CN107917120B - pilot-operated electromagnetic reversing valve - Google Patents
pilot-operated electromagnetic reversing valve Download PDFInfo
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- CN107917120B CN107917120B CN201711076453.2A CN201711076453A CN107917120B CN 107917120 B CN107917120 B CN 107917120B CN 201711076453 A CN201711076453 A CN 201711076453A CN 107917120 B CN107917120 B CN 107917120B
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- 239000007788 liquid Substances 0.000 claims abstract description 50
- 230000009471 action Effects 0.000 claims description 11
- 238000012360 testing method Methods 0.000 claims description 10
- 238000000034 method Methods 0.000 claims description 7
- 230000008859 change Effects 0.000 claims description 6
- 230000008569 process Effects 0.000 claims description 5
- 238000004146 energy storage Methods 0.000 claims 1
- 239000003921 oil Substances 0.000 description 46
- 230000001276 controlling effect Effects 0.000 description 23
- 230000001105 regulatory effect Effects 0.000 description 8
- 238000011056 performance test Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 238000013461 design Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000006641 stabilisation Effects 0.000 description 2
- 238000011105 stabilization Methods 0.000 description 2
- 230000002457 bidirectional effect Effects 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 238000009863 impact test Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 230000000087 stabilizing effect Effects 0.000 description 1
Classifications
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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
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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
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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
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
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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
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/10—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit
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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)
Abstract
A pilot-operated electromagnetic reversing valve applied to on-off control of an energy accumulator is of a double-valve-core structure and comprises a first valve core and a second valve core, wherein the first valve core is communicated with an oil way, the second valve core is connected with a first energy accumulator, when the pressure of an outlet of a pump is larger than a preset value, a control part controls the first valve core to reverse so that the oil way is stopped from a channel of the first energy accumulator, and the second valve core reverses so that a liquid tank is discharged back from oil of the first energy accumulator or liquid is supplied to other parts of a hydraulic system.
Description
Technical Field
The invention relates to a pilot-operated electromagnetic reversing valve, in particular to a pilot-operated electromagnetic reversing valve applied to the on-off control of an energy accumulator.
Background
The accumulator is an important auxiliary device in a hydraulic system, mainly used for storing pressure energy of oil, but has different use effects when being applied to different occasions, such as the application of the accumulator to absorbing pressure and flow pulsation when a hydraulic pump works; or the oil release device is used for storing a large amount of oil in a hydraulic system in a short time, and releasing the oil stored in the energy accumulator when the oil is used, so that the oil is supplied to the system for use, and different functions are realized; however, in order to achieve different use effects by using the accumulator, different hydraulic components and complex-designed hydraulic systems are often required, and the cost is high.
Therefore, it is necessary to design a hydraulic valve for controlling the opening and closing of the accumulator, which has simple structure, low cost and convenient operation, and provides more and better choices for realizing different use effects of the accumulator.
Disclosure of Invention
The invention provides a pilot-operated electromagnetic reversing valve applied to on-off control of an energy accumulator. The pilot-operated electromagnetic directional valve adopts a double-valve-core structure and comprises a first valve core and a second valve core, wherein the first valve core is communicated with an oil path, the second valve core is connected with a first energy accumulator, when the pressure of an outlet of the pump is greater than a preset value, a control part controls the first valve core to change direction so that the oil path is cut off from a channel of the first energy accumulator, and the second valve core changes direction so that oil in the first energy accumulator is discharged back to a liquid tank or supplies liquid to other parts of a hydraulic system.
The inlet of the first valve core is communicated with an oil path of an outlet of a hydraulic pump, the outlet of the first valve core is communicated with the inlet of the second valve core and the first accumulator, the inlet of the second valve core is communicated with the outlet of the first valve core and the first accumulator, a channel connected with a liquid tank is reserved on the second valve core, and the channel is cut off in an initial state.
When the system pressure reaches a certain value, the control part controls the first valve core to change direction so that the oil way is cut off from the first energy accumulator channel, a certain amount of high-pressure oil is stored in the first energy accumulator, and the control part can control the second valve core to change direction according to actual needs according to the actual hydraulic system and working conditions of the electromagnetic directional valve, so that the high-pressure oil reserved in the first energy accumulator supplies liquid to other parts of the hydraulic system or discharges the liquid back to the liquid tank.
