JPH08277806A - Hydraulic controlling valve - Google Patents
Hydraulic controlling valveInfo
- Publication number
- JPH08277806A JPH08277806A JP10699895A JP10699895A JPH08277806A JP H08277806 A JPH08277806 A JP H08277806A JP 10699895 A JP10699895 A JP 10699895A JP 10699895 A JP10699895 A JP 10699895A JP H08277806 A JPH08277806 A JP H08277806A
- Authority
- JP
- Japan
- Prior art keywords
- valve
- pressure
- port
- oil
- spool
- 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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Operation Control Of Excavators (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明はモータグレーダ、高所作
業用車両、油圧クレーン等の産業車両に適用される油圧
制御弁に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic control valve applied to an industrial vehicle such as a motor grader, an aerial work vehicle and a hydraulic crane.
【０００２】[0002]
【従来の技術】油圧アクチュエータへの圧油の切換えと
ともに圧油流量の制御を行う油圧制御弁は従来から存在
した。しかし負荷の大小によって制御流量が変動し結果
的にアクチュエータの位置や作動速度の制御がやりにく
いという欠点があった。2. Description of the Related Art There has been a hydraulic control valve for controlling the flow rate of pressure oil as well as switching the pressure oil to a hydraulic actuator. However, the control flow rate fluctuates depending on the size of the load, and as a result it is difficult to control the position and operating speed of the actuator.
【０００３】[0003]
【発明が解決しようとする課題】又１個の油圧源で複数
のアクチュエータを同時に作動させる場合従来では負荷
圧力が小さいアクチュエータが先に作動してしまい同時
操作が不可能である。このためオペレータは負荷の小さ
い方の流量制御弁を絞りぎみにし又は負荷の大きい方を
開き気味にして同時操作可能な両アクチュエータへの制
御を行わねばならずオペレータにとっては大きな負担で
あった。又これらをさけるべく同時操作の必要なアクチ
ュエータにそれぞれ独立した油圧源を複数装備する方式
もあるが非常にコスト高となってしまうという欠点があ
った。In the case of simultaneously operating a plurality of actuators with a single hydraulic pressure source, the actuator with a small load pressure is operated first, and simultaneous operation is impossible. For this reason, the operator must control the two actuators that can be operated simultaneously by squeezing the flow control valve with the smaller load or opening the one with the larger load, which is a heavy burden on the operator. There is also a system in which a plurality of independent hydraulic power sources are provided for the actuators that need to be operated simultaneously to avoid them, but there is a drawback that the cost becomes very high.
【０００４】本発明の目的は切換弁であって、流量制御
機能をそなえた制御弁において、負荷の大小や負荷の種
類（すなわちメータインあるいはメータアウトの流量制
御）に影響されずに弁開度に応じた一定流量の制御特性
を有し且負荷の異る複数の油圧アクチュエータを同時に
操作する場合にただ一つの油圧源にて可能な油圧制御弁
を提供するにある。An object of the present invention is a switching valve, and in a control valve having a flow rate control function, the valve opening is controlled without being influenced by the magnitude of load or the type of load (that is, meter-in or meter-out flow rate control). An object of the present invention is to provide a hydraulic control valve having a constant flow rate control characteristic and capable of operating a plurality of hydraulic actuators having different loads at the same time with only one hydraulic source.
【０００５】[0005]
【課題を解決するための手段】本発明の油圧制御弁は、
油圧受入ポート３とドレンポート７と２対のシリンダポ
ート２０，２１，２２，２３を有するバルブの本体２
と、前記バルブの本体に設けられた４個の油ポート２−
１，２−２，２−３，２７を有するＡ穴と、前記Ａ穴に
嵌合し且５個の溝９−５，９−４，９−３，９−２，９
−１とメータリングノッチ９−１０と４個の油穴９−
６，９−７，９−９，９−８を有する油路切換用と流量
制御用Ａスプール弁９と、前記バルブの本体に前記Ａ穴
と同様に設けられた４個の油ポート２−５，２−６，２
−７，２８を有するＢ穴と、前記Ｂ穴と嵌合し５個の溝
１０−５，１０−４，１０−３，１０−２，１０−１と
メータリングノッチ１０−１０と４個の油穴１０−６，
１０−７，１０−８，１０−９を有する油路切換用と流
量制御用のＢスプール弁１０と、前記Ａスプール弁の上
流に設けられた圧力補償弁１１と、ブリードオフ弁６
と、前記Ｂスプール弁１０の上流に設けられ前記ブリー
ドオフ弁６に通ずる圧力補償弁１２と、前記Ａスプール
弁の下流に設けられたカウンタバランス機能を有する弁
１２，１３と、前記Ｂスプール弁の下流に設けられたカ
ウンタバランス機能を有する弁１４，１５とを有してな
ることを特徴としている。The hydraulic control valve of the present invention comprises:
A valve body 2 having a hydraulic pressure receiving port 3, a drain port 7 and two pairs of cylinder ports 20, 21, 22, 23.
