Hydraulic control system of gas-hydraulic drive device

Abstract

The present invention relates to a hydraulic control system for a gas-liquid linkage drive device, comprising: an A-channel hydraulic system and a B-channel hydraulic system respectively connected to the gas-liquid linkage drive device; the A-channel hydraulic system and the B-channel hydraulic system respectively deliver hydraulic oil to the gas-liquid linkage drive device through their respective oil supply oil circuits, and the hydraulic oil in the gas-liquid linkage drive device is returned through the oil return oil circuits of the A-channel hydraulic system and the B-channel hydraulic system. An overall modular design is adopted, with a compact structure, small size and light weight. The main features of the present invention are as follows: large thrust, long stroke, and fast closing within 5 seconds; the hydraulic control adopts two-row electrical control; the control is simple and reliable; a completely independent dual-channel hydraulic control system is adopted, which meets the requirements of the single failure criterion and has a redundant design at the same time to ensure functional safety and reliability.

Description

Technical Field

[0001] The invention relates to a hydraulic control system, which is used for controlling a gas-liquid linkage drive device and realizing the functional requirements of slow opening, slow closing, fast closing, and partial closing and opening of the gas-liquid linkage drive device, and belongs to the field of machinery. Background Art

[0002] The large-caliber fast-closing isolation valve is one of the key equipment in the pipeline system of power stations, etc. It undertakes an important safety function. Under special conditions such as accident conditions in the system, it is necessary to achieve rapid closure within 5 seconds to isolate the control pipeline to ensure the safety of the system. The driving device of the large-caliber fast-closing isolation valve usually uses a gas-liquid linkage driving device to achieve rapid closure. The hydraulic control circuit of the existing gas-liquid linkage driving device is mainly controlled and monopolized by foreign countries, and has certain control defects, low reliability, and the risk of misoperation.

[0003] The gas-liquid linkage drive device needs to be designed from the aspects of safety, reliability and independence in terms of control logic. Summary of the invention

[0004] The present invention mainly solves the two-stage electric control mode of slow opening, slow closing and fast closing of the gas-liquid linkage drive device with large thrust and long stroke, making the control simple, safe and reliable; the slow opening time is less than 600s, the slow closing time is less than 360s, and the fast closing time is less than 5s; the fast closing drive is resistant to shock, noise, aging, radiation, electromagnetic compatibility, safety and reliability. It ensures that the gas-liquid linkage drive device meets the normal, abnormal and accident conditions <5s fast closing capability, and reliable operation in severe accident conditions such as damp heat, radiation, earthquake and power failure.

[0005] In order to achieve the above-mentioned purpose, the technical solution provided by the present invention is a hydraulic control system of a gas-liquid linkage drive device, which is suitable for a gas-liquid linkage drive device of a high-temperature, high-pressure, large-caliber fast-closing (fast-closing within 2 to 5 seconds) main steam isolation valve, and comprises: an A-channel hydraulic system and a B-channel hydraulic system respectively connected to the gas-liquid linkage drive device; the A-channel hydraulic system and the B-channel hydraulic system respectively transport hydraulic oil to the gas-liquid linkage drive device through their respective oil supply oil circuits, and the gas-liquid linkage drive device drives the valve to open; the hydraulic oil in the gas-liquid linkage drive device is returned through the oil return oil circuits of the A-channel hydraulic system and the B-channel hydraulic system respectively, and the valve is driven to close;

[0006] Further, the A channel hydraulic system is arranged on one side of the gas-liquid linkage drive device, and the B channel hydraulic system is arranged on the other side of the gas-liquid linkage drive device;

[0007] Furthermore, the A channel hydraulic system and the B channel hydraulic system are completely independent dual-channel modes of the hydraulic control system of the gas-liquid linkage drive device, which meet the requirements of the single failure criterion and have a redundant design to ensure functional safety and reliability;

[0008] Furthermore, the gas-liquid linkage drive device is a gas-liquid linkage hydraulic cylinder, which includes: a piston cylinder, a rodless cavity, a piston and a piston rod; the piston and the piston rod are arranged in the piston cylinder, the lower part of the piston, the piston rod and the inner wall of the piston cylinder form a rod cavity, and the upper part of the piston and the inner wall of the piston cylinder form a rodless cavity; the rodless cavity is used to pass nitrogen, and the two sides of the top of the rodless cavity are respectively connected to a gas storage tank through a pipeline, which is used to store nitrogen energy, and the storage capacity of the gas storage tank provides thrust for the drive device; the rod cavity is used to pass hydraulic oil;

