JPS5891903A - Proportional control valve with pressure compensation - Google Patents
Proportional control valve with pressure compensationInfo
- Publication number
- JPS5891903A JPS5891903A JP18695081A JP18695081A JPS5891903A JP S5891903 A JPS5891903 A JP S5891903A JP 18695081 A JP18695081 A JP 18695081A JP 18695081 A JP18695081 A JP 18695081A JP S5891903 A JPS5891903 A JP S5891903A
- Authority
- JP
- Japan
- Prior art keywords
- boat
- pressure
- actuator
- valve
- control valve
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20576—Systems with pumps with multiple pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30505—Non-return valves, i.e. check valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3105—Neutral or centre positions
- F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
- F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
- F15B2211/31582—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having multiple pressure sources and a single output member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
- F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
- F15B2211/5157—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a return line
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/605—Load sensing circuits
- F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
- F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Operation Control Of Excavators (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
本発明は、ブルドーザなどの土木機械を制御する油圧装
置内に用いる圧力補償付比例制御弁に関するものである
。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a proportional control valve with pressure compensation used in a hydraulic system for controlling civil engineering machines such as bulldozers.
ブルドーザなどの土工機械を制御する九めの油圧装置に
は、油圧ポンプを１個用いるものと２個用いるものとが
あるが、従来の上記油圧装置において、■個の油圧ポン
プを用い友場合、チルトドーザの場合ブレードチルトシ
リンダの速度はブレードリフトの速度に比較して小さく
する必要があるｔめ、ポンプからチルトシリンダへ行く
部分にブリードオフ形式の流量制御弁を設け、少流量を
チルトシリンダへ送っている。There are two types of hydraulic systems that control earth-moving machines such as bulldozers: those that use one hydraulic pump and those that use two hydraulic pumps. In the case of a tilt dozer, the speed of the blade tilt cylinder must be small compared to the speed of the blade lift, so a bleed-off type flow control valve is installed in the section going from the pump to the tilt cylinder to send a small flow rate to the tilt cylinder. ing.
このためブレードをチルト操作したときくも油圧ポンプ
は大流量を吐出しておシ、エネルギの損失が非常に大き
いという問題がある。For this reason, there is a problem in that when the blade is tilted, the hydraulic pump discharges a large amount of flow, resulting in a very large loss of energy.
一方２ポンプシステムの場合、ブレードチルト用小ポン
プを別にもち、ブレードチルトを使用しないとき、その
流量を２ポンプシステムの他方の大ポンプと合流させて
ブレードリフトシリンダに供給するようになっている。On the other hand, in the case of a two-pump system, there is a separate small pump for blade tilt, and when the blade tilt is not used, the flow rate is combined with the other large pump of the two-pump system and supplied to the blade lift cylinder.
このためブレードチルトシリンダを操作し次ときは小ポ
ンプ側しか圧力が上昇せず、大ポンプはアンロードして
いるので、１ポンプシステムに比較してエネルギの損失
が少ない。Therefore, the next time the blade tilt cylinder is operated, the pressure increases only on the small pump side, and the large pump is unloaded, so there is less energy loss compared to a one-pump system.
しかし、ブレードリフトシリンダにて押土、整地作業を
行なうときのように、リフトシリンダを微操作を行なう
場合、リフトシリンダへ行く流量は大小ポンプが合流し
几全流量は必要ない。このため上記２ポンプシステムの
場合、ブレードリフト弁にて合流し九全流量を比例制御
弁にて流量制御している九め、上記微操作範囲では２ポ
ンプとも圧力が上昇し、やはりエネルギの損失が大きい
という問題がある。However, when a blade lift cylinder is used to perform small operations on the lift cylinder, such as when performing earth dozing and ground leveling work, the flow rate going to the lift cylinder is combined with the large and small pumps, and a full flow rate is not required. For this reason, in the case of the above two pump system, the two pumps merge at the blade lift valve and the total flow rate is controlled by the proportional control valve.In the above fine operation range, the pressure of both pumps increases, resulting in energy loss. The problem is that it is large.
