KR100559233B1 - Pressure compensation flow control valve - Google Patents
Pressure compensation flow control valve Download PDFInfo
- Publication number
- KR100559233B1 KR100559233B1 KR1019980041234A KR19980041234A KR100559233B1 KR 100559233 B1 KR100559233 B1 KR 100559233B1 KR 1019980041234 A KR1019980041234 A KR 1019980041234A KR 19980041234 A KR19980041234 A KR 19980041234A KR 100559233 B1 KR100559233 B1 KR 100559233B1
- Authority
- KR
- South Korea
- Prior art keywords
- valve
- pressure
- piston
- hydraulic pump
- flow path
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/048—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded combined with other safety valves, or with pressure control devices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K15/00—Check valves
- F16K15/02—Check valves with guided rigid valve members
- F16K15/021—Check valves with guided rigid valve members the valve member being a movable body around which the medium flows when the valve is open
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/06—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with special arrangements for adjusting the opening pressure
Abstract
단일의 유압펌프에서 토출되는 작동유에 의해 적어도 1이상의 액튜에이터(ACTUATOR)가 작동하는 유압회로에서 액튜에이터의 부하압력에 무관하게 방향절환밸브의 스플 절환량에 따라 작동유 양을 제어하여 액튜에이터의 작동속도를 조정할 수 있도록 한 것이다.In the hydraulic circuit in which at least one actuator is operated by the hydraulic oil discharged from a single hydraulic pump, the operating speed of the actuator is adjusted by controlling the amount of operating oil according to the spool switching amount of the directional valve regardless of the load pressure of the actuator. I would have to.
바람직한 실시예에 의하면, 유압펌프와, 상기 유압펌프로 부터 토출되는 작동유에 의해 작동하는 액튜에이터와, 상기 유압펌프와 액튜에이터 사이에 설치되어 작동유 량 및 흐름방향을 제어하는 방향절환밸브를 포함하는 유압회로의 압력보상 유량제어밸브에 있어서, 상기 유압펌프의 토출유로와 상기 방향절환밸브의 입구유로를 연통 또는 차단하도록 밸브본체내측에 슬라이딩 이동가능하게 설치되어 상기 방향절환밸브의 절환에 따라 위치가 가변조정되는 로드체크밸브와, 상기 로드체크밸브 일단을 가압하여 상기 유압펌프의 토출유로와 상기 방향절환밸브의 입구유로를 차단한 상태를 초기상태로 탄성바이어스하는 탄성부재와, 상기 로드체크밸브 일측으로 슬라이딩 이동가능하게 설치되어 상기 방향절환밸브 절환시 연동되는 제 1 피스톤과, 상기 제 1 피스톤내측에 슬라이딩 이동가능하게 설치되어 상기 로드체크밸브를 닫는방향으로 가압하는 제 2 피스톤과, 일단이 상기 방향절환밸브의 출구포트에 연결되며 타단이 상기 제 1 피스톤의 챔버에 연결되어 상기 액튜에이터에 공급되는 작동유 일부를 상기 제 1 피스톤의 구동신호압으로 공급하는 유로를 구비하여 구성됨을 특징으로 하는 압력보상 유량제어밸브를 제공한다.According to a preferred embodiment, a hydraulic circuit including a hydraulic pump, an actuator operated by the hydraulic oil discharged from the hydraulic pump, and a directional valve installed between the hydraulic pump and the actuator to control the operating flow rate and flow direction In the pressure compensation flow control valve of the present invention, the hydraulic pump is slidably installed in the valve body so as to communicate or block the discharge flow path of the hydraulic pump and the inlet flow path of the directional control valve. A load check valve, an elastic member for biasing one end of the load check valve to shut off the discharge flow path of the hydraulic pump and the inlet flow path of the directional valve, and sliding toward one side of the load check valve; A first piston movably installed and interlocked when the directional valve is switched; The second piston is slidably installed in the first piston and pressurizes the rod check valve in a closing direction, one end of which is connected to the outlet port of the direction switching valve, and the other end of which is connected to the chamber of the first piston. It provides a pressure compensation flow control valve comprising a flow path for supplying a part of the hydraulic oil supplied to the actuator to the drive signal pressure of the first piston.
