ方向に押
圧する力は、後部体３８の後部円形面の第１の受圧部Ａ
と、シリンダ２４の内部前面の環状段部２７である第４
の受圧部Ｄとの面積の和を、該シリンダ２４の該１段部
３０の前部環状平面である第３の受圧部Ｃおよび第２段
部３１の前部環状平面である第２の受圧部Ｂの面積との
和より大きく設定してあるため、該シリンダ２４が圧縮
空気によって受ける力は、Ａ＋Ｄ＞Ｂ＋Ｃとなり、この
シリンダ２４は図２に示した矢印Ｘ方向に動作する。他
方、ピストン４２の胴部４４の前面の係止段部４３の前
部環状平面である第６の受圧部Ｆに圧縮空気が作用して
いるため、該ピストン４２は次の打撃に備えて後退す
る。The force pressing the cylinder 24 in the direction of arrow X in FIG. 2 is applied to the first pressure receiving portion A on the rear circular surface of the rear body 38.
And a fourth annular step 27 on the inner front surface of the cylinder 24.
The sum of the areas of the pressure receiving portion D and the third pressure receiving portion C, which is the front annular plane of the first step portion 30 of the cylinder 24, and the second pressure receiving portion, which is the front annular plane of the second step portion 31 Since it is set to be larger than the sum of the area of the portion B, the force received by the compressed air by the compressed air is A + D> B + C, and the cylinder 24 operates in the arrow X direction shown in FIG. On the other hand, since the compressed air is acting on the sixth pressure receiving portion F which is the front annular flat surface of the locking step portion 43 on the front surface of the body portion 44 of the piston 42, the piston 42 retreats in preparation for the next impact. I do.
【００２４】図２において、大径室１６とシリンダ２４
との間の環状空間に流入した圧縮空気は、第１通孔３４
から第３孔４５を通ってピストン４２の第４孔４６内に
流入すると、排気路である第２通孔３５がピストン４２
の胴部４４で閉鎖されているため、該圧縮空気が膨張し
てシリンダ室２８の後端に位置した円形面である第５の
受圧部Ｅに力が生じ、該シリンダ２４が圧縮空気によっ
て受ける力は、Ａ＋Ｄ＜Ｂ＋Ｃ＋Ｅとなり、このシリン
ダ２４は第２図の矢印Ｙ方向に移動し、他方、ピストン
４２は図２の矢印Ｘ方向に勢いよく前進して前記タガネ
４８の後端を打撃し、該タガネの先端で研削作業を行う
ものである（図３）。In FIG. 2, the large-diameter chamber 16 and the cylinder 24
The compressed air flowing into the annular space between the first through hole 34
Flows through the third hole 45 into the fourth hole 46 of the piston 42, the second through hole 35, which is an exhaust passage,
, The compressed air expands to generate a force on the fifth pressure receiving portion E, which is a circular surface located at the rear end of the cylinder chamber 28, and the cylinder 24 receives the compressed air. The force is A + D <B + C + E, and the cylinder 24 moves in the direction of arrow Y in FIG. 2, while the piston 42 moves forward in the direction of arrow X in FIG. The grinding operation is performed at the tip of the rag (FIG. 3).
【００２５】図３において、ピストン４２がシリンダ２
４内を前進してタガネ４８の後端を打撃すると、該ピス
トン４２の胴部４４はシリンダ室２８内を前進して第２
通孔３５が開口し、該シリンダ室２８内の膨張した圧縮
空気は、第２通孔３５から排気路５５に入り、さらに、
第２孔２２から第２開口１１ｂに進入し、排気孔７を経
て排気ホ−ス５４を介して排気される。それによって、
シリンダ２４が受ける力は、Ａ＋Ｄ＞Ｂ＋Ｃとなって、
図２に示す矢印Ｘ方向、即ち、前進方向に動作する。ま
た、ピストン４２には常に胴部４４の前部環状平面から
なる第６の受圧部Ｆで圧縮空気の力を受けているので後
方に動作し、第２通孔３５を閉鎖させた後、該シリンダ
室２８内に収容したピストン４２の後部側が密閉されて
圧縮空気が再び膨張し、次の打撃に備える。In FIG. 3, the piston 42 is
4 and strikes the rear end of the chisel 48, the body 44 of the piston 42 advances in the cylinder chamber 28 and
The through hole 35 is opened, and the compressed air expanded in the cylinder chamber 28 enters the exhaust passage 55 from the second through hole 35, and further,
The gas enters the second opening 11b from the second hole 22 and is exhausted through the exhaust hole 54 through the exhaust hole 7. Thereby,
The force received by the cylinder 24 is A + D> B + C,
It operates in the direction of arrow X shown in FIG. 2, that is, in the forward direction. Further, since the piston 42 always receives the force of the compressed air at the sixth pressure receiving portion F formed of the front annular flat surface of the body portion 44, the piston 42 operates rearward, and after closing the second through hole 35, The rear side of the piston 42 housed in the cylinder chamber 28 is sealed, and the compressed air expands again to prepare for the next impact.
【００２６】上記の動作を繰り返すことにより、ピスト
ン４２とシリンダ２４とは同期し、重心が相反する方向
に動作するため、衝撃工具の振動を抑えることができ
る。なお、ピストン４２はタガネ４８の後端を打撃し、
また、相反する方向に動作させるため切換バルブの役目
も果たすものである。By repeating the above operation, the piston 42 and the cylinder 24 are synchronized and operate in the directions where the centers of gravity are opposite to each other, so that the vibration of the impact tool can be suppressed. In addition, the piston 42 hits the rear end of the spring 48,
Further, it also serves as a switching valve for operating in opposite directions.