And the four oil ports provided on the valve body 2-
A hole having 1,2-2,2-3,27 and five grooves 9-5,9-4,9-3,9-2,9 fitted in the A hole.
-1, metering notch 9-10 and 4 oil holes 9-
6, 9-7, 9-9, 9-8 oil passage switching and flow rate control A spool valve 9, and four oil ports 2 provided in the main body of the valve in the same manner as the A hole 2 5,2-6,2
B hole having -7, 28, 5 grooves 10-5, 10-4, 10-3, 10-2, 10-1 fitted with the B hole, and metering notch 10-10 and 4 holes Oil hole 10-6
B spool valve 10 for oil passage switching and flow control having 10-7, 10-8, 10-9, pressure compensation valve 11 provided upstream of the A spool valve, and bleed-off valve 6
A pressure compensating valve 12 provided upstream of the B spool valve 10 and communicating with the bleed-off valve 6, valves 12 and 13 having a counter balance function provided downstream of the A spool valve, and the B spool valve. It is characterized in that it has valves 14 and 15 having a counter balance function provided downstream thereof.
【０００６】[0006]
【作用】Ａスプール弁、Ｂスプール弁各のメータリング
ノッチで制御される流量Ｑはメータリングノッチの開口
面積をＡ、その上下の圧力差をΔＰとするとＱ＝ＣＡ√
ΔＰである。Ｃは流量係数である。作業時に刻々と変化
する負荷圧力変動に対し前記ΔＰが一定になるようにブ
リードオフ弁と圧力補償弁が作用する。The flow rate Q controlled by the metering notches of the A spool valve and the B spool valve is Q = CA√, where A is the opening area of the metering notch and ΔP is the pressure difference above and below it.
ΔP. C is a flow coefficient. The bleed-off valve and the pressure compensating valve act so that the ΔP becomes constant with respect to the load pressure fluctuation which changes every moment during work.
【０００７】圧力補償弁は通常ある都合の良い開口面積
で上流側に開弁して居り、この弁のスプリング室に前記
メータリングノッチの上流側圧力（つまり負荷圧力）を
導き、圧力補償弁の端部に作用させその圧力が高くなっ
たときは、それに応じて前記開口面積を拡げ、低くなっ
たときは狭くするように働き圧力補償を行って前記ΔＰ
を一定に保つ。The pressure compensating valve normally opens upstream with some convenient opening area and directs the pressure upstream of the metering notch (ie the load pressure) into the spring chamber of this valve to allow When the pressure is applied to the end portion and the pressure becomes high, the opening area is expanded accordingly, and when it becomes low, the opening area is narrowed to perform pressure compensation, and the ΔP
Keep constant.
【０００８】ブリードオフ弁はそのスプリングのある端
部に前記と同じ負荷圧力を導き、負荷圧力が高くなった
ときは前記スプリングの力に圧力による力を加算して開
口部を狭くする方向に動かし上流側の圧力を上昇させ
る。この圧力をブリードオフ弁の前記と反対側に働かせ
ることで前記負荷圧力に対してＰ＝Ｗ／Ａ′だけ高く一
定に制御され負荷変動に対して圧力補償される。Ｗはス
プリング力、Ａ′は受圧面積である。The bleed-off valve guides the same load pressure to the end portion of the spring, and when the load pressure becomes high, the force due to the pressure is added to the force of the spring to move the valve in a direction to narrow the opening. Increase the upstream pressure. By applying this pressure to the opposite side of the bleed-off valve, P = W / A 'is controlled to be constant higher than the load pressure, and the pressure fluctuation is compensated for. W is the spring force and A'is the pressure receiving area.
【０００９】又外力が作用しているアクチュエータでそ
の外力の方向に作動させる場合、通常油圧のもどり側つ
まりメータアウトの流量制御をしなければならずその場
合前記圧力補償機構は作動不可能である。この条件下で
も圧力補償可能とするため切換と流量制御用Ａスプール
弁、Ｂスプール弁各とアクチュエータ間にカウンタバラ
ンス機能をもった弁が設けられている。この弁は供給側
圧力をもって戻り側弁に受圧させ開弁させることによ
り、戻り側流量を供給側圧力によって制御可能とさせメ
ータアウトの流量制御の場合でも圧力補償を可能とし
た。Further, when actuating in the direction of the external force by an actuator acting on the external force, the return side of the hydraulic pressure, that is, the meter-out flow rate must be controlled, in which case the pressure compensating mechanism cannot operate. . In order to enable pressure compensation even under this condition, a valve having a counter balance function is provided between each of the A spool valve for switching and the flow rate control, the B spool valve and the actuator. This valve receives the pressure on the supply side and opens it by receiving the pressure on the return side, so that the flow rate on the return side can be controlled by the pressure on the supply side, and pressure compensation is possible even in the case of meter-out flow rate control.
