CN114135710A - Hydraulic control system of gas-liquid linkage driving device - Google Patents
Hydraulic control system of gas-liquid linkage driving device Download PDFInfo
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- CN114135710A CN114135710A CN202111463828.7A CN202111463828A CN114135710A CN 114135710 A CN114135710 A CN 114135710A CN 202111463828 A CN202111463828 A CN 202111463828A CN 114135710 A CN114135710 A CN 114135710A
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- 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
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
- F16K31/124—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston servo actuated
- F16K31/1245—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston servo actuated with more than one valve
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- 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
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
- F15B1/024—Installations or systems with accumulators used as a supplementary power source, e.g. to store energy in idle periods to balance pump load
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- 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
- F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
- F15B11/072—Combined pneumatic-hydraulic systems
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- 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
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
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- 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
- F15B13/0401—Valve members; Fluid interconnections therefor
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- 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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/041—Removal or measurement of solid or liquid contamination, e.g. filtering
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- 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
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- 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
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- 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
- F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
- F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
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- 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
- F15B2211/615—Filtering means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fluid-Pressure Circuits (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
Abstract
The invention relates to a hydraulic control system of a gas-liquid linkage driving device, wherein the gas-liquid linkage driving device comprises a gas-liquid linkage cylinder, and the hydraulic control system comprises an A channel hydraulic module, a B channel hydraulic module and an oil supply module; the oil supply module supplies hydraulic oil to a rod cavity of the gas-liquid linkage cylinder, the rod cavity increases oil pressure, the volume of the rod cavity is increased, the volume of the rodless cavity is reduced, and compressed gas in the rodless cavity stores energy; and (3) switching on the hydraulic module of the channel A and/or the hydraulic module of the channel B, releasing oil pressure of the rod cavity, reducing the volume of the rod cavity, releasing energy by compressed gas in the rodless cavity, increasing the volume of the rodless cavity and reducing the volume of the rod cavity. The hydraulic control system adopts a completely independent double-channel hydraulic control system, meets the requirement of a single fault criterion, and has a redundancy design at the same time, thereby ensuring the safety and reliability of functions.
Description
Technical Field
The invention relates to the technical field of hydraulic control, in particular to a hydraulic control system of a gas-liquid linkage driving device.
Background
The main water supply quick closing isolation valve is one of key equipment of a nuclear power station isobaric water reactor nuclear power station pipeline system, bears an important safety function, and needs to be quickly closed within 5s to isolate a full load control pipeline under special working conditions such as accident conditions of the system, so that the safety function of a reactor and the system is ensured. The driving device of the large-caliber quick closing isolation valve generally uses a gas-liquid linkage driving device to realize quick closing, a hydraulic control loop of the existing gas-liquid linkage driving device of the main water supply isolation valve is mainly monopolized by foreign control, and the driving device has certain control defects, low reliability and misoperation risk.
Disclosure of Invention
Aiming at the defects of the prior art, the invention aims to provide a hydraulic control system of a gas-liquid linkage driving device, which has the advantages of compact structure, simple control and high reliability.
In order to achieve the purpose, the invention adopts the following technical scheme:
the hydraulic control system comprises a gas-liquid linkage driving device, wherein the gas-liquid linkage driving device comprises a gas-liquid linkage cylinder, the gas-liquid linkage cylinder comprises a rod cavity and a rodless cavity, the rod cavity of the gas-liquid linkage cylinder is respectively provided with a first oil port and a second oil port, and the rodless cavity of the gas-liquid linkage cylinder is filled with compressed gas; the hydraulic control system comprises an A channel hydraulic module, a B channel hydraulic module and an oil supply module; an oil inlet of the oil supply module is communicated with an oil tank, an oil discharge port of the oil supply module is communicated with an oil inlet of the channel A hydraulic module, and an oil return port of the channel A hydraulic module is communicated with the oil tank; the first oil port of the rod cavity is communicated with the oil inlet of the channel A hydraulic module, the second oil port of the rod cavity is communicated with the oil inlet of the channel B hydraulic module, and the oil return port of the channel B hydraulic module is communicated with an oil tank; the oil supply module supplies hydraulic oil to a rod cavity of the gas-liquid linkage cylinder, the rod cavity increases oil pressure, the volume of the rod cavity is increased, the volume of the rodless cavity is reduced, and compressed gas in the rodless cavity stores energy; and (3) switching on the hydraulic module of the channel A and/or the hydraulic module of the channel B, releasing oil pressure of the rod cavity, reducing the volume of the rod cavity, releasing energy by compressed gas in the rodless cavity, increasing the volume of the rodless cavity and reducing the volume of the rod cavity.
Further, the A channel hydraulic module comprises a first hydraulic control valve assembly, a second hydraulic control valve assembly and a solenoid valve assembly; an oil inlet of the first hydraulic control valve assembly is communicated with a first oil port of the rod cavity and an oil discharge port of the oil supply module respectively, an oil outlet of the first hydraulic control valve assembly is communicated with an oil inlet of the second hydraulic control valve assembly, and an oil outlet of the second hydraulic control valve assembly is communicated with an oil tank; an oil inlet of the electromagnetic valve assembly is communicated with an oil inlet of the second hydraulic control valve assembly, and an oil outlet of the electromagnetic valve assembly is communicated with an oil tank;
the first hydraulic control valve assembly comprises a first two-position three-way electromagnetic valve and a first cartridge valve; an oil inlet of the first two-position three-way electromagnetic valve is respectively communicated with a first oil port of the rod cavity and an oil discharge port of the oil supply module, an oil return port of the first two-position three-way electromagnetic valve is communicated with an oil tank, a working oil port of the first two-position three-way electromagnetic valve is communicated with a control oil port of the first cartridge valve, and an oil inlet of the first cartridge valve is communicated with an oil inlet of the first two-position three-way electromagnetic valve;
the second hydraulic control valve assembly comprises a second two-position three-way electromagnetic valve and a second cartridge valve, the oil outlet of the first cartridge valve is communicated with the oil inlet of the second two-position three-way electromagnetic valve, the oil return port of the second two-position three-way electromagnetic valve is communicated with an oil tank, the working oil port of the second two-position three-way electromagnetic valve is communicated with the control oil port of the second cartridge valve, the oil inlet of the second cartridge valve is communicated with the oil inlet of the second two-position three-way electromagnetic valve, and the oil outlet of the second cartridge valve is communicated with the oil tank;
the electromagnetic valve assembly comprises a first two-position two-way electromagnetic valve, a second two-position two-way electromagnetic valve and a third throttle valve, an oil inlet of the first two-position two-way electromagnetic valve is communicated with an oil inlet of the second cartridge valve, an oil outlet of the first two-position two-way electromagnetic valve is communicated with an oil inlet of the second two-position two-way electromagnetic valve, an oil outlet of the second two-position two-way electromagnetic valve is communicated with an oil inlet of the third throttle valve, and an oil outlet of the third throttle valve is communicated with an oil tank.
Furthermore, the first hydraulic control valve assembly further comprises a second throttle valve, an oil inlet of the second throttle valve is respectively communicated with the first oil port of the rod cavity and the oil discharge port of the oil supply module, and an oil outlet of the second throttle valve is communicated with an oil inlet of the first two-position three-way electromagnetic valve; the channel A hydraulic module further comprises a second overflow valve, an oil inlet of the second overflow valve is communicated with an oil inlet of the second two-position three-way electromagnetic valve, and an oil outlet of the second overflow valve is communicated with an oil tank.
