CN108799256B - Backflushing explosion-proof flow cut-off valve group - Google Patents
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- CN108799256B CN108799256B CN201810973933.7A CN201810973933A CN108799256B CN 108799256 B CN108799256 B CN 108799256B CN 201810973933 A CN201810973933 A CN 201810973933A CN 108799256 B CN108799256 B CN 108799256B
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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
- F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator 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
- F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
- F15B20/005—Leakage; Spillage; Hose burst
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Abstract
The invention provides a backflushing explosion-proof flow cutoff valve group, which is characterized in that: the device comprises a forced control mechanism, a differential pressure induction control mechanism, a forced cylinder control mechanism and a restarting control mechanism which are connected with the energy accumulator and the oil cylinder; the forced control mechanism comprises a main valve core, a valve body, a forced cylinder, a differential pressure spring, a valve core approach switch, a forced cylinder approach switch and a blockage; the differential pressure induction control mechanism comprises a double one-way valve, a stop valve I and a differential pressure compensation valve; the forced cylinder control mechanism comprises a hydraulic valve, a one-way valve I, a one-way valve II and an electromagnetic valve I; the restarting control mechanism comprises a stop valve II and an electromagnetic valve II; the recoil explosion-proof flow cut-off valve group disclosed by the invention does not need an external power source, and the valve group is closed instantaneously by means of self pressure difference, so that the reaction is sensitive, the feedback efficiency is high, and the recoil explosion-proof flow cut-off valve group is almost free from time lag and is especially suitable for high-pressure and ultra-large flow control occasions.
Description
Technical Field
The invention relates to the technical field of flow valve, in particular to a high-pressure ultra-large flow backflushing explosion-proof flow cutoff valve group.
Background
The backflushing explosion-proof flow cutoff valve group is an important component for solving the safety of a high-pressure high-flow accumulator load hydraulic system. This technology was blank in the past and in the country. The product is particularly suitable for a wave compensation hydraulic system of an ocean drilling platform, and the valve group mainly plays a role in flow cutting or stopping under a backflushing explosion-proof automatic mode. When the pipeline is broken or the flange is disconnected and the like is invalid, a large amount of energy is stored in the pressurized gas cylinder of the energy accumulator group in the oil supply system, the output flow is accelerated instantaneously, if the transmission of a pipeline medium is not cut off timely, the high-pressure and high-flow oil energy in the energy accumulator is backflushed and sprayed, the accident is further expanded and spread, serious consequences are caused, and after the accident is ended, a worker is required to go to the site to manually open the valve again to open the valve, so that time and labor are wasted.
In order to solve the technical problem, some related schemes are provided in the prior art, for example, chinese patent CN205745586U discloses a full-automatic explosion-proof emergency shut-off valve, which comprises a main valve and a pilot valve; when the main valve clack and the main valve seat are closed, the inner cavity of the main valve is isolated into an inlet cavity, an outlet cavity and a middle cavity; the pilot valve body is fixedly arranged on the upper end face of the main valve cover, a control cavity is formed between the pilot valve body and the main valve cover, and the upper end of the pilot valve rod is connected with the electromagnetic driving device; the center of the upper end face of the main valve cover is provided with a control channel which is communicated with the outlet cavity and the control cavity, the control channel opening of the upper end face of the main valve cover is provided with a guide valve seat which is matched with the guide valve, a pressure taking channel is arranged between the inlet cavity and the control cavity, the main valve cover is provided with a pressure guiding hole which is communicated with the middle cavity and the inlet cavity, the main valve cover is provided with a pressure releasing hole which is communicated with the middle cavity and the control cavity, a spring is arranged between the back face of the guide valve and the upper wall of the control cavity, and the outer circular surface of the guide valve rod is in dynamic sealing fit with the guide valve body. After the accident is removed and the power supply is restored, the main valve is automatically opened, so that the operation is time-saving and labor-saving. The cut-off valve is suitable for the inlet and outlet pipelines of chemical gas-liquid warehouses such as oil tanks. CN106812751a discloses a hydraulic control system for testing performance of micro-flow electromagnetic pilot valve, which consists of a power driving system, a hydraulic system, a computer control, acquisition and data processing system. The hydraulic control system thoroughly solves the technical problem that the small-flow electromagnetic pilot valve and the main valve are required to be tested simultaneously, thereby truly realizing that the electromagnetic pilot valve is used as an independent tested piece for detection, carrying out full-project detection on the electromagnetic pilot valve according to the detection standard of the reversing valve for the hydraulic support, analyzing the comprehensive performance of the electromagnetic pilot valve more intuitively and scientifically, and providing the electromagnetic pilot valve with excellent performance for the main valve of the electro-hydraulic reversing valve so as to improve the integral service performance of the electro-hydraulic reversing valve.
