JPH078141Y2 - Hydraulic impact tool - Google Patents
Hydraulic impact toolInfo
- Publication number
- JPH078141Y2 JPH078141Y2 JP5918088U JP5918088U JPH078141Y2 JP H078141 Y2 JPH078141 Y2 JP H078141Y2 JP 5918088 U JP5918088 U JP 5918088U JP 5918088 U JP5918088 U JP 5918088U JP H078141 Y2 JPH078141 Y2 JP H078141Y2
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- oil
- hydraulic
- passage
- oil passage
- 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
【考案の詳細な説明】 ［産業上の利用分野］ 本考案は、例えば、さく岩、建築物の破壊、舗装の打割
等に使用される油圧打撃工具に関し、特に、作動油の供
給量の変動に対する作動圧（以下、IN圧という）の変動
を防止できるようにした油圧打撃工具に関するものであ
る。DETAILED DESCRIPTION OF THE INVENTION [Industrial field of application] The present invention relates to a hydraulic impact tool used, for example, for rock cutting, building destruction, pavement cracking, and the like. The present invention relates to a hydraulic impact tool capable of preventing fluctuations in operating pressure (hereinafter referred to as IN pressure) due to fluctuations.
［従来技術］ 一般に、油圧打撃工具は、第２図に示すように、油圧打
撃工具本体１内に前後動可能に挿着されたピストン部材
２と、油圧打撃工具本体１内に工具本体１とピストン部
材２とで形成された前室３及び後室４に作動油を給排し
て上記ピストン部材２の移動方向を切換える切換バルブ
５と、上記後室４及び前室３の作動油を排出する油路6a
〜6gとを備えており、また、作動油を前室３及び後室４
に迅速にかつ安定良く供給するために圧油供給路７に連
通するアキュムレータ８が設けられている。このアキュ
ムレータ８は内部がブラダ8aによって２室に仕切られ、
一方の室8bには窒素等の不活性ガスを封入し、他方の室
8cが多数の小径孔を介して圧油供給路７に連通されてい
る。[Prior Art] Generally, as shown in FIG. 2, a hydraulic impact tool includes a piston member 2 inserted in a hydraulic impact tool body 1 so as to be movable back and forth, and a tool body 1 in the hydraulic impact tool body 1. A switching valve 5 for supplying / discharging hydraulic oil to / from the front chamber 3 and the rear chamber 4 formed by the piston member 2 to switch the moving direction of the piston member 2 and the hydraulic oil in the rear chamber 4 and the front chamber 3. Oil passage 6a
~ 6g, and the hydraulic oil in the front chamber 3 and the rear chamber 4
An accumulator 8 that communicates with the pressure oil supply passage 7 is provided in order to supply the oil quickly and stably. The inside of this accumulator 8 is divided into two chambers by a bladder 8a,
One chamber 8b is filled with an inert gas such as nitrogen, and the other chamber
8c is communicated with the pressure oil supply passage 7 through a large number of small diameter holes.
一般に、アキュムレータ８を備えた油圧打撃工具におい
ては、例えば起動時等の非定常時に作動油のIN圧が不安
定となり、アキュムレータ８が過度に使用され、特にIN
圧が低い時には不活性ガスの圧力によってブラダ8aがア
キュムレータ８と圧油供給路７との間の小径孔が形成さ
れた壁部に打ちつけられ、極端な場合には破損が生じる
という問題がある。Generally, in a hydraulic impact tool equipped with an accumulator 8, the IN pressure of hydraulic oil becomes unstable during non-steady state such as startup, and the accumulator 8 is excessively used.
When the pressure is low, the bladder 8a is struck by the pressure of the inert gas on the wall portion between the accumulator 8 and the pressure oil supply passage 7 in which a small diameter hole is formed, and in an extreme case, there is a problem in that it is damaged.
そこで、上記排油路のうちの油路6e・6fに摺動自在に装
着され、後端部に上記作動油の油圧（これを、IN圧とい
う）を受ける受圧部9bが形成され且つ受圧部9bに作用す
る油圧力で後退して排油量を増加させる弁部材９と、そ
の弁部材９を前進させて排油量を減少させるプリセット
圧設定手段10Aとを有するものが既に提案されている
（実開昭62-19180号公報参照）。Therefore, a pressure receiving portion 9b, which is slidably attached to the oil passages 6e and 6f of the drainage passage and receives the hydraulic pressure of the hydraulic fluid (this is referred to as IN pressure), is formed at the rear end of the pressure receiving portion. It has already been proposed to have a valve member 9 that is moved backward by the hydraulic pressure acting on 9b to increase the amount of discharged oil, and a preset pressure setting means 10A that moves the valve member 9 forward to decrease the amount of discharged oil. (See Japanese Utility Model Publication No. 62-19180).
上記プリセット圧設定手段10Aはプリセット圧設定バネ1
0aとその後端の位置を調整することによりプリセット圧
を調整する調整ネジ10xとを備えている。The preset pressure setting means 10A is a preset pressure setting spring 1
0a and an adjusting screw 10x for adjusting the preset pressure by adjusting the position of the rear end thereof are provided.
