JPH07269507A - Accelerating device for hydraulic cylinder - Google Patents

Accelerating device for hydraulic cylinder

Info

Publication number
JPH07269507A
JPH07269507A JP6061721A JP6172194A JPH07269507A JP H07269507 A JPH07269507 A JP H07269507A JP 6061721 A JP6061721 A JP 6061721A JP 6172194 A JP6172194 A JP 6172194A JP H07269507 A JPH07269507 A JP H07269507A
Authority
JP
Japan
Prior art keywords
valve
pilot
pressure
hydraulic cylinder
line
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
Application number
JP6061721A
Other languages
Japanese (ja)
Other versions
JP3502435B2 (en
Inventor
Hiroyuki Abe
裕之 阿部
Isao Kobayashi
功 小林
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Furukawa Co Ltd
Original Assignee
Furukawa Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Furukawa Co Ltd filed Critical Furukawa Co Ltd
Priority to JP06172194A priority Critical patent/JP3502435B2/en
Publication of JPH07269507A publication Critical patent/JPH07269507A/en
Application granted granted Critical
Publication of JP3502435B2 publication Critical patent/JP3502435B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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  • Operation Control Of Excavators (AREA)
  • Working Measures On Existing Buildindgs (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

PURPOSE:To enable the quick operation of a hydraulic cylinder by connecting a pilot pipe line for a logic valve to the pilot port of the logic valve through a sequence valve. CONSTITUTION:A confluence pipe line 33 equipped with a logic valve 32 is interposed between a contraction action pipe line 8 at the side of a cylinder 1 from a sequence valve 30 and a check valve 31, and an extension action pipe line 7 at the side of an operation valve 4 from a boosting circuit 12 and a low pressure circuit 14. When the hydraulic cylinder 1 is extended, if hydraulic pressure is less than the set pressure of the sequence valve 30 in a pilot pipe line 37 for a logic valve at the time of low loading, pressure oil discharged out of a hydraulic pump 5 is fed to the head side oil chamber 2 of the hydraulic cylinder from the low pressure circuit 14 through the operation valve 4 and a pilot check valve. Since the rod side oil chamber 3 of the hydraulic cylinder 1 is simultaneously communicated with the low pressure circuit 14 through the logic valve 32, the confluence pipe line 33, and operating oil flowing out of the rod side oil chamber 3 of the hydraulic cylinder 1 is also fed to the head side oil chamber 2, so that the hydraulic cylinder 1 is thereby quickly extended.

Description

【発明の詳細な説明】Detailed Description of the Invention

【0001】[0001]

【産業上の利用分野】本発明は、油圧シリンダの増速装
置に関する。
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a speed increasing device for a hydraulic cylinder.

【0002】[0002]

【従来の技術】コンクリート構築物等を破砕する破砕機
は、被破砕物を挟圧破砕するための一対の破砕アーム
と、この破砕アームを回動させる破砕アーム作動用の油
圧シリンダとを備えており、これを建設車両のブームに
装着し、建設車両の油圧システムの制御弁から、破砕ア
ーム作動用の油圧シリンダのヘッド側油室とロッド側油
室とに、それぞれ伸作動管路と縮作動管路とを接続して
いる。破砕機は破砕力に重点をおいて製造され、大径の
油圧シリンダが用いられていたので、装着する建設車両
の油圧システムの油量では伸長時の動きがが遅く作業能
率が悪いという欠点があった。
2. Description of the Related Art A crusher for crushing concrete structures and the like is equipped with a pair of crushing arms for crushing the crushed object under pressure and a hydraulic cylinder for activating the crushing arms for rotating the crushing arms. , This is mounted on the boom of the construction vehicle, and the extension valve and the contraction tube are respectively connected from the control valve of the hydraulic system of the construction vehicle to the head side oil chamber and the rod side oil chamber of the hydraulic cylinder for crushing arm operation. It connects with the road. Since the crusher was manufactured with a focus on crushing force and used large diameter hydraulic cylinders, the drawback of the crusher is that the amount of oil in the hydraulic system of the construction vehicle to be mounted is slow in movement during extension and work efficiency is poor. there were.

【0003】そこで、小径の油圧シリンダを用いて低負
荷伸長時の動きを早くし、破砕作業時には破砕力が大と
なるよう伸作動管路に作動油圧を増圧する増圧装置を設
けたものが提案されている。このような油圧シリンダの
増圧装置には、単動式の増圧ピストンを設けたものと複
動式の増圧ピストンを設けたものとがあるが、単動式の
ものは、往行時のみしか増圧を行わないため能率が悪い
ため、複動式のものが主に使用される。
In view of this, there has been provided a pressure-increasing device for increasing the working oil pressure in the extension working line so as to accelerate the movement at the time of low load extension by using a small diameter hydraulic cylinder and increase the crushing force during the crushing work. Proposed. There are two types of pressure boosters for hydraulic cylinders, one with a single-acting pressure boosting piston and one with a double-acting pressure boosting piston. The double-acting type is mainly used because it is inefficient because it only boosts pressure.

