CN118309825A - High-medium pressure pilot valve and safety valve - Google Patents
High-medium pressure pilot valve and safety valve Download PDFInfo
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- CN118309825A CN118309825A CN202410741311.7A CN202410741311A CN118309825A CN 118309825 A CN118309825 A CN 118309825A CN 202410741311 A CN202410741311 A CN 202410741311A CN 118309825 A CN118309825 A CN 118309825A
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- 238000007789 sealing Methods 0.000 claims abstract description 293
- 230000005489 elastic deformation Effects 0.000 claims abstract description 43
- 230000002441 reversible effect Effects 0.000 claims description 37
- 238000013016 damping Methods 0.000 claims description 12
- 230000000670 limiting effect Effects 0.000 claims description 7
- 238000004073 vulcanization Methods 0.000 claims description 6
- 239000000463 material Substances 0.000 abstract description 13
- 230000004044 response Effects 0.000 abstract description 9
- 230000035945 sensitivity Effects 0.000 abstract description 8
- 230000007246 mechanism Effects 0.000 abstract description 4
- 230000001105 regulatory effect Effects 0.000 description 37
- 230000009471 action Effects 0.000 description 15
- 238000006243 chemical reaction Methods 0.000 description 13
- 230000002829 reductive effect Effects 0.000 description 12
- 239000003566 sealing material Substances 0.000 description 12
- 238000012545 processing Methods 0.000 description 8
- 238000004519 manufacturing process Methods 0.000 description 6
- 239000002131 composite material Substances 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 230000007547 defect Effects 0.000 description 3
- 238000013461 design Methods 0.000 description 3
- 238000007599 discharging Methods 0.000 description 3
- 230000006872 improvement Effects 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000011010 flushing procedure Methods 0.000 description 2
- 239000012528 membrane Substances 0.000 description 2
- 238000009991 scouring Methods 0.000 description 2
- 238000013022 venting Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000009172 bursting Effects 0.000 description 1
- 238000004364 calculation method Methods 0.000 description 1
- 238000004140 cleaning Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000036961 partial effect Effects 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 238000013040 rubber vulcanization Methods 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 239000004636 vulcanized rubber Substances 0.000 description 1
Classifications
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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
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/10—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with auxiliary valve for fluid operation of the main valve
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01D—SEPARATION
- B01D46/00—Filters or filtering processes specially modified for separating dispersed particles from gases or vapours
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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
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/06—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with special arrangements for adjusting the opening pressure
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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
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/164—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side and remaining closed after return of the normal pressure
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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
- F16K47/00—Means in valves for absorbing fluid energy
- F16K47/08—Means in valves for absorbing fluid energy for decreasing pressure or noise level and having a throttling member separate from the closure member, e.g. screens, slots, labyrinths
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Safety Valves (AREA)
Abstract
The invention discloses a pilot valve and a safety valve for high and medium pressure, and relates to the technical field of valves. The high-medium pressure pilot valve adopts a piston structure to replace the existing diaphragm structure so as to adapt to the high-medium pressure working condition environment; after the valve core assembly with different pressure parameters is manufactured and assembled by utilizing the elastic deformation mechanism of the rubber of the sealing surface of the valve seat and the combined valve core, the strokes of the inverted seal and the lower seal of the valve core assembly are adjusted, and different rubber materials elastically deform according to different pressures, so that the pilot valve can be normally opened and closed in different ranges of high and medium pressures, and the pilot valve is ensured to have the characteristics of quick opening, obvious burst opening, quick overpressure opening, high response sensitivity and quick response under the high and medium pressure working condition environment.
Description
Technical Field
The invention relates to the technical field of valves, in particular to a high-medium pressure pilot valve and a safety valve.
Background
The safety valve is one of the most important safety accessories of the pressure vessel and is a reclosable overpressure protection device. The pressure-bearing device is characterized in that the rated quantity of fluid is discharged by utilizing the force of the medium without any external force, so that partial pressure in pressure-bearing devices such as a pressure container, a pressure pipeline or a boiler and the like and equipment is released, the pressure in the system is prevented from exceeding a preset safety value, the damage of the system or the equipment caused by the overpressure is prevented, and the normal operation of the devices and the equipment and the safety of operators are ensured.
After the safety valve is opened, the safety valve can be reset by itself, the safety valve can be used repeatedly, the operation is convenient, and the safety valve is suitable for cleaning media without particles.
In terms of its structural principle, the existing safety valve mainly has two main categories of spring type and lever type. Since the spring type safety valve is sealed by using the acting force of the compression spring, the disadvantage is that the loaded load changes along with the opening of the valve, that is, the acting force of the spring on the valve core increases along with the opening rise of the valve core, which seriously affects the response sensitivity and the opening speed of the safety valve. The lever-type safety valve is sealed by means of lever acting force, and has the defects of low seat returning force caused by heavy structure, easy vibration of a loading mechanism to generate leakage, difficult closing after opening in actual operation and poor sealing performance.
Recently, with the economic development and the improvement of the industrial level, the relief quantity required by the safety valve is larger and larger, and the setting pressure is higher and higher, and a pilot-operated safety valve is also provided. The pilot operated safety valve is composed of main valve and pilot valve, the pilot valve controls the main valve to act, when the medium pressure in the system exceeds the set pressure value, it will firstly open the auxiliary valve and then open the main valve to discharge medium for pressure relief through the power transmission auxiliary device. The valve has the advantages of high setting pressure, large displacement, reliable sealing, no influence of back pressure and the like. Pilot operated safety valves are becoming increasingly popular.
The actuation performance of the pilot operated safety valve generally is two-way: performance parameters and deviations, such as setting pressure and deviations, sealing performance, opening height under excess pressure, opening and closing pressure difference, etc.; the mechanical action characteristics include no frequency hopping, chatter and jamming phenomenon, good repeatability, etc.
The existing pilot operated safety valve has some technical defects in practical use, which are expressed as follows: under the working condition of high pressure and large capacity, the reaction sensitivity, the opening speed and the sealing stability of the back seat closing are poor.
The invention patent application with the name of a low-pressure pilot-operated safety valve is disclosed as CN108708999A and is disclosed as 2018, 10 and 26, and comprises a pilot valve and a main valve, wherein the pilot valve comprises a pilot valve seat, a middle valve box, a pilot valve diaphragm, an upper valve cover, a pilot valve clack and a connecting shaft; the lower end of the middle valve box is connected with the upper end of a valve seat of the pilot valve, a control air chamber is formed, the upper end of the middle valve box is connected with the bottom of the upper valve cover, a diaphragm cavity is formed, the pilot valve diaphragm is fixed between the middle valve box and the upper valve cover, the diaphragm cavity is divided into an upper pilot valve diaphragm cavity and a lower pilot valve diaphragm cavity, a through hole is formed in the middle valve box, the lower pilot valve diaphragm cavity is communicated with the control air chamber, the pilot valve clack is arranged in the control air chamber, the upper end of the pilot valve clack is connected with a connecting shaft, and the upper end of the connecting shaft penetrates through the through hole and is connected to the pilot valve diaphragm; a gap is formed between the connecting shaft and the through hole, so that the lower membrane cavity of the pilot valve is communicated with the control air chamber; the bottom of the middle valve box is provided with an inverted sealing seat, the inverted sealing seat is in contact with the upper end of the valve clack of the pilot valve to seal and block the communication between the lower membrane cavity of the pilot valve and the control air chamber, the upper end of the valve seat of the pilot valve is provided with an outlet sealing seat, and the outlet sealing seat is in contact with the valve clack of the pilot valve to seal and block the outlet of the control air chamber. The pilot valve is opened rapidly and obviously, the overpressure is opened immediately, the reaction is rapid, the pilot valve outlet uses the flow resistance coefficient characteristic, and the pilot valve outlet is selected to be 10% -50%, so that the valve is opened and responded rapidly, and the seat returning is rapid. However, the pilot valve structure is only suitable for low-pressure working conditions and is not suitable for medium-high pressure working conditions of 1.6-42.0 MPa.
Disclosure of Invention
In order to overcome the defects and shortcomings in the prior art, the invention provides a high-medium pressure pilot valve and a safety valve, and aims to provide the pilot valve applicable to a high-medium pressure working condition environment with the pressure of 1.6-42.0 MPa, and the pilot valve still has the characteristics of quick opening, obvious burst opening, quick overpressure opening, high reaction sensitivity and quick reaction under the high-medium pressure working condition environment. The high-medium pressure pilot valve adopts a piston structure to replace the existing diaphragm structure so as to adapt to the high-medium pressure working condition environment; after the valve core assembly with different pressure parameters is manufactured and assembled by utilizing the elastic deformation mechanism of the rubber of the sealing surface of the valve seat and the combined valve core, the back sealing and lower sealing strokes of the valve core assembly are adjusted, and different rubber materials elastically deform according to different pressures, so that the pilot valve can be normally opened and closed in different ranges of high and medium pressures, and the pilot valve is ensured to still have the characteristics of small stroke, small error, quick opening, obvious burst opening, instant opening of overpressure, high response sensitivity, quick response, good seat returning stability and stable control of the seat returning range under the high and medium pressure working condition environment.