[0009] Furthermore, the rod chamber of the gas-liquid linkage hydraulic cylinder is connected to an accumulator, i.e., a pressure-balanced accumulator, through a pipeline to store nitrogen to accommodate thermal expansion of the hydraulic fluid at high temperatures;

[0010] Furthermore, the A channel hydraulic system and the B channel hydraulic system are respectively connected to the two sides of the gas-liquid linkage hydraulic cylinder through their respective oil supply lines and are respectively connected to the rod chamber.

[0011] Furthermore, the hydraulic control system of the gas-liquid linkage drive device further includes an oil pump assembly, which includes: an oil tank, a motor, and a quantitative plunger pump; the A channel hydraulic system and the B channel hydraulic system are respectively connected to the oil tank through their own oil return oil circuits; the A channel hydraulic system and the B channel hydraulic system are respectively connected to their own quantitative plunger pumps through pipelines, the two quantitative plunger pumps are respectively connected to the oil tank through pipelines, and a motor is respectively connected to the two quantitative plunger pumps;

[0012] The above-mentioned circuits of each motor, A channel hydraulic system, and B channel hydraulic system in the hydraulic control system of the gas-liquid linkage drive device are independently set, and complete physical isolation is ensured;

[0013] Furthermore, one end of the pipeline of the two quantitative plunger pumps connected to the oil tank is also connected to an oil suction filter respectively, which is used to filter the hydraulic oil in the oil tank and then supply it to the oil supply line;

[0014] Furthermore, the A channel hydraulic system includes: an oil supply circuit, an oil return circuit, a control circuit and their respective control valve groups; one end of the oil supply circuit is connected to the oil tank through a quantitative plunger pump and a motor, and the other end of the oil supply circuit is connected to the piston cylinder. The control valve group on the oil supply circuit includes: a first one-way valve and a second one-way valve. The hydraulic oil from the oil tank flows through the first one-way valve and the second one-way valve through the oil supply circuit and then enters the piston cylinder; the rear end of the second one-way valve located in the oil supply circuit leads to the oil return circuit. The control valve group on the oil return circuit includes: a stop valve, a normally closed two-way valve, and a normally open two-way valve. The return oil circuit is led out from the oil supply oil circuit and connected in series with a stop valve, a normally closed two-way valve, and a normally open two-way valve in sequence, and then connected to the oil tank; a control oil circuit is led out from a position between the stop valve and the normally closed two-way valve of the return oil circuit, and the control oil circuit is connected to the normally closed two-way valve and the normally open two-way valve of the return oil circuit in a branched form, respectively. The control valve group on the control oil circuit includes: a first solenoid valve, a second solenoid valve, and a third solenoid valve. The first solenoid valve and the second solenoid valve are connected in series to a branch of the control oil circuit connected to the normally closed two-way valve, and the third solenoid valve is connected to a branch of the control oil circuit connected to the normally open two-way valve;

[0015] The first one-way valve and the second one-way valve are both check valves;

[0016] Furthermore, a filter is provided on the oil supply line between the first one-way valve and the second one-way valve;

[0017] Furthermore, a first overflow valve is connected to the oil supply line between the first one-way valve and the filter through a pipeline, and the first overflow valve is connected to the oil tank through a pipeline;

[0018] Furthermore, a throttle valve is provided on the oil supply line at the end position of the second one-way valve, and the opening time of the driving device is adjusted by the throttle valve;

[0019] Furthermore, a second overflow valve is connected to the oil supply line at the end position of the throttle valve through a pipeline;

[0020] Furthermore, the normally closed two-way valve and the normally open two-way valve are both two-way cartridge valves, which are pilot-operated designs for the oil return line. The normally open two-way valve adopts a large and small flow design structure, which can simultaneously meet the needs of slow opening and fast closing of the drive device;

[0021] Furthermore, the normally open two-way valve is also provided with a position switch, and the flow rate of the normally open two-way valve is determined by detecting the state of the position switch, so that the normally open two-way valve of the A channel hydraulic system is in a small flow state during the slow closing operation.