Further, the first hydraulic control valve assembly further comprises a first pressure switch, and the first pressure switch is arranged on an oil path between a working oil port of the first two-position three-way electromagnetic valve and a control oil port of the first cartridge valve;
the second hydraulic control valve assembly further comprises a second pressure switch and a third pressure switch, the second pressure switch is arranged on an oil path between a working oil port of the second two-position three-way electromagnetic valve and a control oil port of the second cartridge valve, and the third pressure switch is arranged on an oil path between an oil inlet of the second two-position three-way electromagnetic valve and an oil inlet of the second cartridge valve;
the first cartridge valve and the second cartridge valve are both flow control cartridge valves, and valve core stroke regulators are arranged on valve covers of the first cartridge valve and the second cartridge valve and are used for regulating respective valve core opening degrees.
Furthermore, the B channel hydraulic module comprises a third hydraulic control valve assembly and a fourth hydraulic control valve assembly, an oil inlet of the third hydraulic control valve assembly is communicated with the second oil port of the rod cavity, an oil outlet of the third hydraulic control valve assembly is communicated with an oil inlet of the fourth hydraulic control valve assembly, and an oil outlet of the fourth hydraulic control valve assembly is communicated with an oil tank;
the third hydraulic control valve assembly comprises a third two-position three-way electromagnetic valve and a third cartridge valve; an oil inlet of the third two-position three-way electromagnetic valve is communicated with a second oil port of the rod cavity, an oil return port of the third two-position three-way electromagnetic valve is communicated with an oil tank, and a working oil port of the third two-position three-way electromagnetic valve is communicated with a control oil port of the third cartridge valve;
the fourth hydraulic control valve assembly comprises the fourth two-position three-way electromagnetic valve and a fourth cartridge valve; an oil outlet of the third cartridge valve is communicated with an oil inlet of the fourth two-position three-way valve, an oil return port of the fourth two-position three-way solenoid valve is communicated with an oil tank, a working oil port of the fourth two-position three-way solenoid valve is communicated with a control oil port of the fourth cartridge valve, an oil inlet of the fourth cartridge valve is communicated with an oil inlet of the fourth two-position three-way solenoid valve, and an oil outlet of the fourth cartridge valve is communicated with the oil tank.
Furthermore, the third hydraulic control valve assembly further comprises a fourth throttle valve, an oil inlet of the fourth throttle valve is communicated with the second oil port of the rod cavity, and an oil outlet of the fourth throttle valve is communicated with an oil inlet of the third two-position three-way electromagnetic valve;
the channel B hydraulic module also comprises a third overflow valve, an oil inlet of the third overflow valve is communicated with an oil inlet of the fourth two-position three-way valve, and an oil outlet of the third overflow valve is communicated with an oil tank;
the channel B hydraulic module further comprises a fifth throttling valve, an oil inlet of the fifth throttling valve is communicated with an oil inlet of the fourth two-position three-way valve, and an oil outlet of the fifth overflow valve is communicated with an oil tank.
Further, the third hydraulic control valve assembly further comprises a fourth pressure switch, and the fourth pressure switch is arranged on an oil path between a working oil port of the third two-position three-way solenoid valve and a control oil port of the third cartridge valve;
the fourth hydraulic control valve assembly further comprises a fifth pressure switch and a sixth pressure switch, the fifth pressure switch is arranged on an oil path between a working oil port of the fourth two-position three-way electromagnetic valve and a control oil port of the fourth cartridge valve, and the sixth pressure switch is arranged on an oil path between an oil inlet of the fourth two-position three-way electromagnetic valve and an oil inlet of the fourth cartridge valve;
and the third cartridge valve and the fourth cartridge valve are both flow control cartridge valves, and valve core stroke regulators are arranged on valve covers of the third cartridge valve and the fourth cartridge valve and are used for regulating respective valve core opening degrees.
Further, the oil supply module comprises a motor, a hydraulic pump, a first overflow valve and a first one-way valve; the motor is in driving connection with the hydraulic pump and is used for driving the hydraulic pump to output hydraulic oil, an oil inlet of the hydraulic pump is communicated with an oil tank, an oil outlet of the hydraulic pump is communicated with an oil inlet of the first overflow valve, an oil outlet of the first overflow valve is communicated with the oil tank, an oil inlet of the first check valve is communicated with an oil inlet of the first overflow valve, and an oil outlet of the first check valve is communicated with an oil inlet of the channel A hydraulic module;
a second one-way valve is arranged on an oil path between the first overflow valve and the hydraulic pump, an oil inlet of the second one-way valve is communicated with an oil outlet of the hydraulic pump, and an oil outlet of the second one-way valve is communicated with an oil inlet of the first overflow valve; a filter is arranged on an oil way between the first check valve and the first overflow valve, an oil inlet of the filter is communicated with an oil inlet of the first overflow valve, and an oil outlet of the filter is communicated with an oil inlet of the first check valve; and an oil outlet of the first throttling valve is respectively communicated with the oil inlet of the channel A hydraulic module and the first oil port of the rod cavity.
Further, a piston and a piston rod are arranged in the rod cavity, one end of the piston rod is connected with the piston, and the other end of the piston rod extends out of the rod cavity; the rodless cavity is connected with a gas storage device, and the gas storage device is two gas storage tanks which are arranged in parallel; the rodless cavity is respectively connected with two pressure transmissions, a pressure gauge and an inflation valve through pipelines, a throttling valve is arranged on the pipeline between each pressure transmitter and the rodless cavity, and throttling valves are arranged on the pipelines between the pressure gauge and the rodless cavity and the pipelines between the inflation valve and the rodless cavity.
The energy accumulator is connected to an oil path between an oil inlet of the channel A hydraulic module and the first oil port with the rod cavity through a throttle valve, two pressure transmitters and two pressure gauges are further arranged on the oil path between the oil inlet of the channel A hydraulic module and the first oil port with the rod cavity, and the two pressure transmitters and the two pressure gauges are respectively connected to the oil path between the oil inlet of the channel A hydraulic module and the first oil port with the rod cavity through the throttle valve.
Compared with the prior art, the invention has the beneficial effects that:
the application provides a hydraulic control system of gas-liquid linkage drive arrangement adopts totally independent binary channels hydraulic control system, satisfies the requirement of single fault criterion promptly, has the redundancy design again simultaneously, guarantees function fail safe nature.
Drawings
FIG. 1 is a schematic diagram of a hydraulic control system of the pneumatic and hydraulic linkage driving device of the present invention;
FIG. 2 is a partial block diagram of FIG. 1;
FIG. 3 is a control logic diagram of the present invention.