この従来の油圧打撃工具においては、IN圧が低下すれ
ば、プリセット圧設定手段10Aのプリセット圧設定バネ1
0aによって弁部材９が前方に移動され、弁部材９によっ
て油路6eから油路6gに通じる油路断面積が絞られ、後室
４の油圧がある程度以上低下することが防止されるの
で、圧油供給路７の油圧即ちIN圧がある程度以下になる
ことが防止される。その結果、アキュムレータ８のブラ
ダ8aがアキュムレータ８と圧油供給路７との間の小径孔
が形成された壁部に打ちつけられる頻度が減少し、ま
た、その打撃が弱くなり、ブラダ8aの耐久性が高められ
る。In this conventional hydraulic impact tool, if the IN pressure decreases, the preset pressure setting spring 1 of the preset pressure setting means 10A
The valve member 9 is moved forward by 0a, the cross-sectional area of the oil passage communicating from the oil passage 6e to the oil passage 6g is reduced by the valve member 9, and the hydraulic pressure in the rear chamber 4 is prevented from decreasing more than a certain degree. The oil pressure of the oil supply passage 7, that is, the IN pressure is prevented from falling below a certain level. As a result, the frequency with which the bladder 8a of the accumulator 8 is struck on the wall portion where the small diameter hole is formed between the accumulator 8 and the pressure oil supply passage 7 is reduced, and the impact is weakened, and the durability of the bladder 8a is reduced. Is increased.
［考案が解決しようとする課題］ しかしながら、上記の従来の油圧打撃工具によれば、プ
リセット圧調整ネジ10xは製造時にプリセット圧を調整
した後に固定されること、及び弁部材９は受圧面9bに作
用するIN圧の油圧力とバネ10xのバネ力との均衡により
その位置が決定されることから、例えば油圧打撃工具が
ある建設機械から他の建設機械に付換えられ、新しい建
設機械の油圧ポンプの容量あるいは吐出量が前の建設機
械のそれよりも大きくなると、弁部材９はIN圧が変動し
ない限り同一の位置を保持するので油路6aと油路6f・6g
間の絞り通路の面積が同一に維持されることから、油路
6eの油圧が前の建設機械の時よりも上昇し、IN圧もこれ
に伴って昇圧する。その結果、バネ10aが圧縮され、弁
部材９が変位して絞り通路断面積が広げられ、油路6eの
油圧は減圧するが前の建設機械の時の油路6eの油圧まで
は減圧されないのでIN圧が高くなって打撃力が必要以上
に強くなるという問題がある。[Problems to be Solved by the Invention] However, according to the above-described conventional hydraulic impact tool, the preset pressure adjusting screw 10x is fixed after the preset pressure is adjusted during manufacturing, and the valve member 9 is fixed to the pressure receiving surface 9b. Since the position is determined by the balance between the hydraulic pressure of the acting IN pressure and the spring force of the spring 10x, for example, a hydraulic impact tool is transferred from one construction machine to another construction machine, and a hydraulic pump of a new construction machine is used. When the capacity or discharge amount of the oil is larger than that of the previous construction machine, the valve member 9 holds the same position unless the IN pressure fluctuates. Therefore, the oil passages 6a and 6f and 6g
Since the area of the throttle passage between the
The hydraulic pressure of 6e rises more than that of the previous construction machine, and the IN pressure also rises accordingly. As a result, the spring 10a is compressed, the valve member 9 is displaced, the cross-sectional area of the throttle passage is expanded, and the hydraulic pressure of the oil passage 6e is reduced, but it is not reduced to the hydraulic pressure of the oil passage 6e at the time of the previous construction machine. There is a problem that the IN pressure becomes higher and the striking force becomes stronger than necessary.
この問題点を解決するためには、油圧源のポンプ容量に
対応してプリセット圧調整ネジ10xを再調整すればよい
のであるが、実際にはユーザがこのような調整作業を行
うことは困難である。In order to solve this problem, the preset pressure adjustment screw 10x should be readjusted according to the pump capacity of the hydraulic power source, but in reality it is difficult for the user to perform such adjustment work. is there.
本考案は、作動油の供給量の変動に対するIN圧の変動を
防止できるようにした油圧打撃工具を提供することを目
的とするものである。An object of the present invention is to provide a hydraulic impact tool capable of preventing fluctuation of IN pressure with respect to fluctuation of supply amount of hydraulic oil.
本考案に係る油圧打撃工具は、油圧打撃工具本体内に前
後動可能に挿着されたピストン部材と、上記油圧打撃工
具本体とピストン部材とで形成された前室または後室に
作動油を給排してピストン部材の移動方向を切換える切
換バルブと、上記前室または上記後室の作動油を排出す
る排油路と、その排油路に摺動自在に装着され、後端部
に上記作動油の油圧を受ける受圧部が形成されており、
受圧部へ作用する油圧力で後退して排油量を増加させる
弁部材と、その弁部材を前進させて排油量を減少させる
プリセット圧設定手段とを有する油圧打撃工具におい
て、上記プリセット圧設定手段が、上記弁部材を前方に
付勢するプリセット圧設定バネと、このプリセット圧設
定バネの後端を受け止める前後動可能に設けられたプラ
ンジャと、このプランジャによって前端が仕切られたプ
リセット圧調整用受圧室と、この受圧室に上記作動油を
供給してプリセット圧を高くする第１油路と、第１油路
に介装され上記作動油の油圧を所定の設定圧に設定する
圧力調整弁と、上記受圧室に上記作動油を供給してプリ
セット圧を圧力調整弁の設定圧より高くする第２油路
と、この第２油路に介装され排油路の油圧が所定の排油
圧よりも低い時に第２油路を開通させる第１遮断弁と、
上記受圧室に供給された作動油を排出してプリセット圧
を低くする第３油路と、この第３油路に介装され排油路
の油圧が所定の排油圧よりも高い時に上記第３油路を開
通する第２遮断弁と、上記第１油路の圧力調整弁より下
流側部分に介装され上記受圧室の内圧が所定値よりも低
い時に第１油路を遮断する第３遮断弁とを備えたもので
ある。A hydraulic striking tool according to the present invention supplies a hydraulic fluid to a piston member which is inserted into a hydraulic striking tool body so as to be movable back and forth and a front chamber or a rear chamber formed by the hydraulic striking tool body and the piston member. A switching valve for discharging and switching the moving direction of the piston member, an oil discharge passage for discharging the operating oil in the front chamber or the rear chamber, and a slidable mount on the oil discharge passage, and the operation end at the rear end. The pressure receiving part that receives the oil pressure of oil is formed,
In the hydraulic impact tool having a valve member that retreats by the hydraulic pressure acting on the pressure receiving portion to increase the amount of drained oil, and a preset pressure setting means that advances the valve member to reduce the amount of drained oil, the preset pressure setting Means for presetting the preset pressure setting spring for urging the valve member forward, a plunger provided so as to be movable back and forth for receiving a rear end of the preset pressure setting spring, and a preset pressure adjusting partitioning the front end by the plunger. A pressure receiving chamber, a first oil passage for supplying the working oil to the pressure receiving chamber to increase the preset pressure, and a pressure adjusting valve interposed in the first oil passage for setting the hydraulic pressure of the working oil to a predetermined set pressure. And a second oil passage for supplying the working oil to the pressure receiving chamber to make the preset pressure higher than the set pressure of the pressure adjusting valve, and the oil pressure of the drain oil passage interposed in the second oil passage is a predetermined drain oil pressure. Second when lower than A first shut-off valve to open the road,
The third oil passage for discharging the hydraulic oil supplied to the pressure receiving chamber to lower the preset pressure, and the third oil passage interposed in the third oil passage when the oil pressure in the drain oil passage is higher than a predetermined exhaust oil pressure. A second shut-off valve that opens the oil passage, and a third shut-off valve that is interposed in a portion of the first oil passage downstream of the pressure adjusting valve and shuts off the first oil passage when the internal pressure of the pressure receiving chamber is lower than a predetermined value. It is equipped with a valve.