【００１０】負荷圧力の異る複数のアクチュエータを同
時に作動させたとき各に設けられたシャトル弁により常
に最も高い負荷圧力が選択され前記ブリードオフ弁に作
用させられることにより複数のアクチュエータを同時に
作動可能とした。When a plurality of actuators having different load pressures are simultaneously actuated, the highest load pressure is always selected by the shuttle valve provided for each actuator and acted on the bleed-off valve, so that the plurality of actuators can be actuated simultaneously. And
【００１１】[0011]
【実施例】本発明に係る第１実施例を図１〜４によって
説明する。図１は本発明に係る第１実施例の２連仕様の
油圧制御弁の中立状態の断面図、図２は図１に示す油圧
制御弁の１つのスプール弁を操作した状態の断面図、図
３は図１に示す油圧制御弁の１つのスプール弁を図２と
逆方向に操作した状態の断面図、図４は図１に示した油
圧制御弁の２つのスプール弁を同時に操作した状態の断
面図である。図１において、油圧制御弁１の本体２に油
圧源５０からの圧油受入れポート３が設けられて居り油
路４を経てブリードオフ弁６を具えた圧力ポート８が設
けられ油は前記ブリードオフ弁の圧力制御用ノッチ６−
１を経てドレンポート７からタンク８０へドレンされて
いる。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment according to the present invention will be described with reference to FIGS. FIG. 1 is a sectional view of a hydraulic control valve of a double specification according to a first embodiment of the present invention in a neutral state, and FIG. 2 is a sectional view of a state in which one spool valve of the hydraulic control valve shown in FIG. 1 is operated, 3 is a cross-sectional view of a state where one spool valve of the hydraulic control valve shown in FIG. 1 is operated in the opposite direction to that of FIG. 2, and FIG. 4 is a state where two spool valves of the hydraulic control valve shown in FIG. 1 are operated simultaneously. FIG. In FIG. 1, a main body 2 of the hydraulic control valve 1 is provided with a pressure oil receiving port 3 from a hydraulic pressure source 50, and a pressure port 8 having a bleed-off valve 6 is provided via an oil passage 4, and the oil is bleed-off as described above. Notch for valve pressure control 6-
It is drained from the drain port 7 to the tank 80 via 1.
【００１２】圧力ポート８には油路切換用と流量制御用
の本体２のＡ穴に嵌合するＡスプール弁９への油圧を制
御するＡ圧力補償弁１１と本体２のＢ穴に嵌合するＢス
プール弁への油圧を制御するＢ圧力補償弁９０が設けら
れ、前記Ａスプール弁の下流にはカウンタバランス弁１
２，１３が設けられ、カウンタバランス弁１２はチェッ
ク弁１６を介してタンクポート２０に、カウンタバラン
ス弁１３はチェック弁１７を介してシリンダポート２１
に通じる。前記Ｂスプール弁の下流にはカウンタバラン
ス弁１４，１５が設けられ、カウンタバランス弁１４は
チェック弁１８を経てシリンダポート２２へ通じカウン
タバランス弁１５はチェック弁１９を経てシリンダポー
ト２３に通じている。シリンダポート２０とシリンダポ
ート２１にアクチュエータ６０が、シリンダポート２２
とシリンダポート２３にアクチュエータ７０が接続され
ている。The pressure port 8 is fitted in the A hole of the main body 2 and the A pressure compensating valve 11 for controlling the hydraulic pressure to the A spool valve 9 which is fitted in the A hole of the main body 2 for oil passage switching and flow rate control. A B pressure compensating valve 90 for controlling the hydraulic pressure to the B spool valve is provided, and the counter balance valve 1 is provided downstream of the A spool valve.
2 and 13 are provided, the counterbalance valve 12 is connected to the tank port 20 via the check valve 16, and the counterbalance valve 13 is connected to the cylinder port 21 via the check valve 17.
Lead to Counter balance valves 14 and 15 are provided downstream of the B spool valve. The counter balance valve 14 communicates with a cylinder port 22 via a check valve 18 and the counter balance valve 15 communicates with a cylinder port 23 via a check valve 19. . The actuator 60 is attached to the cylinder port 20 and the cylinder port 21, and the cylinder port 22
The actuator 70 is connected to the cylinder port 23.