In the figure: 1: gas-liquid linkage cylinder, 1.1: rodless cavity, 1.2: piston, 1.3: piston rod, 1.4: rod cavity, 1.4 a: first oil port, 1.4 b: second oil port, 2: oil tank, 3: channel a hydraulic module, 4: b-channel hydraulic module, 5: oil supply module, PV: accumulators, QV1, QV 2: gas storage tanks, PT12, PT22, QT12, QT 2: pressure transmission, PI1, QI 1: pressure gauge, QA: inflation valves, L20, L22, LP1, LP2, LP3, LP4, LQ1, LQ2, LQ3, LQ 4: throttle valve, YV 11: first two-position three-way solenoid valve, YV 12: second two-position three-way solenoid valve, YV 21: third two-position three-way electromagnetic valve, YV 22: fourth two-position three-way solenoid valve, CE 11: first cartridge valve, CE 12: second cartridge valve, CE 21: third cartridge, CE 22: fourth cartridge valve, YV 13: first two-position two-way solenoid valve, YV 14: second two-position two-way solenoid valve, L12: third throttle valve, L11: second throttle valve, L21: fourth throttle valve, L20: fifth throttle valve, Y10: first relief valve, Y11: second relief valve, Y21: third relief valve, SP 11: first pressure switch, SP 12: second pressure switch, SP 13: third pressure switch, SP 21: fourth pressure switch, SP 22: fifth pressure switch, SP 23: sixth pressure switch, PA 11: first pressure measurement point, PA 12: second pressure measurement point, PA 13: third pressure measurement point, PA 21: fourth pressure measurement point, PA 22: fifth pressure measurement point, PA 23: sixth pressure measurement point, M: a motor, D: hydraulic pump, a 01: second one-way valve, FYL: filter, a 02: first check valve, L10: first throttle valve, HB1, HB 2: buffer, Ta2, Tb 2: oil return port, LS: level switch, TS 1: and (6) a temperature switch.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments.
Example 1
As shown in fig. 1-3, the hydraulic control system of the gas-liquid linkage driving device, the gas-liquid linkage driving device is used for driving the opening and closing of the main water supply isolation valve, and comprises a gas-liquid linkage cylinder 1, the gas-liquid linkage cylinder 1 comprises a rod cavity 1.4 and a rodless cavity 1.1, a piston 1.2 and a piston rod 1.3 are arranged in the rod cavity 1.4, one end of the piston rod 1.3 is connected with the piston 1.2, and the other end of the piston rod 1.3 extends out of the rod cavity 1.4; the rod cavity 1.4 is respectively provided with a first oil port 1.4a and a second oil port 1.4b, and specifically, the first oil port 1.4a and the first second oil port are symmetrically arranged at one end far away from the rodless cavity 1.1. The rodless cavity 1.1 is filled with compressed gas, the compressed gas in the embodiment is compressed nitrogen, the rodless cavity 1.1 is connected with a gas storage device, and the gas storage device is two gas storage tanks (QV 1 and QV 2) which are arranged in parallel; each of the gas accumulators (QV 1, QV 2) is filled with nitrogen gas. The rodless cavity 1.1 is respectively connected with two pressure transmissions QT12, QT2, a pressure gauge QI1 and an inflation valve QA through pipelines, a throttle valve LQ1 and a throttle valve LQ2 are arranged on the pipeline between each pressure transmitter QT12, QT2 and the rodless cavity 1.1, and the throttle valves LQ3 and LQ4 are arranged on the pipeline between the pressure gauge QI1 and the rodless cavity 1.1 and the pipeline between the inflation valve QA and the rodless cavity 1.1.
The hydraulic control system comprises an A channel hydraulic module 3, a B channel hydraulic module 4, an oil supply module 5 and an oil tank 2; an oil inlet of the oil supply module 5 is communicated with the oil tank 2, an oil outlet of the oil supply module 5 is communicated with an oil inlet of the channel A hydraulic module 3, and an oil return end Ta2 of the channel A hydraulic module 3 is communicated with the oil tank 2; a first oil port 1.4a of the rod cavity 1.4 is communicated with an oil inlet of the channel A hydraulic module 3, a second oil port 1.4B of the rod cavity 1.4 is communicated with an oil inlet of the channel B hydraulic module 4, and an oil return port Tb2 of the channel B hydraulic module 4 is communicated with the oil tank 2; when the hydraulic linkage device is used, the oil supply module 5 supplies hydraulic oil to the rod cavity 1.4 of the gas-liquid linkage cylinder 1, the oil pressure of the rod cavity 1.4 is increased, the volume of the rodless cavity 1.1 is reduced, and compressed gas of the rodless cavity 1.1 stores energy; the channel A hydraulic module 3 and/or the channel B hydraulic module 4 are/is conducted, oil pressure of the rod cavity 1.4 is released, the volume of the rod cavity 1.4 is reduced, compressed gas in the rodless cavity 1.1 releases energy, the volume of the rodless cavity 1.1 is increased, and the volume of the rod cavity 1.4 is reduced. It should be noted that in the present embodiment, the two completely independent hydraulic modules (the channel a hydraulic module 3 and the channel B hydraulic module 4) communicated with the rod cavity 1.4 are used to control the movement of the pneumatic-hydraulic linkage cylinder 1, so that the requirement of a single failure criterion is met, and the redundant design is provided to ensure the functional safety and reliability.
The channel A hydraulic module 3 of the embodiment comprises a first hydraulic control valve component, a second hydraulic control valve component and an electromagnetic valve component which are arranged in parallel, wherein an oil inlet of the first hydraulic control valve component is respectively communicated with a first oil port 1.4a of a rod cavity 1.4 and an oil outlet of an oil supply module 5, an oil outlet of the first hydraulic control valve component is communicated with an oil inlet of the second hydraulic control valve component, and an oil outlet of the second hydraulic control valve component is communicated with an oil tank 2; an oil inlet of the electromagnetic valve component is communicated with an oil inlet of the second hydraulic control valve component, and an oil outlet of the electromagnetic valve component is communicated with the oil tank 2; it should be noted that the first hydraulic control valve component is normally open and plays a role in isolation when closed, the second hydraulic control valve component is normally closed and realizes quick valve closing when opened, and the electromagnetic valve component is normally closed and realizes slow valve closing when opened. According to the technical scheme, the slow closing and the fast closing of the valve can be realized through the channel A hydraulic module 3; when oil enters the rod cavity 1.4, the first hydraulic control valve component is opened, the second hydraulic control valve component is closed, and the electromagnetic valve component is closed; when the rod cavity 1.4 discharges oil slowly, the first hydraulic control valve component is opened, the second hydraulic control valve component is closed, and the electromagnetic valve component is opened; when the rod cavity 1.4 discharges oil quickly, the first hydraulic control valve component is opened, the second hydraulic control valve component is opened, and the electromagnetic valve component is closed.