［作用］ 本考案の油圧打撃工具においては、油圧打撃工具を接続
する図示しない油圧ポンプの吐出量が多くなる方に変化
する場合には、排油路の排油圧が規定値よりも高くな
り、第３油路に介装された第２遮断弁が開弁される。こ
れにより上記受圧室内の圧油の一部分が第３油路を介し
て排油路に排出されて上記受圧室の内圧が低くなり、ま
た第１油路の第３遮断弁が遮断される結果、プリセット
圧が減圧されて弁部材が排油量増大側へ移動して排油圧
が規定値に下げられる。このようにして、排油圧が規定
値に減圧されることにより作動油の油圧が所定圧以上に
上昇しなくなる。[Operation] In the hydraulic impact tool of the present invention, when the discharge amount of the hydraulic pump (not shown) connecting the hydraulic impact tool changes to increase, the exhaust hydraulic pressure of the oil discharge passage becomes higher than the specified value, The second cutoff valve interposed in the third oil passage is opened. As a result, a part of the pressure oil in the pressure receiving chamber is discharged to the oil discharge passage through the third oil passage, the internal pressure of the pressure receiving chamber becomes low, and the third cutoff valve in the first oil passage is shut off. The preset pressure is reduced, the valve member moves to the side of increasing the amount of drained oil, and the drain oil pressure is reduced to a specified value. In this way, the exhaust oil pressure is reduced to the specified value, so that the oil pressure of the hydraulic oil does not rise above the predetermined pressure.
また、油圧ポンプの吐出量が少なくなる方に変動する場
合には、排油圧が規定値よりも低くなり、第２油路に介
装された第１遮断弁が開弁され、プリセット圧調整用受
圧室10cのプリセット圧が圧縮調整弁の設定圧よりも高
くなり、プリセット圧が昇圧して弁部材が排油量減少側
に移動する結果、排油圧が規定値に上げられる。このよ
うに、排油圧が規定値に昇圧されることによりIN圧が所
定圧以下に低下しなくなる。Further, when the discharge amount of the hydraulic pump fluctuates toward the smaller side, the exhaust hydraulic pressure becomes lower than the specified value, the first cutoff valve interposed in the second oil passage is opened, and the preset pressure adjustment The preset pressure in the pressure receiving chamber 10c becomes higher than the set pressure of the compression regulating valve, the preset pressure is increased, and the valve member moves to the drain oil amount reduction side, so that the drain oil pressure is raised to the specified value. Thus, the exhaust pressure is increased to the specified value, and the IN pressure does not drop below the predetermined pressure.
［考案の効果］ 本考案の油圧打撃工具によれば、以上説明したように、
油圧打撃工具へ供給される作動油の流量の増大または減
少に対応してプリセット圧を減少させまたは増大させ、
弁部材によって排油絞り通路の流路断面積を拡大または
縮小させて排油圧を規定値に補正することにより、油圧
打撃工具へ供給される作動油の流量の変動に対するIN圧
の変動を防止することができる。[Effect of the Invention] According to the hydraulic impact tool of the present invention, as described above,
The preset pressure is decreased or increased in response to an increase or decrease in the flow rate of hydraulic oil supplied to the hydraulic impact tool,
The valve member enlarges or reduces the flow passage cross-sectional area of the drainage throttle passage to correct the exhaust oil pressure to a specified value, thereby preventing fluctuations in the IN pressure with respect to fluctuations in the flow rate of hydraulic oil supplied to the hydraulic impact tool. be able to.
［実施例］ 以下、本考案の実施例を図面に基いて説明する。[Embodiment] An embodiment of the present invention will be described below with reference to the drawings.
第１図は本考案の実施例に係る土木工事用の油圧打撃装
置の構成の要部を示す構成図であるが、第２図に示す従
来装置と同一の構成部材は同一の符合を付してある。FIG. 1 is a configuration diagram showing a main part of a configuration of a hydraulic hammering device for civil engineering work according to an embodiment of the present invention. The same components as those of the conventional device shown in FIG. 2 have the same reference numerals. There is.
この 油圧打撃工具は、例えば図示しないバックホー、
ユンポ等の建設機械のアームの先端に支持され、その建
設機械の油圧ポンプから圧油の供給を受け、排油をその
建設機械の作動油タンクに戻すように構成されている。This hydraulic impact tool is, for example, a backhoe, not shown.