Description
본 발명은 압력보상 유량제어밸브에 관한 것으로, 더욱 상세하게는 단일의 유압펌프에서 토출되는 작동유에 의해 적어도 1이상의 액튜에이터(ACTUATOR)가 작동하는 유압회로에서 액튜에이터의 부하압력에 무관하게 방향절환밸브의 스플 절환량에 따라 작동유 양을 제어하여 액튜에이터의 작동속도를 조정할 수 있도록 한 압력보상 유량제어밸브에 관한 것이다.The present invention relates to a pressure compensated flow control valve, and more particularly, to a pressure control valve, regardless of a load pressure of an actuator, in a hydraulic circuit in which at least one actuator is operated by hydraulic oil discharged from a single hydraulic pump. It relates to a pressure compensation flow control valve that allows to adjust the operating speed of the actuator by controlling the amount of hydraulic fluid according to the spool switching amount.
따라서, 본 발명의 목적은, 단일의 유압펌프에서 토출되는 작동유에 의해 적어도 1이상의 액튜에이터가 작동하는 유압회로에서 액튜에이터의 부하압력에 무관하게 방향절환밸브의 스플 절환량에 따라 작동유 양을 제어하여 액튜에이터의 작동속도를 조정할 수 있도록 한 압력보상 유량제어밸브를 제공하는 것이다.Accordingly, an object of the present invention is to control the amount of hydraulic oil according to the spool switching amount of the directional valve, regardless of the load pressure of the actuator in the hydraulic circuit in which at least one actuator is operated by the hydraulic oil discharged from a single hydraulic pump. It is to provide a pressure compensation flow control valve to adjust the operating speed of the valve.
전술한 본 발명의 목적은, 유압펌프와, 상기 유압펌프로 부터 토출되는 작동유에 의해 작동하는 액튜에이터와, 상기 유압펌프와 액튜에이터 사이에 설치되어 작동유 량 및 흐름방향을 제어하는 방향절환밸브를 포함하는 유압회로의 압력보상 유량제어밸브에 있어서, 상기 유압펌프의 토출유로와 상기 방향절환밸브의 입구유로를 연통 또는 차단하도록 밸브본체내측에 슬라이딩 이동가능하게 설치되어 상기 방향절환밸브의 절환에 따라 위치가 가변조정되는 로드체크밸브와, 상기 로드체크밸브 일단을 가압하여 상기 유압펌프의 토출유로와 상기 방향절환밸브의 입구유로를 차단한 상태를 초기상태로 탄성바이어스하는 탄성부재와, 상기 로드체크밸브 일측으로 슬라이딩 이동가능하게 설치되어 상기 방향절환밸브 절환시 연동되는 제 1 피스톤과, 상기 제 1 피스톤 내측에 슬라이딩 이동가능하게 설치되어 상기 로드체크밸브를 닫는방향으로 가압하는 제 2 피스톤과, 일단이 상기 방향절환밸브의 출구포트에 연결되며 타단이 상기 제 1 피스톤의 챔버에 연결되어 상기 액튜에이터에 공급되는 작동유 일부를 상기 제 1 피스톤의 구동신호압으로 공급하는 유로를 구비하여 구성됨을 특징으로 하는 압력보상 유량제어밸브를 제공함에 의해 달성된다.The object of the present invention described above includes a hydraulic pump, an actuator operated by hydraulic oil discharged from the hydraulic pump, and a direction switching valve installed between the hydraulic pump and the actuator to control the operating flow rate and flow direction. In the pressure compensation flow control valve of the hydraulic circuit, the hydraulic pump is slidably installed in the valve body so as to communicate or block the discharge flow path of the hydraulic pump and the inlet flow path of the directional control valve. A variable load control valve, an elastic member which pressurizes one end of the load check valve and elastically biases the state in which the discharge flow path of the hydraulic pump and the inlet flow path of the directional control valve are blocked to an initial state, and one side of the load check valve. A first piston which is installed to be movable in a sliding direction and interlocked when the direction switching valve is switched, and A second piston slidably installed inside the first piston to press the rod check valve in a closing direction, one end of which is connected to an outlet port of the direction switching valve, and the other end of which is connected to a chamber of the first piston It is achieved by providing a pressure compensation flow control valve characterized in that it comprises a flow path for supplying a part of the hydraulic oil supplied to the actuator at the drive signal pressure of the first piston.
