JPS591802A - Cylinder controller - Google Patents
Cylinder controllerInfo
- Publication number
- JPS591802A JPS591802A JP58006480A JP648083A JPS591802A JP S591802 A JPS591802 A JP S591802A JP 58006480 A JP58006480 A JP 58006480A JP 648083 A JP648083 A JP 648083A JP S591802 A JPS591802 A JP S591802A
- Authority
- JP
- Japan
- Prior art keywords
- piston
- valve
- valve mechanism
- side pipe
- pressure
- 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
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は、シリンダピストンの運動エネルギーを利用し
て被打撃物を打撃する作業機、例えば油圧ブレーカ、杭
打機、打抜きプレスの流体圧ンリンダ制il+装置に関
する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydraulic cylinder control device for a working machine, such as a hydraulic breaker, a pile driver, or a punching press, which uses the kinetic energy of a cylinder piston to strike an object to be struck.
流体圧7リンダのピストンの運動エネルギーは、ピスト
ン作動行程とビスi・ンの有効受圧面積とピストンに作
用する流体圧の積で与えられる。そして、ピストンの作
動行程と有効受圧面積はシリンダの大きさにより定まる
が、流体圧力はピストンの負荷によって発生する。とこ
ろで従来のこの種の作業機の流体圧シリンダは、例えば
油圧ブレーカの油圧シリンダのように、ピストンが下死
点近くでチゼルを介し被破砕物に衝突した時点で流体圧
が発生するに過ぎない。従って、破砕作業工程であるピ
ストン往行程時のピストンの運動エネルギーは小さなも
のとなる欠点があった。Fluid pressure 7 The kinetic energy of the cylinder piston is given by the product of the piston operating stroke, the effective pressure receiving area of the cylinder, and the fluid pressure acting on the piston. The operating stroke and effective pressure receiving area of the piston are determined by the size of the cylinder, but the fluid pressure is generated by the load on the piston. By the way, in the conventional hydraulic cylinders of this type of work equipment, for example, the hydraulic cylinders of hydraulic breakers, fluid pressure is only generated when the piston collides with the object to be crushed via the chisel near the bottom dead center. . Therefore, there is a drawback that the kinetic energy of the piston during the forward stroke of the piston, which is the crushing process, is small.
本発明は前記の欠点を解消することを目的とするもので
、その構成は、パイロット操作の2位置切換弁によりダ
ブルロッド式複動シリンダをポンプとタンクに選択的に
接続するようにしたシリンダ制御装置において、ダブル
ロッド式複動/リンダにはピストンが上限及び上限近傍
に位置するときにのみタンク11111管路に連通する
第1の弁機構と、ピストンが下限及び下限近傍に位置す
るときにのみポンプ側管路に連通ずる第2の弁機構とを
配設し、2位置切換弁の一方のパイロット室はポンプ側
管路の圧力をパイロット圧力にとるシーケンス弁を介し
て第1の弁機構に接続すると共に、シーケンス弁の上流
を第2の弁機構に接続したことを特徴としている。The present invention aims to eliminate the above-mentioned drawbacks, and consists of a cylinder control system in which a double-rod type double-acting cylinder is selectively connected to a pump and a tank using a pilot-operated two-position switching valve. In the device, the double rod type double acting/cylinder has a first valve mechanism that communicates with the tank 11111 line only when the piston is located at the upper limit and near the upper limit, and a first valve mechanism that communicates with the tank 11111 line only when the piston is located at the lower limit and near the lower limit. A second valve mechanism that communicates with the pump side pipe is arranged, and one pilot chamber of the two-position switching valve is connected to the first valve mechanism via a sequence valve that takes the pressure of the pump side pipe as the pilot pressure. In addition, the upstream side of the sequence valve is connected to the second valve mechanism.
以F本発明の実施例を図面について説明する。第1図に
おいて、(1)は一方の液室(2)を管路(3)、(4
)によりポンプ(5)に、他方の液室(6)を管路(力
、ろボート2位置1)換弁(8)を介して管路(4)と
戻り管路(9)に選択的に接続される差動シリンダで、
被打撃物(10)側に位置するピストンロッド(団の基
端部に環状溝(12)を形成すると共に、ケーシング(
13jのピストンロッド嵌挿孔(14)にはピストン(
15)が下限(図において左行程端)及び下限近傍に位
置するときにのみ環状?M(+2+、液室(2)を介し
てポンプ側の管路(3)に連通ずる室(I6)を形成せ
しめ、この室(I6)とピストンロッド(印の環状溝(
12)とで第2の弁機構を構成している。又、ピストン
ロッド(11)よりも小径とした他方のピストンロッド
(17)の先端部には環状溝(I8)を形成し、この環
状溝は、ピストン(15)が上限(図において右行程端
)及び上限近傍に位置するときにのみケーシング(13
jのピストンロッド嵌挿孔(19)に適宜間隔をおいて
形成されだ室(2+1+と(21)とを連通ずるもので
、これにより室+2F+1は通路(22)、タンク側管
路である戻り管路(9)を経てタンクf23)に連通す
る。このピストンロッド(17)の環状溝(18)と室
+20)、 f21)とで第1の弁機構を構成している
。Hereinafter, embodiments of the present invention will be described with reference to the drawings. In Figure 1, (1) connects one liquid chamber (2) to pipes (3) and (4).