It is configured to be supported at the tip of an arm of a construction machine such as Yumpo, receive pressure oil from a hydraulic pump of the construction machine, and return waste oil to a hydraulic oil tank of the construction machine.
この油圧打撃装置は、油圧打撃工具本体１内に前後動可
能に挿着されたピストン部材２と、上記油圧打撃工具本
体１と上記ピストン部材２との間に形成された前室３及
び後室４に作動油を給排して上記ピストン部材２の移動
方向を切換える切換バルブ５と、前室３と後室４とから
作動油を排出する排油路６と、前室３と後室４とに油圧
供給源からの作動油を供給する圧油供給路７と、アッキ
ュムレータ８と、圧油供給路７の作動油の油圧（以下、
IN圧という）と後室４から排出される圧油の排油圧P
a（第１図の油路6d・6eの油圧のことである。）とに応
動作動し油路6d・6eから油路6fへの圧油流量を調節する
弁部材９と、上記弁部材９を介して排油圧Paを設定する
為のプリセット圧設定機構10とを備えている。This hydraulic striking device includes a piston member 2 inserted into a hydraulic striking tool body 1 so as to be movable back and forth, and a front chamber 3 and a rear chamber formed between the hydraulic striking tool body 1 and the piston member 2. 4, a switching valve 5 for supplying and discharging hydraulic oil to switch the moving direction of the piston member 2, an oil discharge passage 6 for discharging hydraulic oil from the front chamber 3 and the rear chamber 4, the front chamber 3 and the rear chamber 4 And a hydraulic oil supply passage 7 for supplying hydraulic oil from a hydraulic pressure supply source, an accumulator 8, and a hydraulic pressure of the hydraulic oil in the pressure oil supply passage 7 (hereinafter, referred to as
(Referred to as IN pressure) and the hydraulic oil pressure P of the hydraulic oil discharged from the rear chamber 4.
a (a hydraulic pressure of the oil passages 6d and 6e in FIG. 1) and a valve member 9 that adjusts the flow rate of pressure oil from the oil passages 6d and 6e to the oil passage 6f. And a preset pressure setting mechanism 10 for setting the exhaust oil pressure P a via.
上記油圧打撃工具本体１は内部にピストン部材２を収納
するためにシリンダ室1aを有しており、このシリンダ室
1aのピストン部材２の第１ピストン部材2aの外周側に前
室３が、第２ピストン部2bの外周側に後室４が構成され
る。The hydraulic impact tool body 1 has a cylinder chamber 1a for accommodating the piston member 2 therein.
A front chamber 3 is formed on the outer peripheral side of the first piston member 2a of the piston member 2 of 1a, and a rear chamber 4 is formed on the outer peripheral side of the second piston portion 2b.
上記前室３の中間部には第１ピストン部2aで開閉される
パイロット弁孔3cを有し、前室３のパイロット弁孔3cよ
りも前方部分3aは常時圧油供給路７に連通されている。
前室３のパイロット弁孔3cよりも後方部分3bは、切換バ
ルブ５のパイロット受圧室5cに油路5jで連通されピスト
ン部材２が所定の位置よりも後退した時に第１ピストン
部2aによって前方部分3aから遮断され、さらに、これよ
りもピストン部材２が後退したときに排油路６の一部分
をなす油路6aに連通される。A pilot valve hole 3c that is opened and closed by the first piston portion 2a is provided in the middle portion of the front chamber 3, and a portion 3a in front of the pilot valve hole 3c of the front chamber 3 is always communicated with the pressure oil supply passage 7. There is.
A portion 3b of the front chamber 3 which is behind the pilot valve hole 3c is communicated with the pilot pressure receiving chamber 5c of the switching valve 5 by an oil passage 5j, and when the piston member 2 is retracted from a predetermined position, the front portion is formed by the first piston portion 2a. When the piston member 2 is retracted further than this, it is communicated with an oil passage 6a forming a part of the oil discharge passage 6.
上記切換バルブ５について説明すると、上記第１ピスト
ン部2aとパイロット弁孔3cと前室３（3a、3b）とは切換
バルブ５の一部をなすが、上記切換バルブ５は工具本体
１のシリンダ孔に摺動自在に装着されたスリーブ弁部材
5bとこのスリーブ弁部材5bに前半部分が摺動自在に内嵌
され後半部分が工具本体１に嵌合された固定部材20とで
構成され、スリーブ弁部材5bで供給ポート7aと油路室5a
間が開閉されるとともに油路室5aと油路6d間が開閉され
る。Explaining the switching valve 5, the first piston portion 2a, the pilot valve hole 3c, and the front chamber 3 (3a, 3b) form a part of the switching valve 5, but the switching valve 5 is a cylinder of the tool body 1. Sleeve valve member slidably mounted in the hole
5b and a fixed member 20 in which the first half portion is slidably fitted in the sleeve valve member 5b and the latter half portion is fitted in the tool main body 1. The sleeve valve member 5b includes a supply port 7a and an oil passage chamber 5a.
The space is opened and closed, and the space between the oil passage chamber 5a and the oil passage 6d is opened and closed.
