CN109163101B - Implementation method for improving exhaust capacity of air inlet and exhaust valve - Google Patents
Implementation method for improving exhaust capacity of air inlet and exhaust valve Download PDFInfo
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- CN109163101B CN109163101B CN201811293375.6A CN201811293375A CN109163101B CN 109163101 B CN109163101 B CN 109163101B CN 201811293375 A CN201811293375 A CN 201811293375A CN 109163101 B CN109163101 B CN 109163101B
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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
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/14—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with ball-shaped valve member
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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
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/32—Details
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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
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/32—Details
- F16K1/54—Arrangements for modifying the way in which the rate of flow varies during the actuation of the valve
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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
- F16K47/02—Means in valves for absorbing fluid energy for preventing water-hammer or noise
- F16K47/023—Means in valves for absorbing fluid energy for preventing water-hammer or noise for preventing water-hammer, e.g. damping of the valve movement
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
Abstract
The invention discloses a realization method for improving the exhaust capacity of an air intake and exhaust valve, which is based on the establishment of a streamline mathematical model of the air intake and exhaust valve, and is used for calculating the theoretical exhaust capacity, determining the model and specification of a conventional air intake and exhaust valve and calculating the exhaust flow coefficient aiming at a water supply system; designing a variable cross-section intake and exhaust valve with the same specification and streamlined intake and exhaust flow passages, and testing, recording and calculating the actual exhaust volume and the exhaust flow coefficient on an exhaust performance test platform. Tests prove that the exhaust capacity of the variable cross-section intake and exhaust valve is obviously improved, so that the caliber and the number of the variable cross-section intake and exhaust valve can be reduced on the premise of meeting the exhaust requirement, the investment is reduced, the cavitation resistance of the inner element is improved, the service life is prolonged, and the problem of pipe explosion caused by improper type selection of the intake and exhaust valve is solved; the method puts forward and verifies the view that the internal and external pressure differences of the air inlet and outlet valves are different and the air outlet flow coefficients are different for the first time, provides a basis for the perfection of the model selection standard and the establishment of the production technical standard of the water supply industry in China, and has important significance for ensuring the safe operation of the pipeline.
Description
Technical Field
The invention belongs to the field of model selection of air inlet and outlet valves, and particularly relates to a realization method for improving the air exhaust capacity of an air inlet and outlet valve.
Background
The research on the air intake and exhaust valves starts in the 15 th century or around the 60 th year, in recent years, scholars at home and abroad make intensive researches on mathematical models, protection effects, characteristic parameters, model selection rules and the like of the air intake and exhaust valves, and a large number of researches show that correctly designing, selecting and installing the air intake and exhaust valves are one of effective solutions for guaranteeing the initial water filling and the sufficient air exhaust after the accident shutdown of long-distance water transmission pipelines. The intake and exhaust valve has the advantages of simple structure, low manufacturing cost, convenient installation, no limitation of installation conditions and the like, and the currently common intake and exhaust valves in China are divided into 3 types according to functions and operation forms thereof: high-pressure micro exhaust valve, low-pressure high-speed intake and exhaust valve and composite (combined) intake and exhaust valve. The combined type air inlet and outlet valve has the functions of a high-pressure micro air outlet valve and a low-pressure large-amount air inlet and outlet valve, and in order to prevent water hammer caused by too high water filling speed, a plurality of combined type air inlet and outlet valves are provided with waterproof hammer assemblies and have quick opening and slow closing functions and accessories. The air inlet and outlet valve with the buffer mechanism can prevent the floating ball from being blown up by air flow to cause the air inlet and outlet valve to lose exhaust capacity suddenly, thereby reducing the occurrence of pipe explosion accidents caused by high-pressure water hammer due to sudden closing of the air inlet and outlet valve. Pipe explosion accidents caused by unsmooth air intake and exhaust of pipelines due to calculation errors and improper type selection of the air intake and exhaust valves are frequently rare. For example, a water conveying pipeline of a pumping station in a certain city in northwest has the length of 12km, the pipe diameter DN1150 and the maximum static pressure 39m water column, 3 different types of floating ball type exhaust valves are arranged on the pipeline, water runs for 40 days and pipe bursting is carried out for 3 times, and later experiments show that the exhaust volume of the selected floating ball type exhaust valve is seriously insufficient. According to statistics, the pipe explosion 400 times in one year in a certain big city in North China and the pipe explosion 900 times in a certain city in northwest China are carried out. Therefore, how to make the intake/exhaust valve have a more sufficient intake/exhaust amount is an important research direction for preventing accidents.