【0004】複動式の増圧ピストンを備えた増圧装置に
は、増圧ピストンの往復を切換える手段として、増圧ピ
ストンにより直接押動されるプランジャを具えた機械式
切換弁を利用したもの(特開昭60−227001号参
照)や、増圧ピストンからのパイロット油圧により切換
えられるパイロット切換弁を利用したもの(特開平4−
316702号参照)などがある。
A pressure increasing device having a double-acting pressure increasing piston uses a mechanical switching valve having a plunger directly pushed by the pressure increasing piston as means for switching the reciprocation of the pressure increasing piston. (See Japanese Patent Laid-Open No. 60-227001) or a pilot switching valve that is switched by pilot hydraulic pressure from a pressure boosting piston (Japanese Patent Laid-Open No. 4-27041).
316702)).

【0005】また、低負荷伸長時の動きを更に早くする
ため、増圧装置に加え、伸作動管路と縮作動管路との間
を接続する差動バルブユニットを設けて、低負荷伸長時
にはロッド側油室から流出する作動油を伸作動管路に合
流させるようにしたもの(特願昭63−72904号)
もある。しかし、機械式切換弁を利用したものでは、プ
ランジャを押圧するばねの寿命が短く、またシール部が
多くなるという問題がある。
In order to further accelerate the movement at the time of low load extension, in addition to the pressure booster, a differential valve unit for connecting between the extension operation line and the contraction operation line is provided, and at the time of low load extension, The working oil flowing out from the oil chamber on the rod side is joined to the extension working pipe (Japanese Patent Application No. 63-72904).
There is also. However, in the case of using the mechanical switching valve, there are problems that the life of the spring that presses the plunger is short and that the number of sealing portions is large.

【0006】これに対し、パイロット切換弁を利用した
ものは、切換弁の機械的耐久性には優れているが、パイ
ロット圧は切換時に作用するのみであり、常時は作用し
ていないため、パイロット切換弁のスプールの位置が変
動し回路の切換えが不安定になるおそれがある。また、
増圧装置と差動バルブユニットとを設けたものでは、機
械式切換弁を利用しているため、プランジャを押圧する
ばねの寿命が短く、またシール部が多くなるという問題
がある他、差動バルブユニットがスプール弁とパイロッ
ト弁とシーケンス弁とで構成されるため、油路の抵抗が
大で応答性が悪く、バルブブロックが大型化する。
On the other hand, the one using the pilot switching valve is excellent in the mechanical durability of the switching valve, but the pilot pressure acts only at the time of switching and does not always act, so that the pilot pressure The position of the spool of the switching valve may fluctuate and circuit switching may become unstable. Also,
In the case where the pressure booster and the differential valve unit are provided, since the mechanical switching valve is used, there is a problem that the life of the spring that presses the plunger is short, and the number of seal portions is large. Since the valve unit is composed of the spool valve, the pilot valve, and the sequence valve, the resistance of the oil passage is large and the response is poor, and the valve block becomes large.

【0007】[0007]

【発明が解決しようとする課題】本発明は、油圧シリン
ダにおけるかかる問題を解決するものであって、油圧シ
リンダの迅速な作動を可能とし、増圧ピストンの耐久性
を向上させると共に、切換弁による回路の切換えを安定
させて作動を確実にすることができ、装置を小型軽量化
することのできる油圧シリンダの増速装置を提供するこ
とを目的とする。
SUMMARY OF THE INVENTION The present invention solves such a problem in a hydraulic cylinder by enabling a quick operation of the hydraulic cylinder, improving the durability of the pressure boosting piston, and using a switching valve. An object of the present invention is to provide a speed increasing device for a hydraulic cylinder, which can stabilize circuit switching and ensure operation, and can reduce the size and weight of the device.

【0008】[0008]