Specifically, the first pilot-controlled valve assembly comprises a first two-position three-way electromagnetic valve YV11 and a first cartridge valve CE11, the second pilot-controlled valve assembly comprises a second two-position three-way electromagnetic valve YV12 and a second cartridge valve CE12, and the electromagnetic valve assembly comprises a first two-position two-way electromagnetic valve YV13, a second two-position two-way electromagnetic valve YV14 and a third throttle valve L12 which are arranged in series; an oil inlet of a first two-position three-way solenoid valve YV11 is respectively communicated with a first oil port 1.4a of a rod cavity 1.4 and an oil outlet of an oil supply module 5, an oil return port of the first two-position three-way solenoid valve YV11 is communicated with an oil tank 2, a working oil port of a first two-position three-way solenoid valve YV11 is communicated with a control oil port of a first cartridge valve CE11, an oil inlet of the first cartridge valve CE11 is communicated with an oil inlet of a first two-position three-way solenoid valve YV11, an oil outlet of the first cartridge valve CE11 is communicated with an oil inlet of a second two-position three-way solenoid valve YV12, an oil return port of the second two-position three-way solenoid valve YV12 is communicated with the oil tank 2, and a working oil port of a second two-position three-way solenoid valve YV12 is communicated with the control oil port of the second cartridge valve CE 12; an oil inlet of the second cartridge valve CE12 is communicated with an oil inlet of a second two-position three-way electromagnetic valve YV12, and an oil outlet of the second cartridge valve CE12 is communicated with the oil tank 2; an oil inlet of the first two-position two-way solenoid valve YV13 is communicated with an oil inlet of the second cartridge valve CE12, an oil outlet of the first two-position two-way solenoid valve YV13 is communicated with an oil inlet of the second two-position two-way solenoid valve YV14, an oil outlet of the second two-position two-way solenoid valve YV14 is communicated with an oil inlet of a third throttle valve L12, and an oil outlet of the third throttle valve L12 is communicated with the oil tank 2. It should be noted that the third throttle valve L12 is used to adjust the slow closing speed of the valve. The first hydraulic control valve assembly further comprises a second throttle valve L11, an oil inlet of the second throttle valve L11 is respectively communicated with a first oil port 1.4a of the rod cavity 1.4 and an oil outlet of the oil supply module 5, and an oil outlet of the second throttle valve L11 is communicated with an oil inlet of the first two-position three-way electromagnetic valve YV 11.
It should be noted that the pilot-operated solenoid valve formed by the first two-position three-way solenoid valve YV11 and the first cartridge valve CE11 in the first pilot-operated valve assembly plays a role in isolating the passage a; the second hydraulic control valve component is a pilot type electromagnetic valve consisting of a second two-position three-way electromagnetic valve YV12 and a second cartridge valve CE12 and has the function of quickly opening and closing the passage A.
The A channel hydraulic module 3 further comprises a second overflow valve Y11, the oil inlet of the second overflow valve Y11 is communicated with the oil inlet of a second two-position three-way electromagnetic valve YV12, and the oil outlet of the second overflow valve Y11 is communicated with the oil tank 2.
The first pilot-controlled valve assembly of the present embodiment further includes a first pressure switch SP11, where the first pressure switch SP11 is disposed on an oil path between the working oil port of the first two-position three-way solenoid valve YV11 and the control oil port of the first cartridge valve CE11, and is connected to a first pressure measurement point PA 11; the second hydraulic control valve assembly further comprises a second pressure switch SP12 and a third pressure switch SP13, the second pressure switch SP12 is arranged on an oil path between a working oil port of the second two-position three-way electromagnetic valve YV12 and a control oil port of the second cartridge valve CE12 and is connected with a second pressure measuring point PA12, and the third pressure switch SP13 is arranged on an oil path between an oil inlet of the second two-position three-way electromagnetic valve YV12 and an oil inlet of the second cartridge valve CE12 and is connected with a third pressure measuring point PA 13.
The B-channel hydraulic module 4 of the embodiment comprises a third hydraulic control valve assembly and a fourth hydraulic control valve assembly, an oil inlet of the third hydraulic control valve assembly is communicated with the second oil port 1.4B of the rod cavity 1.4, an oil outlet of the third hydraulic control valve assembly is communicated with an oil inlet of the fourth hydraulic control valve assembly, and an oil outlet of the fourth hydraulic control valve assembly is communicated with the oil tank 2; it should be noted that the third hydraulic control valve assembly is normally open and plays a role in isolation when closed, the fourth hydraulic control valve assembly is normally closed and realizes quick valve closing when opened, and the technical scheme can realize quick valve closing through the channel B hydraulic module 4; when oil enters the rod cavity 1.4, the third hydraulic control valve component is opened, and the fourth hydraulic control valve component is closed; when the rod cavity 1.4 discharges oil quickly, the third hydraulic control valve component is opened, and the fourth hydraulic control valve component is opened.
Specifically, the third pilot operated valve assembly includes a third two-position three-way solenoid valve YV21 and a third cartridge valve CE21, and the fourth pilot operated valve assembly includes a fourth two-position three-way solenoid valve YV22 and a fourth cartridge valve CE 22; an oil inlet of a third two-position three-way solenoid valve YV21 is communicated with a second oil port 1.4b of a rod cavity 1.4, an oil return port of the third two-position three-way solenoid valve YV21 is communicated with an oil tank 2, a working oil port of a third two-position three-way solenoid valve YV21 is communicated with a control oil port of a third cartridge valve CE21, an oil inlet of the third cartridge valve CE21 is communicated with an oil inlet of a third two-position three-way solenoid valve YV21, an oil outlet of the third cartridge valve CE21 is communicated with an oil inlet of a fourth two-position three-way solenoid valve YV22, an oil return port of the fourth two-position three-way solenoid valve YV22 is communicated with the oil tank 2, a working oil port of a fourth two-position three-way solenoid valve YV22 is communicated with a control oil port of the fourth cartridge valve CE22, an oil inlet of the fourth cartridge valve CE22 is communicated with an oil inlet of the fourth two-position three-way solenoid valve YV22, and an oil outlet of the fourth cartridge valve CE22 is communicated with the oil tank 2. The third hydraulic control valve assembly further comprises a fourth throttle valve L21, an oil inlet of the fourth throttle valve L21 is communicated with the second oil port 1.4b of the rod cavity 1.4, and an oil outlet of the fourth throttle valve L21 is communicated with an oil inlet of a third two-position three-way electromagnetic valve YV 21.
It should be noted that the pilot-operated solenoid valve formed by the third two-position three-way solenoid valve YV21 and the third cartridge valve CE21 in the third pilot-operated valve assembly plays a role in isolating the passage B; and a pilot type electromagnetic valve formed by the fourth two-position three-way electromagnetic valve YV22 and the fourth cartridge valve CE22 in the fourth hydraulic control valve assembly plays a role in quickly switching on and off the channel B.
The B-channel hydraulic module 4 of the present embodiment further includes a third overflow valve Y21, an oil inlet of the third overflow valve Y21 is communicated with an oil inlet of the fourth two-position three-way solenoid valve YV22, and an oil outlet of the third overflow valve Y21 is communicated with the oil tank 2. The B channel hydraulic module 4 further comprises a fifth throttle valve L20, an oil inlet of the fifth throttle valve L20 is communicated with an oil inlet of a fourth two-position three-way electromagnetic valve YV22, and an oil outlet of the fifth throttle valve L20 is communicated with the oil tank 2. It should be noted that L20 is normally in the off state when the device is running. Because the channel B has no slow closing function, if the channel A is closed, the device needs to be slowly and partially closed, and the equipment cannot stop running, the L20 is started, oil is slowly drained, and the requirement of partial closing is met.
The third pilot operated valve assembly of the present embodiment further includes a fourth pressure switch SP21, and the fourth pressure switch SP21 is disposed on an oil path between the working port of the third two-position three-way solenoid valve YV21 and the control port of the third cartridge valve CE21, and is connected to a fourth pressure measurement point PA 21. The fourth pilot-operated valve assembly further comprises a fifth pressure switch SP22 and a sixth pressure switch SP23, the fifth pressure switch SP22 is arranged on an oil path between a working oil port of the fourth two-position three-way solenoid valve YV22 and a control oil port of the fourth cartridge valve CE22 and is connected with a fifth pressure measuring point PA22, and the sixth pressure switch SP23 is arranged on an oil path between an oil inlet of the fourth two-position three-way solenoid valve YV22 and an oil inlet of the fourth cartridge valve CE22 and is connected with a sixth pressure measuring point PA 23.