【００１３】前記第１実施例の作用を説明する。図１に
示す中立状態において、圧力ポート８の油圧はブリード
オフ弁６の一端に設けられたスプリング２４の荷重とス
プリング２４の設けられている室３４の圧力と対向する
油穴６−２と室６２による圧力とで決定され通常は低圧
力に設定されている。Ａ圧力補償弁１１に設けられたス
プリング２５のある室２７はＡスプール弁９の溝９−１
によりタンクポート２９へ、又Ｂ圧力補償１２に設けら
れたスプリング２６のある室２８はＢスプール弁１０の
溝１０−１によりタンクポート３０に開放されともにド
レンポート７に通じている。室２７はシャトル弁３１を
介して油路３３に導通し、室２８はシャトル弁３２を介
して油路３３に通じている。シャトル弁３１の一方は前
記ブリードオフ弁のスプリングのある室３４に通じてい
る。The operation of the first embodiment will be described. In the neutral state shown in FIG. 1, the oil pressure of the pressure port 8 is the load of the spring 24 provided at one end of the bleed-off valve 6 and the pressure of the chamber 34 in which the spring 24 is provided, and the oil hole 6-2 and the chamber facing each other. It is determined by the pressure of 62 and is usually set to a low pressure. The chamber 27 having the spring 25 provided in the A pressure compensating valve 11 is provided with the groove 9-1 of the A spool valve 9.
To the tank port 29, and the chamber 28 provided with the spring 26 provided in the B pressure compensation 12 is opened to the tank port 30 by the groove 10-1 of the B spool valve 10 and communicates with the drain port 7. The chamber 27 communicates with the oil passage 33 via the shuttle valve 31, and the chamber 28 communicates with the oil passage 33 via the shuttle valve 32. One of the shuttle valves 31 communicates with the spring chamber 34 of the bleed-off valve.
【００１４】図２にＡスプール弁９を矢印３５の方向に
操作してアクチュエータ６０を矢印３６方向に作動さ
せ、Ｂスプール弁１０は操作しない場合を示す。油圧源
５０から送られた圧油は圧油受入ポート３から入り油路
４を通り圧力ポート８に達しブリードオフ弁６で圧力を
制御されＡ圧力補償弁１１の制御穴１１−１を通りチェ
ック弁３７を開いてポート２−２に達しＡスプール弁９
の溝９−４を介してメータリングノッチ９−１０により
制御されポート２−３を通って室３８に至りチェック弁
１７を通りシリンダポート２１からアクチュエータ６０
へ流れアクチュエータ６０は矢印３６の方向へ動き仕事
が行われる。FIG. 2 shows a case where the A spool valve 9 is operated in the direction of arrow 35 to operate the actuator 60 in the direction of arrow 36, and the B spool valve 10 is not operated. The pressure oil sent from the hydraulic pressure source 50 passes through the pressure oil receiving port 3 and the oil passage 4 to reach the pressure port 8. The pressure is controlled by the bleed-off valve 6, and the pressure oil is passed through the control hole 11-1 of the pressure compensating valve 11 for checking. Open valve 37 and reach port 2-2 to reach spool valve 9
Controlled by the metering notch 9-10 through the groove 9-4, through the port 2-3 to the chamber 38, through the check valve 17 and the cylinder port 21 to the actuator 60.
The flow actuator 60 moves in the direction of arrow 36 to perform work.
【００１５】ポート２−３の負荷圧力はＡスプール弁９
の油穴９−７，９−９，９−８を経てポート２７に通じ
Ａ圧力補償弁１１のスプリング２５の作用と同じ方向に
作用し、この２つの力の合力とＡ圧力補償弁１１に働く
チェック弁３７側の圧力が釣合っている。このときポー
ト３９側の圧力とポート２−３側の圧力との差はメータ
リングノッチ９−１０をはさんで一定に制御される。こ
れは負荷圧力、ポート２−３の圧力が上昇するとこの圧
力はＡ圧力補償弁１１に及び制御穴１１−１を開き側に
制御し前記圧力の差は一定に保たれる。The load pressure of the port 2-3 is the A spool valve 9
Through the oil holes 9-7, 9-9, 9-8 of No. 2 and the port 27, and acts in the same direction as the action of the spring 25 of the A pressure compensation valve 11, and the resultant force of these two forces and the A pressure compensation valve 11 The pressure on the working check valve 37 side is balanced. At this time, the difference between the pressure on the port 39 side and the pressure on the port 2-3 side is controlled to be constant across the metering notch 9-10. This is because when the load pressure and the pressure at the ports 2-3 rise, this pressure is controlled to the A pressure compensating valve 11 and the control hole 11-1 to the opening side, and the pressure difference is kept constant.