In the prior art, when a pipeline of a high-pressure and ultra-large-flow liquid medium fails, such as fracture and flange loosening, the pressure flow energy generated instantaneously is huge, and the operation of an electric control valve cannot respond in time, so that serious accidents are caused. Therefore, the design of the automatic control valve closing principle without depending on external force energy and the addition of an electromagnetic manual principle can prevent the high-pressure and high-flow oil energy backflushing injection of the accumulator from causing serious consequences, and the automatic control valve closing principle becomes urgent.
Disclosure of Invention
The invention aims to provide the high-pressure ultra-large-flow backflushing explosion-proof flow cutoff valve group with high working pressure, large flow, small hysteresis, high safety and good dynamic quality.
The technical scheme adopted by the invention is as follows: a recoil explosion-proof flow cut-off valve group is characterized in that: the device comprises a forced control mechanism, a differential pressure induction control mechanism, a forced cylinder control mechanism and a restarting control mechanism which are connected between an energy accumulator B and an oil cylinder A; the forced control mechanism comprises a main valve core, a valve body, a forced cylinder, a differential pressure spring, a valve core approach switch, a forced cylinder approach switch and a blockage; the differential pressure induction control mechanism comprises a double one-way valve, a stop valve I and a differential pressure compensation valve; the forced cylinder control mechanism comprises a hydraulic valve, a one-way valve I, a one-way valve II and an electromagnetic valve I; the restarting control mechanism comprises a stop valve II and an electromagnetic valve II; the energy accumulator B and the oil cylinder A are connected with a main valve core through a pipeline, the main valve core is in a slide valve form, a push rod is arranged in the forced cylinder and directly acts on the slide valve core, a differential pressure spring is arranged between the slide valve core and a valve base, the slide valve core and the differential pressure spring are both arranged in the valve body, and a valve core proximity switch is used for monitoring the distance between the push rod and the slide valve core; the forced cylinder proximity switch is used for monitoring the displacement of a push rod in the forced cylinder; the pressure difference induction control mechanism is communicated with the energy accumulator B and the oil cylinder A through a pipeline, potential energy between the energy accumulator B and the oil cylinder A is utilized to drive the forced cylinder control mechanism to operate, and the forced cylinder control mechanism controls the forced cylinder to operate; the restarting control mechanism is used for restarting the forced control mechanism.
Further, the push rod in the forced cylinder directly acts with the pressure difference spring through the main valve core, and the main valve core is in an open state when normally working under the action of the pressure difference spring; the upper end and the bottom of the main valve core are respectively provided with a control oil pipeline, a control oil circuit at the upper end of the main valve core is communicated with the energy accumulator B, and the control oil pipeline at the bottom of the main valve core is communicated with the oil cylinder A and drives the blockage to act on the bottom of the main valve core.
Further, a piston cavity of the forced cylinder is communicated with a hydraulic valve and a one-way valve I, and the hydraulic valve is also communicated with a one-way valve II and an electromagnetic valve I; the electromagnetic valve I is communicated with the double check valve and the forced cylinder; the hydraulic valve is a two-position three-way electromagnetic valve, and an oil drain port of the hydraulic valve is connected with a piston rod cavity of the forced cylinder and a spring cavity L1 of the hydraulic valve and is connected with an oil tank oil port L.
Further, the differential pressure compensating valve has three interfaces: an inlet P, a spring end control oil port P1 and an outlet T; the inlet P is provided with two branch pipelines, one branch pipeline is connected with the electromagnetic valve II, and the other branch pipeline is communicated with the double check valve; the spring end control oil port P1 is communicated with the electromagnetic valve II, the other end of the double unidirectional valve and the stop valve I; the outlet T is communicated with a piston cavity of the forced cylinder through a one-way valve I and a hydraulic valve, and is also communicated with the other end of the hydraulic valve and an electromagnetic valve I through a one-way valve II; the electromagnetic valve I is also communicated with the double check valve and the forced cylinder; and two ends of the double check valves are respectively connected with the energy accumulator B and the oil cylinder A.
Further, the energy accumulator B is connected with one end of the double-check valve through the stop valve I, and the loaded oil cylinder A is connected with the differential pressure compensation valve and the electromagnetic valve II through the stop valve II.
Further, the hydraulic valve has four ports: the pressure difference compensation valve comprises an R1 interface communicated with the pressure difference compensation valve, interfaces respectively communicated with the forced cylinder and the electromagnetic valve I, and an L1 interface connected with the oil tank L, wherein a pipeline communicated with the electromagnetic valve I and the double forced cylinders is also communicated with a pipeline of the L1 interface in a crossing way; and a damping hole is also arranged on a passage between the outlet T of the differential pressure compensation valve and the one-way valve.