Preferably, the two valve core strings adopt an integrated structure and are connected with the valve body through screw sleeves.
Preferably, the control valve core of the first valve core is provided with an air hole, so that a closed air cavity is formed between an inner cavity of the control valve core and a valve rod of the liquid passing sleeve to prevent the reliable stop in the process of preventing the thrust valve core from acting.
The pilot-operated electromagnetic directional valve can be applied to various hydraulic systems.
Be applied to high-pressure hydraulic pump test system: the high-pressure hydraulic test system comprises a tested hydraulic pump, a second energy accumulator, a pilot electromagnetic reversing valve, a pressure sensor and a control part; the second energy accumulator is communicated with an oil path at the outlet of the hydraulic pump, and the first energy accumulator is communicated with the oil path at the outlet of the hydraulic pump through a pilot electromagnetic reversing valve. The first energy accumulator is a low-pressure energy accumulator with low inflation pressure, and the second energy accumulator is a high-pressure energy accumulator with high inflation pressure.
The method is applied to quick action and fine adjustment loops of the hydraulic cylinder: the system also comprises a hydraulic pump, a pilot type electromagnetic unloading valve, a three-position four-way electromagnetic reversing valve, a pilot type electromagnetic reversing valve, a one-way valve, a hydraulic cylinder and a pressure sensor; the pilot electromagnetic unloading valve and the pressure sensor are connected to the outlet of the hydraulic pump, the hydraulic cylinder is communicated with the outlet of the pilot electromagnetic unloading valve through a three-position four-way reversing valve, meanwhile, the energy accumulator is communicated with the outlet of the pilot electromagnetic unloading valve through the pilot electromagnetic reversing valve, and the outlet of the pilot electromagnetic reversing valve is connected with the lower cavity of the hydraulic cylinder through a one-way valve.
The method is applied to the performance test of the large-flow safety valve: the system also comprises a hydraulic pump, a pilot type electromagnetic unloading valve, a two-position four-way reversing valve, a two-way lock, a hydraulic cylinder, a tested large-flow safety valve, a first pressure sensor, a second pressure sensor, a plurality of groups of pilot type electromagnetic reversing valves and an energy accumulator; the pilot electromagnetic unloading valve and the first pressure sensor are connected to the outlet of the hydraulic pump, the hydraulic cylinder is sequentially connected with the two-way lock, the two-position four-way electromagnetic reversing valve and the outlet of the pilot electromagnetic unloading valve, the plurality of energy accumulators are communicated with the outlet of the pilot electromagnetic unloading valve through the pilot electromagnetic reversing valve, meanwhile, the outlet of the pilot electromagnetic reversing valve is connected with the lower cavity of the hydraulic cylinder through the one-way valve, the tested large-flow safety valve is connected in series to the upper cavity of the hydraulic cylinder, and the front end of the safety valve is connected with the second pressure sensor.
Drawings
FIG. 1 is a schematic diagram of a system for high pressure hydraulic pump testing according to the present disclosure;
FIG. 2 is a schematic view of a valve spool of the pilot operated electromagnetic directional valve of the present disclosure;
FIG. 3 is a system schematic for an accumulator fast-acting circuit of the present disclosure;
FIG. 4 is a system schematic for a high flow safety valve performance test of the present disclosure;
Reference numerals:
1-tested high pressure pump; 2-driving the motor; 3-a filter; 4-a first accumulator; 6-a pressure sensor; 7-a second accumulator; 8-a digital pressure regulating valve; 9-a cooler; 10-safety valve; 11-a liquid tank; 12-pilot type electromagnetic directional valve
8-1-a digital pressure regulating valve damping hole; 8-2-digital pressure regulating valve main valve core; 8-3-digital pressure regulating valve main spring; 8-4-digital pressure regulating valve electromagnetic pilot valve; 8-5-digital pressure regulating valve pilot spool; 8-6-digital pressure regulating valve pilot spring; 8-7-a digital pressure regulating valve pilot valve seat; 8-8-linear stepping motor.