【００１６】前記負荷圧力が下った場合は前記と逆に制
御される。前記のようにＡ圧力補償弁１１はＡスプール
弁９のメータリングノッチ９−１０前後の圧力差を一定
に制御しているためメータリングノッチ９−１０におけ
る開口面積が変らないかぎり流量一定に制御される前記
開口面積はＡスプール弁９のストロークが変らないかぎ
り変らない。ポート２７の圧力は一方ではシャトル弁３
１を押し上げてブリードオフ弁６のスプリング２４の設
けられている室３４に通じスプリング２４の力に力を加
算しているため圧力ポート８の圧力はスプリング２４の
力とポート６−２側の受圧面積から決定される圧力だけ
前記負荷圧力より高く設定される。When the load pressure drops, the control is reversed. As described above, since the A pressure compensating valve 11 controls the pressure difference around the metering notch 9-10 of the A spool valve 9 to be constant, the flow rate is controlled to be constant unless the opening area of the metering notch 9-10 is changed. The above-mentioned opening area does not change unless the stroke of the A spool valve 9 changes. On the other hand, the pressure at port 27 is the shuttle valve 3
1 is pushed up to communicate with the chamber 34 in which the spring 24 of the bleed-off valve 6 is provided, and the force is added to the force of the spring 24. Therefore, the pressure of the pressure port 8 is the force of the spring 24 and the pressure received on the port 6-2 side. It is set higher than the load pressure by a pressure determined from the area.
【００１７】このとき油圧源５０から送られる流量に対
してアクチュエータ６０へ流れこむ流量が少いときはそ
の差分はブリードオフ弁６からタンク８０へドレンされ
ている。アクチュエータ６０からのもどり油の流れを説
明する。供給側のポート３８の圧油はカウンタバランス
弁１３の油路１３−１を通ってカウンタバランス弁１２
の端部に作用しボール弁１２−２が油路１２−１を閉じ
る。このためカウンタバランス弁１２はスプリング１２
−３に対向した圧力を受けバルブ開口部１２−４が開く
方向にスプリング１２−３をたわませながら移動するAt this time, when the flow rate flowing into the actuator 60 is smaller than the flow rate sent from the hydraulic power source 50, the difference is drained from the bleed-off valve 6 to the tank 80. The flow of return oil from the actuator 60 will be described. The pressure oil in the supply-side port 38 passes through the oil passage 13-1 of the counterbalance valve 13 and the counterbalance valve 12
And the ball valve 12-2 closes the oil passage 12-1. For this reason, the counter balance valve 12 has a spring 12
-3 is moved by bending the spring 12-3 in the direction in which the valve opening 12-4 opens by receiving the pressure opposite to -3.
【００１８】Ａスプール弁９は既に矢印３５方向へ操作
されているため溝９−５の働きによりポート２−１とタ
ンクポート２９が通じている。よってアクチュエータ６
０からのもどり油はシリンダポート２０から油圧制御弁
１内へ入りバルブ開口部１２−４を通ってポート２−
１、タンクポート２９を経てドレンポート７からタンク
８０へドレンされる。Since the A spool valve 9 has already been operated in the direction of arrow 35, the port 2-1 and the tank port 29 communicate with each other by the action of the groove 9-5. Therefore, actuator 6
Return oil from 0 enters the hydraulic control valve 1 from the cylinder port 20 and passes through the valve opening 12-4 to the port 2-.
1. Drain from the drain port 7 to the tank 80 via the tank port 29.
【００１９】このとき例えばアクチュエータ６０に矢印
３６方向に外力が作用しているとシリンダポート２１か
らの供給油量に対してアクチュエータ６０が矢印３６の
方向に先走りしようとする。この瞬間供給側のポート３
８の圧力が下がろうとして前記カウンタバランス弁１２
がもどされバルブ開口部１２−４が絞られる。このこと
により前記先走りが制動されることになる。よって外力
と同じ方向へのアクチュエータの作動においても供給側
の制御にて実施できる構成となっている。At this time, for example, if an external force acts on the actuator 60 in the direction of arrow 36, the actuator 60 attempts to move ahead in the direction of arrow 36 with respect to the amount of oil supplied from the cylinder port 21. Port 3 on the supply side at this moment
The counterbalance valve 12 tries to reduce the pressure of 8
The valve opening 12-4 is squeezed and the valve opening 12-4 is squeezed. As a result, the preceding run is braked. Therefore, even when the actuator is actuated in the same direction as the external force, it can be controlled by the supply side.
【００２０】図３はＡスプール弁９を矢印４１の方向へ
操作した図で前記図２に示す操作と逆方向に操作したも
のであって圧油の流れ、弁類の作用は全く同様に構成さ
れている。油圧源５０からの圧油はブリードオフ弁６に
より制御され、さらにＡ圧力補償弁１１によりＡスプー
ル弁９のメータリングノッチ９−１０の上下の圧力差を
一定に制御されシリンダポート２０からアクチュエータ
６０へ流れ矢印４２の方向へ作動して仕事をしもどり油
はシリンダポート２１からカウンタバランス弁１３のバ
ルブ開口部１３−２を通りＡスプール弁９の溝によりタ
ンクポート２９へ流れドレンポート７からタンク８０へ
ドレンされる。FIG. 3 shows the A spool valve 9 operated in the direction of arrow 41, which is operated in the opposite direction to the operation shown in FIG. 2, and the flow of pressure oil and the operation of the valves are exactly the same. Has been done. The pressure oil from the hydraulic pressure source 50 is controlled by the bleed-off valve 6, and further, the pressure difference between the upper and lower sides of the metering notch 9-10 of the A spool valve 9 is controlled to be constant by the A pressure compensating valve 11 and the actuator 60 is operated from the cylinder port 20. The oil returns from the cylinder port 21 to the tank port 29 through the valve opening 13-2 of the counterbalance valve 13 to the tank port 29 by the groove of the A spool valve 9 from the drain port 7 to the tank. It is drained to 80.