【課題を解決するための手段】本発明は、油圧ポンプと
タンクとを、操作弁から伸作動管路と縮作動管路とを介
して、油圧シリンダのヘッド側油室とロッド側油室とに
接続した油圧シリンダの作動装置において、伸作動管路
の途中に、シーケンス弁とパイロット切換弁と複動式増
圧ピストンとを接続した増圧回路、及び、パイロットチ
ェック弁を備えた低圧回路を並列に設け、パイロットチ
ェック弁には縮作動管路からチェック弁パイロット管路
を接続し、パイロット切換弁にはパイロット油室より受
圧面積の小さい保持油室を形成し、保持油室にはパイロ
ット切換弁のサービスポートから保持管路を接続し、縮
作動管路の途中に、シーケンス弁、及びチェック弁を並
列に設け、このシーケンス弁、及びチェック弁より油圧
シリンダ側の縮作動管路と、前記増圧回路、及び低圧回
路より操作弁側の伸作動管路との間にロジック弁を備え
た合流管路を設け、ロジック弁のパイロットポートには
伸作動管路からシーケンス弁を介してロジック弁パイロ
ット管路を接続することにより、上記課題を解決してい
る。
SUMMARY OF THE INVENTION According to the present invention, a hydraulic pump and a tank are connected to a head side oil chamber and a rod side oil chamber of a hydraulic cylinder from an operation valve via an extension actuation line and a compression actuation line. In the hydraulic cylinder actuator connected to, a pressure increasing circuit connecting a sequence valve, a pilot switching valve, and a double-acting pressure increasing piston, and a low pressure circuit equipped with a pilot check valve are provided in the middle of the extension operation pipeline. Installed in parallel, the check valve pilot line is connected to the pilot check valve from the compression actuation line, the holding oil chamber with a smaller pressure receiving area than the pilot oil chamber is formed in the pilot switching valve, and the pilot switching valve is used in the holding oil chamber. A holding line is connected from the service port of the valve, and a sequence valve and a check valve are installed in parallel in the middle of the compression actuation line, and compression is performed on the hydraulic cylinder side from the sequence valve and the check valve. A merging line equipped with a logic valve is provided between the line and the pressure-increasing circuit and the extension actuating line on the operating valve side of the low-pressure circuit. The above problem is solved by connecting the logic valve pilot line via the.

【0009】増圧回路のシーケンス弁の設定圧はロジッ
ク弁パイロット管路のシーケンス弁の設定圧より高く、
ロジック弁パイロット管路のシーケンス弁の設定圧は縮
作動管路のシーケンス弁の設定圧より高く設定する。
The set pressure of the sequence valve of the booster circuit is higher than the set pressure of the sequence valve of the logic valve pilot line,
The set pressure of the sequence valve in the logic valve pilot line is set higher than the set pressure of the sequence valve in the compression actuation line.

【0010】[0010]

【作用】油圧シリンダの伸長時には、低負荷で油圧がロ
ジック弁パイロット管路のシーケンス弁の設定圧以下の
場合、油圧ポンプから吐出された圧油が操作弁、パイロ
ットチェック弁を経て、低圧回路から油圧シリンダのヘ
ッド側油室に供給されると共に、油圧シリンダのロッド
側油室がロジック弁、合流管路を経て低圧回路と連通す
るため、油圧シリンダのロッド側油室から流出する作動
油もヘッド側油室に供給され、油圧シリンダは急速に伸
長する。
[Operation] When the hydraulic cylinder is extended, if the load is low and the hydraulic pressure is less than or equal to the set pressure of the sequence valve in the logic valve pilot line, the pressure oil discharged from the hydraulic pump passes through the operation valve and pilot check valve and then from the low pressure circuit. The hydraulic oil is supplied to the head side oil chamber of the hydraulic cylinder, and the rod side oil chamber of the hydraulic cylinder communicates with the low pressure circuit through the logic valve and the merging conduit. Supplied to the side oil chamber, the hydraulic cylinder expands rapidly.

【0011】油圧がロジック弁パイロット管路のシーケ
ンス弁の設定圧を超えると、ロジック弁パイロット管路
のシーケンス弁が開いてロジック弁を閉じると共に縮作
動管路のシーケンス弁を開き、ロッド側油室から流出す
る作動油が縮作動管路のシーケンス弁から操作弁を経て
タンクに戻るようになるので、油圧シリンダは伸長速度
が低下するが出力が増加する。
When the hydraulic pressure exceeds the set pressure of the sequence valve in the logic valve pilot line, the sequence valve in the logic valve pilot line opens to close the logic valve and the sequence valve in the compression actuating line to open the rod side oil chamber. Since the hydraulic oil flowing out of the hydraulic cylinder returns to the tank from the sequence valve of the contraction operation line via the operation valve, the expansion speed of the hydraulic cylinder decreases but the output increases.

【0012】油圧シリンダが高負荷となり油圧が増圧回
路のシーケンス弁の設定圧を超えると、圧油は増圧回路
のシーケンス弁を経てパイロット切換弁に入り、ここで
切換えられて、複動式増圧ピストンの左右の作動油室に
交互に流入し、右左の増圧室から増圧された圧油が増圧
回路から油圧シリンダのヘッド側油室に供給される。こ
のとき、パイロット切換弁のスプールは、複動式増圧ピ
ストンからのパイロット圧で切換えられてから次の切換
が行われるまでの間、保持管路でパイロット切換弁のサ
ービスポートと連通する保持油室の保持力で所定位置に
保持される。
When the hydraulic cylinder becomes highly loaded and the hydraulic pressure exceeds the set pressure of the sequence valve of the pressure boosting circuit, the pressure oil enters the pilot switching valve via the sequence valve of the pressure boosting circuit, and is switched there to be a double-acting type. The pressure oil alternately flows into the left and right hydraulic oil chambers of the pressure boosting piston, and the pressure oil boosted from the right and left pressure boosting chambers is supplied from the pressure boosting circuit to the head side oil chamber of the hydraulic cylinder. At this time, the spool of the pilot switching valve holds the holding oil that communicates with the service port of the pilot switching valve in the holding pipeline between the time when the pilot pressure is switched by the double-acting pressure boosting piston and the next switching is performed. It is held in place by the holding force of the chamber.