Further, the valve core proximity switch is arranged between the push rod and the main valve core; the forcing cylinder proximity switch is installed in the forcing cylinder.
Further, the recoil explosion proof flow cut-off valve set has an automatic flow shut-off mode and a manual shut-off mode, the automatic flow shut-off mode relies on a forced control mechanism to react spontaneously: when the pipeline between the oil cylinder and the energy accumulator B is seriously invalid or the overrun load stall caused by the system failure falls down, the forced control mechanism can automatically cut off the main oil way, prevent the output of the super-large flow and protect the hydraulic system; the manual closing mode realizes the closing operation of the forced cylinder by means of a forced cylinder control mechanism: the electromagnetic valve I is started and controlled through an electrohydraulic signal in manual operation, and then the pressure difference induction control mechanism is utilized to enable the higher pressure of the pipelines at the two sides of the accumulator B or the oil cylinder A to act on the forced cylinder piston through the double one-way valve, so that the forced cylinder is operated to push the main valve core to move, and the flow between the accumulator and the hydraulic cylinder is cut off.
Further, in the manual closing mode, when the forced cylinder push rod pushes the main valve core to move, the forced cylinder proximity switch and the valve core proximity switch send out signal changes to display the sensing position of manual closing; when the forced cylinder push rod return signal is displayed by the main valve core proximity switch, the main valve opening of the main valve core is in a closed state until the pressure of the oil cylinder A reaches the same pressure as the pressure of the energy accumulator B; when the pressure reaches equilibrium at the upper and lower ends of the main valve core, the main valve core is re-opened, the forced cylinder approach switch indicates the main valve core to be re-opened, and at the same time, the electromagnetic valve II provides flow change at the two ends of the flow balancing main valve core so as to reduce the influence of pressure difference force.
Further, the R1 port and L1 port restart control mechanism of the hydraulic valve is provided with a manual lock valve which controls only the unbalanced effect from the higher cylinder A pressure to the lower accumulator B pressure, but not the higher accumulator B to the lower cylinder A pressure.
Further, the valve port of the differential pressure compensation valve is designed according to the proportion of 1:1, and the valve port is biased to a closing position through an adjustable spring; when the pressure value of the oil cylinder A exceeds the sum of the pressure value of the accumulator B and the spring set value of the differential pressure compensation valve, the valve port of the differential pressure compensation valve overflows, and the overflow action of the differential pressure compensation valve moves control oil in the interface of the hydraulic valve L1, so that the control oil is limited to flow out of a piston cavity of the forced cylinder; at the same time, the cylinder a pressure and the flow through the port of the hydraulic valve R1 for the shifting action are input to the piston chamber of the force cylinder, so that the force cylinder and the main valve spool can be kept closed also in case of some residual leakage at the port L1.
Further, the pressure difference setting for re-opening the hydraulic valve is determined by the elasticity of a spring on the R1 interface; the open/close state of the main spool 1 is monitored by an instruction from a spool proximity switch or the forced cylinder proximity switch.
Furthermore, the electromagnetic valve I and the hydraulic valve can control the opening of the forced cylinder and the main valve core in a linkage way only when the hydraulic valve R1 interface is in a gear shifting position and the system pressure is equal; only when the pressure between accumulator B and cylinder a of the valve block is balanced will the main spool reopen.
Further, the backflushing explosion-proof flow cutoff valve group has a safety monitoring function: 1) When the valve group system works normally, the valve group is in a normally open state, a valve core approach switch on the main valve core is not signaled, and a forced cylinder approach switch on the forced cylinder is in a signal sending state; 2) When the recoil is explosion-proof, the main valve core is in a closed position, and the valve core proximity switch sends out a sensing position for closing the valve port.
Furthermore, the valve group is an electrohydraulic loop controlled valve group, external hydraulic and electric operation is not needed in an automatic mode, the electromagnetic valve I and the electromagnetic valve II are in zero leakage, an external oil drain port of the electromagnetic valve I and the electromagnetic valve II only has leakage oil flow when the valve is manually closed, and no leakage oil exists under normal conditions.
Further, the electromagnetic valve I is an electromagnetic valve with a positioning function and can be kept at a functional position under the condition of power failure.
Further, the restarting control mechanism is communicated with the liquid level pressure at the two ends of the main valve core 1 through the electromagnetic valve II, so that the pressure difference at the two ends of the restarting control mechanism is within the elastic value of the differential pressure spring, and the restarting operation of the valve group is facilitated.