The composite air inlet and outlet valve is the most ideal pipeline water hammer protection valve at present. The large hole opening can intake and exhaust a large amount of air, the small hole opening can exhaust a small amount of air, the basic function of the composite air intake and exhaust valve is that the floating ball structure is the main component, and the floating ball seat is arranged on the floating ball tray under normal conditions. When the empty pipe is filled with water, air upwards moves along the bottom of the floating ball tray and is exhausted to the atmosphere from the periphery of the floating ball through the valve seat, so that a large amount of exhaust functions are realized, and after a large amount of exhaust is quickly carried out to set pressure, all residual trace gases are slowly discharged; after the air is exhausted, water enters the valve body, the floating ball floats under the buoyancy of the water to close the large orifice, and the small exhaust port continues to exhaust the air. When pipeline evacuation or blow out, the floater falls rapidly, in time inhales the air, destroys the pipeline vacuum, and when the water column was closed, the buffer board was closed in advance, and the most air of damming was in the pipeline, and the valve is a small amount of exhaust, cuts off through the air, prevents that the water column from closing to eliminate the closing water hammer. In the closing process, due to the fact that the pressure effects of the large vent hole and the small vent hole are different, the floating ball of the large vent hole is firstly jacked up to be closed, then the small vent hole is closed, the full closing process is delayed, and the pressure rise when the water column is closed is relieved.
According to the perfect research of Wylie, street and the like and the successors, the air intake and exhaust capacity of the air intake and exhaust valve depends on the pressure difference between the inside and the outside of the pipe and the gas temperature. The essential of the pressure pipeline is to meet the air intake and exhaust requirements of the pressure pipeline for safe operation, so that the air intake and exhaust functions of the air intake and exhaust valve must be flexibly realized in the starting, normal operation and accident states of the pressure pipeline, which is the fundamental technical requirement of the design of the air intake and exhaust valve.
Therefore, on the basis of the analysis of the heat insulation process, the isothermal process and the changeable process of the air inlet and exhaust channel of the air inlet and exhaust valve, the change rule of the sectional area of the channel, the air flow speed, the mass flow, the pressure, the temperature and the Mach number is researched, so that the air inlet and exhaust functions of the air inlet and exhaust channel of the combined air inlet and exhaust valve can be realized more fully, and the safety of a pipeline is further protected.
Safe operation of the pipeline relies on the continuous venting of air from the pipeline. The gas storage in the pipeline has multiple hazards, and firstly, the water delivery efficiency is reduced, and the water delivery is interrupted; secondly, water hammer and air explosion of pipelines are caused, the operation safety of water pumps, valves, pipelines and metering instruments is threatened, and even the personal safety is threatened; thirdly, measurement errors are caused to be generated by measuring instruments such as a water meter, a pressure gauge and the like; fourth, corrosion and cavitation of pipes and equipment, etc. are caused. Wherein, the liquid column separation phenomenon is the most unfavorable working condition of pipeline water hammer. Therefore, the intake and exhaust design of the water transmission pipeline increasingly draws attention of experts and engineers about water hammer.
The flow passage design technology of the traditional air intake and exhaust valve requires that the low-pressure exhaust process is divided into two stages: 1) full speed exhaust at low differential pressure; 2) the exhaust speed is limited at higher pressure difference, so that the generation of a closing water hammer is prevented, and the pressure of a pipeline is prevented from rising; 3) the impact of pressure fluctuation on the system, which is aggravated by full-speed exhaust under special working conditions such as a water hammer, is eliminated. The buffer plate (throttling device) is arranged outside the exhaust port of the air inlet and outlet valve, the valve opening of the valve is opened or closed in a grading way, and the air displacement of the pipeline during water filling or water column closing can be controlled by adjusting the size of the vent hole of the buffer plate; the influence of hydraulic impact is reduced by controlling the air displacement, and the air inlet and outlet valves are closed smoothly. The design of the valve body flow passage conforms to the standards of CJ/T19 and GB/T11719, the diameter of the valve body passage adopts the full-bore design, the valve seat hole is consistent with the valve body passage, the wall thickness of the valve body conforms to the GB specification, and the SolidWorks and ANSYS are adopted for stress check.
As shown in fig. 1 and 2, the valve body of the traditional intake and exhaust valve is designed to be cylindrical, after air in the pipe flows into the valve body, the air is often separated from the boundary and generates vortex, turbulence is intensified in the vortex region, meanwhile mass and energy exchange is continuously carried out between the main flow and the vortex region, a large amount of mechanical energy is consumed through friction and violent collision between mass and mass points, intake and exhaust efficiency is reduced, the air in the pipe cannot be exhausted in time, negative pressure in the pipe cannot be destroyed in time, and the influence on the safe operation of a water pipeline is large; in addition, when negative pressure is generated in the pipe, the action of the floating ball of the air inlet and outlet valve is delayed inevitably, the cavitation problem of the conventional runner also occurs occasionally, the air inlet and outlet performance is reduced rapidly along with the increase of the operation life, even the air inlet and outlet valve cannot act, and the project safety is seriously threatened.