12-1 a first valve core; 12-2 second valve core, 12-3 electromagnetic pilot valve for controlling first valve core action; 12-4, an electromagnetic pilot valve for controlling the action of the second valve core;
21 a second valve core thread sleeve; 22 a second spool stem; 23 second spool valve seat; 24 springs; 25, a second valve core liquid passing sleeve; 26 a first spool control spool; 27 a first valve core thread insert; 28 an electromagnetic directional valve; 29 an electromagnetic pilot valve filter; 30 a first poppet stem; 31 small screws; 32 a first spool valve seat; 41 a second valve core valve sleeve liquid through hole; 42 a second valve core valve rod liquid through hole; 43 a first valve core threaded sleeve liquid passing hole; 44 a first spool valve stem weep hole; 45 first valve core air hole;
51 a second spool string; 52 a second spool string;
61-a motor; 62-a hydraulic pump; 63-a pilot type electromagnetic unloading valve; 12-a pilot-operated electromagnetic directional valve; 64-an accumulator; 65-one-way valve; 66-three-position four-way electromagnetic directional valve; 67-hydraulic cylinders; 68-a pressure sensor; 69-liquid box
71-a motor; 72-a hydraulic pump; 73-a pilot electromagnetic unloading valve; 74-two-position four-way electromagnetic directional valve; 75-relief valves; 76-pressure sensor a; 77-one-way valve; 12-a pilot-operated electromagnetic directional valve; 78-an accumulator; 79-bidirectional lock; 80-hydraulic cylinder; 81-pressure sensor B; 82-large flow safety valve to be tested; 83-liquid box
Detailed Description
the technical solutions in the embodiments of the present disclosure will be described below in a clear and complete manner with reference to the drawings in the embodiments of the present disclosure, and it is obvious that the described embodiments are only a part of the embodiments of the present disclosure, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments disclosed herein without making any creative effort, shall fall within the protection scope of the present disclosure.
Example 1
The hydraulic pump testing device can be used for testing a high-pressure hydraulic pump, an oil circuit system is shown in figure 1, a second accumulator 7 is communicated with an outlet oil circuit of a tested hydraulic pump 1, a first accumulator 4 is communicated with the outlet oil circuit of the tested hydraulic pump 1 through a pilot type electromagnetic reversing valve 12, when the pressure of the tested hydraulic pump 1 is larger than a preset value after the tested hydraulic pump 1 is started, a control part controls a first valve core 12-1 to be reversed so that the oil circuit is stopped from a channel of the first accumulator 4, meanwhile, a channel between the first accumulator 4 and a liquid tank 11 is opened through reversing of a second valve core 12-2, and residual oil in the first accumulator 4 returns to the liquid tank through the second valve core 12-2.
The specific working process is as follows:
Firstly, a tested high-pressure pump 1 is started, a system is in a no-load starting state, preset pressure values are set in upper computer software, at the moment, control signals are not sent to an electromagnetic pilot valve 12-3 for controlling the first valve core to act and an electromagnetic pilot valve 12-4 for controlling the second valve core to act of a pilot type double-valve-core electromagnetic directional valve 12, the first valve core 12-1 and the second valve core 12-2 do not act, oil enters a first energy accumulator 4 through the first valve core 12-1, the second energy accumulator 7 is always connected, but due to high inflation pressure of the second energy accumulator, the system pressure does not enable an air bag of the second energy accumulator to generate large deformation, and at the moment, the first energy accumulator 4 with low inflation pressure of the system plays a role in system pressure stabilization. Then, the system is judged in a software circulation mode, when the system pressure is lower than a set pressure value, the upper computer still does not send control signals to the electromagnetic pilot valve 12-3 for controlling the first valve core to act and the electromagnetic pilot valve 12-4 for controlling the second valve core to act of the pilot type double-valve-core electromagnetic directional valve 12, and the system still realizes the pressure stabilization effect by the first energy accumulator 4 with low inflation pressure; when the pressure of the system reaches or exceeds a preset pressure value, control signals are sent to an electromagnetic pilot valve 12-3 for controlling the first valve core to act and an electromagnetic pilot valve 12-4 for controlling the second valve core to act through the pilot type double-valve-core electromagnetic directional valve 12 through upper computer software, the first valve core 12-1 is reversed, the channel from the system to the first energy accumulator 4 is cut off, meanwhile, the second valve core 12-2 is reversed, residual oil in the first energy accumulator 4 returns to a liquid tank through the second valve core 12-2, at the moment, the first energy accumulator 4 is cut off, and the pressure of the system is kept stable by the second energy accumulator 7. And (3) slightly delaying in software of the upper computer, if the time is 500ms, continuing to judge, if the detected high-pressure pump 1 stops working, stopping sending a control signal to an electromagnetic pilot valve of the pilot electromagnetic directional valve 12 by the upper computer, and if the detected high-pressure pump 1 does not stop working, returning to continue circularly judging the relation between the system pressure value and the preset pressure value.