本発明は上記のことにかんがみなされたもので、２ポン
プシステムの油圧装置を改良して、方向制御弁の微操作
範囲において不必要側の油圧ポンプからの圧油をアンロ
ードしてエネルギロスを少なくすることができるように
した圧力補償付比例制御弁を提供しようとするものであ
る。The present invention was conceived in consideration of the above-mentioned problems, and improves the hydraulic system of the two-pump system to unload pressure oil from the unnecessary hydraulic pump in the fine operation range of the directional control valve, thereby reducing energy loss. It is an object of the present invention to provide a proportional control valve with pressure compensation that can reduce the amount of pressure.
以下本発明の実施例を図面に基づいて説明する。Embodiments of the present invention will be described below based on the drawings.
図中１は弁体であり、この弁体１内に圧力補償弁２と方
向制御弁３と２個のロードチェック弁４．５とシャトル
弁６とが組込まれている。In the figure, 1 is a valve body, and a pressure compensation valve 2, a directional control valve 3, two load check valves 4.5, and a shuttle valve 6 are built into this valve body 1.
上記方向制御弁３のスプール３ａが嵌挿される弁穴には
、軸方向中央に位置する入力ポードアと、これの両側に
位置するアクチェータボート８，９と、（らにその外側
に順次位置するパイロットボートｔｏ 、 ｔ ＋およ
びドレンボー塾１２．１３とが設けである。一方スプー
ル３には入力ボートフとこれの両側のアクチェータボー
）８．９との連通を遮断（中立時）、あるいはどちらか
一方を選択的に連通（操作時）する入力ランド１４．１
５と、この人力ランド１４゜凰５の輪方向外側に位置し
、スプール３が中立位置にあるときにはパイａットボー
ト１０．１１をドレンボート１２．１３に連通し、操作
位置のときに、操作側のアクチェータボートとパイ日ッ
トボートとを連通、他側のアクチェータボートドパイロ
ットポートとをドレンボートに連通させるドレン切換ラ
ンド１６．１７とが設けである。上記２個のパイロット
ボー） １０．ｌＪはシャトル弁６を介してパイロット
回路Ｉ８に接続しである。ｔた２個のアクチェータボー
ト８．９はブレードのチルトシリンダ１９０両側に接続
しである。The valve hole into which the spool 3a of the directional control valve 3 is fitted includes an input port door located at the center in the axial direction, actuator boats 8 and 9 located on both sides of the port door (and a pilot port located sequentially outside the input port door). On the other hand, the spool 3 is provided with the input boat and the actuator boats on both sides of it (actuator boats) 8.9. Input lands that selectively communicate (during operation) 14.1
5 and this manual land 14° is located on the outside in the ring direction of the spool 3, and when the spool 3 is in the neutral position, the pilot boat 10.11 is connected to the drain boat 12.13, and when the spool 3 is in the neutral position, it is connected to the drain boat 12.13. Drain switching lands 16 and 17 are provided for communicating the actuator boat on the other side with the piston boat and communicating the actuator boat and pilot port on the other side with the drain boat. above two pilot bows) 10. lJ is connected to pilot circuit I8 via shuttle valve 6. Two actuator boats 8.9 are connected to either side of the blade tilt cylinder 190.
弁体ＩＫは第１および第２ポンプボート２０゜２Ｉが設
けてあり、これの第１ポンプボー）２０１／−大容量の
油圧ポンプＰ、が、１ｌＥ２ポンプポート２１に小容量
の油圧ポンプＰ、が接続しである。そして第１ポンプボ
ート２０は１個の蘭−ドチェック弁４を介して方向制御
弁３の入力ポードアに連通し、ま穴第２ポンプポー）２
１は２個のロッドチェック弁４，５を介して上記入力ポ
ードアに連通するようになっている。The valve body IK is provided with first and second pump ports 20°2I, of which the first pump port 201/- is a large-capacity hydraulic pump P, and the small-capacity hydraulic pump P is connected to the 1lE2 pump port 21. It is connected. The first pump boat 20 communicates with the input port door of the directional control valve 3 through one land check valve 4, and the second pump port 2
1 communicates with the input port door through two rod check valves 4 and 5.
圧力補償弁２のスプール２αが嵌挿される弁穴にはｇ＋
ポンプポート２０に連通する第１ポー・ト２２と、第２
ポンプポート２１と連通する第２ポート２３と、ドレン
ボート２４．２５とパイロットボート２６とが設けであ
る。またこの弁穴の一側にはスプール２ａを一方へ付勢
するばね２フが内装してあう、とのばね２７が収納され
るばね室２８に上記パイロットボート２もが連通しであ
る。まｔ弁穴の他側には上記ばね２フに対向する圧力を
発生させる圧力室２９がスプール２αの端面に対向させ
て構成しである。The valve hole into which the spool 2α of the pressure compensation valve 2 is inserted has a g+
A first port 22 communicating with the pump port 20, and a second port 22 communicating with the pump port 20.