바람직한 실시예에 의하면, 상기 로드체크밸브 일단에 형성되어 절환시 상기 유압펌프의 토출유로로 부터 상기 방향절환밸브의 입구유로측으로 급격한 압력변화를 방지하는 노치부를 더 구비한다.According to a preferred embodiment, it is further provided with a notch portion formed at one end of the load check valve to prevent a sudden pressure change from the discharge flow path of the hydraulic pump to the inlet flow path side of the direction switching valve when switching.
바람직한 실시예에 의하면, 상기 로드체크밸브는 상기 제 1 피스톤 일단을 수용하는 대직경부와 상기 밸브본체의 밸브시이트에 착탈되는 소직경부의 단면적차이에 의해 상기 유압펌프의 토출유로와 상기 방향절환밸브의 입구유로를 개폐하게 된다.According to a preferred embodiment of the present invention, the rod check valve has a discharge area of the hydraulic pump and the directional control valve due to a cross-sectional area difference between a large diameter part accommodating one end of the first piston and a small diameter part detachable from the valve seat of the valve body. Opening and closing the entrance passage.
이하, 본 발명의 바람직한 실시예를 첨부도면에 따라 상세하게 설명하며, 이로 인해 본 발명의 기술적인 범주가 한정되는 것은 아니다.Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings, which is not intended to limit the technical scope of the present invention.
도 1은 본 발명의 실시예에 의한 압력보상 유량제어밸브의 단면도, 도 2는 본 발명의 실시예에 의한 압력보상 유량제어밸브의 작동상태를 나타내는 단면도, 도 3은 본 발명의 실시예에 의한 압력보상 유량제어밸브의 사용상태를 나타내는 유압회로도 이다.1 is a cross-sectional view of the pressure compensation flow control valve according to an embodiment of the present invention, Figure 2 is a cross-sectional view showing the operating state of the pressure compensation flow control valve according to an embodiment of the present invention, Figure 3 is This is a hydraulic circuit diagram showing the use state of the pressure compensated flow control valve.
본 발명의 실시예에 의한 압력보상 유량제어밸브는, 유압펌프(10)와, 이 유압펌프(10)에 연결되어 작동유 공급에 의해 작동하는 액튜에이터(11)(12)(유압실린더)와, 전술한 유압펌프(10)와 액튜에이터(11)(12)사이에 설치되어 작동유 량 및 흐름방향을 제어하는 방향절환밸브(13)(13A)등을 포함하는 유압회로에 적용된다.Pressure compensation flow control valve according to an embodiment of the present invention, the hydraulic pump 10, the actuator (11) (12) (hydraulic cylinder) connected to the hydraulic pump 10 and operated by the hydraulic oil supply, and the above-mentioned It is installed between the hydraulic pump 10 and the actuator 11, 12 is applied to a hydraulic circuit including a direction switching valve (13) (13A) and the like to control the operating flow rate and flow direction.