The first valve core string 51 and the second valve core string 52 are of an integrated structure, are connected through the screws 31 and are connected with the valve body through the screw sleeves, and are convenient to disassemble and assemble. The two electromagnetic pilot valve designs constitute the electromagnetic pilot valve 28 within one valve block.
when the system works, the port P is communicated with the outlet of a tested high-pressure pump, when the system is in a low-pressure state, oil enters the first energy accumulator through the port P, the first valve core valve rod liquid passing hole 44, the first valve core screw sleeve liquid passing hole 43 and the channel A, and the pressure of the system is maintained to be stable by the first energy accumulator. Combining with upper computer software, when the system pressure is higher than the set pressure, at this time, a control signal is sent to two electromagnets of the electromagnetic pilot valve 28 at the same time, the oil in the port P enters the electromagnetic pilot valve 28 through a filter, and enters the control ports K1 and K2 after being reversed by the electromagnetic pilot valve, wherein the oil in the port K1 enters the control chamber, and here acts on the annular end face of the control chamber at the lower end of the first valve core control valve core 26, the acting force of which is greater than the acting force acting on the annular end face at the upper end of the first valve core control valve core 26, pushes the first valve core control valve core 26 to move upwards and is pressed on the first valve seat 32, and here, the first valve core control valve core 26 is provided with an air hole 45 to prevent that a closed air cavity is formed between the inner cavity of the control valve core 26 and the first valve core 30 in the process of pushing the first valve core control valve core 26 to move upwards, so that the first valve, the port P and the first energy accumulator can not be reliably cut off. At the moment, the port P and the first valve core thread sleeve liquid passing hole 43 are cut off, and oil cannot enter the first energy accumulator; meanwhile, the control liquid of the port K2 acts on the control end of the second valve spool valve rod 22, the second valve spool valve rod 22 overcomes the spring force of the spring 24, so that the second valve sleeve liquid passing hole 41 is communicated with the second valve spool valve rod liquid passing hole 42, the residual oil liquid in the first accumulator is communicated with the second valve spool valve rod liquid passing hole 42 through the port A and the second valve sleeve liquid passing hole 41, and returns to the liquid tank through the port T, and the pressure of the system is maintained to be stable by the second accumulator. When the system pressure is lower than the set pressure, the control signal is stopped from being sent to the electromagnetic pilot valve 28, the first valve core string 51 and the second valve core string 52 are reset, and the pressure of the system is maintained to be stable again by the first accumulator.
The system has the advantages that: when the electromagnetic directional control valve is applied to switching of the energy accumulator, compared with a conventional electromagnetic directional valve, the electromagnetic directional control valve is higher in stability, if a certain electromagnetic pilot valve fails, the disturbance on the pressure of the whole hydraulic system is smaller, and the stability of the system is improved. The specific principle is as follows: if the electromagnetic pilot valve controlling the first valve core to act fails, when the system pressure is greater than the set pressure, the control part simultaneously sends a control signal to the electromagnetic pilot valve controlling the first valve core and the second valve core to act, at the moment, the first valve core does not act due to the failure of the electromagnetic pilot valve controlling the first valve core to act, the second valve core is reversed, so that a channel between the first energy accumulator and the liquid tank is opened, and at the moment, high-pressure oil from the hydraulic pump returns to the liquid tank through the channel, so that the first energy accumulator is protected; if the electromagnetic pilot valve controlling the second valve core to act is in fault, when the system pressure is greater than the set pressure, the control part simultaneously sends control signals to the electromagnetic pilot valve controlling the first valve core and the second valve core to act, the first valve core is reversed, so that an oil way at the outlet of the hydraulic pump is cut off from a channel of the first energy accumulator, the system plays a role in stabilizing the pressure by the second energy accumulator, and at the moment, the second valve core controls the electromagnetic pilot valve controlling the second valve core to act in fault, but not act, the direct channel between the first energy accumulator and the liquid tank can not be opened, so that a part of oil liquid can be remained in the first energy accumulator, when the pressure of the system is lower than a set value or the system stops working, the control part stops sending a control signal to the electromagnetic pilot valve which controls the first valve core and the second valve core to act, the first valve core is reset, the first energy accumulator is communicated with a channel of an oil way at the outlet of the hydraulic pump, and oil remained in the first energy accumulator is discharged back to the oil tank through the system;
Example 2
the pilot-operated electromagnetic directional valve in the embodiment can be used for a hydraulic cylinder quick action and fine adjustment loop.