[0022] Furthermore, the structure of the B channel hydraulic system is the same as that of the A channel hydraulic system, and the A channel hydraulic system and the B channel hydraulic system are symmetrically arranged.

[0023] The principle of adopting the technical means of the present invention is:

[0024] The hydraulic module is designed with integration. After different logic control, the quick-closing parts adopt pilot control. When the pilot solenoid valve loses power, it keeps the open function to ensure the reliable operation of the gas-liquid linkage drive device. When the pilot solenoid valve is powered, the gas-liquid linkage drive device closes quickly. The main circuit design of the hydraulic control principle adopts the normally closed two-way valve and the normally open two-way valve in series design. It is controlled by the switch feedback signal on the valve to realize the online slow opening commissioning, inspection and maintenance and quick closing control of the drive device to ensure the normal operation of the pipeline system such as the power station.

[0025] The beneficial effects of the present invention are as follows: the overall modular design is adopted, the structure is compact, the volume is small, and the weight is light.

[0026] The main features of the present invention are as follows:

[0027] (1) Large thrust, long stroke, and quick closing within 5 seconds.

[0028] (2) Hydraulic control adopts two-stage electric control, making the control simple and reliable.

[0029] (3) A fully independent dual-channel hydraulic control system is adopted, which not only meets the requirements of the single failure criterion, but also has a redundant design to ensure functional safety and reliability.

[0030] (4) The integrated, modular and miniaturized design of the hydraulic module reduces the number of pipe connections between hydraulic components, reduces the risk of leakage, and improves the sealing reliability of the hydraulic part. It also reduces the volume, weight and structure of the hydraulic system, thereby reducing the impact on the weight and center of gravity of the entire machine.

[0031] (5) When the gas-liquid linkage drive device is operating normally, the pilot solenoid valve is in a power-off state to ensure the reliable operation of the gas-liquid linkage drive device;

[0032] (6) Through control, the gas-liquid linkage drive device can be partially opened and closed slowly, and the device can be operated without affecting the operation of the device to test the effectiveness of the device;

[0033] (7) Uninterrupted monitoring of the gas-liquid linkage drive device is achieved through digital detection technology, ensuring safe and reliable control of the valve.

[0034] (8) Ensure reliable operation of piping systems in power stations and other power plants under accident conditions such as temperature, radiation and earthquake. BRIEF DESCRIPTION OF THE DRAWINGS

[0035] Figure 1 It is a schematic diagram of the principle of the hydraulic control system of the gas-liquid linkage drive device of the present invention.

[0036] Figure 2 for Figure 1 The local structure diagram of .

[0037] Figure 3 It is the control logic diagram of the present invention.

[0038] In the figure, 1, piston cylinder, 1.1, rodless chamber, 1.2, piston, 1.3, piston rod, 1.4, rod chamber, GV1, gas tank, GV2, gas tank, LV, accumulator, 2, oil tank, M2, A channel motor, M1, B channel motor, D2, A channel quantitative plunger pump, D1, B channel quantitative plunger pump, FLT2, A channel oil suction filter, FLT1, B channel oil suction filter, V2, A channel first one-way valve, V6, A channel second one-way valve, V11, A channel stop valve, CE11, A channel normally closed two-way valve, HE12, A channel normally open two-way valve, YV11, A channel first solenoid valve, YV12, A channel second solenoid valve, YV13 , the third solenoid valve of channel A, FLT4, the filter of channel A, V4, the first overflow valve of channel A, V8, the throttle valve of channel A, V10, the second overflow valve of channel A, SQ1, the position switch of channel A, V1, the first one-way valve of channel B, V5, the second one-way valve of channel B, V21, the stop valve of channel B, CE21, the normally closed two-way valve of channel B, HE22, the normally open two-way valve of channel B, YV21, the first solenoid valve of channel B, YV22, the second solenoid valve of channel B, YV23, the third solenoid valve of channel B, FLT3, the filter of channel B, V3, the first overflow valve of channel B, V7, the throttle valve of channel B, V20, the second overflow valve of channel B, SQ2, the position switch of channel B. DETAILED DESCRIPTION

[0039] like Figure 1-Figure 3 As shown, the technical solution provided by the present invention is a hydraulic control system of a gas-liquid linkage drive device suitable for high-temperature, high-pressure and ultra-large-caliber rapid closing (rapid closing within 2 to 5 seconds). The present invention is described in detail below in conjunction with the accompanying drawings.