따라서, 본 발명의 바람직한 실시예에 의하면, 절환시 전술한 유압펌프(10)의 토출유로(15)와 전술한 방향절환밸브(13)(13A)의 고압측 입구유로(16)를 연통 또는 차단하는 로드체크밸브(17)(load check valve)가 밸브본체(14)내측에 슬라이딩 이동가능하게 설치되며, 전술한 로드체크밸브(17)는 이의 일단을 가압하는 탄성부재(18)에 의해 밸브시이트(19)에 밀착되어 전술한 유압펌프(10)의 토출유로(15)와 방향절환밸브(13)(13A)의 입구유로(16)를 차단한 상태를 초기상태로 설치된다. 로드체크밸브(17)의 내부에는 전방과 후방을 연통시키는 로드체크유로(17b)가 형성된다. 전술한 로드체크밸브(17)일측으로 제 1 직경부(20a), 이 제 1 직경부(20a) 내경보다 작은 내경을 갖는 제 2 직경부(20b) 및 이들 사이에 전술한 액튜에이터(11)(12)에 발생되는 로드압(P3)입구(20c)부가 형성되는 감압밸브(20)를 형성하되, 일측이 전술한 로드체크밸브(17)에 수용되는 제 1 피스톤(21)이 전술한 감압밸브(20)내측에 전술한 제 1 직경부(20a) 및 제 2 직경부(20b)를 따라 슬라이딩 이동가능하게 설치되며, 전술한 제 1 피스톤(21)내측에 피스톤 탄성부재(22)에 의해 전술한 로드체크밸브(17)를 닫는방향으로 가압하는 제 2 피스톤(23)이 슬라이딩 이동가능하게 설치되며, 전술한 액튜에이터(11)(12)에 공급되는 작동유 일부를 전술한 제 1 피스톤(21)챔버에 공급하는 부하압 감지유로(26)(27)는 전술한 방향절환밸브(13)(13A)의 출구포트에 연결된다.Therefore, according to a preferred embodiment of the present invention, when switching, the discharge passage 15 of the hydraulic pump 10 described above and the high pressure side inlet passage 16 of the directional valves 13 and 13A described above are communicated or blocked. A load check valve 17 (load check valve) is installed to be slidably movable in the valve body 14, the above-described load check valve 17 is a valve seat by the elastic member 18 for pressing one end thereof The state in which the discharge passage 15 of the hydraulic pump 10 and the inlet passage 16 of the directional control valves 13 and 13A are blocked in close contact with 19 is provided in an initial state. A load check flow passage 17b is formed inside the load check valve 17 so as to communicate the front and the rear. The first diameter portion 20a on one side of the above-described load check valve 17, the second diameter portion 20b having an inner diameter smaller than the inner diameter of the first diameter portion 20a, and the actuator 11 described therebetween ( A pressure reducing valve 20 in which the rod pressure P3 inlet 20c is formed is formed, and the first piston 21 accommodated at one side of the load check valve 17 is formed as described above. (20) It is installed on the inner side so as to be slidably movable along the first diameter portion 20a and the second diameter portion 20b described above, and is described above by the piston elastic member 22 inside the first piston 21 described above. A second piston 23 pressurizing the rod check valve 17 in the closing direction is installed to be slidably movable, and the first piston 21 is a part of the hydraulic oil supplied to the actuators 11 and 12 described above. The load pressure sensing flow paths 26 and 27 supplied to the chamber are connected to the outlet ports of the aforementioned direction switching valves 13 and 13A.
부하압 감지유로(26)(27)의 합류점에는 셔틀밸브(31)가 설치되어 방향절환밸브 가운데 고압이 형성되는 측의 작동유를 제 1 피스톤(21)의 구동신호압으로 플러그(25)에 공급한다.At the confluence of the load pressure sensing flow paths 26 and 27, a shuttle valve 31 is installed to supply the hydraulic fluid on the side of which the high pressure is formed among the direction switching valves to the plug 25 as the driving signal pressure of the first piston 21. do.
도면부호, 24는 전술한 제 1 피스톤(21)에 축방향으로 관통되게 형성되어 전술한 제 2 피스톤(23)의 초기상태를 유지하도록 전술한 피스톤 탄성부재(22)의 탄성력에 대응하는 압력이 형성되는 제 1 피스톤 유로, 25는 전술한 제 2 피스톤(23)을 가압하는 피스톤 탄성부재(22)의 탄성력을 조정할 수 있는 플러그, 32는 전술한 감압밸브(20)와 로드체크밸브(17)사이에서 작동유 누출되는 것을 방지하는 실링, 33은 전술한 감압밸브(20)와 플러그(25)사이에서 작동유 누출되는 것을 방지하는 실링 이다.Reference numeral 24 denotes a pressure corresponding to the elastic force of the aforementioned piston elastic member 22 so as to be axially penetrated through the aforementioned first piston 21 to maintain the initial state of the aforementioned second piston 23. The first piston flow path is formed, 25 is a plug for adjusting the elastic force of the piston elastic member 22 for pressing the second piston 23 described above, 32 is the pressure reducing valve 20 and the rod check valve 17 described above. Sealing to prevent the leakage of the hydraulic oil between, 33 is a sealing to prevent the leakage of the hydraulic oil between the pressure reducing valve 20 and the plug 25 described above.
전술한 바와같이 형성되는 본 발명의 실시예에 의한 압력보상 유량제어밸브의 작동을 설명하면 다음과 같다.Referring to the operation of the pressure compensation flow control valve according to an embodiment of the present invention formed as described above are as follows.