Compared with the prior art, the invention has the beneficial effects that:
(1) The invention discloses a backflushing explosion-proof flow cut-off valve group, which is a safety valve for preventing pipeline breakage under the working condition of high pressure and large flow, and can be used for cutting off the flow of a hydraulic circuit between a large-sized energy accumulator group and an oil cylinder. When the hydraulic system works normally, the valve bank is in an open state, when a pipeline or a flange breaks and fails, the large-scale hydraulic load mechanism drops the stall degree, and once the hydraulic circuit between the accumulator bank and the oil cylinder breaks and fails, the valve bank does not need external control action, the valve port of the main valve core can be immediately closed, namely, the circuit is automatically cut off and the outlet of the accumulator is closed, thus the high-pressure and high-flow oil energy backflushing injection of the accumulator can be effectively prevented, and secondary accidents are prevented.
(2) The recoil explosion-proof flow cut-off valve group does not need an external power source, and the valve group is closed instantaneously by means of the pressure difference between the self energy accumulator group and the oil cylinder, so that time delay is almost avoided, the reaction is sensitive, and the feedback efficiency is high. The recoil explosion-proof flow cut-off valve is particularly suitable for the control occasion of oil medium with high pressure and super-large flow, the maximum working pressure can reach 30MPa, and the maximum flow can reach 1500L/min.
(3) The recoil explosion-proof flow cut-off valve group provided by the invention has two control operation modes, namely an automatic control operation mode and a manual control operation mode, wherein the automatic flow closing mode is as follows: providing safety protection for the hydraulic system. When the pipeline between the oil cylinder and the energy accumulator is seriously invalid, such as fracture, flange loosening and the like, or the overrun load stall caused by system failure falls down, the valve group can automatically cut off the main oil circuit under the pressure drop effect of the set flow out of tolerance, and the oversized flow output is prevented. The manual closing mode can be used for manually controlling the electromagnetic valve when a pipeline fails or overhauls and maintains are needed, and the forced cutting-off of the valve group and the manual maintenance and overhauling are realized by utilizing the pressure action of the energy accumulator B or the oil cylinder A on the forced cylinder piston.
(4) The recoil explosion-proof flow cut-off valve bank disclosed by the invention has the advantages that the forced control mechanism automatically controls the opening and closing of the valve port of the valve core, the differential pressure induction control mechanism compares and utilizes the pressure of the energy accumulator B or the oil cylinder A so as to drive the forced cylinder control mechanism to operate the forced cylinder, the restarting control mechanism can realize the restarting operation of the valve bank, the remote working condition monitoring can be realized through the valve core approach switch 5 and the forced cylinder approach switch 6, and the working state of the main valve core can be known through a remote distance, so that the valve bank is convenient and quick.
(5) The recoil explosion-proof flow cut-off valve set has an energy-saving effect, and the valve set is opened and closed without an external power source interface.
(6) The recoil explosion-proof flow cut-off valve group has a safety monitoring function: when the forced cylinder proximity switch 6 sends out a signal state, the valve group is in a normally open working state; when the valve core approach switch 5 shows that the valve port of the main valve core is closed, the valve group is in a recoil explosion-proof state.
(7) The recoil explosion-proof flow cut-off valve group has the advantages of compact integral structure, simple and reliable automatic flow cut-off mode, high sensitivity, small hysteresis, high dynamic quality and high reliability, and can stably work even under high pressure with ultra-large flow through the differential pressure flow amplification control principle.
(8) The recoil explosion-proof flow cut-off valve set can be operated to close only by adopting a 24v signal power supply for the forced cylinder control mechanism in a manual mode.
Drawings
FIG. 1 is a schematic diagram of a backflushing explosion proof flow shut-off valve assembly;
the reference numerals are as follows: the valve comprises a main valve core 1, a valve body 2, a forced cylinder 3, a differential pressure spring 4, a valve core approach switch 5, a forced cylinder approach switch 6, a blocking 7, a hydraulic valve 8, a one-way valve I9, a one-way valve II 10, a solenoid valve I11, a double one-way valve 12, a stop valve I13, a stop valve II 14, a differential pressure compensation valve 15, a solenoid valve II 16 and a damping hole 17.
Detailed Description
The invention will be described in further detail below with reference to the drawings and examples. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the invention.