【0013】油圧シリンダの短縮時には、圧油が操作弁
からチェック弁を経て、縮作動管路から油圧シリンダの
ロッド側油室に供給される。当初、低圧回路のパイロッ
トチェック弁は閉じているが、ロッド側油室及び縮作動
管路の油圧が上昇してパイロットチェック弁が開くの
で、油圧シリンダのヘッド側油室の作動油は伸作動管路
の低圧回路側から操作弁を経てタンクに戻る。
When the hydraulic cylinder is shortened, pressure oil is supplied from the operation valve through the check valve to the rod-side oil chamber of the hydraulic cylinder from the compression actuation line. Initially, the pilot check valve in the low-pressure circuit is closed, but the hydraulic pressure in the rod-side oil chamber and the compression actuation line rises and the pilot check valve opens. Return to the tank through the control valve from the low pressure circuit side of the line.

【0014】[0014]

【実施例】図1は本発明の一実施例である油圧シリンダ
の作動装置の回路図である。ここで、油圧シリンダ1の
ヘッド側油室2とロッド側油室3とには、油圧ポンプ5
とタンク6から操作弁4を介して伸作動管路7と縮作動
管路8とが接続されており、この伸作動管路7の途中に
は、シーケンス弁9とパイロット切換弁10と複動式増
圧ピストン11とを接続した増圧回路12、及び、パイ
ロットチェック弁13を備えた低圧回路14が並列に設
けられている。
DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 is a circuit diagram of a hydraulic cylinder actuator according to an embodiment of the present invention. Here, the hydraulic pump 5 is installed in the head side oil chamber 2 and the rod side oil chamber 3 of the hydraulic cylinder 1.
The expansion actuation line 7 and the contraction actuation line 8 are connected from the tank 6 and the operation valve 4 through the operation valve 4, and in the middle of the extension actuation line 7, the sequence valve 9, the pilot switching valve 10 and the double acting A pressure increasing circuit 12 connected to the pressure increasing piston 11 and a low pressure circuit 14 having a pilot check valve 13 are provided in parallel.

【0015】複動式増圧ピストン11は左右に受圧面積
の大きい作動油室16(16L、16R)と受圧面積の
小さい増圧室17(17L、17R)とを備えており、
それぞれパイロット切換弁10の左右のサービスポート
18(18L、18R)と接続されている。また、左右
の増圧室17(17L、17R)は伸作動管路7で油圧
シリンダ1のヘッド側油室2に接続されており、増圧室
17(17L、17R)の流入側と吐出側にはチェック
弁19がそれぞれ配置されている。パイロット切換弁1
0の左右のパイロット油室20(20L、20R)に
は、複動式増圧ピストン11の往復動により交互に左右
の作動油室16(16L、16R)と連通するパイロッ
ト管路21(21L、21R)が接続されている。パイ
ロット切換弁10の戻り管路22はチェック弁23を介
して縮作動管路8と接続されている。このパイロット切
換弁10には、パイロット油室20(20L、20R)
より受圧面積の小さい保持油室24(24L、24R)
が形成されており、左右の保持油室24(24L、24
R)には右左のサービスポート18(18R、18L)
から保持管路25(25L、25R)が接続されてい
る。
The double-acting pressure-increasing piston 11 is provided with left and right hydraulic oil chambers 16 (16L, 16R) having a large pressure-receiving area and pressure-increasing chambers 17 (17L, 17R) having a small pressure-receiving area.
Each of them is connected to the left and right service ports 18 (18L, 18R) of the pilot switching valve 10. Further, the left and right pressure increasing chambers 17 (17L, 17R) are connected to the head side oil chamber 2 of the hydraulic cylinder 1 by the extension working line 7, and the inflow side and the discharge side of the pressure increasing chambers 17 (17L, 17R). A check valve 19 is arranged in each. Pilot switching valve 1
The left and right pilot oil chambers 20 (20L, 20R) of 0 are alternately connected to the left and right hydraulic oil chambers 16 (16L, 16R) by the reciprocating motion of the double-acting pressure increasing piston 11, and the pilot conduits 21 (21L, 21R) is connected. The return line 22 of the pilot switching valve 10 is connected to the compression actuating line 8 via a check valve 23. The pilot switching valve 10 includes a pilot oil chamber 20 (20L, 20R).
Holding oil chamber 24 (24L, 24R) with smaller pressure receiving area
The left and right holding oil chambers 24 (24L, 24
R) Service port 18 (18R, 18L) on the left and right
To the holding pipeline 25 (25L, 25R).