Disclosure of Invention
The invention solves the defects of the prior art, and provides the implementation method for improving the exhaust capability of the air intake and exhaust valve, which can improve the air intake and exhaust functions of the air intake and exhaust valve, and can fully realize the air intake and exhaust functions of the air intake and exhaust valve, possibly reduce the caliber and the number of the air intake and exhaust valve, reduce the engineering, reduce the cavitation phenomenon of parts in the air intake and exhaust valve, prolong the service life of the air intake and exhaust valve, and provide guarantee for the safe operation of pressure pipeline engineering.
The technical scheme adopted by the invention for realizing the purpose is as follows:
an implementation method for improving the exhaust capacity of an air inlet valve and an exhaust valve comprises the following steps:
establishing a streamline mathematical model of an air inlet and outlet valve based on mechanism research of gas state parameters; for each water supply system, theoretical air intake and exhaust amount calculation is carried out according to a streamline mathematical model of an air intake and exhaust valve, the model and specification of a conventional air intake and exhaust valve are determined according to specification, and an exhaust flow coefficient is calculated; recording and calculating the actual displacement of the selected air inlet and outlet valves based on an air outlet performance test platform; designing a variable cross-section intake and exhaust valve with an intake and exhaust flow passage of the same specification being streamline, installing the variable cross-section intake and exhaust valve on an exhaust performance test platform, and recording, testing and calculating the actual exhaust volume and the exhaust flow coefficient of the variable cross-section intake and exhaust valve with the intake and exhaust flow passage being streamline based on the exhaust performance test platform; under the condition of finishing the same air displacement, the variable cross-section air inlet and outlet valve is selected to have a smaller caliber.
Preferably, the intake and exhaust valve streamline mathematical model is as follows:
when in use
When the concentration of the metal oxide is less than 1.892,
wherein:
is the true mass flow of air in the tube through the exhaust outlet of the intake and exhaust valve, CdThe intake and exhaust flow coefficient is the relationship between the real mass flow and the theoretical mass flow of the air in the pipe passing through the exhaust outlet of the intake and exhaust valve during the exhaust period,
the absolute pressure of air in the pipe is shown, and Av is the section of an exhaust outlet of the air inlet and exhaust valve; r is a gas constant, TaIs the temperature in the tube in degrees kelvin,
is atmospheric absolute pressure;
when in use
When the concentration of the active carbon is more than 1.892,
according to the streamline mathematical model of the air intake and exhaust valve, the air intake and exhaust capacity is closely related to the air intake and exhaust flow coefficient, and the air intake and exhaust capacity is improved through an air flow channel adopting the air intake and exhaust valve.
Establishing a flow control equation:
the method comprises the following steps of establishing a mass conservation equation, a flow conservation equation and an energy conservation equation according to a continuous medium control equation, considering the compressibility and turbulence characteristics of air, further comprising a gas state equation and a characteristic line equation of turbulent flow, neglecting masonry force and heat source influence based on a Cartesian coordinate system, and performing dimensionless processing, wherein the conservation form of a three-dimensional continuous medium control equation is as follows:
in the formula: q is a conservative value; E. f, G is the throughput; subscript v is the viscous flux, expressed as follows:
in the formula: ρ is the gas density; u, v and w are flow velocities in x, y and z directions; e is the internal energy per unit mass; p is the pressure intensity; q is the energy flux; reIs Reynolds number; tau is the stress tensor and is equal to the sum of laminar and turbulent shear stresses; the shear stress in each direction is as follows:
in the formula:
laminar shear stress;
is turbulent shear stress; k is the turbulence energy;
the energy flux due to heat conduction is formulated as follows:
in the formula: mu.slIs the molecular viscosity coefficient; mu.stA turbulent flow viscosity coefficient; pr (Pr) oflIs the prandtl number; pr (Pr) oftIs the turbulent flow prandtl number; t is the temperature; gamma is the gas specific heat ratio; ma∞The mach number of the incoming flow;
in order to simulate the streamline characteristics of the air inlet and exhaust channel of the variable-section air inlet and exhaust valve, an RNG k-epsilon model is adopted for data processing.
Further, the variable cross-section air inlet and outlet valve comprises a large-orifice air inlet and outlet device with low-pressure and large-amount air inlet and outlet functions and a buffer device with impact water hammer prevention and closing functions, and the bottom of the large-orifice air inlet and outlet device is connected with the buffer device.