A second port 23 communicating with the pump port 21, a drain boat 24, 25, and a pilot boat 26 are provided. Further, the pilot boat 2 also communicates with a spring chamber 28 in which a spring 27 is housed, and a spring 2f for biasing the spool 2a in one direction is housed on one side of the valve hole. On the other side of the valve hole, a pressure chamber 29 that generates pressure opposing the spring 2 is configured to face the end surface of the spool 2α.
スプール２αには、これがばね２７にて付勢畜れ几とき
に第１ボート２２とドレンボート２４を遮断し、圧力室
２９の圧力にて逆方向に移動したときくこれを連通する
ｗＥ１ランド３ｏと、上記ばね２７の付勢力にてスプー
ル２ａが移動したときＫＩＩ２ボート２３とドレンポー
ト２５との連通を遮断する第２ツンド３１とが設けであ
る。ｉたこのスプール２αにはＩＥ１ボート２２と圧力
室２９とを常時連通ずる導通孔３２が設けである。上記
ばね室２ｇに連通ずるパイロットポート２６は上記シャ
トル弁６にパイロット回路１ｇを介して接続されている
。そしてこのパイロット回路＋ｇＫはＩＪ ＩＪ−フ弁
３３が接続しである。The spool 2α has a wE1 land 3o which is biased by a spring 27 and which shuts off the first boat 22 and the drain boat 24 when the spool 2α is moved, and communicates them when the spool 2α moves in the opposite direction due to the pressure of the pressure chamber 29. Also, a second tunnel 31 is provided which blocks communication between the KII2 boat 23 and the drain port 25 when the spool 2a is moved by the biasing force of the spring 27. The octopus spool 2α is provided with a communication hole 32 that constantly communicates the IE1 boat 22 and the pressure chamber 29. A pilot port 26 communicating with the spring chamber 2g is connected to the shuttle valve 6 via a pilot circuit 1g. This pilot circuit +gK is connected to the IJ-IJ- valve 33.
上記構成における作用を以下に説明する。The operation of the above configuration will be explained below.
（１） 中立時（第１図）
方向制御弁３を中立とじｔ状態で２個のポンプＰ＊ −
Ｐ−からそれぞれ圧油が弁体１の第１．第２ポート２０
．２１に流入すると、このとき方向制御弁３０入カポ−
ドアが閉じられていゐから、圧力補償弁２の第１．第２
ボート２２゜２３の圧力が上昇する。かくすると上記ｇ
＋ポつて圧力１１２９に作用する。そしてこの圧カ宸２
９の押圧力とばね２７による押しカとが釣り合った位置
でスプール２ｇが静止し、この状態で両ポート２２．２
３がドレンポート２４．２５に連通し、上記両ポンプＰ
、 、 Ｐ、からの圧油はドレンされる。なおこのとき
、ばね室２８もバイセットポート２６、°パイセット回
路１８、シャトル弁６、方向制御弁３を介してドレンさ
れている。(1) When in neutral (Fig. 1) With the direction control valve 3 closed in the neutral state, the two pumps P* -
Pressure oil is supplied from P- to the first P- of the valve body 1, respectively. 2nd port 20
．． 21, at this time, the directional control valve 30 input cap-
Since the door is closed, the first valve of the pressure compensation valve 2 is closed. Second
The pressure in boats 22 and 23 increases. Thus, the above g
+Pot acts on pressure 1129. And this pressure knife 2
The spool 2g comes to rest at a position where the pushing force of the spring 27 and the pushing force of the spring 27 are balanced, and in this state both ports 22.2
3 communicates with the drain ports 24 and 25, and both of the pumps P
The pressure oil from , , P is drained. At this time, the spring chamber 28 is also drained via the biset port 26, the pie set circuit 18, the shuttle valve 6, and the directional control valve 3.