In order to solve the problems in the prior art, the invention is realized by the following technical scheme.
The first aspect of the invention provides a high-medium pressure pilot valve, which comprises a pilot valve body, a middle valve box, a pilot valve upper cover, a combined valve core and a connecting shaft, wherein a control air chamber is formed between the middle valve box and the pilot valve body; the pilot valve control medium outlet is communicated with the control air chamber; the lower end of the through hole is provided with an inverted sealing seat which is in sealing fit with the upper end face of the combined valve core to form a sealing pair, the pilot valve body is provided with an adjusting valve seat, the exhaust sealing seat at the upper end of the adjusting valve seat is in sealing fit with the lower end face of the combined valve core to form a sealing pair, the exhaust sealing seat is communicated with a pilot valve medium outlet, and an adjustable damping hole is arranged at the pilot valve medium outlet; the flow resistance coefficient of the pilot valve medium outlet is larger than the flow resistance coefficient of the gas medium flowing from the lower cavity of the piston to the control air chamber; the valve port area of the reverse sealing seat is smaller than that of the exhaust sealing seat; the axial stressed area of the lower cavity of the piston is larger than the area of the valve opening of the exhaust sealing seat; the sealing width of the exhaust sealing seat matched with the lower end face of the combined valve core is larger than that of the inverted sealing seat matched with the upper end face of the combined valve core; the combined valve core is sealed with the reverse sealing seat and the exhaust sealing seat by rubber, and the adjusting valve seat is configured to adjust the distance between the exhaust sealing seat and the reverse sealing seat, so that the working stroke of the piston is ensured to be matched with the elastic deformation range of the rubber seal on the combined valve core.
The working principle of the invention is as follows: the pilot valve is used to control the opening and closing of the main valve, and its control principle is the same as that of the prior art CN108708999 a. Specifically, the adjusting spring of the pilot valve is adjusted, so that the combined valve core of the pilot valve moves downwards, the lower end face of the combined valve core is matched with the exhaust sealing seat at the upper end of the adjusting valve seat to form a sealing pair, and the exhaust sealing seat at the upper end of the adjusting valve seat is embedded into the rubber at the lower end face of the combined valve core by utilizing elastic deformation of the rubber, so that sealing reliability is ensured.
When the valve is in operation, a gas medium is led into the lower cavity of the pilot valve piston through the connecting pipe and the filter by the air inlet of the main valve, the lower cavity of the pilot valve piston is communicated with the control air chamber through the through hole, clean gas medium enters the control air chamber, and then enters the upper cavity of the valve core of the main valve through the pilot valve control medium outlet and the signal pipe which are communicated with the control air chamber. Under the combined action of the pressure of the gas medium and the spring force of the return spring in the upper cavity of the valve core of the main valve, the sealing surface at the lower end of the valve core of the main valve seals the valve seat of the main valve, provides enough sealing specific pressure and ensures the sealing to be reliable.
When the pressure of the gas medium entering the lower cavity of the piston is increased under the overpressure, the adjusting spring force of the pilot valve is overcome to push the pilot valve piston to move upwards, so that the combined valve core is driven to move upwards. At this time, the sealing rubber of the lower end surface of the combined valve core changes from being embedded into the exhaust sealing seat to contacting the exhaust sealing seat due to elastic deformation of the rubber, and when the sealing rubber of the lower end surface of the combined valve core changes to contacting the exhaust sealing seat due to high pressure influence, the sealing force is almost not generated, and the pilot valve medium outlet has a slight exhaust state; meanwhile, the sealing rubber on the upper end surface of the combined valve core is gradually deformed by contacting the inverted sealing seat, and finally the inverted sealing seat is embedded into the sealing rubber on the upper end surface of the combined valve core; when the sealing rubber on the upper end surface of the combined valve core is slightly deformed, the gas medium in the lower cavity of the piston can pass through the through hole and the sealing pair between the inverted sealing seat and the upper end surface of the combined valve core, namely, a small amount of gas can be introduced, so that the pressure in the control gas chamber cannot be immediately reduced. Under the action of gas medium pressure, the combined valve core continues to move upwards, the upper end face of the combined valve core is quite easy to change from a state of contacting the inverted sealing seat to a state that the inverted sealing seat is embedded into sealing rubber of the upper end face of the combined valve core, a closed state is formed, at the moment, the sealing rubber of the lower end face of the combined valve core is contacted with or just separated from an exhaust sealing seat of an adjusting valve seat, sealing conversion is completed (the sealing of the lower end face of the combined valve core and the exhaust sealing seat is converted into the sealing of the upper end face of the combined valve core and the inverted sealing seat), and at the moment, the opening area of the inverted sealing seat is smaller than the opening area of the exhaust sealing seat, the medium pressure in a lower cavity of a piston is unchanged, the integral upward area acted by the medium pressure in a pilot valve is increased, the integral upward force of the pilot valve is increased, the upward thrust of the piston is instantaneously increased, the sealing between the lower end face of the combined valve core and the exhaust sealing seat is rapidly opened, and at the same time, the sealing between the inverted sealing seat and the upper end face of the combined valve core is further closed. The medium gas in the upper cavity of the main valve core is discharged completely from the medium outlet of the pilot valve, the acting force applied to the main valve core is unbalanced, the main valve is opened and discharged in a full stroke rapidly, and the system pressure falls back rapidly.
When the system pressure returns to the set safety pressure, the pressure of the gas medium is smaller than the regulating spring force of the guide valve, the pilot valve piston moves downwards under the action of the regulating spring force of the guide valve, so that the combined valve core is driven to move downwards, at the moment, the state that the sealing rubber on the upper end surface of the combined valve core is embedded by the inverted sealing seat gradually changes into the state that the inverted sealing seat contacts with the sealing rubber on the upper end surface of the combined valve core, the flow resistance coefficient from the lower cavity of the piston to the control air chamber of the pilot valve is matched with the flow resistance coefficient of the pilot valve medium outlet, the flow resistance coefficient of the pilot valve medium outlet is slightly larger than the flow resistance coefficient from the lower cavity of the piston to the control air chamber, the adjustable damping hole at the position of the pilot valve medium outlet is regulated, the flow resistance coefficient of the pilot valve medium outlet can be regulated, the set range of the main valve return seat and the downward movement speed of the main valve core can be obtained by regulating the flow resistance coefficient of the pilot valve medium outlet. Because the working stroke of the piston is matched with the elastic deformation range of the rubber seal on the combined valve core, under the action of the spring force of the pilot valve adjusting spring, the piston and the combined valve core can be subjected to seal conversion (the upper end face of the combined valve core is sealed with the inverted sealing seat and is converted into the lower end face of the combined valve core and is sealed with the exhaust sealing seat) in the moment, because the valve opening area of the inverted sealing seat is smaller than that of the exhaust sealing seat, the integral upward area is reduced due to the fact that the area difference, under the condition that the medium pressure is unchanged, the integral upward force is reduced greatly in the moment, the spring force of the pilot valve adjusting spring rapidly closes the pilot valve medium outlet, and opens the inverted sealing seat, so that a gas medium enters the control air chamber from the lower cavity of the piston, enters the upper cavity of the valve core of the main valve from the control air chamber, the pressure of the upper cavity of the valve core is increased, and the main valve is rapidly closed under the combined action of the spring force of the gas medium pressure and the main valve, so that the valve is reliably sealed.
Further preferably, the working stroke of the piston is controlled within 0.2mm or 0.3mm of elastic deformation of rubber by adjusting the distance between the exhaust seal seat and the reverse seal seat by adjusting the valve seat.
Still more preferably, the working stroke of the piston is controlled within a range of 0.05mm to 0.15mm rubber elastic deformation by adjusting the distance between the exhaust seal seat and the reverse seal seat by adjusting the valve seat.
Further preferably, the exhaust sealing seat at the upper end of the adjusting valve seat is formed by a flange protruding out of the upper end face of the adjusting valve seat, and a limiting step is formed between the exhaust sealing seat and the upper end face of the adjusting valve seat.
Further preferably, the rubber on the combined valve core, which is in sealing fit with the reverse sealing seat and the exhaust sealing seat, is vulcanized on the combined valve core in a vulcanization mode.
Further preferably, the adjusting valve seat is in threaded connection with the pilot valve body, sealing is carried out through an O-shaped sealing ring, and the adjusting valve seat and the pilot valve body are locked together through a locking nut.