Furthermore, the large orifice air inlet and exhaust device comprises a large orifice air inlet and exhaust valve body of an exhaust flow passage with a full-bore diameter formed by small-large-small groups, the area of any flow passing cross section of the exhaust flow passage is not smaller than the specification area of the valve, the flow passage in the valve body is streamline, a floating ball capable of moving up and down is arranged in the large orifice air inlet and exhaust valve body, a floating ball tray is arranged at the bottom of the large orifice air inlet and exhaust valve body, a valve seat is arranged at the top outlet of the large orifice air inlet and exhaust valve body, and a gland is arranged at the top of the valve seat.
Preferably, the valve seat adopts a sealing structure combining a copper alloy seal and a rubber seal.
Preferably, the floating ball is a smooth spherical free floating ball.
Furthermore, the buffer device comprises a buffer valve body with a small-large-small cross section, a buffer plate is arranged in the buffer valve body, a connecting pipe is arranged at the top of the buffer valve body, a water hammer-proof valve clack is sleeved on the connecting pipe, and the upper end of the connecting pipe is connected with the part of the valve body, which is positioned between the large-hole inlet and outlet device and the buffer device.
The large-orifice air inlet and outlet device is composed of a large-orifice air inlet and outlet valve body, a floating ball, a valve seat, a gland and the like, and the buffer device is composed of a buffer valve body, a buffer plate and the like. The runner structure adopts the aerodynamic principle design, and the runner design is streamlined in the valve, can not hinder the air outflow.
The large-orifice air inlet and outlet device is of a floating ball structure, and the floating ball is seated on the floating ball tray under normal conditions. When the empty pipe is filled with water, air passes through the periphery of the floating ball and upwards along the bottom of the floating ball tray and is exhausted to the atmosphere after passing through the valve seat, so that a large amount of exhaust functions are realized; after the air is exhausted, water enters the valve body, and the floating ball floats under the buoyancy of the water to close the air inlet and exhaust part of the large orifice. When pipeline evacuation or blow out, the floater falls rapidly, in time inhales the air, destroys the pipeline vacuum, and when the water column was closed, the buffer board was closed in advance, and the most air of damming was in the pipeline, and the valve is a small amount of exhaust, cuts off through the air, prevents that the water column from closing to eliminate the closing water hammer. The large-orifice air intake and exhaust flow passage is designed in a full-bore mode, the area of any flow cross section of the flow passage is not less than the area of the specification of the valve, and the air intake and exhaust requirements are fully met.
Further, the exhaust performance test platform comprises a roots blower, a silencing device, a pressure release valve, a first pressure transmitter, a rectifying device, a temperature sensor, a differential pressure transmitter, an integrated orifice plate flowmeter, an air inlet and exhaust valve V1, a V2, a V3, a V4, a V5, a V6 and a V7, wherein the air inlet and exhaust valve V1 is connected with an air inlet of the roots blower through an air inlet pipe, an air outlet of the roots blower is connected with an air inlet of the silencing device, an air outlet of the silencing device is connected with a first pipeline, the pressure release valve, the air inlet and exhaust valve V2, the rectifying device and the integrated orifice plate flowmeter are sequentially arranged on the first pipeline from near to far, an air vent and a flange cover for closing the air vent are arranged on the pipeline between the pressure release valve and the air inlet and exhaust valve V2, the flange cover is opened during an air suction test, one end of the air inlet and exhaust valve V3 is communicated, the other end of the air inlet and exhaust valve V3 is connected with one end of a first flange reducer, the other end of the first flange reducer is connected with a first air suction test valve through a first vertical pipe, the first vertical pipe is connected with a first pressure transmitter, the part of a first pipeline, which is positioned between the air inlet and exhaust valve V2 and the air inlet and exhaust valve V3, is communicated with a branch pipe leading to atmosphere, the branch pipe is connected with an air inlet and exhaust valve V6 and an air inlet and exhaust valve V7 in parallel, one end of the air inlet and exhaust valve V5 is connected with a first pipeline, the other end of the air inlet and exhaust valve V5 is connected with one end of a second flange reducer, the other end of the second flange reducer is connected with a second air suction test valve through a second vertical pipe, the second vertical pipe is connected with a second pressure transmitter, a temperature sensor is arranged on the pipeline between the rectifying device and the orifice plate integrated flowmeter, and differential pressure transmitters are, be provided with on the pipeline between integral type orifice plate flowmeter and the valve V5 that advances to exhaust and reserve the interface and be used for sealing the blind flange of this reservation interface, the one end of valve V4 that advances to exhaust is connected on the pipeline between integral type orifice plate flowmeter and the valve V5 that advances to exhaust, the other end of valve V4 that advances to exhaust is connected with the one end of second pipeline, the other end of second pipeline passes through the one end connection of third flange reducing pipe, the other end of third flange reducing pipe passes through connecting pipe and air-intake connection.