) to the pump (5), and selectively connect the other liquid chamber (6) to the pipe (force, filter boat 2 position 1) to the pipe (4) and return pipe (9) via the switching valve (8). With the differential cylinder connected,
An annular groove (12) is formed at the base end of the piston rod (group) located on the side of the hit object (10), and the casing (
A piston (
15) Is it annular only when it is located at the lower limit (left travel end in the figure) and near the lower limit? M(+2+, a chamber (I6) communicating with the pump side pipe line (3) via the liquid chamber (2) is formed, and this chamber (I6) and the piston rod (the annular groove (marked)
12) constitute a second valve mechanism. In addition, an annular groove (I8) is formed at the tip of the other piston rod (17), which has a smaller diameter than the piston rod (11), and the upper limit of this annular groove is the piston (15) (the right stroke end in the figure). ) and the casing (13
The chambers (2+1+ and (21) are formed at appropriate intervals in the piston rod insertion hole (19) of J), and the chamber +2F+1 is connected to the passage (22) and the return line which is the tank side pipe. It communicates with the tank f23) via the pipe line (9). The annular groove (18) of the piston rod (17) and the chamber +20), f21) constitute a first valve mechanism.
6ポ一ト2位置切換弁(8)は、受圧面積を違えたパイ
ロット室t24)、 +25+を備え、受圧面積の大き
なパイロット室(24)はシーケンス弁(2filを介
装した通路(27)により室(20)に、又、パイロッ
ト室(24)とシーケンス弁(26)との間より分岐し
た通路(28)により室(16)に接続し、受圧面積の
小さなパイロット室 □(25)は通路(29)により
管路(3)に接続する。このろボート2位置切換弁(8
)は、パイロン1室(24)に液圧が作用しないとき位
置Bをとり、液圧が作用すると位1侑Aをとる設定であ
る。シーケンス弁(ソロ)のパイロット室C3(++は
通路(3I)によりポンプ側管路(3)に接続している
。The 6-point 2-position switching valve (8) is equipped with pilot chambers t24) and +25+ with different pressure receiving areas, and the pilot chamber (24) with a large pressure receiving area is connected by a passage (27) in which a sequence valve (2fil) is inserted. It is connected to the chamber (20) and to the chamber (16) by a passage (28) branching from between the pilot chamber (24) and the sequence valve (26), and is connected to the pilot chamber with a small pressure-receiving area. (29) connects to pipe (3).This filter boat 2-position switching valve (8
) is set to position B when no hydraulic pressure is applied to the pylon 1 chamber (24), and to position A when hydraulic pressure is applied. The pilot chamber C3 (++ of the sequence valve (solo) is connected to the pump side pipe line (3) through a passage (3I).
なお、6ボ一ト2位置切換弁(8)のパイロット室(2
5)はばねで代用するようにしてもよい。又、前記の第
1の弁機構に例えば検出棒でピストンロッド(17)端
を検出すると閉路から開路に切換わる検出棒付き切換弁
を用いるようにしてもよい。In addition, the pilot chamber (2) of the 6-bottom 2-position switching valve (8)
5) may be replaced with a spring. Further, the first valve mechanism may be a switching valve with a detection rod that switches from closed to open when the end of the piston rod (17) is detected with a detection rod.
次に本発明の作用につき説明する。6ポ一ト2位置切換
弁(8)がパイロット室(2イ)に作用する液圧により
位置Aにあって差動7リンダ(1)の液室(6)をタン
ク+231に連通しピストン(15)が液室(2)のポ
ンプ作@液により図において右行している図示状態にお
いては、ポンプ側管路(3)の液圧は7−ケンス弁t2
[ilのセット圧(設定用力)より低くく/−ケンス弁
+261は通路(27)をブロックしている。Next, the operation of the present invention will be explained. The 6-point 2-position switching valve (8) is in position A due to the hydraulic pressure acting on the pilot chamber (2a), and communicates the liquid chamber (6) of the differential 7 cylinder (1) with the tank +231 so that the piston ( 15) is moving to the right in the figure due to pump operation @ liquid in the liquid chamber (2), the liquid pressure in the pump side pipe line (3) is the 7-can valve t2.