（２） 微操作時（第２図）
方向制御弁３のスプール３を例えば左方へ移動すると、
まず左側のパイロットボードｌｏとドレンポー２トＩ２
との連通が遮断畜れ、その後左側のアクチェータボート
８とパイーットボー）ＩＱとが連通される。従ってアク
チェータであるチルトシリンダ＋９の負荷圧が圧力補償
弁２のばね室２８に導かれる。なおこのとき右側のパイ
ロットボード＋１はドレンポート１３に連通しているが
、シャトル弁６にょ夛こζから上記パイロット圧が逃げ
ることがない。ばね室２８に上記バイ誼ット圧が入ると
、このばね室２８の圧力が上昇し、圧力補償弁２のスプ
ール２１は圧力ｍ２？の圧力に抗して右方へ移動する。(2) During fine operation (Fig. 2) When the spool 3 of the directional control valve 3 is moved to the left, for example,
First, the left pilot board LO and drain port 2 I2
After that, communication between the left actuator boat 8 and the pilot boat IQ is established. Therefore, the load pressure of the tilt cylinder +9, which is an actuator, is guided to the spring chamber 28 of the pressure compensation valve 2. At this time, the pilot board +1 on the right side is in communication with the drain port 13, but the pilot pressure does not escape from the shuttle valve 6. When the above bias pressure enters the spring chamber 28, the pressure in the spring chamber 28 increases, and the spool 21 of the pressure compensating valve 2 reaches a pressure m2? move to the right against the pressure of
かくすると、圧力補償弁２の１１１．１１２ボート２２
．２３とドレンポート２４．２５との連通が遮断され第
１．第２ポー）２２．２３の圧力が上昇する。Thus, 111.112 boat 22 of pressure compensating valve 2
．． 23 and the drain ports 24 and 25 are cut off, and the first drain port 24. The pressure in the second port) 22.23 increases.
方向制御弁３のスプール３αをさらに左方へ移動すると
、左側の入力ランド＋４の切欠１４ｇが左側のアクチェ
ータポート８に連通し、入力ポードアの圧油はこの切欠
１１を通ってアクチェータボートδへ流れ始める。とこ
ろがこの連通関度は小さｂ九めＩＥＩ、第２ポー）２０
゜２１の圧力はさらに上昇し、第！ボー）２０の圧力は
圧力補償弁２の圧力室２９に作用され、この圧力室２９
の圧力が上昇する。従って圧力補償弁２のスプール２α
は上記ばね２７とばね室２８の圧力による押圧力に打勝
って圧力１１２９の圧力による押圧力によシ左方へ移動
される。When the spool 3α of the directional control valve 3 is further moved to the left, the notch 14g of the input land +4 on the left side communicates with the actuator port 8 on the left side, and the pressure oil from the input port door flows through this notch 11 to the actuator boat δ. start. However, this degree of interconnection is small b9 IEI, 2nd po) 20
The pressure at ゜21 rises further, and the pressure at ゜21 increases! The pressure of 20 is applied to the pressure chamber 29 of the pressure compensating valve 2, and this pressure chamber 29
pressure increases. Therefore, the spool 2α of the pressure compensation valve 2
is moved to the left by the pressing force of the pressure 1129, which overcomes the pressing force of the spring 27 and the spring chamber 28.
すると第２ポート２３とドレンポート２５とが徐々に開
き始め、第２ポンプＰ、からの圧油の一部はドレンされ
る。これによシ方向制御弁３の入力ポードアからアクチ
ェータボート８へ流出する流量は減少し、これの流路断
面積に合った流量となる。結局圧力補償弁２はアクチェ
ータボート８と第１ボート２ｏとの圧力差を一定に保つ
ととくなる。Then, the second port 23 and the drain port 25 begin to gradually open, and a portion of the pressure oil from the second pump P is drained. As a result, the flow rate flowing out from the input port door of the directional control valve 3 to the actuator boat 8 is reduced, and becomes a flow rate that matches the cross-sectional area of the flow path. In the end, the pressure compensating valve 2 maintains a constant pressure difference between the actuator boat 8 and the first boat 2o.
このことから入力ポードアから７クチエータボート８へ
の流量はポンプ吐出量、アクチェータの負荷圧に関係な
く入力ポードアかもアクチェータボート８への流量断面
積のみで定められる。Therefore, the flow rate from the input port door to the actuator boat 8 is determined only by the flow cross-sectional area from the input port door to the actuator boat 8, regardless of the pump discharge amount or the load pressure of the actuator.