The working principle is shown in fig. 3, the outlet of the hydraulic pump 62 is connected with a three-position four-way electromagnetic directional valve 66 and a hydraulic cylinder 67, the outlet of the hydraulic pump 62 is connected with a pilot type electromagnetic unloading valve 63 and a pressure sensor 68, and an energy accumulator 64 is communicated with the outlet of the hydraulic pump 62 through the pilot type electromagnetic directional valve 12, wherein the inlet of a first valve core 12-1 is communicated with the outlet of the hydraulic pump 62, the outlet of the first valve core is communicated with the energy accumulator 64, and the outlet of a second valve core 12-2 is communicated with the lower cavity of the hydraulic cylinder 67 through a one-way valve 65.
the accumulator 64 mainly stores oil and supplies liquid to the lower cavity of the hydraulic cylinder so as to realize quick action or fine adjustment of the hydraulic cylinder; the pressure sensor 68 functions as a pressure feedback; the pilot electromagnetic unloading valve 63 mainly plays a role in unloading the system; the check valve 65 mainly plays a role in preventing oil in a lower cavity of the hydraulic cylinder 67 from flowing backwards;
The specific implementation scheme is as follows:
When the three-position, four-way solenoid directional valve 66 is in the neutral position, the hydraulic fluid from the hydraulic pump 62 is now charged to the accumulator 64 through the pilot-operated solenoid directional valve 12. The upper computer feeds back the system pressure through the pressure sensor 68, when the pressure rises to a certain value, a control signal is sent to and kept by the electromagnetic pilot valve 12-3 which controls the action of the first valve core by the pilot electromagnetic directional valve 12, the first valve core 12-1 is switched to be cut off, so that a passage between the main loop and the energy accumulator 64 is cut off, and a certain volume of oil is stored in the energy accumulator 64; meanwhile, a control signal is sent to the pilot electromagnetic unloading valve 63, and the oil discharged by the hydraulic pump 2 is unloaded by the pilot electromagnetic unloading valve 63 and then returns to the tank 69.
If liquid leakage exists in the lower cavity of the hydraulic cylinder 67 or slight jacking needs to be realized, a control signal is sent to and maintained by the electromagnetic pilot valve 12-4 of the pilot electromagnetic directional valve 12 for controlling the second valve core to act, the second valve core 12-2 is reversed, a channel between the energy accumulator 64 and the one-way valve 65 is opened, oil in the energy accumulator 64 enters the lower cavity of the hydraulic cylinder 67 through the one-way valve 65, when the hydraulic cylinder 67 is jacked in place, the electromagnetic pilot valve 12-4 of the pilot electromagnetic directional valve 12 for controlling the second valve core to act stops sending the control signal, and the second valve core 12-2 is reversed and stopped.
When the hydraulic cylinder 67 needs to realize quick jacking, a control signal is sent to the three-position four-way electromagnetic directional valve 66 to enable the three-position four-way electromagnetic directional valve to be in a left position or a right position, meanwhile, the control signal is stopped being sent to the pilot type electromagnetic unloading valve 63 and the electromagnetic pilot valve 12-3 for controlling the action of the first valve core, the first valve core 12-1 is reset, the energy accumulator 64 is communicated with the main loop, the pilot type electromagnetic unloading valve 63 stops unloading, oil from the hydraulic pump 62 and the energy accumulator 64 enters the hydraulic cylinder 67 through the three-position four-way electromagnetic directional valve 66, and the quick action of the hydraulic cylinder 8 can be realized.
The advantages of the embodiment are as follows: in a loop which needs the hydraulic cylinder to act quickly occasionally, a hydraulic pump with a smaller flow can be used for supplying liquid, so that the cost is reduced; meanwhile, leakage of the hydraulic cylinder can be compensated or fine adjustment of the position of the hydraulic cylinder can be realized under the condition that the pump is not started.