[Il is lower than the set pressure (setting power)/-can valve +261 is blocking the passage (27).
ピストン(15)が−1−限近くに達すると、室(2(
刀は環状)[II冒18)により室(21)と連通しタ
ンク(2:(+に通じるが、・Zイロノト宰(21)は
室f2f11との連通を断たれているだめ、ろボート2
位置切換弁(8)は依然位置Aにある。ついでピストン
(15)が上限で停止するとポンプ液圧が昇圧しとの液
圧がシーケンス弁(26)のセット圧を越えると、シー
ケンス弁(26)は位置Bをとりパイロット室(24)
をタンク(23)に連通するため、2位置切換弁(8)
はパイロット室(25)の液圧により位置Bをとり液室
(6)をポンプ(5)に連通ずる。これによりピストン
(15)はその両面に高圧の圧液をうけ、両面の受圧面
積差に基づき上限から下限へ向けて左行する。即ち、ピ
ストン(15)は左行行程の語めから高圧のポンプ作動
液をうける結果大きな運動エネルギーを生じ、下限近<
i/C至り被打撃物(10)に衝突する。このピスト
ン左行時では、室+20)と(21)は環状溝(18)
が室(21)から離れだ時点で連通がしゃ断され、ピス
トンロッド(11)が被打撃物(10)に衝突したとこ
ろで室(Ifi)は環状溝(12)、液室(2)を介し
てポンプ側管路(3)と連通し、パイロット室(24)
にポンプ液圧を導く。これにより切換弁(8)は位置A
をとり、液室(6)をタンク(23)に連通ずるだめ、
ピストン、05)は下限に至ると直ちに折返へして図に
おいて右行し以下前述の動作を反復する。When the piston (15) reaches near the -1- limit, the chamber (2 (
The sword is ring-shaped) [II Chapter 18) and is connected to room (21) Tank (2: (+), but Z Ironoto (21) is cut off from communication with room f2f11, Robot 2
The position switching valve (8) is still in position A. Then, when the piston (15) stops at the upper limit, the pump hydraulic pressure increases, and when the hydraulic pressure exceeds the set pressure of the sequence valve (26), the sequence valve (26) takes position B and opens the pilot chamber (24).
In order to communicate with the tank (23), a two-position switching valve (8) is installed.
takes position B due to the hydraulic pressure in the pilot chamber (25) and communicates the liquid chamber (6) with the pump (5). As a result, the piston (15) receives high-pressure liquid on both sides thereof, and moves to the left from the upper limit to the lower limit based on the difference in pressure-receiving area between the two sides. That is, the piston (15) receives high-pressure pump working fluid from the leftward stroke, and as a result, generates large kinetic energy, which causes the piston (15) to reach a point near the lower limit
The i/C reaches the hit object (10). When the piston moves to the left, chambers +20) and (21) are connected to the annular groove (18).
When the piston rod (11) collides with the object (10), the chamber (Ifi) passes through the annular groove (12) and the liquid chamber (2). Communicates with pump side pipe line (3), pilot chamber (24)
Directs the pump hydraulic pressure to. This causes the switching valve (8) to move to position A.
and connect the liquid chamber (6) to the tank (23),
As soon as the piston 05) reaches its lower limit, it turns around and moves to the right in the figure, repeating the above-described operation.
なお、ピストン右行時のポンプ液圧はピストン左行開始
時の液圧より低下するもなおかなりの高圧を維持してお
り、一方、シーケンス弁(2G)はピストン(15)が
」−限から1往復する間には位置Aに復帰している。Although the pump hydraulic pressure when the piston moves to the right is lower than the hydraulic pressure when the piston starts moving to the left, it still maintains a fairly high pressure.On the other hand, the sequence valve (2G) indicates that the piston (15) It returns to position A during one round trip.
以−上説明したように本発明においては、ピストンは設
定されたピストンの上限と下限との間を自動的に往復動
L7、その往復動過程においてピストンには往行程の始
めからシーケンス弁により規制された高圧の作動液を作
用させているだめ、この種のンリングのピスト/に所望
の大きな運動エネルギーを生せしめることができる。As explained above, in the present invention, the piston automatically reciprocates between the set upper and lower piston limits L7, and during the reciprocating process, the piston is regulated by the sequence valve from the beginning of the forward stroke. By applying the high-pressure hydraulic fluid, it is possible to generate the desired large kinetic energy in the piston of this type of ring.