従って方向制御弁３のスプール３ｅｇのストロ＝りと流
路断面積の関係と、圧力補償弁２のスプール２ＩＫのス
トロークと流路断面積を適切に定めてブルドーザ等の土
工機に使用し几場合、微操作時においては小容量の厘２
ポンプＰ、はアンロードされ、省エネを図れる。Therefore, when using an earth-moving machine such as a bulldozer, the relationship between the stroke length and the cross-sectional area of the flow path of the spool 3eg of the directional control valve 3, and the stroke and cross-sectional area of the flow path of the spool 2IK of the pressure compensation valve 2 are determined appropriately. , during fine operation, a small capacity 2
Pump P is unloaded to save energy.
（３） フルストローク時（！Ｅ３図）方向制御弁３
のスプール３ｔＬを左方へストロークエンドまで移動す
ると、入力ポードアと７クチ工−タボートｇとの流路断
面積が大きくなり、この部分を通過するときの流体圧力
損失が下がるため、１１１１ポート２２の圧力が低下し
、圧力補償弁２のスプール２αはばね２７により右方へ
押され、圧力補償弁２０両ドレンボート２４．２５が閉
じられ第１．第２ポンプ？ｔ −Ｐｔ双方の全流量がア
クチェータへ流れる。(3) At full stroke (!E3 diagram) Directional control valve 3
When the spool 3tL is moved to the left to the stroke end, the cross-sectional area of the flow path between the input port door and the 7-port port 22 increases, and the fluid pressure loss when passing through this part decreases. As the pressure decreases, the spool 2α of the pressure compensation valve 2 is pushed to the right by the spring 27, and both drain boats 24, 25 of the pressure compensation valve 20 are closed. Second pump? The entire flow of both t-Pt flows to the actuator.
（４） リリーフ時
方向制御弁３０操作時において、アクチェータＩ９がス
トロークエンドになったとき、ｔたは大きな外力を受は
次場合は、リリーフ弁３３の設定圧まで回路圧が上昇す
るが、それ以上になるとリリーフ弁３３がリリーフし始
める。すると、圧力補償弁２のばね室２７の圧力と圧力
室２９の圧力のバランスがくずれ、ばね室２７内の圧力
が低くなるから、スプール２ａは圧力室２９の圧力によ
り左方へ移動され、ＩＩＩ、第２ボート２２．２３がド
レンボート２４．２５に連通し、油圧回路の過剰圧力発
生が防止される。(4) During relief When the directional control valve 30 is operated, when the actuator I9 reaches the stroke end, the circuit pressure will rise to the set pressure of the relief valve 33 in the following cases. When the temperature exceeds that level, the relief valve 33 starts to relieve. Then, the balance between the pressure in the spring chamber 27 and the pressure in the pressure chamber 29 of the pressure compensating valve 2 is disrupted, and the pressure in the spring chamber 27 becomes low, so the spool 2a is moved to the left by the pressure in the pressure chamber 29. , the second boat 22.23 communicates with the drain boat 24.25 to prevent excessive pressure from occurring in the hydraulic circuit.
なお上鮎実施例において、纂２ポンプＰ、と第２ポンプ
ポート２１と０間の回路に他の操作弁３４を介装する。In the Kamiayu embodiment, another operating valve 34 is interposed in the circuit between the second pump P and the second pump port 21 and 0.
ｔた方向制御弁３のスプール３！に設ケアｈドレン切換
ランド１６．１７には、スプール３ａを微操作し九とき
において、アクチェータボートｇ、９とパイはットポー
ト＋ｏ、＋ｌ：カＩＥ々に連通するよう切欠１６α、１
７αが設けである。Spool 3 of directional control valve 3! In the care h drain switching lands 16 and 17, when the spool 3a is slightly operated, notches 16α and 1 are formed so that the actuator boats g and 9 and the actuator boats are connected to the bottom ports +o and +l.
7α is provided.