Example 1
As shown in FIG. 1, the recoil explosion-proof flow cut-off valve group comprises a forced control mechanism, a differential pressure induction control mechanism, a forced cylinder control mechanism and a restarting control mechanism which are connected between an energy accumulator B and an oil cylinder A; the forced control mechanism comprises a main valve core 1, a valve body 2, a forced cylinder 3, a differential pressure spring 4, a valve core approach switch 5, a forced cylinder approach switch 6 and a blocking 7; the differential pressure induction control mechanism comprises a double check valve 12, a stop valve I13 and a differential pressure compensation valve 15; the forced cylinder control mechanism comprises a hydraulic valve 8, a one-way valve I9, a one-way valve II 10 and an electromagnetic valve I11; the restarting control mechanism comprises a stop valve II 14 and an electromagnetic valve II 16; the accumulator B and the oil cylinder A are connected with the main valve core 1 through a pipeline, the main valve core 1 is in a slide valve form, a push rod is arranged in the forced cylinder 3 and directly acts on the slide valve core, a pressure difference spring 4 is arranged between the slide valve core and the valve base, the slide valve core and the pressure difference spring 4 are both arranged in the valve body 2, and a valve core approach switch 5 is used for monitoring the distance between the push rod and the slide valve core; the forced cylinder proximity switch 6 is used for monitoring the displacement of the push rod in the forced cylinder 3; the differential pressure induction control mechanism is communicated with the energy accumulator B and the oil cylinder A through pipelines, potential energy between the energy accumulator B and the oil cylinder A is utilized to drive the forced cylinder control mechanism to operate, and the forced cylinder control mechanism controls the forced cylinder 3 to operate; the restarting control mechanism is used for restarting the forced control mechanism.
The push rod in the forced cylinder 3 directly acts with the differential pressure spring 4 through the main valve core 1, and the main valve core 1 is in an open state when normally working under the action of the differential pressure spring 4; the upper end and the bottom of the main valve core 1 are respectively provided with a control oil pipeline, the control oil circuit at the upper end of the main valve core is communicated with the energy accumulator B, and the control oil pipeline at the bottom of the main valve core 1 is communicated with the oil cylinder A and drives the block 7 to act on the bottom of the main valve core 1.
The piston cavity of the forced cylinder 3 is communicated with a hydraulic valve 8 and a one-way valve I9, and the hydraulic valve 8 is also communicated with a one-way valve II 10 and an electromagnetic valve I11; the electromagnetic valve I11 is communicated with the double check valve 12 and the forced cylinder 3; the hydraulic valve 8 is a two-position three-way electromagnetic valve, and an oil drain port of the hydraulic valve is connected with a piston rod cavity of the forced cylinder 3 and a spring cavity L1 of the hydraulic valve 8 and is connected with the mailbox L.
The differential pressure compensating valve 15 has three interfaces: an inlet P, a spring end control oil port P1 and an outlet T; the inlet P is provided with two branch pipelines, one branch pipeline is connected with the electromagnetic valve II 16, and the other branch pipeline is communicated with the double check valve 12; the spring end control oil port P1 is communicated with the electromagnetic valve II 16, the other end of the double check valve 12 and the stop valve I13; the outlet T is communicated with a piston cavity of the forced cylinder 3 through a one-way valve I9 and a hydraulic valve 8, and is also communicated with the other end of the hydraulic valve 8 and an electromagnetic valve I11 through a one-way valve II 10; the electromagnetic valve I11 is also communicated with the double check valve 12 and the forced cylinder 3; the two ends of the double check valve 12 are respectively connected with the energy accumulator B and the oil cylinder A.
The accumulator B is connected with one end of the double check valve 12 through a stop valve I13, and the loaded oil cylinder A is connected with a differential pressure compensation valve 15 and an electromagnetic valve II 16 through a stop valve II 14.
The hydraulic valve 8 has four interfaces: an R1 interface communicated with the differential pressure compensation valve 15, an interface respectively communicated with the forced cylinder 3 and the electromagnetic valve I11, and an L1 interface connected with the oil tank L, wherein a pipeline communicated with the electromagnetic valve I11 and the double forced cylinder 3 is also communicated with a pipeline of the L1 interface in a crossing way; the passage between the outlet T of the differential pressure compensating valve 15 and the check valve 10 also has a damping orifice 17.
The valve core approach switch 5 is arranged between the push rod and the main valve core 1; a forcing cylinder proximity switch 6 is installed in the forcing cylinder 3.
The recoil explosion-proof flow cut-off valve set is provided with an automatic flow closing mode and a manual closing mode, and the automatic flow closing mode reacts spontaneously by virtue of a forced control mechanism: when the pipeline between the oil cylinder and the energy accumulator is seriously invalid or the overrun load stall caused by the system failure falls down, the forced control mechanism can automatically cut off the main oil way, prevent the output of the ultra-large flow and protect the hydraulic system; the manual closing mode realizes the closing operation of the forced cylinder 3 by means of the forced cylinder control mechanism: the electromagnetic valve I11 is started and controlled through an electrohydraulic signal in manual operation, and then the pressure difference induction control mechanism is utilized to enable the higher pressure of the pipelines at the two sides of the accumulator B or the oil cylinder A to act on the piston of the forced cylinder 3 through the double check valve 12, so that the forced cylinder 3 is operated to push the main valve core 1 to move, and the flow between the accumulator and the hydraulic cylinder is cut off.