【0016】パイロットチェック弁13には縮作動管路
8からチェック弁パイロット管路26が接続されてい
る。縮作動管路8の途中には、シーケンス弁30、及び
チェック弁31を並列に設け、このシーケンス弁30、
及びチェック弁31より油圧シリンダ1側の縮作動管路
8と、増圧回路12、及び低圧回路14より操作弁4側
の伸作動管路7との間には、ロジック弁32を備えた合
流管路33が設けられている。なお、この実施例では、
チェック弁31の油圧シリンダ1側にオリフィス34が
設けられている。ロジック弁33のパイロットポート3
5には伸作動管路7からシーケンス弁36を介してロジ
ック弁パイロット管路37が接続されている。合流管路
33にはロジック弁32のみが設けられスプール弁を用
いないため、管路の抵抗が大幅に低減され応答性がよく
なり、バルブブロックが小型軽量化される。
The pilot check valve 13 is connected to the check valve pilot line 26 from the compression actuation line 8. A sequence valve 30 and a check valve 31 are provided in parallel in the middle of the compression operation pipe line 8.
A confluence of a logic valve 32 is provided between the compression actuation line 8 on the hydraulic cylinder 1 side of the check valve 31 and the extension actuation line 7 on the operation valve 4 side of the pressure increase circuit 12 and the low pressure circuit 14. A pipe line 33 is provided. In this example,
An orifice 34 is provided on the hydraulic cylinder 1 side of the check valve 31. Pilot port 3 of logic valve 33
A logic valve pilot line 37 is connected to 5 from the extension operation line 7 through a sequence valve 36. Since only the logic valve 32 is provided in the merging pipe line 33 and no spool valve is used, the resistance of the pipe line is significantly reduced, the responsiveness is improved, and the valve block is reduced in size and weight.

【0017】ここで、縮作動管路8のシーケンス弁30
の設定圧はロジック弁パイロット管路37のシーケンス
弁36の設定圧より低く設定され、ロジック弁パイロッ
ト管路37のシーケンス弁36が開くと、ロジック弁パ
イロット管路37の油圧ですぐに縮作動管路8のシーケ
ンス弁30が開くように構成されている。また、増圧回
路12のシーケンス弁9の設定圧はロジック弁パイロッ
ト管路37のシーケンス弁の設定圧より高く設定されて
いる。
Here, the sequence valve 30 of the compression actuation line 8
The set pressure of is set lower than the set pressure of the sequence valve 36 of the logic valve pilot line 37, and when the sequence valve 36 of the logic valve pilot line 37 opens, the hydraulic pressure of the logic valve pilot line 37 immediately causes the contraction operation pipe. The sequence valve 30 in line 8 is configured to open. The set pressure of the sequence valve 9 of the pressure boosting circuit 12 is set higher than the set pressure of the sequence valve of the logic valve pilot line 37.

【0018】油圧シリンダ1の伸長時には、低負荷で油
圧がロジック弁パイロット管路37のシーケンス弁36
の設定圧以下の場合、油圧ポンプ5から吐出された圧油
が操作弁4、パイロットチェック弁13を経て、低圧回
路14から油圧シリンダ1のヘッド側油室2に供給され
ると共に、油圧シリンダ1のロッド側油室3がロジック
弁32、合流管路33を経て低圧回路14と連通するた
め、油圧シリンダ1のロッド側油室3から流出する作動
油もヘッド側油室2に供給され、油圧シリンダ1は急速
に伸長する。
When the hydraulic cylinder 1 extends, the hydraulic pressure is low and the sequence valve 36 of the logic valve pilot line 37 has a low hydraulic pressure.
When the pressure is less than or equal to the set pressure of, the pressure oil discharged from the hydraulic pump 5 is supplied from the low pressure circuit 14 to the head side oil chamber 2 of the hydraulic cylinder 1 via the operation valve 4 and the pilot check valve 13, and the hydraulic cylinder 1 Since the rod side oil chamber 3 of the hydraulic cylinder 1 communicates with the low pressure circuit 14 via the logic valve 32 and the merging pipe line 33, the hydraulic oil flowing out from the rod side oil chamber 3 of the hydraulic cylinder 1 is also supplied to the head side oil chamber 2, Cylinder 1 extends rapidly.

【0019】油圧がロジック弁パイロット管路37のシ
ーケンス弁36の設定圧を超えると、ロジック弁パイロ
ット管路37のシーケンス弁36が開いてロジック弁3
2を閉じると共に、縮作動管路8のシーケンス弁30を
開き、ロッド側油室3から流出する作動油が縮作動管路
8のオリフィス34、シーケンス弁30から操作弁4を
経てタンク6に戻るようになるので、油圧シリンダ1は
伸長速度が低下するが出力が増加する。
When the hydraulic pressure exceeds the set pressure of the sequence valve 36 of the logic valve pilot line 37, the sequence valve 36 of the logic valve pilot line 37 opens and the logic valve 3
2 is closed and the sequence valve 30 of the compression actuation pipe 8 is opened, and the hydraulic oil flowing out from the rod side oil chamber 3 returns to the tank 6 from the orifice 34 of the compression actuation pipe 8 and the sequence valve 30 via the operation valve 4. As a result, the expansion speed of the hydraulic cylinder 1 decreases, but the output increases.