Preferably, the air inlet of the silencing device is connected with the air outlet of the Roots blower through an elastic joint.
The invention has the following advantages:
1. the air intake and exhaust performance is improved:
according to the streamline mathematical model of the air intake and exhaust valve, the air intake and exhaust capacity is not determined only by the temperature and the pressure inside and outside the pipe, the actual air intake and exhaust capacity is deviated from the theoretical air intake and exhaust capacity, the energy conservation law indicates that partial kinetic energy of flowing gas can be lost in the air intake and exhaust channel, and the greater the loss of the kinetic energy, the air intake and exhaust function of the air intake and exhaust valve cannot be embodied.
Fluent in CFD is widely used in related fields such as fluid and the like, and is used as a calculation tool to perform grid division, model establishment and simulation on the basis of the improved design of the variable-section flow passage intake and exhaust valve flow passage. The flowing state of the gas in the flow channel is improved, and the occurrence of gas flow vortexes in the flow channel is reduced, so that the energy loss is reduced, and the gas inlet and outlet performance can be better improved;
2. the cavitation problem is reduced, and the service life of the air inlet and outlet valve is prolonged;
firstly, when a floating ball in an air inlet and outlet valve acts, water flow in a flow channel flows at a high speed to generate cavitation; secondly, the action of the floating ball generating negative pressure in the pipe is delayed to a certain extent, bubbles in water are separated out due to the negative pressure in the flow channel, when the floating ball falls down, the pressure in the pipe is increased, the bubbles collapse, and cavitation is generated on the flow channel and the inner parts of the flow channel. The flow channel is streamlined, so that a negative pressure area is reduced, the cavitation problem can be effectively relieved, and the service life of the air inlet and outlet valve is prolonged.
3. Reducing the shape-selecting caliber of the air inlet and outlet valve and reducing the engineering investment
Novel inlet and exhaust valve based on variable cross section runner design has more abundant intake and exhaust ability, compares with conventional inlet and exhaust valve, under the prerequisite that realizes equal intake and exhaust gas volume, can select less bore, also can reduce inlet and exhaust valve quantity, reduces the engineering to reduce inlet and exhaust valve inner part cavitation, extension inlet and exhaust valve life provides the guarantee for pipeline under pressure engineering safe operation.
The invention firstly proposes the concept of dynamic air intake and exhaust flow coefficient and how to correctly use the air intake and exhaust flow coefficient, and the introduction of the dynamic air intake and exhaust flow coefficient can make up the problem of lack of an air intake and exhaust flow coefficient using method in domestic specifications; the basic idea of the variable cross-section design of the air inlet and exhaust flow passage of the combined type air inlet and exhaust valve is fully utilized to play the air inlet and exhaust functions of the combined type air inlet and exhaust valve; the basic idea of the variable cross-section design of the air inlet and exhaust flow passage of the combined type air inlet and exhaust valve provides a main technical basis for the optimal design of the air inlet and exhaust flow passage of the combined type air inlet and exhaust valve. The invention provides technical basis for the perfect revision of the model selection standard of the air inlet and outlet valve and the establishment of the production technical standard of the air inlet and outlet valve products in the water supply industry in China, so that the project has important significance for ensuring the safe and reliable operation of the pressure pipeline.
Drawings
FIG. 1 is a theoretical flow diagram of the gases in the intake and exhaust valves;
FIG. 2 is a flow chart of an intake/exhaust passage in a conventional intake/exhaust valve;
FIG. 3 is a schematic longitudinal sectional view of the intake/exhaust valve with variable cross-section;
FIG. 4 is a flow chart of intake and exhaust passages of the intake and exhaust valves with variable cross sections;
FIG. 5 is a schematic view of a structure of an exhaust function testing platform;
FIG. 6 is a schematic top view of the testing platform for testing exhaust function;
FIG. 7 is a graph of DN150 theoretical displacement and standard displacement of intake and exhaust valves and their exhaust coefficients;
FIG. 8 is a theoretical displacement, normalized displacement curve of the intake and exhaust valves with variable cross-section and their exhaust coefficients.