[0040] The hydraulic control system of the gas-liquid linkage driving device comprises: an A channel hydraulic system and a B channel hydraulic system respectively connected to the gas-liquid linkage driving device;

[0041] The hydraulic system of channel A is arranged on one side of the gas-liquid linkage drive device, and the hydraulic system of channel B is arranged on the other side of the gas-liquid linkage drive device;

[0042] The gas-liquid linkage driving device is a gas-liquid linkage hydraulic cylinder, which includes: a piston cylinder 1, a rodless chamber 1.1, a piston 1.2 and a piston rod 1.3; the piston 1.2 and the piston rod 1.3 are arranged in the piston cylinder 1, the lower part of the piston 1.2, the piston rod 1.3 and the inner wall of the piston cylinder 1 form a rod chamber 1.4, and the upper part of the piston 1.2 and the inner wall of the piston cylinder 1 form a rodless chamber 1.1; the rodless chamber 1.1 is used for passing nitrogen, and the two sides of the top of the rodless chamber 1.1 are respectively connected to a gas storage tank GV1, GV2 through pipelines, which are used to store nitrogen energy, and the storage capacity of the gas storage tanks GV1 and GV2 provides thrust for the driving device; the rod chamber 1.4 is used for passing hydraulic oil;

[0043] The top of the rodless chamber 1.1 of the gas-liquid linkage hydraulic cylinder is connected to an accumulator LV, i.e., a pressure balance accumulator, through a pipeline, which stores nitrogen to adapt to the thermal expansion of the hydraulic fluid at high temperature;

[0044] The A channel hydraulic system and the B channel hydraulic system are respectively connected to the two sides of the gas-liquid linkage hydraulic cylinder through their respective oil supply lines and are respectively connected to the rod chamber 1.4.

[0045] The hydraulic control system of the gas-liquid linkage drive device also includes an oil pump assembly, which includes: an oil tank 2, motors M1, M2, and quantitative plunger pumps D1, D2; the A channel hydraulic system and the B channel hydraulic system are respectively connected to the oil tank 2 through their own return oil circuits; the A channel hydraulic system and the B channel hydraulic system are respectively connected to their own quantitative plunger pumps D1, D2 through pipelines, the two quantitative plunger pumps D1, D2 are respectively connected to the oil tank 2 through pipelines, and the two quantitative plunger pumps D1, D2 are respectively connected to a motor M1, M2;

[0046] One end of the pipeline of the two quantitative plunger pumps D1 and D2 connected to the oil tank 2 is also connected to an oil suction filter FLT1 and FLT2 respectively, which is used to filter the hydraulic oil in the oil tank 2 and then supply it to the oil supply circuit;

[0047] The A channel hydraulic system includes: an oil supply circuit, an oil return circuit, a control circuit and their respective control valve groups; one end of the oil supply circuit is connected to the oil tank 2 through a quantitative plunger pump D2 and a motor M2, and the other end of the oil supply circuit is connected to the piston cylinder 1. The control valve group on the oil supply circuit includes: a first check valve V2 and a second check valve V6. The hydraulic oil from the oil tank 2 flows through the first check valve V2 and the second check valve V6 through the oil supply circuit and enters the piston cylinder 1; the rear end of the second check valve V6 located in the oil supply circuit leads to the return circuit. The control valve group on the return circuit includes: a stop valve V11, a normally closed two-way valve CE11, and a normally open two-way valve HE12. The return circuit is led out from the oil supply circuit and connected in series in sequence. The stop valve V11, the normally closed two-way valve CE11, and the normally open two-way valve HE12 are connected in series and then connected to the oil tank 2; a control oil circuit is led out from a position between the stop valve V11 and the normally closed two-way valve CE11 of the oil return oil circuit, and the control oil circuit is respectively connected to the normally closed two-way valve CE11 and the normally open two-way valve HE12 of the oil return oil circuit in a branched form, and the control valve group on the control oil circuit includes: a first solenoid valve YV11, a second solenoid valve YV12, and a third solenoid valve YV13, the first solenoid valve YV11 and the second solenoid valve YV12 are connected in series to the branch of the control oil circuit connected to the normally closed two-way valve CE11, and the third solenoid valve YV13 is connected to the branch of the control oil circuit connected to the normally open two-way valve HE12;

[0048] The first one-way valve V2 and the second one-way valve V6 are both check valves;