【0020】油圧シリンダ1が高負荷となり油圧が増圧
回路12のシーケンス弁9の設定圧を超えると、圧油は
増圧回路12のシーケンス弁9を経てパイロット切換弁
10に入り、ここで切換えられて、複動式増圧ピストン
11の左右の作動油室16(16L、16R)に交互に
流入し、右左の増圧室17(17L、17R)で増圧さ
れた圧油が増圧回路12から油圧シリンダ1のヘッド側
油室2に供給される。
When the hydraulic cylinder 1 becomes highly loaded and the hydraulic pressure exceeds the set pressure of the sequence valve 9 of the pressure increasing circuit 12, the pressure oil enters the pilot switching valve 10 via the sequence valve 9 of the pressure increasing circuit 12 and switches there. Then, the pressure oil alternately flows into the left and right hydraulic oil chambers 16 (16L, 16R) of the double-acting pressure increasing piston 11, and the pressure oil increased in the right and left pressure increasing chambers 17 (17L, 17R) is increased by the pressure increasing circuit. It is supplied to the head side oil chamber 2 of the hydraulic cylinder 1 from 12.

【0021】このとき、パイロット切換弁のスプール
は、複動式増圧ピストンからのパイロット圧で切換えら
れてから次の切換が行われるまでの間、保持管路でパイ
ロット切換弁のサービスポートと連通する保持油室の保
持力で所定位置に保持される。例えば、パイロット切換
弁10が図示の状態であると、圧油は左の作動油室16
Lに流入して複動式増圧ピストン11は右へ移動し、右
の増圧室17Rから増圧された圧油が吐出され、左の増
圧室17Lには圧油が吸入される。この行程の間、右の
保持油室24Rは保持管路25Rで左のサービスポート
18Lと連通しているので、パイロット切換弁10のス
プールは図示の状態で保持され変動を生じない。複動式
増圧ピストン11が右へ移動して、左の作動油室16L
と左のパイロット管路21Lとが連通すると、左のパイ
ロット油室20Lに圧油が流入するため、パイロット切
換弁10のスプールは右へ移動して圧油を右の作動油室
16Rへ送るように切換わり、以後この切換動作が繰返
される。
At this time, the spool of the pilot switching valve communicates with the service port of the pilot switching valve in the holding pipe between the switching by the pilot pressure from the double-acting pressure increasing piston and the next switching. It is held in place by the holding force of the holding oil chamber. For example, when the pilot switching valve 10 is in the illustrated state, the pressure oil is left in the hydraulic fluid chamber 16 on the left.
The double-acting pressure-increasing piston 11 moves to the right by flowing into L, the pressure oil that has been increased in pressure is discharged from the right pressure increasing chamber 17R, and the pressure oil is sucked into the left pressure increasing chamber 17L. During this stroke, the right holding oil chamber 24R communicates with the left service port 18L through the holding pipe line 25R, so the spool of the pilot switching valve 10 is held in the illustrated state and does not fluctuate. The double-acting booster piston 11 moves to the right, and the left hydraulic oil chamber 16L
And the left pilot pipe line 21L communicate with each other, the pressure oil flows into the left pilot oil chamber 20L, so that the spool of the pilot switching valve 10 moves to the right to send the pressure oil to the right hydraulic oil chamber 16R. Then, this switching operation is repeated.

【0022】油圧シリンダ1の短縮時には、圧油が操作
弁4からチェック弁31を経て、縮作動管路8から油圧
シリンダ1のロッド側油室3に供給される。当初、低圧
回路14のパイロットチェック弁13は閉じているが、
ロッド側油室3及び縮作動管路8の油圧が上昇してパイ
ロットチェック弁13が開くので、油圧シリンダ1のヘ
ッド側油室2の作動油は伸作動管路7の低圧回路14側
から操作弁4を経てタンク6に戻る。
When the hydraulic cylinder 1 is shortened, pressure oil is supplied from the operation valve 4 to the check valve 31 and then to the rod-side oil chamber 3 of the hydraulic cylinder 1 from the compression actuation line 8. Initially, the pilot check valve 13 of the low pressure circuit 14 is closed,
Since the hydraulic pressures in the rod-side oil chamber 3 and the compression actuation line 8 rise and the pilot check valve 13 opens, the operating oil in the head-side oil chamber 2 of the hydraulic cylinder 1 is operated from the low-pressure circuit 14 side of the extension actuation line 7. Return to tank 6 via valve 4.