上記スリーブ弁部材5bの前端部には圧油供給ポート7aの
圧力を受ける第１受圧面5dが形成され、後端部にはパイ
ロット受圧室5dが形成され、後端部にはパイロット受圧
室5cの内圧を受ける第２受圧面5eが形成されている。ま
た、その前端部の外周部の第１受圧面5dより前方部分に
は供給ポート7aと後室４に油路4aで接続された油路室5a
間を開閉する弁面5fが形成され、スリーブ弁部材5bの前
端近傍部内周の弁面5gと固定部材20の前端部の弁体部20
aとで油路室5aと油路6d間が開閉されるが、スリーブ弁
部材5bが後方へ移動して供給ポート7aと油路室5a間を開
いたときに油路室5aと油路6d間が閉じられ、また弁体5b
が前方へ移動して供給ポート7aと油路室5a間が閉じられ
たときに油路室5aと油路6d間は弁体部20aの外周側の絞
り通路6cを介して連通される。A first pressure receiving surface 5d that receives the pressure of the pressure oil supply port 7a is formed at the front end of the sleeve valve member 5b, a pilot pressure receiving chamber 5d is formed at the rear end, and a pilot pressure receiving chamber 5c is formed at the rear end. Is formed with a second pressure receiving surface 5e that receives the internal pressure of. Further, an oil passage chamber 5a connected to the supply port 7a and the rear chamber 4 by an oil passage 4a is provided in front of the first pressure receiving surface 5d at the outer peripheral portion of the front end portion thereof.
A valve surface 5f that opens and closes the space is formed, and the valve surface 5g at the inner periphery of the sleeve valve member 5b near the front end and the valve body portion 20 at the front end of the fixed member 20 are formed.
The oil passage chamber 5a and the oil passage 6d are opened and closed by a and the oil passage chamber 5a and the oil passage 6d are opened when the sleeve valve member 5b is moved rearward to open between the supply port 7a and the oil passage chamber 5a. The space is closed, and the valve body 5b
Moves forward and when the supply port 7a and the oil passage chamber 5a are closed, the oil passage chamber 5a and the oil passage 6d communicate with each other through the throttle passage 6c on the outer peripheral side of the valve body portion 20a.
上記排油路６について説明すると、前室３の圧油を抜く
為のポート3dは油路6aで集合排油路6gに接続され、後室
４は油路4aで油路室5aに接続され、油路室5aは絞り通路
6cを介して固定部材20の内部の油路6dに断続的に接続さ
れる。そして、油路6dは固定部材20を直交状に貫いた油
路と固定部材20の中心部に形成された油路とからなり、
油路6dの下流側にはこれよりも大径の油路6e及びこの油
路6eよりも大径で集合排油路6gに連なる油路6fが順に形
成され、前記弁部材９の前半部分は集合排油路6gを横断
して後方へ延び油路6fを挿通して油路6eに油密摺動自在
に嵌合されている。Explaining the oil discharge passage 6 described above, the port 3d for removing pressure oil in the front chamber 3 is connected to the collective oil discharge passage 6g by the oil passage 6a, and the rear chamber 4 is connected to the oil passage chamber 5a by the oil passage 4a. , The oil passage chamber 5a is a throttle passage
It is intermittently connected to the oil passage 6d inside the fixing member 20 via 6c. The oil passage 6d is composed of an oil passage that penetrates the fixing member 20 in an orthogonal manner and an oil passage formed in the central portion of the fixing member 20,
On the downstream side of the oil passage 6d, an oil passage 6e having a larger diameter than this and an oil passage 6f having a larger diameter than this oil passage 6e and connected to the collecting oil discharge passage 6g are formed in order, and the first half portion of the valve member 9 is It extends rearward across the collective oil discharge passage 6g and is inserted into the oil passage 6f to be fitted in the oil passage 6e so as to be slidable in an oil-tight manner.
上記弁部材９について説明すると、その前半部は筒状に
形成されてその前端には油路6eの油圧を受ける受圧部9a
が形成され、またその後半部は固定部材20に形成された
シリンダ孔に収容されて、弁部材９の後端のピストン部
9fの前側には環状油室21が形成され、この環状油室21は
油路7aで圧油供給路７に接続され、ピストン部9fの前端
部にはIN圧を受ける受圧部9bが形成されている。弁部材
９の前端部には油路6d・6eを連通する油路9cが形成さ
れ、この油路9cの周壁に油路9cと集合排油路6gとを油路
6fを介して連通させる小径の連通孔9dが周方向及び軸心
方向に規則的に並べて形成してある。Explaining the valve member 9, the front half of the valve member 9 is formed in a tubular shape, and the front end of the valve member 9a receives the hydraulic pressure of the oil passage 6e.
Is formed, and the latter half is housed in a cylinder hole formed in the fixed member 20, and the piston portion at the rear end of the valve member 9 is formed.
An annular oil chamber 21 is formed on the front side of 9f, the annular oil chamber 21 is connected to the pressure oil supply passage 7 by an oil passage 7a, and a pressure receiving portion 9b for receiving IN pressure is formed at the front end portion of the piston portion 9f. ing. An oil passage 9c that connects the oil passages 6d and 6e is formed at the front end of the valve member 9, and the oil passage 9c and the collecting oil discharge passage 6g are connected to the oil passage 9c on the peripheral wall of the oil passage 9c.
Small-diameter communication holes 9d communicating with each other via 6f are formed so as to be regularly arranged in the circumferential direction and the axial direction.
上記弁部材９の後半部は前半部よりも大径で、その後半
部内には後端に開口するバネ収容部9gが形成され、バネ
収容部9gは連通孔9eにより油路9cに連通されている。こ
れにより、弁部材９の後端面にも排油圧Paが作用するこ
とから、弁部材９には弁部材９の前端面に作用する排油
圧Paと弁部材９の後端面に作用する排油圧Paと受圧部9b
に作用するIN圧とが作用する。そして、弁部材９の前端
面と後端面との面積差は比較的小さく且つ排油圧PaはIN
圧に比較して小さいことから、弁部材９に作用する油圧
力は受圧面9bに作用するIN圧の油圧力が支配的になる。The latter half portion of the valve member 9 has a larger diameter than the front half portion, and a spring accommodating portion 9g that opens to the rear end is formed in the latter half portion, and the spring accommodating portion 9g is communicated with the oil passage 9c through the communication hole 9e. There is. Exhaust Thus, since the acting discharge pressure P a is also the rear end surface of the valve member 9, the valve member 9 which acts on the rear end surface of the exhaust pressure P a and the valve member 9 which acts on the front end face of the valve member 9 Hydraulic pressure P a and pressure receiving part 9 b
IN pressure that acts on acts. The area difference between the front end face and the rear end face of the valve member 9 is relatively small, and the exhaust oil pressure P a is IN
Since it is smaller than the pressure, the oil pressure acting on the valve member 9 is dominated by the oil pressure of the IN pressure acting on the pressure receiving surface 9b.