도 1 및 도 3에 도시된 바와같이, 전술한 방향절환밸브(13)(13A)가 중립위치에 있는 경우, 전술한 유압펌프(10)의 토출유로(15)측 압력(P1)과 전술한 방향절환밸브(13)(13A)의 입구유로(16)측 압력(P2)이 동일하게 되므로, 전술한 감압밸브(20)와 로드체크밸브(17)사이에 장착되는 전술한 탄성부재(18)에 의해 전술한 로드체크밸브(17)는 밸브시이트(19)에 밀착되며, 전술한 제 1 피스톤(21)은 전술한 피스톤 탄성부재(22)에 의해 전술한 감압밸브(20)바닥면에 접촉되는 초기상태를 유지하게 된다. 이때, 전술한 방향절환밸브(13)(13A)는 중립상태로서 전술한 유압펌프(10)로부터 토출되는 작동유 공급이 차단되므로 전술한 액튜에이터(11)(12)는 동작하지 않게된다.As shown in Figs. 1 and 3, when the directional valve 13 (13A) described above is in a neutral position, the pressure P1 on the discharge flow path 15 side of the hydraulic pump 10 described above and the aforementioned Since the pressure P2 on the inlet flow path 16 side of the direction switching valves 13 and 13A becomes the same, the aforementioned elastic member 18 mounted between the pressure reducing valve 20 and the rod check valve 17 described above is provided. The rod check valve 17 is in close contact with the valve seat 19, and the first piston 21 is in contact with the bottom of the pressure reducing valve 20 by the piston elastic member 22. Maintain initial state. At this time, since the supply of the hydraulic oil discharged from the hydraulic pump 10 described above is blocked in the above-mentioned direction switching valves 13 and 13A, the actuators 11 and 12 described above are not operated.
그리고, 전술한 액튜에이터(11)를 단독으로 조작하기 위하여 전술한 방향절환밸브(13)를 좌측 또는 우측방향으로 절환시키는 경우, 이때, 전술한 감압밸브(20)내부의 압력(P)은 오리피스(30)를 통과하여 탱크(T)로 귀환되어 제로(ZERO)상태이며, 전술한 제 1 피스톤(21)은 전술한 방향절환밸브(13)를 통과하여 전술한 액튜에이터(11)에 발생되는 압력(P3)에 의하여 도면상에서 좌측방향으로 슬라이딩 이동하며, 전술한 로드체크밸브(17)는 유압펌프(10)의 토출유로(15)측 압력(P1)이 전술한 방향절환밸브(13)의 고압측 입구유로(16)의 압력(P2)보다 높기 때문에 전술한 로드체크밸브(17)의 직경(D1)(D2)차이에 따른 단면적차(A1-A2)에 의해 도면상에서 좌측방향으로 슬라이딩 이동된다(도 2에 도시됨).In addition, in the case where the aforementioned direction switching valve 13 is switched to the left or the right direction in order to operate the above-described actuator 11 alone, the pressure P inside the pressure reducing valve 20 described above is orifice ( 30 passes through the tank T, returns to the tank T, and is in a ZERO state. The aforementioned first piston 21 passes through the aforementioned directional valve 13 to generate the pressure generated in the above-described actuator 11 ( Sliding movement in the left direction on the drawing by P3), the above-described load check valve 17 is a high pressure side of the above-mentioned direction switching valve 13 pressure P1 of the discharge flow path 15 side of the hydraulic pump 10 Since it is higher than the pressure P2 of the inlet flow path 16, it is slidably moved to the left in the drawing by the cross-sectional area difference A1-A2 according to the diameter D1 (D2) difference of the above-mentioned rod check valve 17 ( Shown in FIG. 2).
이때, 전술한 방향절환밸브(13)의 입구유로(16)에 감압압력(P2)은 거의 발생하지 않고, 전술한 방향절환밸브(13)의 절환양에 따라 전술한 유압펌프(10)로 부터 토출되는 작동유는 전술한 액튜에이터(11)에 공급되어 이를 구동시키게 된다.At this time, the pressure reducing pressure P2 is hardly generated in the inlet flow path 16 of the directional control valve 13 described above, and from the hydraulic pump 10 described above according to the switching amount of the directional valve 13 described above. The hydraulic oil discharged is supplied to the above-described actuator 11 to drive it.