【0023】[0023]

【発明の効果】以上説明したように、本発明の油圧シリ
ンダの増速装置は、油圧シリンダの伸長時、低負荷の場
合は迅速に作動することができ、高負荷の場合は、増圧
回路により高出力が可能となる。増圧ピストンには機械
式切換弁を用いないため耐久性に優れ、また、パイロッ
ト切換弁は複動式増圧ピストンからのパイロット圧でパ
イロット切換弁が切換えられてから次の切換が行われる
までの間、保持油室の保持力で所定位置に保持されるの
で回路の切換えを安定させ、増圧ピストンの作動を確実
にすることができる。また、装置が小型軽量化される。
As described above, the speed increasing device for a hydraulic cylinder according to the present invention can quickly operate when the hydraulic cylinder is extended when the load is low, and when the load is high, the booster circuit is operated. This enables high output. Since the mechanical boost switching piston is not used for the booster piston, it has excellent durability.In addition, the pilot switching valve is used until the next switching is performed after the pilot switching valve is switched by the pilot pressure from the double-acting booster piston. During this period, the holding force of the holding oil chamber holds the predetermined position, so that circuit switching can be stabilized and the operation of the pressure boosting piston can be ensured. Further, the device is reduced in size and weight.

【図面の簡単な説明】[Brief description of drawings]

【図1】本発明の一実施例である油圧シリンダの増速装
置の回路図である。
FIG. 1 is a circuit diagram of a speed increasing device for a hydraulic cylinder that is an embodiment of the present invention.

【符号の説明】[Explanation of symbols]

1 油圧シリンダ 2 ヘッド側油室 3 ロッド側油室 4 操作弁 5 油圧ポンプ 6 タンク 7 伸作動管路 8 縮作動管路 9 シーケンス弁 10 パイロット切換弁 11 複動式増圧ピストン 12 増圧回路 13 パイロットチェック弁 14 低圧回路 16 作動油室 17 増圧室 18 サービスポート 20 パイロット油室 21 パイロット管路 24 保持油室 25 保持管路 26 チェック弁パイロット管路 30 シーケンス弁 31 チェック弁 32 ロジック弁 33 合流管路 36 シーケンス弁 37 ロジック弁パイロット管路 1 Hydraulic Cylinder 2 Head Side Oil Chamber 3 Rod Side Oil Chamber 4 Operation Valve 5 Hydraulic Pump 6 Tank 7 Extension Actuating Pipeline 8 Compression Actuating Pipeline 9 Sequence Valve 10 Pilot Switching Valve 11 Double Acting Pressure Boosting Piston 12 Pressure Boosting Circuit 13 Pilot check valve 14 Low pressure circuit 16 Hydraulic oil chamber 17 Booster chamber 18 Service port 20 Pilot oil chamber 21 Pilot line 24 Holding oil chamber 25 Holding line 26 Check valve Pilot line 30 Sequence valve 31 Check valve 32 Logic valve 33 Confluence Pipe line 36 Sequence valve 37 Logic valve Pilot line

Claims (2)

【特許請求の範囲】[Claims] 【請求項1】 油圧ポンプとタンクとを、操作弁から伸
作動管路と縮作動管路とを介して、油圧シリンダのヘッ
ド側油室とロッド側油室とに接続した油圧シリンダの作
動装置において、前記伸作動管路の途中に、シーケンス
弁とパイロット切換弁と複動式増圧ピストンとを接続し
た増圧回路、及び、パイロットチェック弁を備えた低圧
回路を並列に設け、前記パイロットチェック弁には縮作
動管路からチェック弁パイロット管路を接続し、前記パ
イロット切換弁にはパイロット油室より受圧面積の小さ
い保持油室を形成し、該保持油室にはパイロット切換弁
のサービスポートから保持管路を接続し、前記縮作動管
路の途中に、シーケンス弁、及びチェック弁を並列に設
け、該シーケンス弁、及びチェック弁より油圧シリンダ
側の縮作動管路と、前記増圧回路、及び低圧回路より操
作弁側の伸作動管路との間にロジック弁を備えた合流管
路を設け、該ロジック弁のパイロットポートには伸作動
管路からシーケンス弁を介してロジック弁パイロット管
路を接続したことを特徴とする油圧シリンダの増速装
置。
1. An operating device for a hydraulic cylinder, wherein a hydraulic pump and a tank are connected from an operation valve to an oil chamber on a head side and an oil chamber on a rod side of a hydraulic cylinder via an extension operation line and a compression operation line. In the middle of the extension operation pipeline, a pressure increasing circuit connecting a sequence valve, a pilot switching valve and a double-acting pressure increasing piston, and a low pressure circuit equipped with a pilot check valve are provided in parallel, and the pilot check is performed. A check valve pilot line is connected to the valve from a compression actuation line, and a holding oil chamber having a smaller pressure receiving area than the pilot oil chamber is formed in the pilot switching valve, and a service port of the pilot switching valve is formed in the holding oil chamber. From this, a holding valve is connected, a sequence valve and a check valve are provided in parallel in the middle of the compression actuation line, and the sequence valve and the compression actuation line on the hydraulic cylinder side from the check valve, A merging conduit provided with a logic valve is provided between the pressure increasing circuit and the extension operation conduit on the operating valve side of the low pressure circuit, and the pilot port of the logic valve is connected from the extension operation conduit through the sequence valve. A hydraulic cylinder speed-up device characterized in that a logic valve pilot line is connected.
【請求項2】 増圧回路のシーケンス弁の設定圧をロジ
ック弁パイロット管路のシーケンス弁の設定圧より高
く、ロジック弁パイロット管路のシーケンス弁の設定圧
を縮作動管路のシーケンス弁の設定圧より高く設定した
ことを特徴とする請求項1記載の油圧シリンダの増速装
置。
2. The set pressure of the sequence valve of the booster circuit is higher than the set pressure of the sequence valve of the logic valve pilot line, and the set pressure of the sequence valve of the logic valve pilot line is set of the sequence valve of the compression actuating line. 2. The speed increasing device for a hydraulic cylinder according to claim 1, wherein the speed increasing device is set higher than the pressure.
JP06172194A 1994-03-30 1994-03-30 Speed increasing device for hydraulic cylinder Expired - Fee Related JP3502435B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP06172194A JP3502435B2 (en) 1994-03-30 1994-03-30 Speed increasing device for hydraulic cylinder