[0049] A filter FLT4 is provided on the oil supply line located between the first one-way valve V2 and the second one-way valve V6;

[0050] A first overflow valve V4 is connected to the oil supply line between the first check valve V2 and the filter FLT4 through a pipeline, and the first overflow valve V4 is connected to the oil tank 2 through a pipeline;

[0051] A throttle valve V8 is also provided on the oil supply line at the end position of the second one-way valve V6, and the opening time of the driving device is adjusted by the throttle valve V8;

[0052] A second relief valve V10 is connected to the oil supply line at the end position of the throttle valve V8 through a pipeline;

[0053] The normally closed two-way valve CE11 and the normally open two-way valve HE12 are both two-way cartridge valves, which are pilot-operated designs for the oil return line. The normally open two-way valve HE12 adopts a large and small flow design structure, which can simultaneously meet the needs of slow opening and fast closing of the drive device;

[0054] The normally open two-way valve HE12 is also provided with a position switch SQ1. The flow rate of the normally open two-way valve HE12 is determined by detecting the state of the position switch SQ1, so that the normally open two-way valve HE12 of the A channel hydraulic system is in a small flow state during the slow closing operation.

[0055] The B channel hydraulic system includes: an oil supply circuit, an oil return circuit, a control circuit and their respective control valve groups; one end of the oil supply circuit is connected to the oil tank 2 through a quantitative plunger pump D1 and a motor M1, and the other end of the oil supply circuit is connected to the piston cylinder 1. The control valve group on the oil supply circuit includes: a first check valve V1 and a second check valve V5. The hydraulic oil from the oil tank 2 flows through the first check valve V1 and the second check valve V5 through the oil supply circuit and then enters the piston cylinder 1; the rear end of the second check valve V5 located in the oil supply circuit leads to the oil return circuit. The control valve group on the oil return circuit includes: a stop valve V21, a normally closed two-way valve CE21, and a normally open two-way valve HE22. The oil return circuit is led out from the oil supply circuit and connected in series in sequence. The shut-off valve V21, the normally closed two-way valve CE21, and the normally open two-way valve HE22 are connected in series and then connected to the oil tank 2; a control oil circuit is led out from a position between the shut-off valve V21 of the oil return circuit and the normally closed two-way valve CE21, and the control oil circuit is respectively connected to the normally closed two-way valve CE21 and the normally open two-way valve HE22 of the oil return circuit in a branched form, and the control valve group on the control oil circuit includes: a first solenoid valve YV21, a second solenoid valve YV22, and a third solenoid valve YV23, the first solenoid valve YV21 and the second solenoid valve YV22 are connected in series to a branch of the control oil circuit connected to the normally closed two-way valve CE21, and the third solenoid valve YV23 is connected to a branch of the control oil circuit connected to the normally open two-way valve HE22;

[0056] The first one-way valve V1 and the second one-way valve V5 are both check valves;

[0057] A filter FLT3 is provided on the oil supply line located between the first one-way valve V1 and the second one-way valve V5;

[0058] A first overflow valve V3 is connected to the oil supply line between the first check valve V1 and the filter FLT3 through a pipeline, and the first overflow valve V3 is connected to the oil tank 2 through a pipeline;

[0059] A throttle valve V7 is also provided on the oil supply line at the end position of the second one-way valve V5, and the opening time of the driving device is adjusted by the throttle valve V7;

[0060] A second relief valve V20 is connected to the oil supply line at the end position of the throttle valve V7 through a pipeline;

[0061] The normally closed two-way valve CE21 and the normally open two-way valve HE22 are both two-way cartridge valves, which are pilot-operated designs for the oil return line. The normally open two-way valve HE22 adopts a large and small flow design structure, which can simultaneously meet the needs of slow opening and fast closing of the drive device;

[0062] The normally open two-way valve HE22 is also provided with a position switch SQ2.

[0063] Further explanation of the above structure:

[0064] 1. The hydraulic module of the gas-liquid linkage drive device adopts A and B completely independent dual-channel hydraulic control systems, which meet the requirements of the single failure criterion and have redundant design to ensure functional safety and reliability.