In the manual closing mode, when the push rod of the forcing cylinder 3 pushes the main valve core 1 to move, the forcing cylinder proximity switch 6 and the valve core proximity switch 5 send out signal changes to display the sensing position of manual closing; when the push rod return signal of the forced cylinder 3 is displayed by the main valve core 1 approaching switch 5, the main valve opening of the main valve core 1 is in a closed state until the pressure of the oil cylinder A reaches the same pressure as the pressure of the accumulator B; when the pressure reaches equilibrium at the upper and lower ends of the main spool 1, the main spool 1 reopens, forcing the cylinder proximity switch 6 to indicate the main spool 1 reopen, and at the same time, the solenoid valve ii 16 will provide a flow change across the flow balanced main spool 1 to reduce the differential pressure force effects.
The R1 interface and L1 interface restart control mechanism of the hydraulic valve 8 is provided with a manual lock valve that controls only the unbalanced effect from the higher cylinder a pressure to the lower accumulator B pressure, but cannot control the higher accumulator B to the lower cylinder a pressure.
The recoil explosion-proof flow cut-off valve group does not need an external power source, and the valve group is closed instantaneously by means of the pressure difference between the self energy accumulator group and the oil cylinder, so that time delay is almost avoided, the reaction is sensitive, and the feedback efficiency is high. The recoil explosion-proof flow cut-off valve is particularly suitable for the control occasion of oil medium with high pressure and super-large flow, the maximum working pressure can reach 30MPa, and the maximum flow can reach 1500L/min.
Example 2
As shown in FIG. 1, the recoil explosion-proof flow cut-off valve group comprises a forced control mechanism, a differential pressure induction control mechanism, a forced cylinder control mechanism and a restarting control mechanism which are connected between an energy accumulator B and an oil cylinder A; the forced control mechanism comprises a main valve core 1, a valve body 2, a forced cylinder 3, a differential pressure spring 4, a valve core approach switch 5, a forced cylinder approach switch 6 and a blocking 7; the differential pressure induction control mechanism comprises a double check valve 12, a stop valve I13 and a differential pressure compensation valve 15; the forced cylinder control mechanism comprises a hydraulic valve 8, a one-way valve I9, a one-way valve II 10 and an electromagnetic valve I11; the restarting control mechanism comprises a stop valve II 14 and an electromagnetic valve II 16; the accumulator B and the oil cylinder A are connected with the main valve core 1 through a pipeline, the main valve core 1 is in a slide valve form, a push rod is arranged in the forced cylinder 3 and directly acts on the slide valve core, a pressure difference spring 4 is arranged between the slide valve core and the valve base, the slide valve core and the pressure difference spring 4 are both arranged in the valve body 2, and a valve core approach switch 5 is used for monitoring the distance between the push rod and the slide valve core; the forced cylinder proximity switch 6 is used for monitoring the displacement of the push rod in the forced cylinder 3; the differential pressure induction control mechanism is communicated with the energy accumulator B and the oil cylinder A through pipelines, potential energy between the energy accumulator B and the oil cylinder A is utilized to drive the forced cylinder control mechanism to operate, and the forced cylinder control mechanism controls the forced cylinder 3 to operate; the restarting control mechanism is used for restarting the forced control mechanism. The specific structure and functions of the components are the same as those of embodiment 1.
Furthermore, the valve port of the differential pressure compensating valve 15 is designed in a 1:1 ratio, and is biased to a closed position by an adjustable spring arrangement; when the pressure value of the oil cylinder A exceeds the sum of the pressure value of the accumulator B and the spring set value of the differential pressure compensation valve 15, the valve port of the differential pressure compensation valve 15 overflows, and the overflow action of the differential pressure compensation valve 15 enables control oil in the interface of the hydraulic valve 8L1 to move, so that the control oil is limited to flow out of a piston cavity of the forced cylinder 3; at the same time, the cylinder a pressure and the flow through the port of the hydraulic valve 8R1 for the shifting action are fed into the piston chamber of the force cylinder 3, so that the force cylinder 3 and the main valve element 1 are kept closed also in the case of some residual leakage at the L1 port.
The pressure difference setting for re-opening the hydraulic valve 8 is determined by the elasticity of the spring on the R1 interface; the open/close state of the main valve element 1 is monitored by an instruction from a valve element proximity switch 5 and a forced cylinder proximity switch 6.
Only when the interface of the hydraulic valve 8R1 is in a gear shifting position and the system pressure is equal, the electromagnetic valve I11 and the hydraulic valve 8 can control the opening of the forced cylinder 3 and the main valve core 1 in a linkage manner; only when the pressure between accumulator B and cylinder a of the valve block is balanced will main spool 1 reopen.