Example 3
the pilot-operated electromagnetic reversing valve in the embodiment can be used for performance tests of large-flow safety valves.
The working principle diagram is shown in fig. 4, a driving motor 71 drives a hydraulic pump 72 to suck liquid from a liquid tank 83, the oil returns to the liquid tank 83 through a two-position four-way electromagnetic directional valve 74, a two-way lock 79 and a hydraulic cylinder 80, a pilot type electromagnetic unloading valve 73, an overflow valve 75 and a pressure sensor A76 are further connected in series with the outlet of the hydraulic pump 72, a three-group energy accumulator 78 is connected in parallel with the outlet of the hydraulic pump 72 through three-group pilot type electromagnetic directional valves 12, wherein the inlet of a first valve core 12-1 of the pilot type electromagnetic directional valve 12 is connected with the outlet of the hydraulic pump 72, the outlet is communicated with the energy accumulator 78, and meanwhile, the first valve core 12-2 of each group of the pilot type electromagnetic directional valves 12 is communicated with the lower cavity of the hydraulic cylinder 80 through a one-way; in addition, the tested large-flow safety valve 82 is connected in parallel with the upper cavity of the hydraulic cylinder 80, and the front end of the tested large-flow safety valve is connected with a pressure sensor B81 in series.
The two-position four-way electromagnetic directional valve 74 plays a role in controlling the hydraulic cylinder 80 to reset; the bidirectional lock 79 plays a role in reducing impact on the two-position four-way electromagnetic directional valve 74 during impact test; the pilot electromagnetic unloading valve 73 plays a role in unloading the hydraulic system, the overflow valve 75 plays a role in overload protection, and the pressure sensor A76 plays a role in detecting the pressure at the outlet of the hydraulic pump 72; the accumulator 78 functions to store a volume of hydraulic oil; the pilot-operated electromagnetic directional valve 12 functions to control the accumulator 78 to charge and discharge liquid, wherein the first valve core 12-1 controls the charge liquid and the second valve core 12-2 controls the discharge liquid; the check valve 77 functions to prevent the reverse flow of the oil in the lower chamber of the hydraulic cylinder 80; the pressure sensor B81 functions to monitor the pressure profile during opening of the subject mass flow relief valve 82.
the specific working process is as follows:
in the initial state, the two-position four-way electromagnetic directional valve 74 is in the right position. The driving motor 71 drives the hydraulic pump 72 to operate, oil is filled into the energy accumulator 78 through the pilot type electromagnetic directional valve 12, the upper computer detects a pressure value acquired by the pressure sensor A76, when the system pressure reaches a certain value, the upper computer sends a control signal to the electromagnetic pilot valve 12-3 of the pilot type electromagnetic directional valve 12 for controlling the action of the first valve core and keeps the control signal, at the moment, the first valve core 12-1 is reversed, so that a passage between the main loop and the energy accumulator 78 is cut off, and at the moment, high-pressure oil with a constant volume is stored in the energy accumulator 78; meanwhile, a control signal is sent to the pilot electromagnetic unloading valve 73, so that the oil discharged by the hydraulic pump 2 is unloaded to the liquid return tank 83 through the pilot electromagnetic unloading valve 73.
then, a control signal is sent to and maintained by an upper computer to a plurality of electromagnetic pilot valves 12-4 which control the action of the second valve core through the pilot type electromagnetic directional valves 12, at the moment, high-pressure oil in the energy accumulator 78 enters the lower cavity of the hydraulic cylinder 80 through the one-way valve 77 to push the piston rod to move upwards quickly, when the pressure in the upper cavity of the hydraulic cylinder 80 reaches the opening pressure of the tested large-flow safety valve 82, the tested large-flow safety valve 82 opens to discharge liquid, the nominal flow of the tested large-flow safety valve 82 is calculated through testing the liquid discharge amount and the opening time of the safety valve, and a pressure curve is drawn through a numerical value fed back by the pressure sensor B81 to obtain the pressure characteristic of the tested large-flow safety.
after the tested safety valve 13 is tested, stopping sending a control signal to the pilot type electromagnetic unloading valve 73, simultaneously sending a control signal to the two-position four-way electromagnetic directional valve 74 to change the direction of the pilot type electromagnetic unloading valve, enabling oil from the hydraulic pump 2 to enter the upper cavity of the hydraulic cylinder 80 through the two-way lock 79 to push the piston rod, and after the piston rod returns, stopping sending a control signal to the two-position four-way electromagnetic directional valve 74 to reset and stop the piston rod; sending a control signal to the two-position four-way electromagnetic directional valve 74 to unload the system; meanwhile, the electromagnetic pilot valve 12-3 for controlling the first valve core to act and the electromagnetic pilot valve 12-4 for controlling the second valve core to act of the pilot electromagnetic directional valve 12 stop sending control signals, the first valve core 12-1 and the second valve core 12-2 reset, and the whole system enters the next test period.