The oil supply module 5 of the present embodiment includes a motor M, a hydraulic pump D, a second check valve a01, a first overflow valve Y10, a filter FYL, a first check valve a02, and a first throttle valve L10; the motor M is in driving connection with the hydraulic pump D and used for driving the hydraulic pump D to output hydraulic oil, an oil inlet of the hydraulic pump D is communicated with the oil tank 2, an oil outlet of the hydraulic pump D is communicated with the second check valve A01, an oil outlet of the second check valve A01 is connected with an oil inlet of the first overflow valve Y10, an oil outlet of the first overflow valve Y10 is communicated with the oil tank 2, an oil inlet of the filter FYL is communicated with an oil inlet of the first overflow valve Y10, an oil outlet of the filter FYL is communicated with an oil inlet of the first check valve A02, an oil outlet of the first check valve A02 is communicated with an oil inlet of the first throttle valve L10, and an oil outlet of the first throttle valve L10 is respectively communicated with an oil inlet of the second throttle valve L11 and a first oil port 1.4a of the rod cavity 1.4.
The embodiment further comprises an energy accumulator PV, the energy accumulator PV is connected to an oil path between an oil inlet of the a-channel hydraulic module 3 and the first oil port 1.4a of the rod cavity 1.4 through a throttle valve LP1, two pressure transmitters PT12, PT22 and a pressure gauge PI1 are further arranged on the oil path between the oil inlet of the a-channel hydraulic module 3 and the first oil port 1.4a of the rod cavity 1.4, and the two pressure transmitters PT12, PT22 and the pressure gauge PI1 are connected to the oil path between the oil inlet of the a-channel hydraulic module 3 and the first oil port 1.4a of the rod cavity 1.4 through throttle valves LP2, LP3 and LP4 respectively.
In the present embodiment, the first cartridge valve CE11, the second cartridge valve CE12, the third cartridge valve CE21 and the fourth cartridge valve CE22 are all flow control cartridge valves, and valve core stroke regulators are provided on valve covers of the first cartridge valve CE11, the second cartridge valve CE12, the third cartridge valve CE21 and the fourth cartridge valve CE22, and are used for regulating respective valve core opening degrees. The valve core stroke adjuster in the embodiment is a manual adjusting knob, and when the valve core stroke adjuster is used, the time for rapidly closing the valve is modified through the adjusting knob.
The above structure will be further explained:
1. the hydraulic module of the gas-liquid linkage driving device adopts an A, B completely independent double-channel hydraulic control system, meets the requirement of a single fault criterion, and has a redundancy design to ensure the safety and reliability of functions.
2. Designing a hydraulic module; the hydraulic control is modularized and miniaturized through an integrated design, and the hydraulic parts are reasonably arranged on an integrated block, so that the pipeline connection among the hydraulic parts is reduced, the leakage risk is reduced, and the sealing reliability of a hydraulic part is improved; and the volume, the weight and the structure of the hydraulic system part are reduced, so that the influence on the weight and the center of gravity of the whole machine is reduced.
3. Designing a hydraulic principle; the hydraulic control adopts two-column electric control; the control system is simple and reliable; the hydraulic system adopts an independent double-channel hydraulic control system, and is respectively provided with an A channel hydraulic control system and a B channel hydraulic control system, so that the requirement of a single fault criterion is met when the safety function is executed; the independent double-system structure realizes the on-line maintenance of the whole machine; the digital analog signal output function realizes the on-line uninterrupted monitoring and intelligent control of the whole process.
4. A control logic; control logic design is carried out from the aspects of safety reliability and independence, and the control of slow opening, slow closing, fast closing and partial closing and opening functions of the channel A, the channel B and the channel A + B of the driving device is realized by respectively controlling the power on and the power off of the motor M and the electromagnetic valve. The control of the quick closing function of the gas-liquid linkage device for less than 5 seconds under normal, abnormal and accident working conditions is ensured.
5. Electrical control design; the temperature (temperature switch TS 1), the pressure, the liquid level and the like of the driving device are detected and controlled in a digital detection mode; the control function adopts the channel A, the channel B and the channel A + B to control respectively, and the safety and reliability of the driving device are ensured.
6. According to the 1E-level equipment and circuit independence principle, the channel M, A and the channel B of the motor are independently arranged, and complete physical isolation is guaranteed; the class 1E equipment, control cables and connectors meet the requirements of class 1E certification standards. The use of the nuclear power station is met, and the reliable operation of the nuclear power station under the conditions of temperature, irradiation and earthquake under the accident condition is realized.
According to the specific principle of the hydraulic control system of the gas-liquid linkage driving device of the invention described above: the thrust of the gas-liquid linkage driving device is derived from the energy stored in the nitrogen-filled gas storage tank (QV 1, QV 2). And starting the hydraulic pump D, and pushing the piston 1.2 to retract by high-pressure oil and compressing nitrogen to store energy. When the quick-closing solenoid valve (the second two-position three-way solenoid valve YV12 and/or the fourth two-position three-way solenoid valve YV 22) is electrified, the corresponding flow control valve (the second cartridge valve CE12 and/or the fourth cartridge valve CE 22) is opened, the oil pressure is released, and meanwhile, the air storage tank (QV 1, QV 2) compresses nitrogen to push the piston 1.2 to move downwards, so that the valve is closed. The quick closing time can be adjusted to 1s to 5s by adjusting the opening degree of the flow control valve (the second cartridge CE12 and/or the fourth cartridge CE 22). A small pressure balanced accumulator PV is installed in the hydraulic circuit to accommodate thermal expansion of the hydraulic fluid at high temperatures.
1.2 mode of operation
The pneumatic-hydraulic linkage drive should have been properly pre-charged with nitrogen prior to any operation.
1.2.1 opening
The gas-liquid linkage drive device opening time may be adjusted by the first throttle valve L10. And starting a motor M of the hydraulic pump D, and allowing hydraulic oil to enter the hydraulic pump D through a filter FYL. When the hydraulic oil level is too low, the level switch LS will change state.
Hydraulic oil passing through the hydraulic pump D enters the rod chamber 1.4 through the second check valve a01, the first check valve a02 and the filter FYL, and pushes the piston rod 1.3 to move upward to compress nitrogen. At this stage, the pressure gauge PI1 displays the hydraulic oil pressure locally, and the pressure transmitter PT1 and the pressure transmitter PT2 are remotely monitored. Meanwhile, hydraulic oil enters the channel A through the first cartridge valve CE11, pilot pressure is applied to the second cartridge valve CE12 through the second two-position three-way electromagnetic valve YV12, and the second cartridge valve CE12 is closed; meanwhile, hydraulic oil enters a channel B through the third cartridge valve CE21, pilot pressure is applied to the fourth cartridge valve CE22 through the fourth two-position three-way electromagnetic valve YV22, and the fourth cartridge valve CE22 is closed; thereby intercepting the oil return path.