한편, 도 1 및 도 3에 도시된 바와같이, 전술한 액튜에이터(11)(12)를 구동시키기 위하여 전술한 방향절환밸브(13)(13A)를 도면상에서 좌측 또는 우측방향으로 동시에 절환시키는 경우, 전술한 방향절환밸브(13)에 발생되는 부하압력을 30 Kg/㎠, 전술한 방향절환밸브(13A)에 발생되는 부하압력을 100 Kg/㎠으로 가정하면, 전술한 유압펌프(10)의 토출유로(15)에 발생되는 압력은 적어도 100 Kg/㎠이상 이다.On the other hand, as shown in Figs. 1 and 3, when the above-mentioned direction switching valves 13 and 13A are simultaneously switched in the left or right direction on the drawing in order to drive the above-described actuators 11 and 12, Assuming that the load pressure generated in the aforementioned directional valve 13 is 30 Kg / cm 2 and the load pressure generated in the aforementioned directional valve 13A is 100 Kg / cm 2, the discharge of the hydraulic pump 10 described above is performed. The pressure generated in the flow path 15 is at least 100 Kg / cm 2 or more.
따라서, 전술한 유압펌프(10)로 부터 토출되는 작동유는 토출유로(15)를 따라 전술한 감압밸브(20)입구측에 유입된다. 즉, 전술한 방향절환밸브(13)(13A)의 절환에 의해 전술한 액튜에이터(11)(12)의 부하압을 검출하는 부하압 감지유로(26)(27)는 차단되며, 전술한 방향절환밸브(13)(13A)의 출구포트로 연통되어 전술한 부하압 감지유로(26)(27)에 의해 전술한 액튜에이터(11)(12)에 발생되는 부하압력이 전술한 감압밸브(20)에 공급된다.Therefore, the hydraulic oil discharged from the hydraulic pump 10 described above flows into the aforementioned pressure reducing valve 20 inlet side along the discharge passage 15. That is, the load pressure detection flow paths 26 and 27 for detecting the load pressure of the actuators 11 and 12 described above are blocked by the switching of the direction change valves 13 and 13A described above, and the direction change described above. The load pressure generated in the above-described actuators 11 and 12 by the above-described load pressure sensing passages 26 and 27 communicating with the outlet ports of the valves 13 and 13A is applied to the above-described pressure reducing valve 20. Supplied.
그러나, 전술한 셔틀밸브(31)에 의해 전술한 액튜에이터(11)(12)의 부하압력 중 최고압력(P)을 검출하여 유로(28)(29)를 통하여 전술한 감압밸브(20)측으로 공급되므로 전술한 제 1 피스톤(21)을 도 1의 도면상에서 우측방향으로 슬라이딩 이동시켜 전술한 로드체크밸브(17)를 폐쇄시키는 방향으로 가압하게 된다. 이때, 전술한 방향절환밸브(13)(13A)가 개방되어 감압된 압력(P2)가 전술한 액튜에이터(11)(12)의 부하압력(P3)보다 낮을 경우, 전술한 로드체크밸브(17)가 이의 직경차(D1)(D2)에 의한 단면적(A1-A2)차이에 따라 전술한 밸브시트부(19)에 접촉하게 된다. 이로 인해 전술한 액튜에이터(11)(12)의 역작동을 방지할 수 있게된다.However, the maximum pressure P of the load pressures of the actuators 11 and 12 described above is detected by the aforementioned shuttle valve 31 and supplied to the pressure reducing valve 20 side through the flow paths 28 and 29. Therefore, the above-described first piston 21 is slid in the right direction on the drawing of FIG. 1 to press the rod check valve 17 in the direction of closing. At this time, when the above-mentioned direction switching valve 13 (13A) is opened and the pressure P2 reduced in pressure is lower than the load pressure P3 of the above-mentioned actuators 11 and 12, the above-mentioned load check valve 17 The valve seat portion 19 is brought into contact with each other according to the difference in the cross-sectional area A1-A2 due to the diameter difference D1 and D2 thereof. This makes it possible to prevent the reverse operation of the actuators 11 and 12 described above.