The energy accumulators with different quantities can be selected for testing according to the safety valves with different nominal flow rates, and aiming at the unused energy accumulators, before the performance test of the safety valves, control signals are sent to the electromagnetic pilot valves 12-3 of the corresponding pilot electromagnetic reversing valves 12 for controlling the first valve core to act, so that the channels of the energy accumulators and the main loop are cut off.
The system has the advantage that the performance test of the high-flow safety valve can be realized by utilizing the plurality of energy accumulators and the pilot type electromagnetic reversing valve under the condition that the liquid supply amount of the hydraulic pump is insufficient. The operation is simple, and the automation degree is high.
The above embodiments are only suitable for illustrating the present disclosure, and not limiting the present disclosure, and those skilled in the relevant art can make various changes and modifications without departing from the spirit and scope of the present disclosure, so that all equivalent technical solutions also belong to the scope of the present disclosure, and the scope of the present disclosure should be defined by the claims.
Claims (6)
1. The utility model provides a be applied to energy storage ware on-off control's pilot-operated type electromagnetic directional valve which characterized in that: the pilot-operated electromagnetic directional valve adopts a double-valve-core structure and comprises a first valve core and a second valve core, wherein the first valve core is communicated with an oil way, and the second valve core is connected with a first energy accumulator;
The inlet of the first valve core is communicated with an oil path of an outlet of a hydraulic pump, the outlet of the first valve core is communicated with the inlet of the second valve core and the first accumulator, the inlet of the second valve core is communicated with the outlet of the first valve core and the first accumulator, a channel connected with a liquid tank is reserved on the second valve core, and the channel is cut off in an initial state;
The first accumulator is connected with one outlet of the first valve core, the connection is communicated in an initial state, and an inlet of the second valve core is connected with the other outlet of the first valve core;
When the pressure of the outlet of the pump is larger than a preset value, the control part controls the first valve core to change direction so that the oil way is cut off from the first accumulator channel, and the control part controls the second valve core to change direction so that the oil of the first accumulator flows to the inlet of the second valve core through one outlet of the first valve core and the other outlet of the first valve core, and then the oil is discharged back to the liquid tank or supplies liquid to other parts of the hydraulic system.
2. the pilot-operated electromagnetic directional valve according to claim 1, characterized in that: the valve core string of the first valve core and the second valve core adopts an integrated structure and is connected with the valve body through a threaded sleeve.
3. The pilot-operated electromagnetic directional valve according to claim 1 or 2, characterized in that: the control valve core of the first valve core is provided with an air hole, so that in the process of preventing the thrust valve core from acting, a closed air cavity is formed between the inner cavity of the control valve core and the valve rod of the liquid passing sleeve, and the control valve core cannot be reliably stopped.
4. A high pressure hydraulic pump test system characterized in that: the pilot type electromagnetic directional valve comprises the pilot type electromagnetic directional valve according to any one of claims 1 to 3, and further comprises a second accumulator, wherein the second accumulator is communicated with an outlet oil path of a tested hydraulic pump, the first accumulator is communicated with an outlet oil path of the hydraulic pump through the pilot type electromagnetic directional valve, the first accumulator is a low-pressure accumulator with low inflation pressure, and the second accumulator is a high-pressure accumulator with high inflation pressure.
5. The utility model provides a pneumatic cylinder fast action and fine setting return circuit system which characterized in that: comprising a pilot-operated electromagnetic directional valve according to any one of claims 1-3, the system comprising a hydraulic pump, a pilot-operated electromagnetic unloading valve, a three-position four-way electromagnetic directional valve, a check valve, a hydraulic cylinder, a pressure sensor; the pilot-operated electromagnetic unloading valve and the pressure sensor are connected to the outlet of the hydraulic pump, the hydraulic cylinder is communicated with the outlet of the pilot-operated electromagnetic unloading valve through the three-position four-way reversing valve, meanwhile, the first energy accumulator is communicated with the outlet of the pilot-operated electromagnetic unloading valve through the pilot-operated electromagnetic reversing valve, and the outlet of the pilot-operated electromagnetic reversing valve is connected with the lower cavity of the hydraulic cylinder through the one-way valve.