When the oil return path is closed, the system will start to increase the pressure and push the piston rod 1.3 upwards until the piston rod 1.3 reaches the fully retracted position. During normal operation, hydraulic system pressure is monitored by pressure transmitters (PT 1) and pressure transmitters (PT 2), the pressure transmitters PT12, PT22 transmitting 4-20mA signals to the instrumentation system. The 4-20mA signal is converted into a real-time pressure value in the system, and the start and stop of a D motor (M) of the hydraulic pump are controlled by the instrument control system according to the change condition of the pressure value, so that the system pressure is compensated (based on the minimum system pressure requirement).
If the quick closing function is started in the opening process, the gas-liquid linkage driving device is quickly closed within 1 s-5 s.
1.2.2 Slow closing
During normal operation, the gas-liquid linkage drive piston rod 1.3 is in a fully retracted state. In this mode, the second two-position three-way solenoid valve YV12 of the a-channel and the fourth two-position three-way solenoid valve YV22 of the B-channel should remain de-energized to prevent the hydraulic oil from flowing back to the tank 2.
During slow closing operation, the first two-position two-way solenoid valve YV13 and the second two-position two-way solenoid valve YV14 are electrified, system hydraulic oil returns to the oil tank 2 through the first two-position two-way solenoid valve YV13 and the second two-position two-way solenoid valve YV14 until the piston rod 1.3 reaches the full extension position, the power is cut off, and slow closing is finished. During this time, the hydraulic pump motor M is turned off to prevent the hydraulic pump D from compensating the system pressure. The slow off time can be adjusted by the third throttle valve L12.
The slow closing function is irrelevant to safety, and if the quick closing function is started in the slow closing process, the gas-liquid linkage driving device is quickly closed within 1-5 s.
1.2.3 quick shut-off 1 (Single row electric A channel)
When the channel A is rapidly closed, the electric second two-position three-way electromagnetic valve YV12 is electrified, the second cartridge valve CE12 is opened, the air storage tanks (QV 1 and QV 2) compress nitrogen to push the piston 1.2 to move downwards, hydraulic oil below the piston 1.2 returns to the oil tank 2 through the first cartridge valve CE11, the second cartridge valve CE12 and the oil return opening Ta2, the rapid return oil of the hydraulic oil is diffused by the buffer HB1, the piston rod 1.3 rapidly extends until the piston rod 1.3 reaches a fully extended position, and the channel A rapid closing operation is finished.
The second cartridge CE12 is provided with a manual adjustment knob by means of which the user can modify the quick-closure times.
1.2.4 quick close 2 (Single row electric B channel)
When the B channel is rapidly closed, the fourth two-position three-way electromagnetic valve YV22 is electrified, the fourth cartridge valve CE22 is opened, the air storage tanks (QV 1 and QV 2) compress nitrogen to push the piston 1.2 to move downwards, hydraulic oil below the piston 1.2 returns to the oil tank 2 through the third cartridge valve CE21, the fourth cartridge valve CE22 and the oil return opening Tb2, the rapid oil return of the hydraulic oil is diffused by the buffer HB2, meanwhile, the piston rod 1.3 rapidly extends until the piston rod 1.3 reaches a fully extended position, and the B channel rapid closing operation is finished.
The fourth cartridge CE22 is provided with a manual adjustment knob by which the user can modify the tight quick close time.
1.2.5 quick shut-off 3 (two rows A + B)
This operating mode involves at the same time a quick closure 1 (a-channel) + a quick closure 2 (B-channel), which results in twice the amount of oil returning to the tank 2. The channel A and the channel B are used for simultaneously executing the safety function under the accident condition, but when the single fault of the safety level control system (the electromagnetic valves supplying power in the same row cannot be powered) is considered, the gas-liquid linkage driving device can still realize the quick closing function under the condition that the electromagnetic valves in the quick closing channel in only one row are available.
1.2.6 on-load test
The purpose of the on-load test is to verify that the functions of the electronic and hydraulic components required to perform the quick-shut down operation are working properly. This mode of operation is used for routine diagnostic/maintenance purposes only and does not affect the safety function of the gas-liquid linkage drive. The hydraulic pump D is continuously and continuously operated during this test. Each column channel must be tested individually to ensure that the off-load tested channel has a quick shut down function.
The A/B channels are isolated by energizing solenoid valves YV11(A channel)/YV 21(B channel) to apply pilot pressure to the cartridge valves CE11/CE 21.
The pressure switch SP11/SP21 gives a feedback signal indicating that pilot pressure is present to close the cartridge CE11/CE21, isolating the channel from the system.
The function of the solenoid valve on the channel will be tested when the on-load test is performed. By energizing and de-energizing the second two-position, three-way solenoid valve YV12 for channel A, the pressure switch SP12 should change state to confirm the function of the solenoid valve. The same applies to the fourth two-position three-way solenoid valve YV22 of passage B and the pressure switch SP 22. The pressure switch is also used to monitor the switching function of the cartridge valve in the pilot operated valve assembly.
1.2.6.1 load test-channel A-CE 11/YV11
The first cartridge CE11 isolates the A channel from the system under pilot pressure. The pilot pressure to the first cartridge CE11 may be monitored using a pressure switch SP 11. When the first two-position three-way electromagnetic valve YV11 is electrified, a pilot pipeline leading to the first cartridge valve CE11 is pressurized, a pressure switch SP11 is high in pressure, and the first cartridge valve CE11 is closed; when the first two-position three-way electromagnetic valve YV11 loses electricity, the pilot pipeline loses pressure, the pressure switch SP11 is low-pressure, and the first cartridge valve CE11 is opened.
1.2.6.2 Loading test A channel-CE 12/YV12
During the test, the gas-liquid linkage drive should remain retracted and the hydraulic pump motor M should remain energized.
CE12/YV12 test: the first two-position three-way solenoid valve YV11 is energized, the pressure switch SP11 is high pressure, and the first cartridge valve CE11 is closed. At this time, the second pressure switch SP12 and the third pressure switch SP13 are at high pressure, and the second two-position three-way solenoid valve YV12 is energized, and the second pressure switch SP12 and the third pressure switch SP13 are at low pressure, which indicates that the second two-position three-way solenoid valve YV12 is energized and the second cartridge valve CE12 is opened from closed, indicating that the second two-position three-way solenoid valve YV12 and the second cartridge valve CE12 are effective. And after the test is finished, the second two-position three-way electromagnetic valve YV12 is de-energized, and then the first two-position three-way electromagnetic valve YV11 is de-energized to recover the original state before the test.
1.2.6.3 on-load test-channel B-CE 21/YV21
The third cartridge CE21 isolates the B channel from the system under pilot pressure. The pilot pressure to the third cartridge CE21 may be monitored using a pressure switch SP 21. When the third two-position three-way solenoid valve YV21 is energized, the pilot line leading to the third cartridge valve CE21 is pressurized, SP21 is high-pressure, and the third cartridge valve CE21 is closed; when the third two-position three-way solenoid valve YV21 loses power, the pilot pipeline loses pressure, the fourth pressure switch SP21 is low-pressure, and the third cartridge valve CE21 is opened.
1.2.6.4 load test B channel-CE 22/YV22
During the test, the gas-liquid linkage drive should remain retracted and the hydraulic pump motor M should remain energized.