Further preferably, the upper end of the regulating valve seat is provided with a pressure relief air chamber, the pressure relief air chamber is positioned in the middle of the exhaust sealing seat, and the pressure relief air chamber is communicated with a pilot valve medium outlet on the pilot valve body through an opening on the side wall of the regulating valve seat.
Still more preferably, a vent cavity is formed between the regulating valve seat and the pilot valve body, a buffer air chamber on the regulating valve seat is communicated with the vent cavity through an opening on the side wall of the regulating valve seat, and the vent cavity is communicated with a pilot valve medium outlet; and the upper end and the lower end of the exhaust cavity are sealed between the adjusting valve seat and the mounting hole of the adjusting valve seat through sealing rings.
Further preferably, the upper end of the connecting shaft penetrates through the piston, extends out of the top of the piston, and is fixed on the connecting shaft through a ball nut of the extending part of the connecting shaft and a piston fixing step on the connecting shaft; the lower end of the connecting shaft and the combined valve core are integrally formed.
Still more preferably, an adjusting spring assembly is assembled in the pilot valve upper cover, and the lower part of the adjusting spring assembly is connected with a ball nut.
The second aspect of the invention provides a high-medium pressure pilot-operated safety valve, which comprises a pilot valve and a main valve, wherein the main valve comprises a main valve body, a main valve seat, a main valve core, a main valve sleeve and a main valve cover; the main valve cover is fixedly connected with the main valve body to fix the main valve cover in the main valve body; the inner diameter area of the upper cavity of the main valve core is larger than the opening area of the valve seat of the main valve; the upper cavity of the valve core is provided with a return spring, one end of the return spring is connected with the valve core of the main valve, and the other end of the return spring is connected with the valve cover of the main valve; the pilot valve medium inlet is communicated with the main valve air inlet through a connecting pipe, and the pilot valve control medium outlet is communicated with the valve core upper cavity through a signal pipe; the medium outlet of the pilot valve is communicated with the outside or the air outlet of the main valve.
It is further preferred that a filter is provided on the connecting tube between the main valve inlet and the pilot valve medium inlet, said filter being configured to filter gas flowing from the main valve inlet into the pilot valve medium inlet.
Compared with the prior art, the beneficial technical effects brought by the invention are as follows:
1. According to the application, the diaphragm structure of the pilot valve in the prior art (CN 108708999A) is replaced by a piston structure, so that the condition of medium and high pressure working conditions can be met, the rubber seal on the combined valve core is large in hardness when the condition of medium and high pressure is met, the elastic deformation of the rubber seal is far smaller than the elastic deformation of the rubber seal under the condition of low pressure, and the friction coefficient of the piston is large when the piston is sealed under the condition of high pressure, if the diaphragm structure of the pilot valve in the prior art is replaced by the piston structure, the working stroke of the diaphragm structure of the pilot valve cannot meet the performance requirements, and the performance requirements of quick opening, obvious burst opening, quick overpressure opening, high reaction sensitivity and quick reaction of the pilot valve cannot be met. On the basis of the prior art, the adjusting valve seat is additionally arranged to adjust the distance between the exhaust sealing seat and the reverse sealing seat, so that the adjustment of the piston stroke is realized, and the problem that the accuracy and the stability of the pilot valve cannot meet the market demand when the high-pressure working pressure is more than 32.0MPa is solved. Through adjusting the setting of disk seat, make the combination case of different pressure parameter after manufacturing processing assembly, can adjust the interval of back seal seat and exhaust seal seat to the stroke of control piston, can be according to different pressure, different rubber materials elastic deformation realizes the normal start-stop of pilot valve in high, middling pressure different scope.
2. According to the application, the diaphragm structure of the pilot valve in the prior art (CN 108708999A) is replaced by a piston structure, and in order to meet the high-pressure requirement, the sealing between the piston and the piston cavity also needs to meet the high-pressure sealing requirement, so that the friction coefficient between the piston and the piston cavity wall is larger, and the performance requirement of the pilot valve cannot be met if the working stroke of the piston is larger. The application controls the stroke of the piston within the elastic deformation range of the sealing rubber of the combined valve core, thus meeting the performance requirement of the pilot valve. However, in such a small range of working stroke, there are many factors that cannot meet the requirements in the actual manufacturing process, such as errors in the processing of product parts, errors in assembly, shrinkage during vulcanization of rubber, errors due to changes in weather temperature, and the like. When the piston structure meets the requirement of high pressure, particularly when the working set pressure exceeds 32.0MPa, the normal working of the pilot valve of the high-pressure pilot type safety valve cannot be realized due to the improvement of manufacturing and processing precision and technology. Therefore, the adjusting valve seat is added, the combined valve core with different pressure parameters is adjusted to adjust the stroke of the combined valve core between the reverse sealing seat and the exhaust sealing seat after manufacturing, processing and assembling by adjusting the structural design of the valve seat, and the normal opening and closing of the pilot valve in different ranges of high and medium pressure can be realized according to different pressures and different elastic deformation amounts of rubber materials. After the combined valve core of the pilot valve is used for a long time, the elastic deformation quantity of the sealing rubber on the combined valve core is changed, and the valve seat can be adjusted to compensate.
3. The adjustable damping hole is arranged at the pilot valve medium outlet of the pilot valve, the flow resistance coefficient from the lower cavity of the piston to the control air chamber channel is matched with the flow resistance coefficient of the exhaust valve port, and the flow resistance coefficient of the exhaust valve port is slightly larger than the flow resistance coefficient from the lower cavity of the piston to the control air chamber channel, so that the opening and closing range of the pressure level of 1.6-42.0 Mpa is adjustable. Meanwhile, through the matching relation and the combination of the adjustable damping holes, the valve core back seat of the pilot valve can be controlled to be closed in the sealing specific pressure range, the working pressure and the set pressure can be satisfied to work in a very close range, and the opening and closing pressure difference can be controlled to be 4-5%.
4. The regulating valve seat can regulate the working stroke of the piston according to the elastic deformation of the vulcanized rubber on the combined valve core, can meet the condition that the elastic deformation of the sealing rubber in medium pressure is within 0.3mm or 0.2mm, and the elastic deformation of the sealing rubber in high pressure (such as 42.0MPa working condition) is about 0.05mm to 0.15mm, and is determined according to the elastic deformation of the rubber, so that when the sealing of the upper end face and the lower end face of the combined valve core is switched, one group of sealing is just separated, and the other group of sealing is embedded to realize sealing, thereby meeting the sealing performance of the sealing in medium pressure and the sealing in high pressure, and meeting the performance requirement of a pilot valve.
5. Because the upper sealing surface and the lower sealing surface of the combined valve core of the pilot valve are made of rubber materials, the matching relation between the elastic change of rubber and the sealing widths of the reverse sealing seat and the exhaust sealing seat can be adapted to the requirements of different setting pressures. When the pilot valve works, the acting force of the lower cavity of the piston is balanced with the force of the pressure regulating spring, and the rubber sealing material only needs to meet the sealing specific pressure relation, so that the general material solves the problem of reliable high-medium pressure sealing of 1.6-42.0 Mpa which cannot be solved for a long time.
6. The invention utilizes the fact that the medium force of the medium acting on the lower cavity of the piston is opposite to the medium force acting on the exhaust sealing seat, and the axial stressed area of the lower cavity of the piston is larger than the area difference formed by the area of the valve opening of the exhaust sealing seat to form the sealing specific pressure. When the valve is designed, the rubber is controlled to work in an elastic range and is under static pressure, so that the advantage that the sealing of the guide valve assembly of the 42Mpa high-pressure valve can be realized by adopting a universal rubber material is realized, and a foundation is laid for realizing the rapid switching of the sealing of the combined valve core by utilizing the elastic deformation of the rubber, so that the opening and closing stroke of the guide valve can be adjusted.
7. The exhaust sealing seat is formed by the flange protruding out of the upper end face of the adjusting valve seat, so that a limiting step is formed between the exhaust sealing seat and the upper end face of the adjusting valve seat, and deformation of the sealing surface compression rubber of the lower end face of the combined valve core is ensured to be in a rubber elastic deformation range. Furthermore, the exhaust sealing seats with different valve port sizes and the exhaust sealing seats with different heights formed by flanges with different heights can be matched in a mode of changing the adjusting valve seat, so that the exhaust sealing seats are better matched with sealing rubber on the lower end face of the combined valve core.
8. In the application, the rubber sealing material is directly vulcanized on the combined valve core in a vulcanization mode, so that the stability of connection between the rubber material and the combined valve core is ensured, and the tightness of rubber is improved.
9. According to the invention, the distance between the exhaust sealing seat and the reverse sealing seat on the upper end surface of the adjusting valve seat is adjusted by the threaded fit of the adjusting nut and the adjusting valve seat, and the adjusting precision can be controlled by the threaded distance of the threaded fit of the adjusting nut and the adjusting valve seat, so that the adjusting valve seat can be finely adjusted within the range of 0.05-0.15 mm.