従って、上記弁部材９は基本的に受圧部9bに作用するIN
圧の油圧力とプリセット圧設定機構10のプリセット圧設
定バネ10aの弾性力との均衡によってその位置が定ま
り、IN圧が上昇すると弁部材９が後方移動して連通孔9d
からなる絞り通路の面積が拡大し、これにより排油圧Pa
が低下してIN圧を低下させる一方、IN圧が低下すると弁
部材９が前方移動して絞り通路の面積を縮小してIN圧を
増加させるようになっている。Therefore, the valve member 9 basically acts on the pressure receiving portion 9b IN
The position is determined by the balance between the hydraulic pressure of the pressure and the elastic force of the preset pressure setting spring 10a of the preset pressure setting mechanism 10, and when the IN pressure rises, the valve member 9 moves backward and the communication hole 9d.
Expanding the area of the throttle passage consisting, thereby discharging the hydraulic pressure P a
When the IN pressure decreases, the valve member 9 moves forward to reduce the area of the throttle passage to increase the IN pressure.
ここで、圧油供給路７から供給される圧油の流量が増加
したときにもIN圧の上昇が生じないように、次のような
プリセット圧設定機構10が採用されている。Here, the following preset pressure setting mechanism 10 is employed so that the IN pressure does not rise even when the flow rate of the pressure oil supplied from the pressure oil supply passage 7 increases.
即ち、上記プリセット圧設定機構10は、上記弁部材９を
前方に付勢するプリセット圧設定バネ10aと、工具本体
１のシリンダ孔に装着されプリセット圧設定バネ10aの
後端を受け止めるプランジャ10bと、このプランジャに
よって前端が区画されているプリセット圧調整用受圧室
10cと、この受圧室10cに接続された第１油路11、第２油
路13及び第３油路15とを備えている。That is, the preset pressure setting mechanism 10 includes a preset pressure setting spring 10a for urging the valve member 9 forward, and a plunger 10b mounted in a cylinder hole of the tool body 1 for receiving the rear end of the preset pressure setting spring 10a. Preset pressure adjusting pressure receiving chamber whose front end is divided by this plunger
10c and the 1st oil passage 11, the 2nd oil passage 13, and the 3rd oil passage 15 which were connected to this pressure receiving room 10c are provided.
上記第１油路11は、上記受圧室10cを圧油供給路７の切
換バルブ５より上流側部分に接続するもので、上記受圧
室10cの内圧が所定値よりも高い時にこの第１油路11に
介装された第３遮断弁17が開弁され、第１油路11の第３
遮断弁17より上流部分に介装された圧力調整弁12によっ
て設定圧に調整された作動油が上記受圧室10cに供給さ
れて受圧室10cのプリセット圧が設定されるようになっ
ている。The first oil passage 11 connects the pressure receiving chamber 10c to a portion of the pressure oil supply passage 7 upstream of the switching valve 5, and when the internal pressure of the pressure receiving chamber 10c is higher than a predetermined value, the first oil passage 11 is connected. The third shut-off valve 17 installed in the valve 11 is opened, and the third cutoff valve 17 of the first oil passage 11 is opened.
The hydraulic oil adjusted to the set pressure by the pressure adjusting valve 12 provided upstream of the shutoff valve 17 is supplied to the pressure receiving chamber 10c to set the preset pressure of the pressure receiving chamber 10c.
上記第２油路13は、上記受圧室10cと圧油供給路７の切
換バルブ５より上流側部分との間に第１油路11と並列に
接続され、上記油路室5aの油圧が所定圧よりも低い時に
この第２油路13に介装された第１遮断弁14が開弁されて
上記受圧室10cに作動油が供給され、プリセット圧が上
記圧力調整弁12の設定圧より高められるようになってい
る。The second oil passage 13 is connected in parallel with the first oil passage 11 between the pressure receiving chamber 10c and a portion of the pressure oil supply passage 7 upstream of the switching valve 5, so that the oil pressure in the oil passage chamber 5a is predetermined. When the pressure is lower than the pressure, the first cutoff valve 14 interposed in the second oil passage 13 is opened to supply the working oil to the pressure receiving chamber 10c, and the preset pressure is higher than the set pressure of the pressure adjusting valve 12. It is designed to be used.
上記第３油路15は、上記受圧室10cと集合排油路6gとの
間に接続され、油路室5aの油圧が所定値よりも高い時に
この第３油路15に介装された第２遮断弁16が開弁されて
上記受圧室10cに供給された作動油が集合排油路6gに排
出され、プリセット圧を低下させるようになっている。The third oil passage 15 is connected between the pressure receiving chamber 10c and the collecting oil discharge passage 6g, and is inserted in the third oil passage 15 when the oil pressure in the oil passage chamber 5a is higher than a predetermined value. The 2 cutoff valve 16 is opened, and the hydraulic oil supplied to the pressure receiving chamber 10c is discharged to the collecting oil discharge passage 6g to lower the preset pressure.
上記第１油路11の第３遮断弁17よりも下流側には第１遮
断弁14の開弁時に作動油が第１油路11の方へ逆流するの
を防止する逆止弁19が介装されている。A check valve 19 is provided downstream of the third cutoff valve 17 in the first oil passage 11 to prevent the hydraulic oil from flowing back toward the first oil passage 11 when the first cutoff valve 14 is opened. It is equipped.