6. A large-traffic relief valve capability test system which characterized in that: the system comprises the pilot-operated electromagnetic directional valve according to any one of claims 1 to 3, and further comprises a hydraulic pump, a pilot-operated electromagnetic unloading valve, a two-position four-way directional valve, a two-way lock, a hydraulic cylinder, a tested large-flow safety valve, a first pressure sensor and a second pressure sensor, a plurality of groups of pilot-operated electromagnetic directional valves and the first accumulator; the pilot electromagnetic unloading valve and the first pressure sensor are connected to the outlet of the hydraulic pump, the hydraulic cylinder is connected with the two-way lock, the two-position four-way electromagnetic reversing valve is connected to the outlet of the pilot electromagnetic unloading valve, the first energy accumulators are communicated with the outlet of the pilot electromagnetic unloading valve through the pilot electromagnetic reversing valve, the outlet of the pilot electromagnetic reversing valve is connected with the lower cavity of the hydraulic cylinder through a one-way valve, the tested large-flow safety valve is connected in series to the upper cavity of the hydraulic cylinder, and the front end of the tested large-flow safety valve is connected with the second pressure sensor.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201711076453.2A CN107917120B (en) | 2017-11-03 | 2017-11-03 | pilot-operated electromagnetic reversing valve |
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| CN201711076453.2A CN107917120B (en) | 2017-11-03 | 2017-11-03 | pilot-operated electromagnetic reversing valve |
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| CN107917120A CN107917120A (en) | 2018-04-17 |
| CN107917120B true CN107917120B (en) | 2019-12-10 |
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| CN108591137A (en) * | 2018-07-12 | 2018-09-28 | 西南交通大学 | A kind of novel robot hydraulic knuckle drive system |
| CN110950244B (en) * | 2019-10-14 | 2020-12-08 | 武汉船用机械有限责任公司 | Hydraulic control system of servo oil cylinder |
| CN111174888A (en) * | 2020-02-04 | 2020-05-19 | 中冶南方连铸技术工程有限责任公司 | Overload protection method and system for weighing sensor |
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| US5992146A (en) * | 1996-04-12 | 1999-11-30 | Caterpillar Inc. | Variable rate ride control system |
| CN101526441B (en) * | 2009-04-23 | 2011-04-20 | 北京天地玛珂电液控制系统有限公司 | Large-flow safety valve test system |
| CN202833392U (en) * | 2012-09-17 | 2013-03-27 | 三一重型装备有限公司 | Electro-hydraulic main control valve and hydraulic system |
| CN203463120U (en) * | 2013-06-24 | 2014-03-05 | 山西平阳广日机电有限公司 | Mining intrinsically-safe electric-hydraulic control reversing valve |
| CN103623630A (en) * | 2013-12-02 | 2014-03-12 | 中煤北京煤矿机械有限责任公司 | Full-automatic high-pressure back-flushing filtering station |
| JP6205339B2 (en) * | 2014-08-01 | 2017-09-27 | 株式会社神戸製鋼所 | Hydraulic drive |
| CN104728203B (en) * | 2015-03-26 | 2017-11-07 | 北京煤科天玛自动化科技有限公司 | A kind of electric-hydraulic control reversing valve with internal pressure relief function |
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Address after: 101399 No.27, Linhe Development Zone, Shunyi District, Beijing Patentee after: CCTEG Beijing Tianma Intelligent Control Technology Co.,Ltd. Patentee after: BEIJING CCRI-TIANMA AUTOMATION TECHNOLOGY Co.,Ltd. Address before: 100013, Beijing, Chaoyang District, Hepingli Youth ditch East Road, building 5, one floor Patentee before: BEIJING TIANDI-MARCO ELECTRO-HYDRAULIC CONTROL SYSTEM Co.,Ltd. Patentee before: BEIJING CCRI-TIANMA AUTOMATION TECHNOLOGY Co.,Ltd. |
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