Description of reference numerals: 1. a Roots blower; 2. a muffler device; 3. a pressure relief valve; 4. a pressure transmitter; 5. a rectifying device; 6. a temperature sensor; 7. a differential pressure transmitter; 8. an integral orifice plate flowmeter; 9. a flange cover 10 and a flange elbow; 11. a flange reducer pipe; 12. an upright tube; 13. an inspiratory test valve; 14. an elastic joint; 15. a first conduit; 16. a second conduit; 17. a third flange reducer pipe; 18. a connecting pipe; 19. an air inlet pipe; 20. a cushion valve body; 21. a buffer plate; 22. a large orifice air intake and exhaust valve body; 23. a valve seat; 24. a floating ball; 25. a floating ball tray; 26. and (7) pressing the cover.
Detailed Description
The technical solutions of the present invention will be described clearly and completely with reference to the accompanying drawings, and it is obvious that the described embodiments are some, but not all embodiments of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Specifically, the following description is provided: in the present invention, "low pressure" generally refers to initial water-filling or emptying conditions; the large amount is a concept corresponding to the trace amount, the intake and exhaust of the trace intake and exhaust valve are all trace, and the intake and exhaust of the high-speed intake and exhaust valve are all large; in AWWA M51 (american society for water and utilities) standard, the large-diameter intake and exhaust valve is also referred to as a high-speed intake and exhaust valve (also innovative part of the present invention), and the general bore diameter of 10-150mm is the large-bore intake and exhaust valve.
"intake and exhaust flow coefficient" is simply referred to as "intake and exhaust coefficient"; the "exhaust flow rate coefficient" is simply referred to as "exhaust coefficient".
The implementation method for improving the exhaust capacity of the air inlet and exhaust valve comprises the following steps: establishing a streamline mathematical model of an air inlet and outlet valve based on mechanism research of gas state parameters; for each water supply system, theoretical air intake and exhaust amount calculation is carried out according to a streamline mathematical model of an air intake and exhaust valve, the model and the specification of a conventional air intake and exhaust valve are determined according to the specification of a CJT 217-2013 water supply pipeline composite high-speed air intake and exhaust valve, and an exhaust flow coefficient is calculated; recording and calculating the actual displacement of the selected air inlet and outlet valves based on an air outlet performance test platform; designing a variable cross-section intake and exhaust valve with an intake and exhaust flow passage of the same specification being streamline, installing the variable cross-section intake and exhaust valve on an exhaust performance test platform, and recording, testing and calculating the actual exhaust volume and the exhaust flow coefficient of the variable cross-section intake and exhaust valve with the intake and exhaust flow passage being streamline based on the exhaust performance test platform; under the condition of finishing the same air displacement, the variable cross-section air inlet and outlet valve is selected to have a smaller caliber. On the premise of ensuring the safety of a water supply system, tests prove that the exhaust capacity of the variable cross-section air inlet and outlet valve is obviously improved, which is mainly reflected in that the exhaust flow coefficient is greatly improved; on the premise of meeting the exhaust requirement, the caliber and the number of the air inlet and exhaust valves can be reduced, so that the engineering investment is reduced, the negative pressure area is reduced, the anti-cavitation capability of parts in the exhaust valves is improved, and the service life of the air inlet and exhaust valves is prolonged.
Further, the intake and exhaust valve streamline mathematical model is as follows:
the air flow of the air inlet and outlet valves is similar to the air flow of the nozzle, and the nozzle is mathematically modeled according to the assumptions of Wylie and street:
energy equation:
where k is the adiabatic index (air k ═ 1.4), R is the gas constant, T is the temperature, and v is the velocity; by integration we can get:
v2is the outlet air flow rate,
for inlet air absolutePressure, p1In order to be the inlet air density,
absolute pressure of outlet air, T1Is the inlet air temperature;
substituting the continuity equation to obtain:
wherein the content of the first and second substances,
is the theoretical mass flow of air in the pipe when the air passes through the air inlet and outlet valve and the air outlet is A2Is the section of an exhaust outlet of the air inlet and exhaust valve;
this expression provides an "upper limit value" corresponding to the true mass flow, since it assumes that the isentropic variations of the air are fully reversible;
in fact, the process is irreversible due to friction and turbulence, the true mass flow is low:
if CdFor the intake-exhaust flow coefficient, i.e. the relationship between the true mass flow and the theoretical mass flow of the air in the duct through the intake-exhaust valve exhaust outlet during exhaust, then when the flow through the intake-exhaust valve is subsonic, i.e. when the flow through the intake-exhaust valve is subsonic
When the concentration of the metal oxide is less than 1.892,
wherein the content of the first and second substances,
the actual mass flow of the air in the pipe when the air passes through the air inlet and outlet valve and the air outlet,