以上のように構成された油圧打撃装置においては、スリ
ーブ弁部材5bが後方移動して、油路室5a・油路5bを介し
て後室４〜作動油を供給し、ピストン部材２の前方移動
によりパイロット受圧室5cの油圧が上昇して再びスリー
ブ弁部材5bが前方移動して供給ポート7aと油路室5a間を
閉じるとともに油路室5aと油路6d間を連通させ、これを
繰り返してピストン部材２が前後に往復駆動される。In the hydraulic striking device configured as described above, the sleeve valve member 5b moves rearward, supplies the working oil to the rear chamber 4 through the oil passage chamber 5a and the oil passage 5b, and moves the piston member 2 forward. Due to this, the oil pressure in the pilot pressure receiving chamber 5c rises and the sleeve valve member 5b again moves forward, closing the supply port 7a and the oil passage chamber 5a and communicating between the oil passage chamber 5a and the oil passage 6d, and this is repeated. The piston member 2 is driven back and forth.
ところで、建設機械から供給される油圧及び油量が規定
値の場合には、第１油路11の第３遮断弁17を開弁させて
上記受圧室10cに圧力調整弁12によって圧力調整された
作動油が供給され、従来の油圧打撃工具と同じように作
動することになる。By the way, when the hydraulic pressure and the amount of oil supplied from the construction machine are specified values, the third cutoff valve 17 of the first oil passage 11 is opened and the pressure is adjusted in the pressure receiving chamber 10c by the pressure adjusting valve 12. The hydraulic oil is supplied and operates in the same manner as a conventional hydraulic impact tool.
そして、例えば、吐出量が規定値よりも多い油圧ポンプ
を有する建設機械にこの油圧打撃装置を付け換えた場合
のように、圧油供給路７に供給される作動油の流量が規
定値より多くなる場合には、排油圧Paの上昇に応じて油
路室5aの油圧が所定値よりも高くなり、第３油路15の第
２遮断弁16が開弁される。これにより上記受圧室10c内
の圧油の一部分を第３油路15を介して集合排油路6gに排
出されて上記受圧室10cの油圧が下がる一方、第３遮断
弁17が閉弁される。こうして、プリセット圧の減圧に応
じてプランジャ10bが後退して、弁部材９が受圧部9bに
作用するIN圧の油圧力とバネ10aのバネ力とがバランス
するまで後方に移動し、油路6eと集合排油路6gとを接続
する絞り通路面積が拡大されて排油圧Paが低下し、油路
室5aの油圧が所定値に下げられてIN圧の変動が防止され
る。Then, for example, as in the case of replacing the hydraulic impact device with a construction machine having a hydraulic pump whose discharge amount is larger than the specified value, the flow rate of the hydraulic oil supplied to the pressure oil supply passage 7 is larger than the specified value. If made, the oil pressure in the oil passage chamber 5a becomes higher than the predetermined value in accordance with the increase in the exhaust pressure P a, the second shut-off valve 16 of the third oil passage 15 is opened. As a result, a part of the pressure oil in the pressure receiving chamber 10c is discharged to the collecting oil discharge passage 6g through the third oil passage 15 to lower the hydraulic pressure in the pressure receiving chamber 10c, while the third shutoff valve 17 is closed. . In this way, the plunger 10b retracts according to the reduction of the preset pressure, and the valve member 9 moves rearward until the oil pressure of the IN pressure acting on the pressure receiving portion 9b and the spring force of the spring 10a are balanced, and the oil passage 6e. set oil discharge passage 6g been throttle passage area is enlarged to connect the the discharge pressure P a decreased to, oil pressure in the oil passage chamber 5a fluctuations in lowered with iN pressure to a predetermined value is prevented.
これに対して、例えば、吐出量が規定値よりも少ない油
圧ポンプを有する建設機械にこの油圧打撃装置を付け換
えた場合のように、圧油供給路７に供給される作動油の
流量が規定値より少なくなる場合には、排油圧Paの低下
に応じて油路室5aの油圧が所定値よりも低くなり、第２
油路13に介装された第１遮断弁14が開弁され、上記受圧
室10cの油圧が圧力調整弁12の設定圧よりも高くなり、
プリセット圧が昇圧して弁部材９が前方へ移動し、絞り
通路の面積が縮小されて排油圧Paが上昇し、油路室5aの
油圧が所定値に上げられてIN圧の変動が防止される。On the other hand, for example, the flow rate of the hydraulic oil supplied to the pressure oil supply passage 7 is regulated as in the case where the hydraulic striking device is replaced with a construction machine having a hydraulic pump whose discharge amount is smaller than a prescribed value. When it becomes smaller than the value, the oil pressure in the oil passage chamber 5a becomes lower than the predetermined value in accordance with the decrease in the exhaust oil pressure P a , and the second
The first cutoff valve 14 interposed in the oil passage 13 is opened, the hydraulic pressure in the pressure receiving chamber 10c becomes higher than the set pressure of the pressure adjusting valve 12,
The preset pressure rises, the valve member 9 moves forward, the area of the throttle passage is reduced, the discharge hydraulic pressure P a rises, the hydraulic pressure of the oil passage chamber 5a is raised to a predetermined value, and the fluctuation of the IN pressure is prevented. To be done.
第１図は本考案の一実施例に係る油圧打撃装置の構成の
要部を示す構成図、第２図は従来例に係る油圧打撃装置
の構成の要部を示す構成図である。 １……油圧打撃工具本体、２……ピストン部材、３……
前室、４……後室、５……切換バルブ、6a〜6g……油
路、９……弁部材、9b……受圧部、10……プリセット圧
設定手段、10a……プリセット圧設定バネ、10b……プラ
ンジャ、10c……受圧室、11……第１油路、12……圧力
調整弁、13……第２油路、14……第１遮断弁、15……第
３油路、16……第２遮断弁、17……第３遮断弁。FIG. 1 is a configuration diagram showing a main part of a configuration of a hydraulic striking device according to an embodiment of the present invention, and FIG. 2 is a configuration diagram showing a main part of a configuration of a hydraulic striking device according to a conventional example. 1 ... Hydraulic impact tool body, 2 ... Piston member, 3 ...