10. In the invention, the pressure relief chamber is arranged on the regulating valve seat, and when the lower seal of the combined valve core and the exhaust sealing seat of the regulating valve seat are opened, a medium firstly flows into the pressure relief chamber and then is discharged to the atmosphere through the adjustable damping hole of the medium outlet of the pilot valve. Therefore, in the process of outwards discharging medium gas in the upper cavity of the valve core of the main valve, the medium outlet of the regulating valve seat and the pilot valve is throttled, depressurized and exhausted, and is subjected to medium gas scouring, so that the sealing surface of the lower end surface of the combined valve core avoids the medium gas scouring, and the long-service life use condition of high-medium pressure sealing is ensured.
11. The pilot valve is in a high-inlet low-outlet exhaust mode, and even if the combined valve core sealing rubber is sealed for a long time under the influence of factors such as deformation, low-temperature hardening and the like, the pilot valve can be reliably sealed. The medium pressure is discharged with high precision when exceeding the set pressure, the downward sealing force is increased when the medium pressure is reduced, the sealing is more reliable, and the problem that the safety valve is lifted in advance due to the influence of sealing materials of the safety valve is thoroughly solved.
12. The main valve of the application adopts a valve core piston type structure, and the axial inner diameter area of the valve core cavity is larger than the area of the valve seat of the main valve outlet, thus forming self-sealing seal, namely, the pressure is high, and the sealing specific pressure is larger, so the sealing is reliable. When the system works normally, the valve is sealed reliably and has zero leakage under the action of the return spring and the specific sealing pressure. And meanwhile, the upper end of the main valve core is lengthened during design so as to fill most of the cavity volume of the valve core, so that the upper cavity volume of the valve core is reduced. The pilot valve is increased in stressed area at the moment of overpressure opening of the system, the pilot valve medium outlet is rapidly opened, the small volume pressure of the upper cavity of the main valve is rapidly reduced, the main valve is rapidly opened and discharged in a full stroke manner, the abrupt opening effect is obvious, and the system pressure is rapidly released; the pressure is reduced, the pressure of a medium outlet of the pilot valve is reduced, the pilot valve cannot be sealed by the reverse seal, the seal between the reverse seal seat and the combined valve core is opened, the seal between the combined valve core and the exhaust seal seat is closed, medium rapidly enters an upper cavity of the main valve core with smaller volume, the pressure of the cavity of the valve core rapidly rises, and the main valve return seat is closed under the action of the area difference of a main valve return spring and S Valve core 、S Valve seat .
Drawings
FIG. 1 is a schematic view of the structure of the pilot valve of the present invention;
FIG. 2 is a schematic diagram of the mating structure of the combination valve core and the reverse seal seat and vent seal seat in the pilot valve of the present invention;
FIG. 3 is a schematic diagram of the main valve of the present invention;
FIG. 4 is a schematic structural view of a high-medium pressure pilot operated safety valve according to the present invention;
Reference numerals: 1. pilot valve, 2, main valve, 3, pilot valve body, 4, middle valve box, 5, pilot valve upper cover, 6, combined valve core, 7, connecting shaft, 8, control air chamber, 9, piston, 10, piston cavity, 11, through hole, 12, pilot valve medium inlet, 13, piston lower cavity, 14, pilot valve control medium outlet, 15, reverse sealing seat, 16, adjusting valve seat, 17, exhaust sealing seat, 18, pilot valve medium outlet, 19, adjustable damping hole, 20, flange, 21, limit step, 22, adjusting valve seat mounting hole, 23, locking nut, 24, buffer air chamber, 25, exhaust cavity, 26, ball nut, 27, piston fixing step, 28, adjusting spring assembly, 29, main valve body, 30, main valve seat, 31, main valve core, 32, main valve sleeve, 33, main valve cover, 34, valve core upper cavity, 35, return spring, 36, connecting pipe, 37, air inlet, 38, signal pipe, 39, main valve air outlet, 40, filter.
Detailed Description
The following are example embodiments of the invention defined by the claims and their equivalents, taken in conjunction with the accompanying drawings, in which the specific details are to be regarded as illustrative only and not limiting the scope of the invention. Accordingly, various changes and modifications to the embodiments may be made by one of ordinary skill in the art without departing from the scope and spirit of the invention.
As a preferred embodiment of the present invention, referring to fig. 1 and 2 of the accompanying specification, this embodiment discloses a pilot valve of high and medium pressure, which comprises a pilot valve body 3, a middle valve box 4, a pilot valve upper cover 5, a combined valve core 6 and a connecting shaft 7, wherein a control air chamber 8 is formed between the middle valve box 4 and the pilot valve body 3, the combined valve core 6 is positioned in the control air chamber 8, a piston cavity 10 is formed by the upper end of the middle valve box 4 being concave inwards, a piston 9 is hermetically and slidingly assembled in the piston cavity 10, a through hole 11 is arranged between the piston cavity 10 and the control air chamber 8, the connecting shaft 7 is assembled in the through hole 11, the upper end of the connecting shaft 7 is connected with the piston 9, the lower end of the connecting shaft 7 is connected with the combined valve core 6, a pilot valve medium inlet 12 is communicated with a piston lower cavity 13, and the piston lower cavity 13 is communicated with the control air chamber 8 through the through hole 11; the pilot valve control medium outlet 14 is communicated with the control air chamber 8; the lower end of the through hole 11 is provided with an inverted sealing seat 15 which is in sealing fit with the upper end face of the combined valve core 6 to form a sealing pair, the pilot valve body 3 is provided with an adjusting valve seat 16, an exhaust sealing seat 17 at the upper end of the adjusting valve seat 16 is in sealing fit with the lower end face of the combined valve core 6 to form a sealing pair, the exhaust sealing seat 17 is communicated with a pilot valve medium outlet 18, and an adjustable damping hole 19 is arranged at the pilot valve medium outlet 18; the flow resistance coefficient of the pilot valve medium outlet 18 is larger than the flow resistance coefficient of the gas medium flowing from the piston lower cavity 13 to the control air chamber 8; the valve port area of the reverse sealing seat 15 is smaller than the valve port area of the exhaust sealing seat 17; the axial stressed area of the lower piston cavity 13 is larger than the valve port area of the exhaust sealing seat 17; the sealing width of the exhaust sealing seat 17 matched with the lower end face of the combined valve core 6 is larger than the sealing width of the inverted sealing seat 15 matched with the upper end face of the combined valve core 6; the combined valve core 6 is in rubber seal with the reverse sealing seat 15 and the exhaust sealing seat 17, and the adjusting valve seat 16 is configured to adjust the distance between the exhaust sealing seat 17 and the reverse sealing seat 15, so that the working stroke of the piston 9 is ensured to be matched with the elastic deformation range of the rubber seal on the combined valve core 6.
The structure of the pilot valve of high and medium pressure that this embodiment provided is improved on the basis of the pilot valve structure of prior art CN108708999A, and the pilot valve structure among the prior art is only applicable to low pressure operating mode, can't adapt to high and medium pressure operating mode, and specific reason is that the pilot valve among the prior art utilizes the diaphragm structure to carry out opening and shutting of pilot valve, when pressure is great, surpasses the pressure that the diaphragm can bear, and the diaphragm will break, and the pilot valve inefficacy. In order to adapt to high and medium pressure working conditions (1.6-42.0 MPa), the diaphragm structure in the prior art is replaced by a piston 9 structure, but the performance requirement of the high and medium pressure working conditions on the pilot valve cannot be met by replacing the diaphragm structure by the piston 9 structure. The piston 9 has larger friction coefficient when sealed under the working condition of high and medium pressure, and if the working stroke of the piston 9 is large, the performance requirements on quick opening, obvious abrupt opening, instant opening of overpressure, high response sensitivity and quick response of the pilot valve cannot be met.
And under the working condition of high and medium pressure, the hardness of the sealing rubber on the combined valve core 6 is also larger, and the elastic deformation quantity of the sealing rubber is far smaller than that of the rubber sealing material for the pilot valve under the working condition of low pressure. Therefore, by combining the stroke of the piston 9 and the elastic deformation of the rubber seal on the combined valve core 6, the working stroke of the piston 9 is matched with the elastic deformation range of the rubber seal on the combined valve core 6, so that the pilot valve can still keep the performances of quick opening, obvious burst opening, instant overpressure opening, high response sensitivity and quick response while meeting the sealing requirement of the high and medium pressure working condition.