[0065] 2. Hydraulic module design: The hydraulic control is modularized and miniaturized through integrated design, and the hydraulic components are reasonably arranged on an integrated block, which reduces the pipeline connections between the hydraulic components, reduces the risk of leakage, and improves the sealing reliability of the hydraulic part; and reduces the volume, weight and structure of the hydraulic system, thereby reducing the impact on the weight and center of gravity of the whole machine.

[0066] 3. Hydraulic principle design;

[0067] 3.1 The hydraulic control adopts two-row electric control, making the control simple and reliable.

[0068] 3.2 Hydraulic control system design adopts an independent dual-channel hydraulic control system, with A and B channel hydraulic control systems respectively, to achieve independent slow opening, slow closing and fast closing functions, ensuring that it meets the requirements of the single fault criterion when performing safety functions;

[0069] 3.3 The main circuit of the hydraulic system adopts a pilot-operated large-flow normally closed two-way valve and a large-flow normally open two-way valve in series. The normally open two-way valve adopts a large and small flow design structure, which can simultaneously meet the needs of slow opening and fast closing of the drive device;

[0070] 3.3 The independent dual system structure enables online maintenance of the whole machine; the digital analog signal output function enables online uninterrupted monitoring and intelligent control of the whole process.

[0071] 4. Control logic: Design the control logic from the aspects of safety, reliability and independence, and control the slow opening, slow closing, fast closing, partial closing and opening functions of the A channel, B channel and A+B channel of the drive device by controlling the power on and off of the motor and the solenoid valve respectively. Ensure the control of the quick closing function of the gas-liquid linkage device in <5s under normal, abnormal and accident conditions.

[0072] 5. Electrical control design: The temperature, pressure, liquid level, etc. of the drive device are detected and controlled through digital detection. The control function is controlled by channel A, channel B, and channel A+B respectively to ensure the safety and reliability of the drive device.

[0073] 6. According to the principle of independence of 1E-level equipment and circuits, motor A, motor B, channel A, and channel B are set up independently, and complete physical isolation is ensured; 1E-level equipment, control cables, and connectors meet the requirements of 1E-level identification standards. They meet the requirements of power station use and can operate reliably under temperature, radiation, and earthquake environments under accident conditions.

[0074] According to the above description, the specific principle of the hydraulic control system of the gas-liquid linkage drive device of the present invention is as follows:

[0075] The thrust of the drive unit comes from the energy stored in the nitrogen-filled tank. Start the hydraulic oil pump, and the high-pressure oil pushes the piston back and compresses the nitrogen energy storage. When the quick-closing solenoid valve is energized, the corresponding flow control valve will be opened, thereby releasing the oil pressure. At the same time, the tank compresses the nitrogen to push the piston downward, thereby closing the valve. By adjusting the opening of the flow control valve, the quick closing time can be adjusted to less than 2s~5s.

[0076] Operation Mode

[0077] Prior to any operation, the drive should be properly pre-charged with nitrogen.

[0078] The control logic of the drive device is described as follows:

[0079] Before any operation, the drive unit should be properly pre-charged with nitrogen. The control solenoid valve is in a de-energized state.

[0080] 1) Open

[0081] Start the hydraulic pump motor M1 / M2, and the hydraulic oil enters the hydraulic pump through the oil suction filter FLT1 / FLT2; when the hydraulic oil level is too low, the level switch LVL will change state.

[0082] The hydraulic oil from the hydraulic pump enters the piston cylinder 1 through the check valves V1, V2, filters FLT3, FLT4, check valves V5, V6, and at the same time, the compressed nitrogen is used to store energy in the gas storage tanks GV1, GV2.

[0083] At the same time, the hydraulic oil enters the A and B channels through the two-way cartridge valve (CE11 / CE21), and applies pilot pressure to the two-way cartridge valve (CE11 and CE21) through the control solenoid valve in the de-energized state (A channel: YV11 / YV12, B channel: YV21 / YV22), closing the two-way cartridge valve and thus cutting off the oil return path.

[0084] When the oil return path is closed, the system starts to increase pressure and pushes the piston rod 1.3 to retract until the piston rod 1.3 reaches the fully retracted position, stopping the pump motor M1 / M2 and the opening process ends.

[0085] The opening time of the drive device can be adjusted via the throttle valves V7 and V8.

[0086] The slow opening of the drive device can also be achieved by using a separate motor or pump.

[0087] If the rapid closing function is activated during the opening process, the drive will close rapidly within the specified time.