is the absolute pressure of air in the pipe, and Av is the section of an exhaust outlet of the air inlet and exhaust valve,
atmospheric absolute pressure;
when in use
Above 1.892, sonic conditions are reached at the flow outlet and the air velocity remains constant, since supersonic flow cannot exist in the converging nozzle; in this case, assuming that the air temperature in the duct remains constant, then there is a constant volume flow, but the mass flow is varied, the mass flow increases with increasing duct pressure, which also increases the air density, and therefore, when the air temperature in the duct remains constant, the air density increases as the duct pressure increases
When the concentration of the active carbon is more than 1.892,
according to the streamline mathematical model of the air inlet and outlet valve, the air inlet and outlet capacity is closely related to the air inlet and outlet flow coefficient, and the air inlet and outlet capacity is improved by adopting an air flow channel of the air inlet and outlet valve;
establishing a flow control equation:
the method comprises the following steps of establishing a mass conservation equation, a flow conservation equation and an energy conservation equation according to a continuous medium control equation (N-S equation) when the air flow in an air inlet and outlet valve flow passage is high, considering the compressibility and the turbulence characteristic of the air, further comprising a gas state equation and a characteristic line equation of turbulent flow, neglecting masonry force and heat source influence on the basis of a Cartesian coordinate system, and performing dimensionless processing, wherein the conservation form of a three-dimensional N-S equation is as follows:
in the formula: q is a conservative value; E. f, G is the throughput; subscript v is the viscous flux, expressed as follows:
in the formula: ρ is the gas density; u, v and w are flow velocities in x, y and z directions; e is the internal energy per unit mass; p is the pressure intensity; q is the energy flux; reIs Reynolds number; tau is the stress tensor and is equal to the sum of laminar and turbulent shear stresses; the shear stress in each direction is as follows:
in the formula:
laminar shear stress;
is turbulent shear stress; k is the turbulence energy;
the energy flux due to heat conduction is formulated as follows:
in the formula: mu.slIs the molecular viscosity coefficient; mu.stA turbulent flow viscosity coefficient; pr (Pr) oflIs the prandtl number; pr (Pr) oftIs the turbulent flow prandtl number; t is the temperature; gamma is the gas specific heat ratio; ma∞The mach number of the incoming flow;
in order to simulate the streamline characteristics of the air inlet and exhaust channel of the variable-section air inlet and exhaust valve, an RNG k-epsilon model is adopted for data processing.
As shown in fig. 3 to 4, the variable cross-section air inlet and outlet valve comprises a large-orifice air inlet and outlet device with low-pressure and large-amount air inlet and outlet functions, and a buffer device with impact water hammer prevention and water hammer closing functions, wherein the bottom of the large-orifice air inlet and outlet device is connected with the buffer device. The large-orifice air inlet and exhaust device comprises a large-orifice air inlet and exhaust valve body 22 of an exhaust flow passage with a full-bore diameter formed by small-large-small groups, the area of any flow-passing cross section of the exhaust flow passage is not smaller than the specification area of the valve, the flow passage in the valve body is streamline, a floating ball 24 capable of moving up and down is arranged in the large-orifice air inlet and exhaust valve body 22, a floating ball tray 25 is arranged at the bottom of the large-orifice air inlet and exhaust valve body, a valve seat 23 is arranged at the outlet of the top of the large-orifice air inlet and exhaust valve body 22, and a gland 26 is; the buffer device comprises a buffer valve body 20 with a small-large-small cross section, a buffer plate 21 is arranged in the buffer valve body 20, a connecting pipe is arranged at the top of the buffer valve body 20, a water hammer-proof valve clack is sleeved on the connecting pipe, and the upper end of the connecting pipe is connected with the part of the valve body, which is positioned between the large-hole inlet and outlet device and the buffer device.
Preferably, the valve seat 23 adopts a sealing structure combining copper alloy sealing and rubber sealing, and the sealing performance is good.
Preferably, the floating ball 24 is a smooth spherical free floating ball, which is not guided and blocked, and the floating ball 24 moves completely freely, so that the phenomenon that the floating ball 24 cannot move normally due to blockage of impurities is avoided.
The large-hole inlet and exhaust device has low-pressure and large-amount inlet and exhaust functions, the buffer device has the functions of preventing impact water hammer and closing water hammer, the combined type inlet and exhaust valve is structurally guaranteed to timely feed and exhaust air when a pipeline normally runs, and the closing water hammer is effectively protected when a pump is stopped or a valve is closed.
The large-orifice air inlet and outlet device comprises a large-orifice air inlet and outlet valve body 22, a floating ball 24, a valve seat 23, a gland 26 and the like, and the buffer device comprises a buffer valve body 20, a buffer plate 21 and the like. The runner structure adopts the aerodynamic principle design, and the runner design is streamlined in the valve, can not hinder the air outflow.