As a preferred implementation manner of the embodiment, a rubber material with elastic deformation of 0.2mm or less than 0.3mm is selected as the rubber sealing material on the combined valve core 6, and the rubber material can meet the sealing performance requirement of any pressure in high and medium pressure working conditions (1.6-42.0 MPa) and also can meet the performance requirement of the pilot valve. Therefore, the working stroke of the piston 9 is preferably controlled to be within 0.2mm or within 0.3 mm.
Because the elastic deformation amount of the rubber sealing material is small, many factors in actual manufacturing and processing cannot meet the requirements, such as errors in processing of product parts, errors generated during assembly, shrinkage during vulcanization of rubber, errors generated due to climate temperature change and the like, cannot be effectively realized, the working stroke of the piston 9 is controlled within the elastic deformation amount of the rubber sealing of the combined valve core 6, and particularly when the working set pressure exceeds 32.0MPa, the normal operation of the high-pressure pilot-operated safety valve and the pilot-operated safety valve cannot be realized due to the improvement of manufacturing and processing precision and process. In order to break through the breakthrough of the high-pressure high-precision and high-stability pilot valve and the pilot safety valve in the domestic technology, the problem that the precision and the stability of the pilot safety valve are difficult to meet the demands of market users when the high-pressure working pressure is more than 32.0MPa is solved, the valve seat 16 is specially arranged, the distance between the inverted sealing seat 15 above the combined valve seat 6 and the exhaust sealing seat 17 below the combined valve seat 6 can be adjusted after the combined valve seat 6 with different pressure parameters is manufactured, processed and assembled by adjusting the structural design of the valve seat 16, and therefore the working stroke of the piston 9 is adjusted. So as to overcome the processing errors, assembly errors, rubber vulcanization errors and the like of the product parts.
After the valve seat 16 is additionally regulated, different rubber materials can be elastically deformed according to different pressure working conditions, so that the pilot valve can be normally opened and closed in different high and medium pressure ranges. More preferably, the working stroke of the piston 9 is controlled within the range of 0.05mm-0.15mm rubber elastic deformation by adjusting the distance between the exhaust seal seat 17 and the reverse seal seat 15 by adjusting the valve seat 16. Further reduces the working stroke of the piston 9, so that the pilot valve works more sensitively and with higher precision.
The regulating valve seat 16 is combined with the piston 9 structure, the piston 9 working stroke control and the rubber elastic deformation control, so that the technical performance parameters of the pilot valve and the pilot safety valve are newly broken through under the high and medium pressure working condition, and the pilot valve and the pilot safety valve are in an advanced level in domestic and international markets.
The working principle of the invention is as follows: the pilot valve is used to control the opening and closing of the main valve, and its control principle is the same as that of the prior art CN108708999 a. Specifically, the adjusting spring of the pilot valve is adjusted, so that the combined valve core 6 of the pilot valve moves downwards, the lower end face of the combined valve core 6 is matched with the exhaust sealing seat 17 at the upper end of the adjusting valve seat 16 to form a sealing pair, and the exhaust sealing seat 17 at the upper end of the adjusting valve seat 16 is embedded into rubber at the lower end face of the combined valve core 6 by utilizing elastic deformation of the rubber, so that sealing reliability is ensured.
During operation, a gas medium is led into the pilot valve piston lower cavity 13 through the connecting pipe 36 and the filter 40 from the main valve air inlet 37, the pilot valve piston lower cavity 13 is communicated with the control air chamber 8 through the through hole 11, clean gas medium enters the control air chamber 8, and then enters the valve core upper cavity 34 of the main valve through the pilot valve control medium outlet 14 and the signal pipe 38 which are communicated with the control air chamber 8. Under the combined action of the pressure of the gas medium and the spring force of the return spring 35 in the upper valve element cavity 34 of the main valve, the sealing surface at the lower end of the main valve element 31 seals the main valve seat 30, provides enough specific pressure for sealing, and ensures the sealing to be reliable.
When the pressure of the gas medium entering the lower piston cavity 13 is increased, the pilot valve piston 9 is pushed to move upwards against the adjusting spring force of the pilot valve, and the combined valve core 6 is driven to move upwards. At this time, the sealing rubber of the lower end surface of the combined valve core 6 is changed from being embedded in the exhaust sealing seat 17 to contacting the exhaust sealing seat 17 due to elastic deformation of the rubber, and when the sealing rubber of the lower end surface of the combined valve core 6 becomes contacting the exhaust sealing seat 17 due to high pressure influence, the sealing force is almost absent, and the pilot valve medium outlet 18 has a slight exhaust state; meanwhile, the sealing rubber on the upper end surface of the combined valve core 6 is gradually deformed by contacting the inverted sealing seat 15, and finally the inverted sealing seat 15 is embedded into the sealing rubber on the upper end surface of the combined valve core 6; when the sealing rubber on the upper end surface of the combined valve core 6 is slightly deformed, the gas medium in the lower piston cavity 13 can pass through the through hole 11 and the sealing pair between the inverted sealing seat 15 and the upper end surface of the combined valve core 6, namely, a small amount of gas can be introduced, so that the pressure in the control air chamber 8 cannot be immediately reduced. Under the action of gas medium pressure, the combined valve core 6 continues to move upwards, because the sealing width between the upper end face of the combined valve core 6 and the inverted sealing seat 15 is narrower, the upper end face of the combined valve core 6 is easily changed from a state of contacting the inverted sealing seat 15 to a state that the inverted sealing seat 15 is embedded into sealing rubber of the upper end face of the combined valve core 6, a closed state is formed, at the moment, the sealing rubber of the lower end face of the combined valve core 6 is contacted with or just separated from the exhaust sealing seat 17 of the regulating valve seat 16, sealing conversion is completed (the sealing conversion between the lower end face of the combined valve core 6 and the exhaust sealing seat 17 is converted into the sealing between the upper end face of the combined valve core 6 and the inverted sealing seat 15), and at the moment, the medium pressure in the lower cavity 13 of the piston is unchanged, the overall upward area of the pilot valve is increased, the overall upward force of the pilot valve is increased, the upward thrust is born by the piston, the sealing between the lower end face of the combined valve core 6 and the exhaust sealing seat 17 is rapidly opened, and at the same time, the sealing between the upper end face of the combined valve core 6 is further tightly sealed. The medium gas in the upper cavity of the main valve core 31 is discharged from the medium outlet of the pilot valve completely, the acting force applied to the main valve core 31 is unbalanced, the main valve is opened and discharged in a full stroke rapidly, and the system pressure falls back rapidly.
When the system pressure returns to the set safety pressure, the gas medium pressure is smaller than the regulating spring force of the pilot valve, the pilot valve piston 9 moves downwards under the action of the regulating spring force of the pilot valve, so as to drive the combined valve core 6 to move downwards, at the moment, the sealing rubber on the upper end surface of the combined valve core 6 gradually changes from the embedded state of the inverted sealing seat 15 to the state that the inverted sealing seat 15 contacts the sealing rubber on the upper end surface of the combined valve core 6, the flow resistance coefficient from the lower piston cavity 13 of the pilot valve to the control air chamber 8 is matched with the flow resistance coefficient of the pilot valve medium outlet 18, the flow resistance coefficient of the pilot valve medium outlet 18 is slightly larger than the flow resistance coefficient from the lower piston cavity 13 to the control air chamber 8, the adjustable damping hole 19 at the pilot valve medium outlet 18 is regulated, the flow resistance coefficient of the pilot valve medium outlet 18 can be regulated, the set main valve seat returning range and the downward moving speed of the main valve core 31 can be obtained. Because the working stroke of the piston 9 is matched with the elastic deformation range of the rubber seal on the combined valve core 6, under the action of the spring force of the pilot valve adjusting spring, the piston 9 and the combined valve core 6 can finish sealing conversion (the upper end surface of the combined valve core 6 and the inverted sealing seat 15 are sealed and converted into the lower end surface of the combined valve core 6 and the exhaust sealing seat 17) instantly, because the valve port area of the inverted sealing seat 15 is smaller than the valve port area of the exhaust sealing seat 17 due to the fact that the area difference, the whole upward area is reduced, under the condition that the medium pressure is unchanged, the whole upward force is instantly and greatly reduced, the spring force of the pilot valve adjusting spring rapidly closes the pilot valve medium outlet 18, and opens the inverted sealing seat 15, so that gas medium enters the control air chamber 8 from the lower cavity 13 of the piston, enters the upper cavity 34 of the main valve from the control air chamber 8, the pressure of the upper cavity 34 of the valve rises, under the combined action of the gas medium pressure and the spring force of the reset spring 35 of the main valve, the main valve is rapidly closed, and the valve is reliably sealed.