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP06172194A JP3502435B2 (en) 1994-03-30 1994-03-30 Speed increasing device for hydraulic cylinder

Publications (2)

Publication Number Publication Date
JPH07269507A true JPH07269507A (en) 1995-10-17
JP3502435B2 JP3502435B2 (en) 2004-03-02

Family

ID=13179378

Family Applications (1)

Application Number Title Priority Date Filing Date
JP06172194A Expired - Fee Related JP3502435B2 (en) 1994-03-30 1994-03-30 Speed increasing device for hydraulic cylinder

Country Status (1)

Country Link
JP (1) JP3502435B2 (en)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007298072A (en) * 2006-04-28 2007-11-15 Hokuto Kenki Service Kk Hydraulic drive unit, and pinching treatment device equipped with it
JP2012067917A (en) * 2011-09-30 2012-04-05 Hokuto Kenki Service Kk Hydraulic drive device, and pinching treatment apparatus with the same
CN108105177A (en) * 2016-11-25 2018-06-01 天津凡旋科技有限公司 Automatically controlled pressure relief mechanism with dual buck functionality
CN108105175A (en) * 2016-11-25 2018-06-01 天津科企生产力促进有限公司 Pass through the automatically controlled pressure relief mechanism of overflow valve pressurize
CN108105174A (en) * 2016-11-25 2018-06-01 天津晟金创科技有限公司 Automatically controlled pressure relief mechanism with pressure holding function
CN108105207A (en) * 2016-11-25 2018-06-01 天津宝仑信息技术有限公司 Automatically controlled pressure relief mechanism
CN108105178A (en) * 2016-11-25 2018-06-01 天津凤宜科技有限公司 There is differential automatically controlled pressure relief mechanism
KR20190038012A (en) * 2017-09-29 2019-04-08 강토중공업(주) Hydraulic Shear With Increase In Speed And Pressure

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007298072A (en) * 2006-04-28 2007-11-15 Hokuto Kenki Service Kk Hydraulic drive unit, and pinching treatment device equipped with it
JP2012067917A (en) * 2011-09-30 2012-04-05 Hokuto Kenki Service Kk Hydraulic drive device, and pinching treatment apparatus with the same
CN108105177A (en) * 2016-11-25 2018-06-01 天津凡旋科技有限公司 Automatically controlled pressure relief mechanism with dual buck functionality
CN108105175A (en) * 2016-11-25 2018-06-01 天津科企生产力促进有限公司 Pass through the automatically controlled pressure relief mechanism of overflow valve pressurize
CN108105174A (en) * 2016-11-25 2018-06-01 天津晟金创科技有限公司 Automatically controlled pressure relief mechanism with pressure holding function
CN108105207A (en) * 2016-11-25 2018-06-01 天津宝仑信息技术有限公司 Automatically controlled pressure relief mechanism
CN108105178A (en) * 2016-11-25 2018-06-01 天津凤宜科技有限公司 There is differential automatically controlled pressure relief mechanism
CN108105177B (en) * 2016-11-25 2020-08-11 北京科荣达航空设备科技有限公司 Electric control pressure relief mechanism with dual pressure reduction functions
CN108105178B (en) * 2016-11-25 2020-09-08 上海朝冶机电成套设备有限公司 Electric control pressure relief mechanism with differential function
CN108105175B (en) * 2016-11-25 2020-10-27 大唐邓州生物质能热电有限责任公司 Electric control pressure relief mechanism for pressure maintaining through overflow valve
KR20190038012A (en) * 2017-09-29 2019-04-08 강토중공업(주) Hydraulic Shear With Increase In Speed And Pressure

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