【００２７】[0027]
【考案の効果】本考案は、衝撃工具の振動を防止するた
めにピストンとシリンダが受ける圧縮空気の圧力によ
り、ピストンとシリンダを同期させて互いの重心が相反
する方向に動作させることによって振動を制御するの
で、工具の作業性が良くなってはつり作業や研削作業の
際の作業員の疲れが少なく、また、衝撃工具の振動を防
止するためのばねを使用しないため機械的故障が少なく
なるほか、構造が簡単で軽量化が図れるという利点を有
するものである。According to the present invention, in order to prevent the vibration of the impact tool, the piston and the cylinder are synchronized by the pressure of the compressed air received by the piston and the cylinder and the centers of gravity of the piston and the cylinder are moved in opposite directions to generate the vibration. By controlling, the workability of the tool is improved, so that the worker is less tired during the lifting and grinding work, and the mechanical failure is reduced because no spring is used to prevent the vibration of the impact tool. The advantage is that the structure is simple and the weight can be reduced.
【図１】本考案に係る衝撃工具のバルブを閉じた状態の
一部破断した断面図である。FIG. 1 is a partially cutaway sectional view of the impact tool according to the present invention with a valve closed.
【図２】本考案に係る衝撃工具のバルブを開いた状態の
一部破断した断面図である。FIG. 2 is a partially broken cross-sectional view of the impact tool according to the present invention with the valve opened.
【図３】本考案に係る衝撃工具のピストンが前進したタ
ガネを打撃した状態の断面図である。FIG. 3 is a cross-sectional view of the impact tool according to the present invention in a state in which the piston hits the forwardly-moving spring;
２ バルブ本体 ５ 開閉弁 １３ ハウジング １４ 支持孔 １９ ガイド部 ２４ シリンダ ３８ 後部体 ４２ ピストン ４８ タガネ Ａ 第１の受圧部 Ｂ 第２の受圧部 Ｃ 第３の受圧部 Ｄ 第４の受圧部 Ｅ 第５の受圧部 Ｆ 第６の受圧部 2 Valve body 5 On-off valve 13 Housing 14 Support hole 19 Guide part 24 Cylinder 38 Rear body 42 Piston 48 Longitudinal A First pressure receiving part B Second pressure receiving part C Third pressure receiving part D Fourth pressure receiving part E Fifth Pressure receiving part F sixth pressure receiving part
Claims (2)
シリンダを摺動自在に設け、該シリンダには流体圧力を
受けて前方へ押圧する第１の受圧部と、前記ピストンが
後方へ押圧されると同時に該シリンダを前方へ押圧する
第４の受圧部とを設け、さらに、前記シリンダには該シ
リンダを後方へ押圧する第２及び第３の受圧部と、前記
ピストンが前方へ押圧されると同時に該シリンダを後方
へ押圧する第５の受圧部とを設けたことを特徴とする衝
撃工具。1. A cylinder having a piston built therein is slidably provided in a housing. The cylinder has a first pressure receiving portion which receives a fluid pressure and presses forward, and when the piston is pressed rearward. At the same time, a fourth pressure receiving portion for pressing the cylinder forward is provided, and the cylinder is further provided with second and third pressure receiving portions for pressing the cylinder rearward, and simultaneously with the piston being pressed forward. An impact tool comprising: a fifth pressure receiving portion that presses the cylinder backward.
４の受圧部との面積の和が、前記第２の受圧部と第３の
受圧部との面積の和よりも大きく且つ該第２及び第３の
受圧部の面積と第５の受圧部との面積の和よりも小さく
設定したことを特徴とする請求項１に記載の衝撃工具。2. The sum of the areas of a first pressure receiving portion and a fourth pressure receiving portion provided in the cylinder is larger than the sum of the areas of the second pressure receiving portion and the third pressure receiving portion, and The impact tool according to claim 1, wherein the impact tool is set to be smaller than the sum of the area of the second and third pressure receiving portions and the area of the fifth pressure receiving portion.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1993052620U JP2587778Y2 (en) | 1993-09-03 | 1993-09-03 | Impact tool |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1993052620U JP2587778Y2 (en) | 1993-09-03 | 1993-09-03 | Impact tool |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0717482U JPH0717482U (en) | 1995-03-28 |
| JP2587778Y2 true JP2587778Y2 (en) | 1998-12-24 |
Family
ID=12919856
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1993052620U Expired - Lifetime JP2587778Y2 (en) | 1993-09-03 | 1993-09-03 | Impact tool |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2587778Y2 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3900379B2 (en) * | 1996-11-12 | 2007-04-04 | 日東工器株式会社 | Pneumatic hammer tool |
| JP2004276185A (en) * | 2003-03-17 | 2004-10-07 | Makita Corp | Design support system of working tool and working tool |
| JP2004330377A (en) * | 2003-05-09 | 2004-11-25 | Makita Corp | Working tool |
| JP6782958B2 (en) * | 2016-06-10 | 2020-11-11 | 不二空機株式会社 | Impact tool |
| JP6737497B2 (en) * | 2016-06-10 | 2020-08-12 | 不二空機株式会社 | Impact tool |
| TWI778908B (en) * | 2022-01-21 | 2022-09-21 | 大里興業股份有限公司 | Pneumatic impact tool with improved damping structure |
-
1993
- 1993-09-03 JP JP1993052620U patent/JP2587778Y2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0717482U (en) | 1995-03-28 |
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