CE22/YV22 test: the third two-position three-way solenoid valve YV21 is energized, the fourth pressure switch SP21 is high pressure, and the third cartridge valve CE21 is closed. At this time, the fifth pressure switch SP22 and the sixth pressure switch SP23 are at high pressure, and the fourth two-position three-way solenoid valve YV22 is energized, and the fifth pressure switch SP22 and the sixth pressure switch SP23 are at low pressure, which explains that the fourth two-position three-way solenoid valve YV22 is energized and the fourth cartridge valve CE22 is opened from closed, which shows that the fourth two-position three-way solenoid valve YV22 and the fourth cartridge valve CE22 are effective. And after the test is finished, the fourth two-position three-way electromagnetic valve YV22 is de-energized, and then the first two-position three-way electromagnetic valve YV11 is de-energized to recover the original state before the test.
1.2.710% slow closing and opening
In normal use, the gas-liquid linkage driving device can keep an opening state for a long time. To keep the piston 1.2 seal lubricated, to verify the mechanical operation of the gas-liquid linkage drive, a partial shut-off function needs to be performed.
During slow closing, the slow closing can be started by electrifying the first two-position two-way electromagnetic valve YV13 and the second two-position two-way electromagnetic valve YV14, and when the closing stroke position reaches 10 percent, the slow closing function is stopped. When the piston 1.2 returns to the fully open state, the 10% on/off test is completed.
Compared with the prior art, the embodiment has the beneficial effects that: the control system can realize two-row electric system control of slow opening, slow closing and fast closing of the gas-liquid linkage driving device with high thrust and long stroke; the two-column electric system makes the control simple and reliable. The slow opening time is less than 480s, the slow closing time is less than 180s, and the fast closing time is less than 5 s; the hydraulic module is designed in an integrated manner, the quick closing part is controlled in a pilot mode, and the reliable operation of the gas-liquid linkage driving device is ensured when a pilot electromagnetic valve is not electrified; when the pilot electromagnetic valve is electrified, the safety and the quick closing of the gas-liquid linkage driving device are ensured. The online detection function is realized, and the pressure switch can judge and control the fault or the state of the electromagnetic valve or the main valve online through different logic controls of the electromagnetic valve, so that online replacement or maintenance is carried out, and the normal operation of equipment is guaranteed; the quick-closing driving device solves the technical problems of shock resistance, noise, aging resistance, irradiation resistance, electromagnetic compatibility, safety and reliability and the like. The gas-liquid linkage driving device can meet the requirements of normal and abnormal quick closing capability with the accident working condition less than 5s, and can reliably operate under the severe accident working condition environments such as damp and hot, irradiation, earthquake, power loss and the like.
The above description is only for the preferred embodiment of the present invention, but the scope of the present invention is not limited thereto, and any person skilled in the art should be considered to be within the technical scope of the present invention, and the technical solutions and the inventive concepts thereof according to the present invention should be equivalent or changed within the scope of the present invention.
Claims (10)
1. Hydraulic control system of gas-liquid linkage drive arrangement, its characterized in that: the gas-liquid linkage driving device comprises a gas-liquid linkage cylinder, the gas-liquid linkage cylinder comprises a rod cavity and a rodless cavity, the rod cavity of the gas-liquid linkage cylinder is respectively provided with a first oil port and a second oil port, and compressed gas is filled in the rodless cavity of the gas-liquid linkage cylinder; the hydraulic control system comprises an A channel hydraulic module, a B channel hydraulic module and an oil supply module; an oil inlet of the oil supply module is communicated with an oil tank, an oil discharge port of the oil supply module is communicated with an oil inlet of the channel A hydraulic module, and an oil return port of the channel A hydraulic module is communicated with the oil tank; the first oil port of the rod cavity is communicated with the oil inlet of the channel A hydraulic module, the second oil port of the rod cavity is communicated with the oil inlet of the channel B hydraulic module, and the oil return port of the channel B hydraulic module is communicated with an oil tank; the oil supply module supplies hydraulic oil to a rod cavity of the gas-liquid linkage cylinder, the rod cavity increases oil pressure, the volume of the rod cavity is increased, the volume of the rodless cavity is reduced, and compressed gas in the rodless cavity stores energy; and (3) switching on the hydraulic module of the channel A and/or the hydraulic module of the channel B, releasing oil pressure of the rod cavity, reducing the volume of the rod cavity, releasing energy by compressed gas in the rodless cavity, increasing the volume of the rodless cavity and reducing the volume of the rod cavity.
2. The hydraulic control system of a gas-liquid linkage drive device according to claim 1, characterized in that: the A channel hydraulic module comprises a first hydraulic control valve component, a second hydraulic control valve component and an electromagnetic valve component; an oil inlet of the first hydraulic control valve assembly is communicated with a first oil port of the rod cavity and an oil discharge port of the oil supply module respectively, an oil outlet of the first hydraulic control valve assembly is communicated with an oil inlet of the second hydraulic control valve assembly, and an oil outlet of the second hydraulic control valve assembly is communicated with an oil tank; an oil inlet of the electromagnetic valve assembly is communicated with an oil inlet of the second hydraulic control valve assembly, and an oil outlet of the electromagnetic valve assembly is communicated with an oil tank;
the first hydraulic control valve assembly comprises a first two-position three-way electromagnetic valve and a first cartridge valve; an oil inlet of the first two-position three-way electromagnetic valve is respectively communicated with a first oil port of the rod cavity and an oil discharge port of the oil supply module, an oil return port of the first two-position three-way electromagnetic valve is communicated with an oil tank, a working oil port of the first two-position three-way electromagnetic valve is communicated with a control oil port of the first cartridge valve, and an oil inlet of the first cartridge valve is communicated with an oil inlet of the first two-position three-way electromagnetic valve;
the second hydraulic control valve assembly comprises a second two-position three-way electromagnetic valve and a second cartridge valve, the oil outlet of the first cartridge valve is communicated with the oil inlet of the second two-position three-way electromagnetic valve, the oil return port of the second two-position three-way electromagnetic valve is communicated with an oil tank, the working oil port of the second two-position three-way electromagnetic valve is communicated with the control oil port of the second cartridge valve, the oil inlet of the second cartridge valve is communicated with the oil inlet of the second two-position three-way electromagnetic valve, and the oil outlet of the second cartridge valve is communicated with the oil tank;
the electromagnetic valve assembly comprises a first two-position two-way electromagnetic valve, a second two-position two-way electromagnetic valve and a third throttle valve, an oil inlet of the first two-position two-way electromagnetic valve is communicated with an oil inlet of the second cartridge valve, an oil outlet of the first two-position two-way electromagnetic valve is communicated with an oil inlet of the second two-position two-way electromagnetic valve, an oil outlet of the second two-position two-way electromagnetic valve is communicated with an oil inlet of the third throttle valve, and an oil outlet of the third throttle valve is communicated with an oil tank.
3. The hydraulic control system of a gas-liquid linkage drive device according to claim 2, characterized in that: the first hydraulic control valve assembly further comprises a second throttling valve, an oil inlet of the second throttling valve is communicated with a first oil port of the rod cavity and an oil discharge port of the oil supply module respectively, and an oil outlet of the second throttling valve is communicated with an oil inlet of the first two-position three-way electromagnetic valve; the channel A hydraulic module further comprises a second overflow valve, an oil inlet of the second overflow valve is communicated with an oil inlet of the second two-position three-way electromagnetic valve, and an oil outlet of the second overflow valve is communicated with an oil tank.