그리고, 전술한 유로(28)(29)에 최대 부하압력(P)이 작용하게 된다. 예를 들어 전술한 액튜에이터(12)의 부하압력이 100 Kg/㎠으로 작용하게 되므로, 고압측 감압밸브(20)는 내부의 압력(P), 액튜에이터(12)가 100 Kg/㎠으로 압력평형을 유지하게 되며, 전술한 방향절환밸브(13)의 입구유로(15)측 압력(P2)은 전술한 방향절환밸브(13)의 스트로크변위량에 따른 통과면적에 대한 유량의 압력손실분 만큼 증가한 압력으로 유지하면서 액튜에이터(11)를 작동시킨다.The maximum load pressure P acts on the flow paths 28 and 29 described above. For example, since the load pressure of the actuator 12 described above acts at 100 Kg / cm 2, the high pressure side pressure reducing valve 20 has an internal pressure P, and the actuator 12 has a pressure balance of 100 Kg / cm 2. The pressure P2 on the inlet flow path 15 side of the directional valve 13 is maintained at a pressure increased by the pressure loss of the flow rate with respect to the passage area according to the stroke displacement of the directional valve 13. While operating the actuator (11).
그리고, 전술한 저압측 감압밸브(20)는 70 Kg/㎠ 압력으로 전술한 로드체크밸브(17)를 폐쇄하는 방향으로 작용하게 되므로 70 Kg/㎠을 감압하게 된다.The low pressure side pressure reducing valve 20 described above acts in the direction of closing the aforementioned load check valve 17 at a pressure of 70 Kg / cm 2, thereby reducing the pressure of 70 Kg / cm 2.
따라서, 전술한 액튜에이터(11)(12)의 작동속도는 부하압력에 관계없이 전술한 방향절환밸브(13)(13A)의 스플 절환량에 따라 공급되는 작동유 량에 의해 결정된다.Therefore, the operation speed of the above-mentioned actuators 11 and 12 is determined by the operating oil amount supplied according to the above-mentioned spool switching amount of the direction switching valves 13 and 13A irrespective of the load pressure.
이상에서와같이, 바람직한 실시예에 의하면, 단일의 유압펌프에서 토출되는 작동유에 의해 적어도 1이상의 액튜에이터가 작동하는 유압회로에서 액튜에이터의 부하압력에 무관하게 방향절환밸브의 스플 절환량에 따라 작동유 양을 제어하여 액튜에이터의 작동속도를 조정할 수 있도록 한 이점을 갖는다.As described above, according to a preferred embodiment, in the hydraulic circuit in which at least one actuator is operated by the hydraulic oil discharged from a single hydraulic pump, the amount of hydraulic oil is changed according to the spool switching amount of the directional valve regardless of the load pressure of the actuator. It has the advantage of being able to adjust the operating speed of the actuator by controlling it.
도 1은 본 발명의 실시예에 의한 압력보상 유량제어밸브의 단면도,1 is a cross-sectional view of a pressure compensation flow control valve according to an embodiment of the present invention,
도 2는 본 발명의 실시예에 의한 압력보상 유량제어밸브의 작동상태를 나타내는 단면도,2 is a cross-sectional view showing an operating state of the pressure compensation flow control valve according to an embodiment of the present invention;
도 3은 본 발명의 실시예에 의한 압력보상 유량제어밸브의 사용상태를 나타내는 유압회로도 이다.3 is a hydraulic circuit diagram showing a state of use of the pressure compensation flow control valve according to an embodiment of the present invention.