The backflushing explosion-proof flow cutoff valve group has a safety monitoring function: 1) When the valve group system works normally, the valve group is in a normally open state, a valve core approach switch 5 on the main valve core 1 has no signal, and a forced cylinder approach switch 6 on the forced cylinder 3 is in a signal sending state; 2) When the recoil is explosion-proof, the main valve core 1 is in a closed position, and a valve core proximity switch 5 sends out a sensing position of a valve port closing indication.
The valve group is an electrohydraulic loop controlled valve group, no external hydraulic and electric operation is needed in an automatic mode, the electromagnetic valve I11 and the electromagnetic valve II 16 are in zero leakage, the leakage oil flow is only generated when the valve is manually closed by an external oil drain port, and no leakage oil exists under normal conditions.
The electromagnetic valve I11 is an electromagnetic valve with a positioning function and can be kept in a functional position under the condition of power failure.
The restarting control mechanism is communicated with the liquid level pressure at the two ends of the main valve core 1 through the electromagnetic valve II 16, so that the pressure difference at the two ends of the restarting control mechanism is within the elastic value of the differential pressure spring 4, and the restarting operation of the valve group is facilitated.
The invention discloses a backflushing explosion-proof flow cut-off valve group, which is a safety valve for preventing pipeline breakage under the working condition of high pressure and large flow, and can be used for cutting off the flow of a hydraulic circuit between a large-sized energy accumulator group and an oil cylinder. When the hydraulic system works normally, the valve bank is in an open state, when a pipeline or a flange breaks and fails, the large-scale hydraulic load mechanism drops the stall degree, and once the hydraulic circuit between the accumulator bank and the oil cylinder breaks and fails, the valve bank does not need external control action, the valve port of the main valve core can be immediately closed, namely, the circuit is automatically cut off and the outlet of the accumulator is closed, thus the high-pressure and high-flow oil energy backflushing injection of the accumulator can be effectively prevented, and secondary accidents are prevented.
The recoil explosion-proof flow cut-off valve group has the advantages of compact integral structure, simple and reliable automatic flow cut-off mode, high sensitivity, small hysteresis, high dynamic quality and high reliability, and can stably work even under high pressure with ultra-large flow through the differential pressure flow amplification control principle.
While the foregoing description illustrates and describes the preferred embodiments of the present invention, as noted above, it is to be understood that the invention is not limited to the forms disclosed herein but is not to be construed as excluding other embodiments, and that various other combinations, modifications and environments are possible and may be made within the scope of the inventive concepts described herein, either by way of the foregoing teachings or by those of skill or knowledge of the relevant art. And that modifications and variations which do not depart from the spirit and scope of the invention are intended to be within the scope of the appended claims.
Claims (6)
1. A recoil explosion-proof flow cut-off valve group is characterized in that: the device comprises a forced control mechanism, a differential pressure induction control mechanism, a forced cylinder control mechanism and a restarting control mechanism which are connected between an energy accumulator B and an oil cylinder A; the forced control mechanism comprises a main valve core (1), a valve body (2), a forced cylinder (3), a differential pressure spring (4), a valve core proximity switch (5), a forced cylinder proximity switch (6) and a blockage (7); the push rod in the forced cylinder (3) directly acts with the pressure difference spring (4) through the main valve core (1), and the main valve core (1) is in an open state when normally working under the action of the pressure difference spring (4); the upper end and the bottom of the main valve core (1) are respectively provided with a control oil pipeline, a control oil circuit at the upper end of the main valve core is communicated with the energy accumulator B, and the control oil pipeline at the bottom of the main valve core (1) is communicated with the oil cylinder A and drives the block (7) to act on the bottom of the main valve core (1); the differential pressure induction control mechanism comprises a double one-way valve (12), a stop valve I (13) and a differential pressure compensation valve (15); the forced cylinder control mechanism comprises a hydraulic valve (8), a one-way valve I (9), a one-way valve II (10) and an electromagnetic valve I (11); the restarting control mechanism comprises a stop valve II (14) and an electromagnetic valve II (16); the piston cavity of the forced cylinder (3) is communicated with a hydraulic valve (8) and a one-way valve I (9), and the hydraulic valve (8) is also communicated with a one-way valve II (10) and an electromagnetic valve I (11); the electromagnetic valve I (11) is communicated with the double check valve (12) and the forced cylinder (3); the hydraulic valve (8) is a two-position three-way electromagnetic valve, and an oil drain port of the hydraulic valve is connected with a piston rod cavity of the forced cylinder (3) and a spring cavity L1 of the hydraulic valve (8) and is connected with an oil tank oil port L; the differential pressure compensation valve (15) has three interfaces: an inlet P, a spring end control oil port P1 and an outlet T; the inlet P is provided with two branch pipelines, one branch pipeline is connected with the