本発明は以上のようになり、入力ポードアと、チルトシ
リンダ等のアクチェータに連通するアクチェータボート
８，９と、ドレンボート１２゜１３とパイロットボート
１０，１１を有する弁穴に、移動することにより上記ア
クチェータボートε、９が入力ポードアあるいはアクチ
ェータボート８．９に選択的に連通し、またこのとき入
力ポードアに連通するアクチェータボートに上記パイロ
ットボートを連通ずるスプール３ａを嵌挿し穴方向制御
弁３と、第１．第２ボート２２．２３と、ドレンボート
２４．２５と、ばね２７が内装され、かつパイロットボ
ート２６を有して一側部に設は次ばね室２８と、他側部
に設けた圧力１１２９を有する弁穴に、ばねｊ１２１１
に発生する押し力にて移動し友ときに第１ポート２２、
第２ポート２３とドレンボート２４゜２５との連通を順
次遮断するランド３０．３１と、第１ボート２２と圧力
室２９とを連通する導通孔３２を有するスプール２ａを
嵌挿し次圧力補償弁２とからなシ、上記方向制御弁３と
圧力補償弁２の両パイロットボート１０，１１゜２６を
接続し、また方向制御弁３の入力ボートフと圧力補償弁
の第１ボー）２２に連通する第１ポンプポート２０と、
上記入力ポードアと第２ボート２３に連通する第２ボｙ
プポート２畠とを設けて圧力補償付比例制御弁を構成し
たから、ＩＩＥＩポンプボート２０とｇｇ２ポンプポー
ト２１Ｋそれぞれ油圧ポンプｐ、 、 ｐ、を接続しｆ
Ｉ−１ポンプシステムにおいて、方向制御弁３を微操作
間ｉ！ｉにおいて、１個のポンプ吐出量でたりる場合に
は他方の油圧ポンプからの圧油は圧力補償弁２よりアノ
ロードされ、このアノロードされた方の油圧ポンプの駆
動力が小さくなり、エネルギカスを少なくすることがで
きる。The present invention is as described above, and by moving to a valve hole having an input port door, actuator boats 8 and 9 communicating with an actuator such as a tilt cylinder, a drain boat 12 and a pilot boat 10 and 11. The actuator boat ε, 9 selectively communicates with the input port door or the actuator boat 8.9, and at this time, a spool 3a that communicates the pilot boat with the actuator boat communicating with the input port door is fitted into the hole directional control valve 3, 1st. A second boat 22, 23, a drain boat 24, 25, and a spring 27 are installed inside, and it has a pilot boat 26 installed on one side, and a spring chamber 28 and a pressure 1129 installed on the other side. Spring j1211 in the valve hole with
When the first port 22 is moved by the pushing force generated by the
A spool 2a having a land 30.31 that sequentially blocks communication between the second port 23 and the drain boat 24, 25, and a communication hole 32 that communicates the first boat 22 and the pressure chamber 29 is fitted into the spool 2a. In addition, the pilot boats 10 and 11 of the directional control valve 3 and the pressure compensation valve 2 are connected, and the input boat of the directional control valve 3 and the first boat 22 of the pressure compensation valve are connected to each other. 1 pump port 20,
A second port communicating with the input port door and the second boat 23
Since a proportional control valve with pressure compensation has been constructed by providing port 2 and port 2, connect hydraulic pumps p, p, p, respectively to IIEI pump port 20 and gg2 pump port 21K.
In the I-1 pump system, the directional control valve 3 is finely operated during i! In case i, when the discharge amount of one pump is sufficient, the pressure oil from the other hydraulic pump is anoroded by the pressure compensating valve 2, and the driving force of the anorodized hydraulic pump becomes smaller, reducing the energy consumption. It can be reduced.
図面は本発明の実施例を示すもので、第１図は中立時、
ｓ［２図は微操作時、第３図はフルストローク時のそれ
ぞれの操作状態を示す断面図である。
２は圧力補償弁、３は方向制御弁、２６゜３αはスプー
ル、７は入カポ−）、ｇ、９はアクチェータボート、＋
０．１１．２６はパイロットボート、ｇ２．１３．２４
．２５はドレンボート、２０．２１はポンプポート、２
２゜２３は第１．第２ポート、２−７はばね、２８はば
ね室、２９は圧力室、３０．３１はランド、３２は導通
孔。The drawings show an embodiment of the present invention, and FIG. 1 shows the neutral state,
s [Figure 2 is a cross-sectional view showing the operation state during fine operation, and Figure 3 is a sectional view showing the operation state during full stroke. 2 is a pressure compensation valve, 3 is a directional control valve, 26゜3α is a spool, 7 is an input capo), g, 9 is an actuator boat, +
0.11.26 is a pilot boat, g2.13.24
．． 25 is the drain boat, 20.21 is the pump port, 2
2°23 is the first. The second port, 2-7 is a spring, 28 is a spring chamber, 29 is a pressure chamber, 30.31 is a land, and 32 is a conduction hole.