On the basis of the working principle, when the pilot valve is further described, the regulating valve seat 16 of the pilot valve is regulated, the combined valve core 6 is regulated to the position of the reverse sealing seat 15 of the valve box 4 in the pilot valve, which is 1/3-1/2 of the elastic deformation amount of the rubber sealing material on the upper end surface of the combined valve core 6, the regulating spring component 28 of the pilot valve is regulated, the precompression F Bullet is set, so that the pressure value for safety protection of a pressure container or a pipeline equipment system, namely the opening pressure P s of the pilot valve and the main valve can be set, when the pilot valve is designed, the sealing reliability is ensured by utilizing the area difference formed by the sealing area of the piston cavity 10 and the valve port area of the exhaust sealing seat 17 on the regulating valve seat 16 and the spring force F Bullet of the pilot valve regulating spring component 28, namely the relation of P s*(S Piston 9-S Exhaust gas )＜F Bullet is satisfied, wherein S Piston 9 is the effective area of the pilot valve piston lower cavity 13, and S Exhaust gas is the valve port 17 area of the valve port sealing seat 16.
When the pressure of the gas in the pilot valve control air chamber 8 is P (S Piston 9-S Exhaust gas )＜F Bullet ) and reaches or exceeds the preset value P is more than or equal to P s, namely the pressure P of the gas in the pilot valve piston lower cavity 13 to the pilot valve piston 9 (S Piston 9-S Exhaust gas )≥F Bullet ; at the moment, the pilot valve piston 9 overcomes the adjusting spring force F Bullet and drives the combined valve core 6 to move upwards, when the pilot valve is designed, the flow resistance coefficient of a channel from the piston lower cavity 13 to the control air chamber 8 is matched with the flow resistance coefficient of a pilot valve medium outlet 18, the flow resistance coefficient of the pilot valve medium outlet 18 is slightly larger than the flow resistance coefficient of a channel from the piston lower cavity 13 to the control air chamber 8, and the elastic deformation principle of rubber is combined, so that when the pressure of the medium of the combined valve core 6 is increased, the combined valve core 6 just contacts the reverse sealing seat 15, a slight gas medium enters the control air chamber 8 from the piston lower cavity 13, the lower end surface of the combined valve core 6 just leaves the exhaust sealing seat 17, the slight gas medium enters the pilot valve medium outlet 18 for discharging, and the gas medium in the state of the pilot valve sealing seat 17 only leaks slightly, and the gas medium in the pilot valve cavity 13 still leaks slightly enough to the control air chamber P Piston 9-S Exhaust gas )≥F Bullet (S79 is still satisfied).
Further, when designing the pilot valve, the sealing width of the pilot valve reverse sealing seat 15 is smaller than the sealing width of the exhaust sealing seat 17 on the adjusting valve seat 16, as the combined valve core 6 continues to move upwards, the force of instant upward pushing is converted from P (S Piston 9-S Exhaust gas ) to P (S Piston 9-S Pouring ),S Pouring is the valve port area of the reverse sealing seat 15 on the valve box 4 in the pilot valve, and S Pouring ＜S Exhaust gas is provided), the increased force P (S Exhaust gas -S Pouring ) quickly pushes the pilot valve combined valve core 6 to move upwards, the upper end face of the pilot valve combined valve core 6 and the reverse sealing seat 15 are completely sealed and closed, the lower end face of the pilot valve combined valve core 6 completely leaves the exhaust sealing seat 17, the opening pressure P s is quickly converted into the exhaust pressure P d, and the pilot valve is opened and discharged in a full stroke.
In the middle-high pressure working condition, because the pressure of the gas medium is higher, the combined valve core 6 will slightly exhaust when not completely separated from the exhaust sealing seat 17, the sealing condition is realized according to the elastic deformation amount of the rubber sealing material on the lower end face of the combined valve core 6 compressed by the exhaust sealing seat 17, for example, when the combined valve core 6 is completely sealed, the elastic deformation amount of the rubber sealing material on the lower end face of the combined valve core 6 compressed by the exhaust sealing seat 17 is 0.3mm, if the combined valve core 6 moves up by 0.1mm, the deformation amount of the rubber sealing material on the lower end face of the combined valve core 6 compressed by the exhaust sealing seat 17 becomes 0.2mm, at this time, the slight exhaust may occur, at this time, the upper end face of the combined valve core 6 is just contacted with the inverted sealing seat 15, or the rubber sealing material on the upper end face of the inverted sealing seat 15 compressed by 0.1mm generates the elastic deformation amount, and the gas still enters the control air chamber 8 from the through hole 11.
In general, the aperture of the through hole 11 on the valve box 4 in the pilot valve is 2-3mm, the valve port area of the reverse sealing seat 15 of the pilot valve combined valve core 6 is larger than the aperture of the through hole 11, the combined valve core 6 can meet the flow area of the through hole 11 and the pilot valve medium outlet 18 only by 0.2-0.3 mm of stroke, the normal circulation of a gas medium is ensured, the rubber sealing of the combined valve core 6 can realize the conversion of the reverse sealing seat 15 of the pilot valve and the exhaust sealing seat 17 on the regulating valve seat 16 within the elastic deformation range (the elastic deformation range of the rubber sealing is controlled within 0.3mm, the pressure of the rubber sealing is controlled within 1.6MPa-25MPa under the medium pressure working condition, and even the opening and closing conversion stroke of the pilot valve combined valve core 6 (namely the working stroke of the piston 9) is controlled within 0.2mm or within 0.3 mm); the pilot valve combined valve core 6 and the reverse sealing seat 15 of the middle valve box 4 form a sealing pair, namely a channel between a groove in the middle of the connecting shaft 7 of the combined valve core 6 and the through hole 11 is blocked. Because the valve port of the exhaust sealing seat 17 at the upper end of the regulating valve seat 16 in the pilot valve is in an open state due to the upward movement of the pilot valve combined valve core 6, the gas medium in the upper cavity of the main valve core 31 is discharged outwards from the pilot valve medium outlet 18.
In the present application, the system daily operational stress of the pilot valve can be expressed as:
F Switch for closing =P Worker's work *(S Piston 9-S Exhaust gas );①
Instant stress for overpressure opening of system: f Opening device =P Row of rows *(S Piston 9-S Pouring );②
Where S Piston 9 represents the effective area of the pilot valve piston 9 (mm 2）;S Pouring represents the valve port area of the pilot valve back seal seat 15 (mm 2）;S Exhaust gas represents the valve port area of the vent seal seat 17 on the regulator valve seat 16 in the pilot valve (mm 2）;F Switch for closing represents the pilot valve closing operating pressure (N); F Opening device represents the pilot valve venting pressure (N); P Worker's work represents the relief valve operating pressure (MPa); P Row of rows represents the relief valve venting pressure (MPa)).
S Piston 9 in formulas ① and ② is the effective area of the pilot valve piston 9, S Exhaust gas ＞S Pouring ,P Row of rows ＞P Switch for closing , so the opening moment F Opening device is far greater than F Switch for closing , the pilot valve is opened rapidly, the structure is obvious in bursting effect, and the overpressure is opened immediately and reflects rapidly. The pilot valve opens the combined valve core 6 and the reverse sealing seat 15 is closed, the pilot valve discharges the air in the air chamber of the upper cavity of the main valve, and the area difference of S Exhaust gas ＞S Pouring forms the range of the reverse seat. When the pilot valve is designed, the flow resistance coefficient of the passage from the lower piston cavity 13 to the control air chamber 8 is matched with the flow resistance coefficient of the pilot valve medium outlet 18, and the flow resistance coefficient of the pilot valve medium outlet 18 is slightly larger than the flow resistance coefficient of the passage from the lower piston cavity 13 to the control air chamber 8; because the action of the combined valve core 6 is a dynamic process, different setting pressure grades are overlapped, the flow velocity of the channels is also dynamically changed, and the flow resistance coefficient is also dynamically changed, so a quantitative calculation formula cannot be obtained, but only a mechanism that the flow resistance coefficients of the two channels are required to be matched and the flow resistance coefficient of the pilot valve medium outlet 18 is slightly larger is mastered, the damping hole of the pilot valve medium outlet 18 is made to be adjustable, in actual use, for safety valves with different setting pressure grades, the range of a seat can be adjusted and controlled by matching the sizes of the damping holes of the pilot valve medium outlet 18, the opening and closing pressure difference can be controlled to be 4-5%, the valve opening stability is good, the accuracy of the seat adjusting range is high, and the seal is safe and reliable.
As an implementation manner of this embodiment, referring to fig. 2 of the specification, the exhaust sealing seat 17 at the upper end of the adjusting valve seat 16 is formed by a flange 20 protruding from the upper end surface of the adjusting valve seat 16, and a limiting step 21 is formed between the exhaust sealing seat 17 and the upper end surface of the adjusting valve seat 16. The deformation of the sealing surface compression rubber of the lower end surface of the combined valve core 6 is ensured to be within the elastic deformation range of the rubber. Further, by changing the adjusting valve seat 16, the exhaust sealing seat 17 with different valve port sizes and the exhaust sealing seat 17 with different heights formed by the flanges 20 with different heights can be adapted to better adapt to the sealing rubber of the lower end face of the combined valve core 6.