第1図は本発明の実施例を示す油圧回路図である。
1・・・差動シリンダ、5・・ポンプ、8・・・ろボー
ト2位置切換弁、10・・・被打撃物、12.18・・
・環状溝、15・・・ピストン、16,20.21・・
・室、24.ろ0・・パイロット室、26・・シーケン
ス弁。
特W「出願人 川崎重工業株式会社
代理人 弁理士太田謙三FIG. 1 is a hydraulic circuit diagram showing an embodiment of the present invention. 1...Differential cylinder, 5...Pump, 8...Robot 2-position switching valve, 10...Object to be hit, 12.18...
・Annular groove, 15... Piston, 16, 20.21...
・Room, 24. Ro0...Pilot room, 26...Sequence valve. Special W “Applicant Kawasaki Heavy Industries Co., Ltd. Agent Patent Attorney Kenzo Ota
Claims (1)
動/リンダをポンプとタンクに選択的に接続するように
したシリンダ制御装置において、ダブルロッド式複動シ
リンダにはピストンが上限及び上限近傍に位置するとき
にのみタンク側管路に連通ずる第1の弁機構と、ピスト
ンが下限及び下限近傍に位置するときにのみポンプ側管
路に連通ずる第2の弁機構とを配設し、2位置切換弁の
一方のパイロット室はポンプ側管路の圧力をパイロット
圧力にとる/−ケンス弁を介して第1の弁機構に接続す
ると共に、/−ケンス弁の上流を第2の弁機構に接続し
たことを特徴とするシリンダ制御装置。In a cylinder control device that uses a pilot-operated two-position switching valve to selectively connect a double-rod type double-acting/cylinder to a pump and a tank, the double-rod type double-acting cylinder has a piston located at the upper limit and near the upper limit. A first valve mechanism that communicates with the tank side pipe only when the piston is located at the lower limit and a second valve mechanism that communicates with the pump side pipe only when the piston is at the lower limit or near the lower limit are provided, and the two-position switchover mechanism is provided. The pilot chamber on one side of the valve takes the pressure of the pump side pipe as the pilot pressure/- is connected to the first valve mechanism via the can valve, and /- is connected upstream of the can valve to the second valve mechanism. A cylinder control device characterized by:
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP58006480A JPS591802A (en) | 1983-01-17 | 1983-01-17 | Cylinder controller |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP58006480A JPS591802A (en) | 1983-01-17 | 1983-01-17 | Cylinder controller |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP9300978A Division JPS5520929A (en) | 1978-07-29 | 1978-07-29 | Cylinder controller |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS591802A true JPS591802A (en) | 1984-01-07 |
JPH02562B2 JPH02562B2 (en) | 1990-01-08 |
Family
ID=11639633
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP58006480A Granted JPS591802A (en) | 1983-01-17 | 1983-01-17 | Cylinder controller |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS591802A (en) |
-
1983
- 1983-01-17 JP JP58006480A patent/JPS591802A/en active Granted
Also Published As
Publication number | Publication date |
---|---|
JPH02562B2 (en) | 1990-01-08 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US9162297B2 (en) | Hydraulic device for hydraulic cylinders | |
CA2486037A1 (en) | Pattern selector valve for control levers of a work vehicle | |
JP4031088B2 (en) | Excavator control device | |
US3973595A (en) | Arrangement for actuating mechanically independent valves in a pressure fluid system | |
JPS591802A (en) | Cylinder controller | |
JPS5831483B2 (en) | cylinder control device | |
JP3502435B2 (en) | Speed increasing device for hydraulic cylinder | |
JP2554476B2 (en) | Speed-up circuit for hydraulic cylinders such as crushers | |
JPS591803A (en) | Cylinder controller | |
EP2719839B1 (en) | Hydraulic circuit for a hydraulic cylinder | |
JPH07127601A (en) | Intensifying circuit for oil pressure | |
US20040050243A1 (en) | Percussion hydraulic apparatus | |
JPS55108538A (en) | Hydraulic circuit for hydraulic shovel | |
JPH034801Y2 (en) | ||
KR100283001B1 (en) | Speed increase valve for crusher | |
JPS6343603B2 (en) | ||
JP3497549B2 (en) | Pressure booster | |
JPH0320359Y2 (en) | ||
SU1035308A1 (en) | Pneumatic hydraulic drive | |
JPH0390778A (en) | Booster device | |
JP2561872Y2 (en) | Hydraulic pressure booster circuit | |
JP2900324B2 (en) | Hydraulic crusher drive circuit | |
GB1291311A (en) | Machine having a fluid operated boom or other movable member | |
GB2311331A (en) | Hydraulic ram booster | |
WO1996026023A1 (en) | Hydraulic actuator for punches and suchlike movable members for working sheet metal, and hydraulic system incorporating this actuator |