4. The hydraulic control system of a gas-liquid linkage drive device according to claim 2, characterized in that: the first hydraulic control valve assembly further comprises a first pressure switch, and the first pressure switch is arranged on an oil path between a working oil port of the first two-position three-way electromagnetic valve and a control oil port of the first cartridge valve;
the second hydraulic control valve assembly further comprises a second pressure switch and a third pressure switch, the second pressure switch is arranged on an oil path between a working oil port of the second two-position three-way electromagnetic valve and a control oil port of the second cartridge valve, and the third pressure switch is arranged on an oil path between an oil inlet of the second two-position three-way electromagnetic valve and an oil inlet of the second cartridge valve;
the first cartridge valve and the second cartridge valve are both flow control cartridge valves, and valve core stroke regulators are arranged on valve covers of the first cartridge valve and the second cartridge valve and are used for regulating respective valve core opening degrees.
5. The hydraulic control system of a gas-liquid linkage drive device according to claim 1, characterized in that: the B channel hydraulic module comprises a third hydraulic control valve assembly and a fourth hydraulic control valve assembly, an oil inlet of the third hydraulic control valve assembly is communicated with the second oil port of the rod cavity, an oil outlet of the third hydraulic control valve assembly is communicated with an oil inlet of the fourth hydraulic control valve assembly, and an oil outlet of the fourth hydraulic control valve assembly is communicated with an oil tank;
the third hydraulic control valve assembly comprises a third two-position three-way electromagnetic valve and a third cartridge valve; an oil inlet of the third two-position three-way electromagnetic valve is communicated with a second oil port of the rod cavity, an oil return port of the third two-position three-way electromagnetic valve is communicated with an oil tank, and a working oil port of the third two-position three-way electromagnetic valve is communicated with a control oil port of the third cartridge valve;
the fourth hydraulic control valve assembly comprises the fourth two-position three-way electromagnetic valve and a fourth cartridge valve; an oil outlet of the third cartridge valve is communicated with an oil inlet of the fourth two-position three-way valve, an oil return port of the fourth two-position three-way solenoid valve is communicated with an oil tank, a working oil port of the fourth two-position three-way solenoid valve is communicated with a control oil port of the fourth cartridge valve, an oil inlet of the fourth cartridge valve is communicated with an oil inlet of the fourth two-position three-way solenoid valve, and an oil outlet of the fourth cartridge valve is communicated with the oil tank.
6. The hydraulic control system of a gas-liquid linkage drive device according to claim 5, characterized in that: the third hydraulic control valve assembly further comprises a fourth throttle valve, an oil inlet of the fourth throttle valve is communicated with a second oil port of the rod cavity, and an oil outlet of the fourth throttle valve is communicated with an oil inlet of the third two-position three-way electromagnetic valve;
the channel B hydraulic module also comprises a third overflow valve, an oil inlet of the third overflow valve is communicated with an oil inlet of the fourth two-position three-way valve, and an oil outlet of the third overflow valve is communicated with an oil tank;
the channel B hydraulic module further comprises a fifth throttling valve, an oil inlet of the fifth throttling valve is communicated with an oil inlet of the fourth two-position three-way valve, and an oil outlet of the fifth overflow valve is communicated with an oil tank.
7. The hydraulic control system of a gas-liquid linkage drive device according to claim 5, characterized in that: the third hydraulic control valve assembly further comprises a fourth pressure switch, and the fourth pressure switch is arranged on an oil path between a working oil port of the third two-position three-way electromagnetic valve and a control oil port of the third cartridge valve;
the fourth hydraulic control valve assembly further comprises a fifth pressure switch and a sixth pressure switch, the fifth pressure switch is arranged on an oil path between a working oil port of the fourth two-position three-way electromagnetic valve and a control oil port of the fourth cartridge valve, and the sixth pressure switch is arranged on an oil path between an oil inlet of the fourth two-position three-way electromagnetic valve and an oil inlet of the fourth cartridge valve;
and the third cartridge valve and the fourth cartridge valve are both flow control cartridge valves, and valve core stroke regulators are arranged on valve covers of the third cartridge valve and the fourth cartridge valve and are used for regulating respective valve core opening degrees.
8. The hydraulic control system of a gas-liquid linkage drive device according to any one of claims 1 to 7, characterized in that: the oil supply module comprises a motor, a hydraulic pump, a first overflow valve and a first one-way valve; the motor is in driving connection with the hydraulic pump and is used for driving the hydraulic pump to output hydraulic oil, an oil inlet of the hydraulic pump is communicated with an oil tank, an oil outlet of the hydraulic pump is communicated with an oil inlet of the first overflow valve, an oil outlet of the first overflow valve is communicated with the oil tank, an oil inlet of the first check valve is communicated with an oil inlet of the first overflow valve, and an oil outlet of the first check valve is communicated with an oil inlet of the channel A hydraulic module;
a second one-way valve is arranged on an oil path between the first overflow valve and the hydraulic pump, an oil inlet of the second one-way valve is communicated with an oil outlet of the hydraulic pump, and an oil outlet of the second one-way valve is communicated with an oil inlet of the first overflow valve; a filter is arranged on an oil way between the first check valve and the first overflow valve, an oil inlet of the filter is communicated with an oil inlet of the first overflow valve, and an oil outlet of the filter is communicated with an oil inlet of the first check valve; and an oil outlet of the first throttling valve is respectively communicated with the oil inlet of the channel A hydraulic module and the first oil port of the rod cavity.
9. The hydraulic control system of a gas-liquid linkage drive device according to claim 8, characterized in that: a piston and a piston rod are arranged in the rod cavity, one end of the piston rod is connected with the piston, and the other end of the piston rod extends out of the rod cavity; the rodless cavity is connected with a gas storage device, and the gas storage device is two gas storage tanks which are arranged in parallel; the rodless cavity is respectively connected with two pressure transmissions, a pressure gauge and an inflation valve through pipelines, a throttling valve is arranged on the pipeline between each pressure transmitter and the rodless cavity, and throttling valves are arranged on the pipelines between the pressure gauge and the rodless cavity and the pipelines between the inflation valve and the rodless cavity.
10. The hydraulic control system of a gas-liquid linkage drive device according to claim 1, characterized in that: the hydraulic control system is characterized by further comprising an energy accumulator, the energy accumulator is connected to an oil path between an oil inlet of the A channel hydraulic module and the first oil port with the rod cavity through a throttle valve, two pressure transmitters and a pressure gauge are further arranged on the oil path between the oil inlet of the A channel hydraulic module and the first oil port with the rod cavity, and the two pressure transmitters and the pressure gauge are connected to the oil path between the oil inlet of the A channel hydraulic module and the first oil port with the rod cavity through the throttle valve respectively.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111463828.7A CN114135710A (en) | 2021-12-02 | 2021-12-02 | Hydraulic control system of gas-liquid linkage driving device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111463828.7A CN114135710A (en) | 2021-12-02 | 2021-12-02 | Hydraulic control system of gas-liquid linkage driving device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN114135710A true CN114135710A (en) | 2022-03-04 |
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ID=80387483
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111463828.7A Pending CN114135710A (en) | 2021-12-02 | 2021-12-02 | Hydraulic control system of gas-liquid linkage driving device |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN114135710A (en) |
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2021
- 2021-12-02 CN CN202111463828.7A patent/CN114135710A/en active Pending
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