As a further embodiment of the present embodiment, the rubber on the combined valve core 6 that is in sealing engagement with the back seal seat 15 and the exhaust seal seat 17 is vulcanized on the combined valve core 6 by vulcanization. The rubber sealing material is directly vulcanized on the combined valve core 6, so that the stability of connection between the rubber material and the combined valve core 6 is ensured, and the sealing property of rubber is improved.
As a further implementation of the present embodiment, referring to fig. 1 of the specification, the adjusting valve seat 16 is in threaded connection with the pilot valve body 3, sealed by an O-ring, and the adjusting valve seat 16 is locked with the pilot valve body 3 by a lock nut 23. The position of the valve seat 16 is adjusted by means of threads.
As a further implementation manner of the embodiment, the pilot valve body 3 is provided with an adjusting valve seat mounting hole 22, the adjusting valve seat 16 is assembled in the adjusting valve seat mounting hole 22 in a sealing way, a limiting piece for limiting the rotation of the adjusting valve seat 16 is arranged in the adjusting valve seat mounting hole 22, the pilot valve body 3 is provided with an adjusting nut which rotates relative to the pilot valve body 3, the adjusting nut is in threaded fit with the adjusting valve seat 16, and the distance between the exhaust sealing seat 17 and the reverse sealing seat 15 at the upper end of the adjusting valve seat 16 is adjusted by rotating the adjusting nut. The adjustment of the distance between the exhaust sealing seat 17 and the reverse sealing seat 15 on the upper end surface of the adjusting valve seat 16 is realized through the threaded fit of the adjusting nut and the adjusting valve seat 16, and the adjustment precision is controlled through the threaded screw distance of the threaded fit of the adjusting nut and the adjusting valve seat 16, so that the adjusting valve seat 16 can realize fine adjustment within the range of 0.05-0.15 mm.
As a further implementation manner of the embodiment, referring to fig. 1 of the specification, a relief air chamber 24 is arranged at the upper end of the adjusting valve seat 16, the relief air chamber 24 is positioned in the middle of the exhaust sealing seat 17, and the relief air chamber 24 is communicated with the pilot valve medium outlet 18 on the pilot valve body 3 through an opening on the side wall of the adjusting valve seat 16. An exhaust cavity 25 is formed between the regulating valve seat 16 and the pilot valve body 3, a buffer air chamber 24 on the regulating valve seat 16 is communicated with the exhaust cavity 25 through an opening on the side wall of the regulating valve seat 16, and the exhaust cavity 25 is communicated with the pilot valve medium outlet 18; the adjusting valve seat 16 and the adjusting valve seat mounting hole 22 are sealed by sealing rings at the upper end and the lower end of the exhaust cavity 25.
The regulating valve seat 16 is provided with a pressure relief chamber, and when the lower seal of the combined valve core 6 and the exhaust sealing seat 17 of the regulating valve seat 16 are opened, medium firstly flows into the pressure relief chamber and then is discharged to the atmosphere through the adjustable damping hole 19 of the pilot valve medium outlet 18. Therefore, in the process of outwards discharging medium gas in the valve core upper cavity 34 of the main valve, the exhaust of the regulating valve seat 16 and the pilot valve medium outlet 18 is throttle pressure-reducing exhaust and bears the flushing of the medium gas, so that the sealing surface of the lower end surface of the combined valve core 6 avoids the flushing of the medium gas, and the long service condition of high-medium pressure sealing is ensured.
As a further implementation manner of the embodiment, the upper end of the connecting shaft 7 penetrates through the piston 9, protrudes out of the top of the piston 9, and fixes the piston 9 on the connecting shaft 7 through a ball nut 26 of the protruding part of the connecting shaft 7 and a piston fixing step 27 on the connecting shaft 7; the lower end of the connecting shaft 7 and the combined valve core 6 are integrally formed. An adjusting spring assembly 28 is assembled in the pilot valve upper cover 5, and the lower part of the adjusting spring assembly 28 is connected with a ball nut 26.
As a further embodiment of the present invention, referring to fig. 3 and 4 of the accompanying drawings, there is provided a high-medium pressure pilot-operated safety valve comprising a pilot valve according to the first aspect of the present invention and a main valve, the main valve comprising a main valve body 29, a main valve seat 30, a main valve spool 31, a main valve sleeve 32 and a main valve cover 33, the main valve seat 30 being provided in the main valve body 29, the main valve sleeve 32 being also provided in the main valve body 29 and on the main valve seat 30, the main valve spool 31 being slidably provided in the main valve sleeve 32, the lower end of the main valve spool 31 cooperating with the main valve seat 30 to form a sealing pair, the upper end of the main valve spool 31 extending towards the spool upper chamber 34 to fill the spool upper chamber 34; the main valve cover 33 is fixedly connected with the main valve body 29 to fix the main valve cover 32 in the main valve body 29; the inner diameter area of the upper cavity of the main valve core 31 is larger than the opening area of the main valve seat 30; the valve core upper cavity 34 is provided with a return spring 35, one end of the return spring 35 is connected with the main valve core 31, and the other end is connected with the main valve cover 33; the pilot valve medium inlet 12 is communicated with a main valve air inlet 37 through a connecting pipe 36, and the pilot valve control medium outlet 14 is communicated with the valve core upper cavity 34 through a signal pipe 38; the pilot valve medium outlet 18 communicates with the outside or with the main valve air outlet 39.
In the embodiment, the main valve core 31 adopts a piston 9 structure, and the axial inner diameter area of the upper cavity 34 of the core is larger than the valve port area of the main valve seat 30. The acting force is calculated as follows:
The system is stressed in daily work, the upper and lower parts of the valve core are inlet pressure P Worker's work , and the acting area S Valve core of the valve core (downwards stressed) is slightly larger than the upwards acting area S Valve seat of the valve seat. When the system works daily, under the action of the pressure of the gas medium and the spring force of the return spring 35, the main valve core 31 is sealed on the main valve seat 30, the sealing is reliable and zero in leakage, and when the main valve is closed, the closing pressure is as follows: f Closing =P Worker's work *（S Valve core -S Valve seat ）+F Composite bullet ;③
When the main valve is discharged: f Discharge of =P Row of rows *S Valve seat -F Composite bullet ;④
Wherein S Valve core denotes the area of the main valve spool 31 (mm 2）;S Valve seat denotes the area of the main valve seat 30 (mm 2), and S Valve core ＞S Valve seat ;F Closing denotes the main valve closing operating pressure (N), F Discharge of denotes the main valve discharge pressure (N), P Worker's work denotes the relief valve operating pressure (MPa), and P Row of rows denotes the relief valve discharge pressure (MPa).
P Worker's work *（S Valve core -S Valve seat ) in the formula ③ is a necessary sealing force, namely self-sealing, namely the higher the pressure is, the larger the sealing specific pressure is, and the main valve adopts different sealing surface materials, so that the pressure sealing working condition of 1.6-42.0 MPa can be satisfied. F Composite bullet provides only a return force. When the pilot valve is opened, P Row of rows *S Valve seat is far larger than F Composite bullet , so that the main valve is rapidly opened and discharged in a full stroke, the abrupt opening effect is obvious, the system pressure is rapidly released, the pressure is reduced, the pressure range of the pilot valve seat is set by the ratio of (S Living body -S Discharge of ) to (S Living body -S Pouring ), the flow resistance coefficient from the lower cavity 13 of the pilot valve piston to the channel of the control air chamber 8 is matched with the flow resistance coefficient of the exhaust valve port, the area difference balance principle and the flow resistance coefficient matching relationship are fully utilized, the high-precision regulation of the pilot valve seat is realized, the pilot valve seat is closed, and the main valve seat is closed.
It is further preferred that a filter 40 is provided on the connecting tube 36 between the main valve inlet 37 and the pilot valve medium inlet 12, said filter 40 being configured to filter the gas flowing from the main valve inlet 37 into the pilot valve medium inlet 12. The bottom of the main valve core 31 is provided with a sealing gasket for contacting with the main valve seat 30 and sealing the main valve seat 30. The upper end of the main valve return spring 35 is contacted with the upper end of the main valve cover 33, and the lower end is contacted with the main valve core 31; the axial area of the main valve spool 31 chamber is larger than the surface area of the valve seat opening.
The above embodiment is only one of modes for realizing the technical solution of the present application, and the scope of the present application is not limited to the above embodiment, but includes other embodiments which can be changed by one of ordinary skill in the art according to the technical solution of the present application.