[0088] 2) Slow closing

[0089] During the slow closing operation, the drive piston rod 1.3 is in a fully retracted state.

[0090] Slow closing includes slow closing of channel A and slow closing of channel B. When operating slow closing, the state of position switch SQ1 / SQ2 on the two-way cartridge valve can be detected online to determine whether the two-way valve with large and small flow is in the small flow state. When operating slow closing, any channel can be selected for slow closing operation.

[0091] ●A channel slow closing operation:

[0092] When the A channel is operated slowly, first energize the solenoid valve YV13, detect the state of SQ1 through the instrumentation system, determine that the two-way cartridge valve HE12 is in the throttling state, and prove that the solenoid valve YV13 and the two-way cartridge valve HE12 are effective; then energize the solenoid valves YV11 and YV12, the two-way cartridge valve CE11 should be opened, the hydraulic oil returns to the oil tank through HE12, and the piston rod moves slowly downward, proving that the solenoid valves YV11, YV12 and the two-way cartridge valve CE11 are effective; maintain the current state until the piston rod 1.3 reaches the fully extended position, and the slow closing operation ends; if a partial slow closing operation is to be achieved, the solenoid valves YV11 and YV12 can be de-energized, the two-way cartridge valve CE11 is closed, the hydraulic oil circuit is blocked, and the main valve remains open to end the slow closing. During this period, turn off the hydraulic pump motor M2 to prevent the hydraulic pump from compensating for the system pressure.

[0093] The slow closing function is not related to safety. If the fast closing function is activated during the slow closing process, the drive will be closed quickly within the specified time.

[0094] ●B channel slow closing operation:

[0095] The slow closing operation of channel B is similar to that of channel A. During the slow closing operation of channel B, the status of the solenoid valves YV21, YV22, YV23 and the two-way cartridge valves CE21 and HE22 can be detected online.

[0096] 3) Channel A fast shutdown (single row power)

[0097] When the A channel is quickly closed, YV13 remains in the de-energized state and the solenoid valves YV11 and YV12 are energized. Then the two-way cartridge valve CE11 opens, and the compressed nitrogen in the gas tank pushes the piston downward. The hydraulic oil under the piston will return to the oil tank through the two-way cartridge valve (CE11 and HE12), and the piston rod 1.3 will be extended quickly until it reaches the fully extended position. The A channel quick closing operation is completed.

[0098] The two-way cartridge valve CE11 has a manual adjustment knob that can adjust the fast closing time of channel A.

[0099] If any of the solenoid valves YV11 and YV12 fails, the two-way cartridge valve CE11 will still open, allowing the main valve to close quickly.

[0100] 4) Channel B fast closing (single row power)

[0101] When the B channel is quickly closed, YV23 remains in the de-energized state and the solenoid valves YV21 and YV22 are energized. Then the two-way cartridge valve CE21 opens, and the compressed nitrogen in the gas tank pushes the piston downward. The hydraulic oil under the piston will return to the oil tank 2 through the two-way cartridge valve (CE21 and HE22), and the piston rod 1.3 will be extended quickly until it reaches the fully extended position. The B channel quick closing operation is completed.

[0102] The 2-way cartridge valve CE21 has a manual adjustment knob to adjust the fast closing time of channel B.

[0103] If any of the solenoid valves YV21 and YV22 fails, the two-way cartridge valve CE21 will still be open, allowing the main valve to close quickly.

[0104] 5) A+B channel fast closing (two-column power)

[0105] This operation mode involves both the A channel fast closing and the B channel fast closing, which will result in twice the amount of oil returning to the tank. In normal operation, the A channel fast closing and the B channel fast closing should be used simultaneously, but in critical situations, a separate fast closing channel operation can also achieve the purpose of fast closing.

[0106] The above description is only a preferred specific implementation manner of the present invention, but the protection scope of the present invention is not limited thereto. All technicians familiar with the technical field shall, within the technical scope disclosed in the present invention, make equivalent replacements or changes based on the technical scheme of the present invention and the concept of the present invention, which should be covered by the protection scope of the present invention.