【００２１】図４はＡスプール弁９を矢印４３方向へ、
同時にＢスプール弁１０を矢印４４方向へ操作しアクチ
ュエータ６０を矢印４５方向へ、アクチュエータ７０を
矢印４６方向へ作動させている状態を示す。アクチュエ
ータ６０の負荷がアクチュエータ７０の負荷に比べて十
分に大きい場合通常油圧源５０から送られる圧油はアク
チュエータ７０側の負荷によって決定される。このため
負荷圧力の高いアクチュエータ６０へは流れない。これ
を防止して負荷の異るアクチュエータを同時に作動させ
るために設けられているのがシャトル弁回路である。ア
クチュエータ７０側の負荷圧力はシャトル弁３２を押し
上げて油路４７に及びシャトル弁３１に作用している。
同時にアクチュエータ６０側の負荷圧力はシャトル弁３
１の他の入口に作用して居りこちらの方の圧力の方が高
いのでこの方の圧力がシャトル弁３１を通りブリードオ
フ弁６のスプリング２４のある室３４に作用する。FIG. 4 shows the A spool valve 9 in the direction of arrow 43,
At the same time, the B spool valve 10 is operated in the direction of arrow 44 to operate the actuator 60 in the direction of arrow 45 and the actuator 70 in the direction of arrow 46. When the load on the actuator 60 is sufficiently larger than the load on the actuator 70, the pressure oil normally sent from the hydraulic pressure source 50 is determined by the load on the actuator 70 side. Therefore, it does not flow to the actuator 60 having a high load pressure. A shuttle valve circuit is provided to prevent this and to simultaneously operate actuators having different loads. The load pressure on the actuator 70 side pushes up the shuttle valve 32 and acts on the oil passage 47 and the shuttle valve 31.
At the same time, the load pressure on the actuator 60 side is the shuttle valve 3
Since this pressure is acting on the other inlet of 1, the pressure on this side passes through the shuttle valve 31 and acts on the chamber 34 having the spring 24 of the bleed-off valve 6.
【００２２】これにより前記のとおりブリードオフ弁６
の働きにより圧力ポート８側の圧力は前記負荷圧力の高
い方のアクチュエータ６０側の負荷圧力以上に制御され
る。これにより負荷圧力の異るアクチュエータでも同時
に独立して作動させることが可能である。本システムを
３連以上の仕様にしても油路４７へ接続すれば容易にシ
ステムを構成できる。Thus, as described above, the bleed-off valve 6
The pressure on the side of the pressure port 8 is controlled to be equal to or higher than the load pressure on the side of the actuator 60 having the higher load pressure. This allows actuators with different load pressures to be operated independently at the same time. Even if this system has specifications of three or more stations, the system can be easily configured by connecting to the oil passage 47.
【００２３】[0023]
【発明の効果】本発明は次の効果がある。メータインと
メータアウトの両方において、圧力補償の流量制御が可
能なため制御性作業性の向上が計られる。複数の負荷の
異るアクチュエータを一つの油圧源にて独立操作可能な
ため母機の作業性向上が計られるとともに従来技術で同
機能を実施する場合（例えば油圧源を複数用意する等）
に比べ非常に経済的であり省スペースも計られる。The present invention has the following effects. In both meter-in and meter-out, pressure compensating flow rate control is possible, which improves controllability and workability. When multiple actuators with different loads can be operated independently by one hydraulic power source, workability of the mother machine can be improved and the same function is implemented by the conventional technology (for example, multiple hydraulic power sources are prepared).
It is much more economical and saves space compared to.
【図１】本発明に係る第１実施例の２連仕様の油圧制御
弁の中立状態の断面図。FIG. 1 is a cross-sectional view of a dual hydraulic control valve of a first embodiment according to the present invention in a neutral state.
【図２】図１に示す油圧制御弁の１つのスプール弁を操
作した状態の断面図。2 is a cross-sectional view of a state where one spool valve of the hydraulic control valve shown in FIG. 1 is operated.
【図３】図１に示す油圧制御弁の１つのスプール弁を図
２に示すものと逆方向に操作した状態の断面図。3 is a cross-sectional view of a state where one spool valve of the hydraulic control valve shown in FIG. 1 is operated in a direction opposite to that shown in FIG.