Claims (10)
1. The utility model provides a high-medium pressure pilot valve, this pilot valve includes pilot valve body (3), well valve box (4), pilot valve upper cover (5), combination case (6) and connecting axle (7), forms control air chamber (8) between well valve box (4) and pilot valve body (3), and combination case (6) are located control air chamber (8), its characterized in that: the upper end of the middle valve box (4) is concaved inwards to form a piston cavity (10), a piston (9) is hermetically and slidably assembled in the piston cavity (10), a through hole (11) is arranged between the piston cavity (10) and the control air chamber (8), a connecting shaft (7) is assembled in the through hole (11), the upper end of the connecting shaft (7) is connected with the piston (9), the lower end of the connecting shaft (7) is connected with the combined valve core (6), a pilot valve medium inlet (12) is communicated with a piston lower cavity (13), and the piston lower cavity (13) is communicated with the control air chamber (8) through the through hole (11); the pilot valve control medium outlet (14) is communicated with the control air chamber (8); the lower end of the through hole (11) is provided with a reverse sealing seat (15) which is in sealing fit with the upper end face of the combined valve core (6) to form a sealing pair, the pilot valve body (3) is provided with an adjusting valve seat (16), an exhaust sealing seat (17) at the upper end of the adjusting valve seat (16) is in sealing fit with the lower end face of the combined valve core (6) to form a sealing pair, the exhaust sealing seat (17) is communicated with a pilot valve medium outlet (18), and an adjustable damping hole (19) is formed at the pilot valve medium outlet (18); the flow resistance coefficient of the pilot valve medium outlet (18) is larger than the flow resistance coefficient of the gas medium flowing from the lower piston cavity (13) to the control air chamber (8); the valve port area of the reverse sealing seat (15) is smaller than the valve port area of the exhaust sealing seat (17); the axial stressed area of the lower piston cavity (13) is larger than the valve port area of the exhaust sealing seat (17); the sealing width of the exhaust sealing seat (17) matched with the lower end face of the combined valve core (6) is larger than that of the inverted sealing seat (15) matched with the upper end face of the combined valve core (6); the combined valve core (6) is sealed with the reverse sealing seat (15) and the exhaust sealing seat (17) in a rubber mode, the adjusting valve seat (16) is used for adjusting the distance between the exhaust sealing seat (17) and the reverse sealing seat (15), and the working stroke of the piston (9) is matched with the elastic deformation range of the rubber seal on the combined valve core (6).
2. A high and medium pressure pilot valve as defined in claim 1, wherein: the working stroke of the piston (9) is controlled within 0.2mm or 0.3mm of rubber elastic deformation by adjusting the distance between the exhaust sealing seat (17) and the reverse sealing seat (15) through adjusting the valve seat (16).
3. A high and medium pressure pilot valve as defined in claim 2, wherein: the working stroke of the piston (9) is controlled within the range of 0.05mm-0.15mm rubber elastic deformation by adjusting the distance between the exhaust sealing seat (17) and the reverse sealing seat (15) through adjusting the valve seat (16).
4. A high and medium pressure pilot valve as claimed in any one of claims 1-3, wherein: the exhaust sealing seat (17) at the upper end of the adjusting valve seat (16) is formed by a flange (20) protruding out of the upper end face of the adjusting valve seat (16), and a limiting step (21) is formed between the exhaust sealing seat (17) and the upper end face of the adjusting valve seat (16).
5. A high and medium pressure pilot valve as claimed in any one of claims 1-3, wherein: rubber on the combined valve core (6) in sealing fit with the reverse sealing seat (15) and the exhaust sealing seat (17) is vulcanized on the combined valve core (6) in a vulcanization mode.
6. A high and medium pressure pilot valve as claimed in any one of claims 1-3, wherein: the adjusting valve seat (16) is in threaded connection with the pilot valve body (3), is sealed through an O-shaped sealing ring, and locks the adjusting valve seat (16) and the pilot valve body (3) together through a locking nut (23).
7. A high and medium pressure pilot valve as claimed in any one of claims 1-3, wherein: the upper end of the adjusting valve seat (16) is provided with a pressure relief air chamber (24), the pressure relief air chamber (24) is positioned in the middle of the exhaust sealing seat (17), and the pressure relief air chamber (24) is communicated with a pilot valve medium outlet (18) on the pilot valve body (3) through an opening on the side wall of the adjusting valve seat (16).
8. A high and medium pressure pilot valve as defined in claim 7, wherein: an exhaust cavity (25) is formed between the adjusting valve seat (16) and the pilot valve body (3), a pressure relief air chamber (24) on the adjusting valve seat (16) is communicated with the exhaust cavity (25) through an opening on the side wall of the adjusting valve seat (16), and the exhaust cavity (25) is communicated with the pilot valve medium outlet (18); the upper end and the lower end of the exhaust cavity (25) are sealed between the adjusting valve seat (16) and the adjusting valve seat mounting hole (22) through sealing rings.
9. The utility model provides a high-medium pressure guide formula relief valve which characterized in that: the pilot valve and the main valve according to any one of claims 1-8, wherein the main valve comprises a main valve body (29), a main valve seat (30), a main valve core (31), a main valve sleeve (32) and a main valve cover (33), the main valve seat (30) is arranged in the main valve body (29), the main valve sleeve (32) is also arranged in the main valve body (29) and is arranged on the main valve seat (30), the main valve core (31) is arranged in the main valve sleeve (32) in a sliding way, the lower end of the main valve core (31) is matched with the main valve seat (30) to form a sealing pair, and the upper end of the main valve core (31) extends towards a valve core upper cavity (34) so as to fill the valve core upper cavity (34); the main valve cover (33) is fixedly connected with the main valve body (29) to fix the main valve cover (32) in the main valve body (29); the inner diameter area of the upper cavity of the main valve core (31) is larger than the opening area of the main valve seat (30); the valve core upper cavity (34) is provided with a return spring (35), one end of the return spring (35) is connected with the main valve core (31), and the other end is connected with the main valve cover (33); the pilot valve medium inlet (12) is communicated with the main valve air inlet (37) through a connecting pipe (36), and the pilot valve medium outlet (14) is communicated with the valve core upper cavity (34) through a signal pipe (38); the pilot valve medium outlet (18) is communicated with the outside or is communicated with the main valve air outlet (39).
10. A high and medium pressure pilot operated relief valve as defined in claim 9, wherein: a filter (40) is provided on the connecting tube (36) between the main valve inlet (37) and the pilot valve medium inlet (12), the filter (40) being configured to filter gaseous medium flowing from the main valve inlet (37) into the pilot valve medium inlet (12).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410741311.7A CN118309825B (en) | 2024-06-11 | 2024-06-11 | High-medium pressure pilot valve and safety valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410741311.7A CN118309825B (en) | 2024-06-11 | 2024-06-11 | High-medium pressure pilot valve and safety valve |
Publications (2)
| Publication Number | Publication Date |
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| CN118309825A true CN118309825A (en) | 2024-07-09 |
| CN118309825B CN118309825B (en) | 2024-08-13 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202410741311.7A Active CN118309825B (en) | 2024-06-11 | 2024-06-11 | High-medium pressure pilot valve and safety valve |
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| Country | Link |
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| CN (1) | CN118309825B (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6161570A (en) * | 1999-06-01 | 2000-12-19 | Tyco Flow Control, Inc. | Pilot-operated relief valve |
| WO2019179517A1 (en) * | 2018-03-23 | 2019-09-26 | 浙江三花智能控制股份有限公司 | Electronic expansion valve |
| CN110529618A (en) * | 2019-09-04 | 2019-12-03 | 刘州豪 | A kind of straight-through two-seater control valve |
| CN111981168A (en) * | 2020-08-31 | 2020-11-24 | 四川长仪油气集输设备股份有限公司 | Pilot operated safety valve |
| CN216158380U (en) * | 2021-08-25 | 2022-04-01 | 上海飞奥燃气设备有限公司 | Gas circuit speed increaser with pressure reducing function |
-
2024
- 2024-06-11 CN CN202410741311.7A patent/CN118309825B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6161570A (en) * | 1999-06-01 | 2000-12-19 | Tyco Flow Control, Inc. | Pilot-operated relief valve |
| WO2019179517A1 (en) * | 2018-03-23 | 2019-09-26 | 浙江三花智能控制股份有限公司 | Electronic expansion valve |
| CN110529618A (en) * | 2019-09-04 | 2019-12-03 | 刘州豪 | A kind of straight-through two-seater control valve |
| CN111981168A (en) * | 2020-08-31 | 2020-11-24 | 四川长仪油气集输设备股份有限公司 | Pilot operated safety valve |
| CN216158380U (en) * | 2021-08-25 | 2022-04-01 | 上海飞奥燃气设备有限公司 | Gas circuit speed increaser with pressure reducing function |
Also Published As
| Publication number | Publication date |
|---|---|
| CN118309825B (en) | 2024-08-13 |
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