Claims (1)
連通ずるアクチェータボート８．９と、ドレンボート１
２．１３とパイロットボート１０゜１１を有する弁穴に
１移動することによシ上記アクチェータボート８＃９が
入力ポードアあるいはアクチェータボート８．９に選択
的に連通し、まｔこのとき入力ポードアに連通するアク
チェータボートに上記パイロットボートを連通するスプ
ール３αを嵌挿した方向制御弁３と、第鼻、ＩＥ２ボー
ト２２．２３と、ドレンボート２４．２５とげね２７が
内装され、かつパイロットボート２６を有して一側部に
設は次ばね室２８と、他側部に設けた圧力室２９とを有
する弁穴に、ばね室２８に発生する押し力にて移動した
ときにＩＥＩポート２２．第２ボート２３とドレンポー
）２４．２５との連通を順次遮断するランド３０．３１
と、１ｌｉｌボート２２と圧力室２９とを連通ずる導通
孔３２を有するススール２αを嵌挿した圧力補償弁２と
からなり、上記方向制御弁３と圧力補償弁２の両パイロ
ットポートＩＯ，１１，２６を接続−し、また方向制御
弁３の入力ポードアと圧力補償弁の填１ボート２２に連
通する第１ポンプボート２０１！：、上記入力ポードア
と第２ボート２３に連通ずる第２ポンプポート２１とを
設けてなることを特徴とする圧力補償付比例制御弁。An input boat 7, an actuator boat 8.9 connected to an actuator such as a tilt cylinder, and a drain boat 1.
2.13 and the pilot boat 10°11, the actuator boat 8#9 selectively communicates with the input port door or the actuator boat 8.9; A directional control valve 3 in which a spool 3α that communicates with the pilot boat is inserted into an actuator boat that communicates with the pilot boat, a nostril, an IE2 boat 22, 23, a drain boat 24, 25, and a thorn 27 are installed inside, and the pilot boat 26 is connected to the pilot boat 26. When moved by the pushing force generated in the spring chamber 28, the IEI port 22. Land 30.31 that sequentially blocks communication between the second boat 23 and drain port 24.25
and a pressure compensating valve 2 fitted with a suture 2α having a conduction hole 32 that communicates between the 1lil boat 22 and the pressure chamber 29, and both pilot ports IO, 11, and 2 of the directional control valve 3 and pressure compensating valve 2 26 and also communicates with the input port door of the directional control valve 3 and the filler boat 22 of the pressure compensation valve! A proportional control valve with pressure compensation, characterized in that a second pump port 21 is provided which communicates with the input port door and the second boat 23.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18695081A JPS5891903A (en) | 1981-11-24 | 1981-11-24 | Proportional control valve with pressure compensation |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18695081A JPS5891903A (en) | 1981-11-24 | 1981-11-24 | Proportional control valve with pressure compensation |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5891903A true JPS5891903A (en) | 1983-06-01 |
| JPH0250323B2 JPH0250323B2 (en) | 1990-11-02 |
Family
ID=16197556
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP18695081A Granted JPS5891903A (en) | 1981-11-24 | 1981-11-24 | Proportional control valve with pressure compensation |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5891903A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60129501U (en) * | 1984-02-10 | 1985-08-30 | 株式会社小松製作所 | Proportional control valve with pressure compensation |
| JP2014159864A (en) * | 2013-02-21 | 2014-09-04 | Toshiba Mach Co Ltd | Hydraulic controller and construction machine mounting the hydraulic controller thereon |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS54136493U (en) * | 1978-03-15 | 1979-09-21 |
-
1981
- 1981-11-24 JP JP18695081A patent/JPS5891903A/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS54136493U (en) * | 1978-03-15 | 1979-09-21 |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60129501U (en) * | 1984-02-10 | 1985-08-30 | 株式会社小松製作所 | Proportional control valve with pressure compensation |
| JP2014159864A (en) * | 2013-02-21 | 2014-09-04 | Toshiba Mach Co Ltd | Hydraulic controller and construction machine mounting the hydraulic controller thereon |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0250323B2 (en) | 1990-11-02 |
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