【図４】図１に示す油圧制御弁の２つのスプール弁を同
時に操作した状態の断面図。4 is a cross-sectional view of a state in which two spool valves of the hydraulic control valve shown in FIG. 1 are simultaneously operated.
１…油圧制御弁、２…本体、２−１，２−２，２−３，
２−５，２−６，２−７…ポート、３…圧油受入ポー
ト、４…油路、６…リードオフ弁、６−１…圧力制御用
ノッチ、６−２…油穴、７…ドレンポート、８…圧力ポ
ート、９…Ａスプール弁、９−１，９−２，９−３，９
−４，９−５…溝、９−６，９−７，９−８，９−９…
油穴、９−１０…メータリングノッチ、１０…Ｂスプー
ル弁、１０−１，１０−２，１０−３，１０−４，１０
−５…溝、１０−６，１０−７，１０−８，１０−９…
油穴、１０−１０…メータリングノッチ、１１…Ａ圧力
補償弁、１１−１…調整穴、９０…Ｂ圧力補償弁、１２
…カウンタバランス弁、１２−１…油路、１２−２…ボ
ール弁、１２−３…スプリング、１２−４…バルブ開口
部、１３…カウンタバランス弁、１３−１…油路、１３
−２…バルブ開口部、１４…カウンタバランス弁、１５
…カウンタバランス弁、１６，１７，１８，１９…チェ
ック弁、２０，２１，２２，２３…シリンダポート、２
４…スプリング、２５…スプリング、２７…ポート、２
８…ポート、２９，３０…タンクポート、３１，３２…
シャトル弁、３３…油路、３４…室，３５，３６…矢
印、３７…チェック弁、３８，３９…室、４１，４２，
４３，４４…矢印、４７…油路、５０…油圧源、６０，
７０…アクチュエータ、８０…タンク。1 ... Hydraulic control valve, 2 ... Main body, 2-1, 2-2, 2-3,
2-5, 2-6, 2-7 ... Port, 3 ... Pressure oil receiving port, 4 ... Oil passage, 6 ... Reed-off valve, 6-1 ... Pressure control notch, 6-2 ... Oil hole, 7 ... Drain port, 8 ... Pressure port, 9 ... A spool valve, 9-1, 9-2, 9-3, 9
-4, 9-5 ... Groove, 9-6, 9-7, 9-8, 9-9 ...
Oil hole, 9-10 ... Metering notch, 10 ... B spool valve, 10-1, 10-2, 10-3, 10-4, 10
-5 ... groove, 10-6, 10-7, 10-8, 10-9 ...
Oil hole, 10-10 ... Metering notch, 11 ... A pressure compensating valve, 11-1 ... Adjusting hole, 90 ... B pressure compensating valve, 12
... counterbalance valve, 12-1 ... oil passage, 12-2 ... ball valve, 12-3 ... spring, 12-4 ... valve opening portion, 13 ... counterbalance valve, 13-1 ... oil passage, 13
-2 ... Valve opening, 14 ... Counter balance valve, 15
... Counter balance valve, 16,17,18,19 ... Check valve, 20,21,22,23 ... Cylinder port, 2
4 ... Spring, 25 ... Spring, 27 ... Port, 2
8 ... Port, 29,30 ... Tank port, 31,32 ...
Shuttle valve, 33 ... Oil passage, 34 ... Chamber, 35, 36 ... Arrow, 37 ... Check valve, 38, 39 ... Chamber, 41, 42,
43, 44 ... Arrows, 47 ... Oil passage, 50 ... Hydraulic power source, 60,
70 ... Actuator, 80 ... Tank.
Claims (1)
（７）と２対のシリンダポート（２０）（２１）（２
２）（２３）を有するバルブの本体（２）と、前記バル
ブの本体に設けられた４個の油ポート（２−１）（２−
２）（２−３）（２７）を有するＡ穴と、前記Ａ穴に嵌
合し且５個の溝（９−５）（９−４）（９−３）（９−
２）（９−１）とメータリングノッチ（９−１０）と４
個の油穴（９−６）（９−７）（９−９）（９−８）を
有する油路切換用と流量制御用Ａスプール弁９と、前記
バルブの本体に前記Ａ穴と同様に設けられた４個の油ポ
ート（２−５）（２−６）（２−７）（２８）を有する
Ｂ穴と、前記Ｂ穴と嵌合し５個の溝（１０−５）（１０
−４）（１０−３）（１０−２）（１０−１）とメータ
リングノッチ（１０−１０）と４個の油穴（１０−６）
（１０−７）（１０−８）（１０−９）を有する油路切
換用と流量制御用のＢスプール弁（１０）と、前記Ａス
プール弁の上流に設けられた圧力補償弁（１１）と、ブ
リードオフ弁（６）と、前記Ｂスプール弁（１０）の上
流に設けられ前記ブリードオフ弁（６）に通ずる圧力補
償弁（１２）と、前記Ａスプール弁の下流に設けられた
カウンタバランス機能を有する弁（１２），（１３）
と、前記Ｂスプール弁の下流に設けられたカウンタバラ
ンス機能を有する弁（１４）（１５）とを有してなるこ
とを特徴とする油圧制御弁。1. A hydraulic pressure receiving port (3), a drain port (7), and two pairs of cylinder ports (20) (21) (2).