*도면중 주요 부분에 사용된 부호의 설명* Explanation of symbols used in the main part of the drawing
10: 유압펌프10: hydraulic pump
11,12: 액튜에이터11,12: Actuator
13,13A: 방향절환밸브13, 13A: Directional switching valve
14: 밸브본체14: valve body
15: 토출유로15: discharge flow path
16: 방향절환밸브 입구유로16: Directional valve inlet flow passage
17: 로드체크밸브(LOAD CHECK VALVE)17: LOAD CHECK VALVE
18: 탄성부재18: elastic member
19: 밸브시트부19: valve seat
20: 감압밸브20: pressure reducing valve
21: 제 1 피스톤21: first piston
22: 피스톤 탄성부재22: piston elastic member
23: 제 2 피스톤23: second piston
26,27: 부하압 감지유로26,27: Load pressure sensing euro
28,29: 유로28,29: Euro
31: 셔틀밸브31: shuttle valve
Claims (2)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1019980041234A KR100559233B1 (en) | 1998-09-30 | 1998-09-30 | Pressure compensation flow control valve |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1019980041234A KR100559233B1 (en) | 1998-09-30 | 1998-09-30 | Pressure compensation flow control valve |
Publications (2)
Publication Number | Publication Date |
---|---|
KR20000021944A KR20000021944A (en) | 2000-04-25 |
KR100559233B1 true KR100559233B1 (en) | 2006-08-10 |
Family
ID=19552864
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
KR1019980041234A KR100559233B1 (en) | 1998-09-30 | 1998-09-30 | Pressure compensation flow control valve |
Country Status (1)
Country | Link |
---|---|
KR (1) | KR100559233B1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100631064B1 (en) * | 2001-12-21 | 2006-10-02 | 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 | hydraulic apparatus for construction heavy equipment |
KR102590810B1 (en) * | 2021-08-19 | 2023-10-19 | 한국기계연구원 | Leakage preventing valve |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0276904A (en) * | 1988-06-29 | 1990-03-16 | Hitachi Constr Mach Co Ltd | Hydraulic drive device |
KR950014792U (en) * | 1993-11-04 | 1995-06-17 | 대우중공업 주식회사 | Hydraulic supplement device of hydraulic motor |
KR100255013B1 (en) * | 1996-02-23 | 2000-05-01 | 오까노 사다오 | Hydraulic pressure control valve mechanism |
-
1998
- 1998-09-30 KR KR1019980041234A patent/KR100559233B1/en not_active IP Right Cessation
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0276904A (en) * | 1988-06-29 | 1990-03-16 | Hitachi Constr Mach Co Ltd | Hydraulic drive device |
KR950014792U (en) * | 1993-11-04 | 1995-06-17 | 대우중공업 주식회사 | Hydraulic supplement device of hydraulic motor |
KR100255013B1 (en) * | 1996-02-23 | 2000-05-01 | 오까노 사다오 | Hydraulic pressure control valve mechanism |
Also Published As
Publication number | Publication date |
---|---|
KR20000021944A (en) | 2000-04-25 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP2579202Y2 (en) | Operating valve with pressure compensation valve | |
JP2557000B2 (en) | Control valve device | |
US5673557A (en) | Displacement control system for variable displacement type hydraulic pump | |
JP2008534887A (en) | Directional control valve and control device with directional control valve | |
EP0416130B1 (en) | Hydraulic valve capable of pressure compensation | |
KR100559233B1 (en) | Pressure compensation flow control valve | |
CA2586868A1 (en) | Hydraulic pressure control apparatus and hydraulic circuit | |
KR940008818B1 (en) | Hydraulic circuit | |
KR20080077007A (en) | Actuator control device | |
US4825907A (en) | Low restriction fluid control valve | |
KR20020063807A (en) | Spacer type pressure reducing valve | |
JP3534324B2 (en) | Pressure compensating valve | |
JP4428856B2 (en) | Switching valve | |
KR100511197B1 (en) | Apparatus of hydrauric control valve | |
JP3742729B2 (en) | Hydraulic control device | |
JP3317448B2 (en) | Load pressure detector for pressure compensated hydraulic circuit | |
KR100520486B1 (en) | Brake valve | |
JP3344745B2 (en) | Hydraulic control circuit | |
JP2564086Y2 (en) | Operation control device | |
JP2886189B2 (en) | Control valve device | |
US20190376534A1 (en) | Electromagnetic pressure reducing valve and fluid pressure control device including electromagnetic pressure reducing valve | |
JPH06280805A (en) | Pressure oil supply device | |
JP2000097210A (en) | Hydraulic control device | |
JP4566041B2 (en) | Flow control mechanism | |
JPH077601Y2 (en) | Confluence controller |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
N231 | Notification of change of applicant | ||
A201 | Request for examination | ||
E902 | Notification of reason for refusal | ||
E701 | Decision to grant or registration of patent right | ||
GRNT | Written decision to grant | ||
LAPS | Lapse due to unpaid annual fee |