electromagnetic valve II (16), and the other branch pipeline is communicated with the double check valve (12); the spring end control oil port P1 is communicated with the electromagnetic valve II (16), the other end of the double check valve (12) and the stop valve I (13); the outlet T is communicated with a piston cavity of the forced cylinder (3) through a one-way valve I (9) and a hydraulic valve (8), and is also communicated with the other end of the hydraulic valve (8) and an electromagnetic valve I (11) through a one-way valve II (10); the electromagnetic valve I (11) is also communicated with the double one-way valve (12) and the forced cylinder (3) at the same time; the two ends of the double unidirectional valves (12) are respectively connected with the energy accumulator B and the oil cylinder A; the accumulator B is connected with one end of the double-check valve (12) through a stop valve I (13), and the loaded oil cylinder A is connected with the differential pressure compensation valve (15) and the electromagnetic valve II (16) through a stop valve II (14); the energy accumulator B and the oil cylinder A are connected with a main valve core (1) through a pipeline, the main valve core (1) is in a slide valve form, a push rod is arranged in the forced cylinder (3) and directly acts on the slide valve core, a pressure difference spring (4) is arranged between the slide valve core and a valve base, the slide valve core and the pressure difference spring (4) are both arranged in the valve body (2), and the valve core proximity switch (5) is used for monitoring the distance between the push rod and the slide valve core; the forced cylinder proximity switch (6) is used for monitoring the displacement of the push rod in the forced cylinder (3); the pressure difference induction control mechanism is communicated with the energy accumulator B and the oil cylinder A through pipelines, potential energy between the energy accumulator B and the oil cylinder A is utilized to drive the forced cylinder control mechanism to operate, and the forced cylinder control mechanism controls the forced cylinder (3) to operate; the restarting control mechanism is used for restarting the forced control mechanism.
2. The backflushing explosion proof flow shut off valve set of claim 1, wherein: the hydraulic valve (8) has four interfaces: an R1 interface communicated with the differential pressure compensation valve (15), interfaces respectively communicated with the forced cylinder (3) and the electromagnetic valve I (11), and an L1 interface connected with an oil tank oil port L, wherein a pipeline communicated with the electromagnetic valve I (11) and the double-forced cylinder (3) is also communicated with a pipeline of the L1 interface in a crossing way; a damping hole (17) is also arranged on a passage between the outlet T of the differential pressure compensation valve (15) and the one-way valve (10).
3. The backflushing explosion proof flow shut off valve set of claim 1, wherein: the valve core approach switch (5) is arranged between the push rod and the main valve core (1); the forced cylinder approach switch (6) is installed in the forced cylinder (3).
4. The backflushing explosion proof flow shut off valve set of claim 1, wherein: the recoil explosion-proof flow cutoff valve group is provided with an automatic flow closing mode and a manual closing mode, and the automatic flow closing mode reacts spontaneously by means of a forced control mechanism: when the pipeline between the oil cylinder A and the energy accumulator B is broken or seriously fails, or the overrun load stall caused by the system failure falls down, the forced control mechanism can automatically cut off a main oil way, prevent the output of super-large flow and protect a hydraulic system; the manual closing mode relies on a forced cylinder control mechanism to effect closing operation of the forced cylinder (3): the electromagnetic valve I (11) is started and controlled through an electrohydraulic signal in a manual operation mode, and then a pressure difference induction control mechanism is utilized to enable the higher pressure of the pipelines on the two sides of the energy accumulator B or the oil cylinder A to act on the forcing cylinder (3) through the double one-way valve (12), so that the forcing cylinder (3) is operated to push the main valve core (1) to move, and the flow between the energy accumulator and the hydraulic cylinder is cut off.
5. The backflushing explosion proof flow shut off valve set of claim 4, wherein: in the manual closing mode, when the push rod of the forced cylinder (3) pushes the main valve core (1) to move, the forced cylinder proximity switch (6) and the valve core proximity switch (5) send out signal changes to display the sensing position of manual closing; when a push rod return signal of the forced cylinder (3) is displayed by a proximity switch (5) of the main valve core (1), a main valve opening of the main valve core (1) is in a closed state until the pressure of the oil cylinder A reaches the same pressure as that of the energy accumulator B; when the pressure reaches balance at the upper end and the lower end of the main valve core (1), the main valve core (1) is opened again, the forced cylinder proximity switch (6) indicates the main valve core (1) to be opened again, and meanwhile, the electromagnetic valve II (16) provides flow change at the two ends of the flow balance main valve core (1) so as to reduce the influence of pressure difference.
6. The backflushing explosion proof flow shut off valve set of claim 1, wherein: the R1 interface and L1 interface restarting control mechanism of the hydraulic valve (8) is provided with a manual locking valve which only controls the unbalanced effect from the higher cylinder A pressure to the lower accumulator B pressure and cannot control the pressure from the higher accumulator B to the lower cylinder A.
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