Claims

1. A hydraulic control system for a gas-liquid linkage drive device, characterized in that: include: A channel hydraulic system and B channel hydraulic system are respectively connected to the gas-liquid linkage drive device; the A channel hydraulic system and the B channel hydraulic system respectively deliver hydraulic oil to the gas-liquid linkage drive device through their respective oil supply oil circuits, and the hydraulic oil in the gas-liquid linkage drive device is returned through the oil return oil circuits of the A channel hydraulic system and the B channel hydraulic system; The gas-liquid linkage driving device is a gas-liquid linkage hydraulic cylinder; the top of the rodless chamber of the gas-liquid linkage hydraulic cylinder is connected to an accumulator through a pipeline; The A channel hydraulic system includes: an oil supply circuit, an oil return circuit, a control circuit and their respective control valve groups; one end of the oil supply circuit is connected to the oil tank through a quantitative plunger pump and a motor, and the other end of the oil supply circuit is connected to the piston cylinder. The control valve group on the oil supply circuit includes: a first check valve and a second check valve. The hydraulic oil from the oil tank flows through the first check valve and the second check valve through the oil supply circuit and then enters the piston cylinder; the rear end of the second check valve located in the oil supply circuit leads to the oil return circuit. The control valve group on the oil return circuit includes: a stop valve, a normally closed two-way valve, a normally open two-way valve, and an oil return circuit. The oil circuit is led out from the oil supply oil circuit and connected in series with the stop valve, the normally closed two-way valve, and the normally open two-way valve in sequence, and then connected to the oil tank; the control oil circuit is led out from the position between the stop valve and the normally closed two-way valve of the oil return oil circuit, and the control oil circuit is connected to the normally closed two-way valve and the normally open two-way valve of the oil return oil circuit in a branched form, and the control valve group on the control oil circuit includes: a first solenoid valve, a second solenoid valve, and a third solenoid valve, the first solenoid valve and the second solenoid valve are connected in series to the branch of the control oil circuit connected to the normally closed two-way valve, and the third solenoid valve is connected to the branch of the control oil circuit connected to the normally open two-way valve; The normally closed two-way valve and the normally open two-way valve are both two-way cartridge valves, which are pilot-operated designs for the oil return line. The normally open two-way valve is also provided with a position switch, and the flow rate of the normally open two-way valve is determined by detecting the state of the position switch.

2. The hydraulic control system of the gas-liquid linkage drive device according to claim 1, characterized in that: The A channel hydraulic system is arranged on one side of the gas-liquid linkage drive device, and the B channel hydraulic system is arranged on the other side of the gas-liquid linkage drive device; the A channel hydraulic system and the B channel hydraulic system are a completely independent dual-channel mode of the hydraulic control system of the gas-liquid linkage drive device.

3. The hydraulic control system of the gas-liquid linkage drive device according to claim 2, characterized in that: The gas-liquid linkage hydraulic cylinder comprises: a piston cylinder, a rodless cavity, a piston and a piston rod; the piston and the piston rod are arranged in the piston cylinder, the lower part of the piston, the piston rod and the inner wall of the piston cylinder form a rod cavity, and the upper part of the piston and the inner wall of the piston cylinder form a rodless cavity; the rodless cavity is used to pass nitrogen, and the two sides of the top of the rodless cavity are respectively connected to a gas storage tank through pipelines for storing nitrogen energy.

4. The hydraulic control system of the gas-liquid linkage drive device according to claim 3, characterized in that: The A channel hydraulic system and the B channel hydraulic system are respectively connected to the two sides of the gas-liquid linkage hydraulic cylinder through their respective oil supply lines and are respectively connected to the rod chamber.

5. The hydraulic control system of the gas-liquid linkage drive device according to any one of claims 1 to 4, characterized in that: It also includes an oil pump assembly, which includes: an oil tank, a motor, and a quantitative plunger pump; the A channel hydraulic system and the B channel hydraulic system are respectively connected to the oil tank through their own return oil circuits; the A channel hydraulic system and the B channel hydraulic system are respectively connected to their own quantitative plunger pumps through pipelines, the two quantitative plunger pumps are respectively connected to the oil tank through pipelines, and a motor is respectively connected to the two quantitative plunger pumps.

6. The hydraulic control system of the gas-liquid linkage drive device according to claim 1, characterized in that: A throttle valve is also arranged on the oil supply line at the end position of the second one-way valve.

7. The hydraulic control system of the gas-liquid linkage drive device according to claim 5, characterized in that: The structure of the B channel hydraulic system is the same as that of the A channel hydraulic system, and the A channel hydraulic system and the B channel hydraulic system are symmetrically arranged.

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