2) A valve body (2) having (23) and four oil ports (2-1) (2-) provided in the valve body.
2) A hole having (2-3) (27) and five grooves (9-5) (9-4) (9-3) (9-) fitted in the A hole.
2) (9-1) and metering notch (9-10) and 4
Oil passage switching and flow rate control A spool valve 9 having individual oil holes (9-6) (9-7) (9-9) (9-8), and the same as the A hole in the valve body. B hole having four oil ports (2-5), (2-6), (2-7), and (28) provided in, and five grooves (10-5) (fitted with the B hole). 10
-4) (10-3) (10-2) (10-1), metering notch (10-10) and four oil holes (10-6)
(10-7) (10-8) (10-9) B spool valve (10) for oil passage switching and flow rate control, and a pressure compensation valve (11) provided upstream of the A spool valve. A bleed-off valve (6), a pressure compensation valve (12) provided upstream of the B spool valve (10) and communicating with the bleed-off valve (6), and a counter provided downstream of the A spool valve. Valves with balance function (12), (13)
And a valve (14) (15) having a counter balance function provided downstream of the B spool valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10699895A JP3499962B2 (en) | 1995-04-06 | 1995-04-06 | Hydraulic control valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10699895A JP3499962B2 (en) | 1995-04-06 | 1995-04-06 | Hydraulic control valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH08277806A true JPH08277806A (en) | 1996-10-22 |
| JP3499962B2 JP3499962B2 (en) | 2004-02-23 |
Family
ID=14447896
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10699895A Expired - Lifetime JP3499962B2 (en) | 1995-04-06 | 1995-04-06 | Hydraulic control valve |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3499962B2 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006132700A (en) * | 2004-11-08 | 2006-05-25 | Kayaba Ind Co Ltd | Valve device |
| JP2006132699A (en) * | 2004-11-08 | 2006-05-25 | Kayaba Ind Co Ltd | Valve device |
| WO2014014146A1 (en) * | 2012-07-19 | 2014-01-23 | 볼보 컨스트럭션 이큅먼트 에이비 | Flow control valve for construction machinery |
| CN104594437A (en) * | 2013-10-30 | 2015-05-06 | 斗山英维高株式会社 | Driving control device of excavator |
| JP2016023575A (en) * | 2014-07-18 | 2016-02-08 | コベルコ建機株式会社 | Cover of hydraulic driving device |
| CN111963506A (en) * | 2020-08-07 | 2020-11-20 | 太原理工大学 | Multi-way valve of double-valve-core crane capable of accurately controlling micro flow |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4935301B2 (en) * | 2006-11-01 | 2012-05-23 | コベルコ建機株式会社 | Hydraulic pipe pressure release device and hydraulic pipe structure |
-
1995
- 1995-04-06 JP JP10699895A patent/JP3499962B2/en not_active Expired - Lifetime
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006132700A (en) * | 2004-11-08 | 2006-05-25 | Kayaba Ind Co Ltd | Valve device |
| JP2006132699A (en) * | 2004-11-08 | 2006-05-25 | Kayaba Ind Co Ltd | Valve device |
| JP4558451B2 (en) * | 2004-11-08 | 2010-10-06 | カヤバ工業株式会社 | Valve device |
| JP4578207B2 (en) * | 2004-11-08 | 2010-11-10 | カヤバ工業株式会社 | Valve device |
| WO2014014146A1 (en) * | 2012-07-19 | 2014-01-23 | 볼보 컨스트럭션 이큅먼트 에이비 | Flow control valve for construction machinery |
| US9810244B2 (en) | 2012-07-19 | 2017-11-07 | Volvo Construction Equipment Ab | Flow control valve for construction machinery |
| CN104594437A (en) * | 2013-10-30 | 2015-05-06 | 斗山英维高株式会社 | Driving control device of excavator |
| CN104594437B (en) * | 2013-10-30 | 2017-04-12 | 斗山英维高株式会社 | driving control device of excavator |
| JP2016023575A (en) * | 2014-07-18 | 2016-02-08 | コベルコ建機株式会社 | Cover of hydraulic driving device |
| CN111963506A (en) * | 2020-08-07 | 2020-11-20 | 太原理工大学 | Multi-way valve of double-valve-core crane capable of accurately controlling micro flow |
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| Publication number | Publication date |
|---|---|
| JP3499962B2 (en) | 2004-02-23 |
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