Front chamber, 4 ... Rear chamber, 5 ... Switching valve, 6a-6g ... Oil passage, 9 ... Valve member, 9b ... Pressure receiving part, 10 ... Preset pressure setting means, 10a ... Preset pressure setting spring , 10b ...... Plunger, 10c ...... Pressure receiving chamber, 11 ...... First oil passage, 12 ...... Pressure adjusting valve, 13 ...... Second oil passage, 14 ...... First shut-off valve, 15 ...... Third oil passage , 16 …… Second shutoff valve, 17 …… Third shutoff valve.
Claims (1)
れたピストン部材と、 上記油圧打撃工具本体とピストン部材とで形成された前
室または後室に作動油を給排してピストン部材の移動方
向を切換える切換バルブと、 上記前室または上記後室の作動油を排出する排油路と、 その排油路に摺動自在に装着され、後端部に上記作動油
の油圧を受ける受圧部が形成されており、受圧部へ作用
する油圧力で後退して排油量を増加させる弁部材と、 その弁部材を前進させて排油量を減少させるプリセット
圧設定手段とを有する油圧打撃工具において、 上記プリセット圧設定手段が、 上記弁部材を前方に付勢するプリセット圧設定バネと、 このプリセット圧設定バネの後端を受け止める前後動可
能に設けられたプランジャと、 このプランジャによって前端が仕切られたプリセット圧
調整用受圧室と、 この受圧室に上記作動油を供給してプリセット圧を高く
する第１油路と、 第１油路に介装され上記作動油の油圧を所定の設定圧に
設定する圧力調整弁と、上記受圧室に上記作動油を供給
してプリセット圧を圧力調整弁の設定圧より高くする第
２油路と、 この第２油路に介装され排油路の油圧が所定の排油圧よ
りも低い時に第２油路を開通させる第１遮断弁と、 上記受圧室に供給された作動油を排出してプリセット圧
を低くする第３油路と、この第３油路に介装され排油路
の油圧が所定の排油圧よりも高い時に上記第３油路を開
通する第２遮断弁と、 上記第１油路の圧力調整弁より下流側部分に介装され上
記受圧室の内圧が所定値よりも低い時に第１油路を遮断
する第３遮断弁とを備えたことを特徴とする油圧打撃工
具。Claim: What is claimed is: 1. A piston member, which is inserted into a main body of a hydraulic impact tool so as to be movable back and forth, and a piston which supplies and discharges hydraulic oil to a front chamber or a rear chamber formed by the main body of the hydraulic impact tool and the piston member. A switching valve for switching the moving direction of the member, an oil discharge passage for discharging the hydraulic oil in the front chamber or the rear chamber, and a slidable mount on the oil discharge passage, and a hydraulic pressure of the hydraulic oil for the rear end portion. A pressure receiving portion for receiving is formed, and has a valve member that retreats by the hydraulic pressure acting on the pressure receiving portion to increase the amount of discharged oil, and a preset pressure setting means that advances the valve member to reduce the amount of discharged oil. In the hydraulic impact tool, the preset pressure setting means includes a preset pressure setting spring that biases the valve member forward, a plunger that is movable forward and backward to receive a rear end of the preset pressure setting spring, and the plunger. Yo A preset pressure adjusting pressure receiving chamber whose front end is partitioned, a first oil passage for supplying the working oil to the pressure receiving chamber to increase the preset pressure, and a hydraulic pressure of the working oil interposed in the first oil passage. A pressure adjusting valve for setting a predetermined set pressure, a second oil passage for supplying the working oil to the pressure receiving chamber to make the preset pressure higher than the set pressure of the pressure adjusting valve, and a second oil passage interposed in the second oil passage. A first shutoff valve that opens the second oil passage when the oil pressure in the oil discharge passage is lower than a predetermined oil pressure, and a third oil passage that discharges the hydraulic oil supplied to the pressure receiving chamber to reduce the preset pressure. A second shut-off valve which is interposed in the third oil passage and opens the third oil passage when the oil pressure in the drain oil passage is higher than a predetermined exhaust oil pressure; and a downstream side of the pressure adjusting valve in the first oil passage. And a third shut-off valve which is interposed in the portion and shuts off the first oil passage when the internal pressure of the pressure receiving chamber is lower than a predetermined value. Hydraulic impact tool, wherein the door.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5918088U JPH078141Y2 (en) | 1988-04-29 | 1988-04-29 | Hydraulic impact tool |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5918088U JPH078141Y2 (en) | 1988-04-29 | 1988-04-29 | Hydraulic impact tool |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH01163081U JPH01163081U (en) | 1989-11-14 |
| JPH078141Y2 true JPH078141Y2 (en) | 1995-03-01 |
Family
ID=31284964
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP5918088U Expired - Lifetime JPH078141Y2 (en) | 1988-04-29 | 1988-04-29 | Hydraulic impact tool |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH078141Y2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SE536903C2 (en) * | 2012-11-28 | 2014-10-21 | Atlas Copco Rock Drills Ab | Device at distribution valve for a rock drill and rock drill |
| AT513849B1 (en) * | 2013-03-04 | 2014-08-15 | Tmt Bbg Res And Dev Gmbh | Control of the working frequency of a striking mechanism |
-
1988
- 1988-04-29 JP JP5918088U patent/JPH078141Y2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH01163081U (en) | 1989-11-14 |
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