The large-orifice air inlet and outlet device is of a floating ball structure, and under a normal condition, a floating ball 24 is seated on a floating ball tray 25. When the empty pipe is filled with water, air passes through the periphery of the floating ball 24 upwards along the bottom of the floating ball tray 25 and is exhausted to the atmosphere after passing through the valve seat 23, so that a large amount of exhaust functions are realized; after the air is exhausted, water enters the valve body, and the floating ball 24 floats under the buoyancy of the water to close the air inlet and exhaust part of the large orifice. When the pipeline is emptied or the pipe burst is drained, the floating ball 24 falls rapidly to suck air in time to break the vacuum of the pipeline, when the water column is closed, the buffer board 21 is closed in advance, most of the air is intercepted in the pipeline, the valve exhausts a small amount of air, and the water column is prevented from being closed through the air partition, so that the closing water hammer is eliminated. The large-orifice air intake and exhaust flow passage is designed in a full-bore mode, the area of any flow cross section of the flow passage is not less than the area of the specification of the valve, and the air intake and exhaust requirements are fully met.
As shown in fig. 5 to 6, further, the exhaust performance test platform comprises a roots blower 1, a silencer (FX- Φ 350)2, a pressure release valve 3, a first pressure transmitter (MC15A)4, a rectifier (ZLQ-DN350)5, a temperature sensor (WZP100)6, a differential pressure transmitter (MC1570A)7, an integrated orifice plate flowmeter (LT-LG)8, an air inlet and exhaust valve V1, V2, V3, V4, V5, V6, V7, wherein the air inlet and exhaust valve V1 is connected with an air inlet of the roots blower 1 through an air inlet pipe 19, an air outlet of the roots blower 1 is connected with an air inlet of the silencer 2, an air outlet of the silencer 2 is connected with a first pipeline 15, the pressure release valve 3, the air inlet and exhaust valve V2, the rectifier (ZLQ-DN350)5, and the integrated orifice plate flowmeter (LT-LG)8 are sequentially arranged on the first pipeline 15 from near to far from the silencer 2, a vent hole and a flange cover for closing the vent hole are arranged on a pipeline between the pressure release valve 3 and the air inlet and outlet valve V2, the flange cover 9 is opened during air suction test, one end of the air inlet and outlet valve V3 is communicated with the part of the first pipeline between the air inlet and outlet valve V2 and the rectifying device (ZLQ-DN350)5, the other end of the air inlet and outlet valve V3 is connected with one end of the first flange reducer 11, the other end of the first flange reducer 11 is connected with the first air suction test valve 13 through a first vertical pipe 12, the first vertical pipe 12 is connected with a first pressure transmitter (MC15A)4, the part of the first pipeline 15 between the air inlet and outlet valve V2 and the air inlet and outlet valve V3 is communicated with a branch pipe leading to atmosphere, the branch pipe is provided with the air inlet and outlet valve V6 and the air inlet and outlet valve V7 in parallel, one end of the air inlet and outlet valve V5 is connected with the first pipeline 15, the other end of the second flange, The other end of the second flange reducer pipe is connected with a second air suction test valve through a second vertical pipe, a second pressure transmitter (MC15A) is connected onto the second vertical pipe, a temperature sensor (WZP100)6 is arranged on a pipeline between a rectifying device (ZLQ-DN350)5 and an integrated orifice plate flowmeter (LT-LG)8, a differential pressure transmitter (MC1570A)7 is further arranged on pipelines on two sides of the integrated orifice plate flowmeter (LT-LG)8, a reserved connector and a flange cover used for sealing the reserved connector are arranged on a pipeline between the integrated orifice plate flowmeter (LT-LG)8 and an air inlet and exhaust valve V5, one end of an air inlet and exhaust valve V4 is connected onto a pipeline between the integrated orifice plate flowmeter (LT-LG)8 and an air inlet and exhaust valve V5, the other end of the air inlet and exhaust valve V4 is connected with one end of the second pipeline 16, the other end of the second pipeline 16 is connected with one end of a third flange reducer pipe, the other end of the third flange reducer 17 is connected to an intake pipe 19 through a connecting pipe 18.
Preferably, the inlet of the muffler device (FX- Φ 350)2 is connected to the outlet of the roots blower 1 via an elastic joint 14.
Testing procedure of exhaust experiment
1. The valves and the measuring instrument are installed on the pipeline according to the figures 5 to 6, the air inlet and outlet valves V1, V2 and V5 are opened, the air inlet and outlet valves V3 and V4 are closed, the air inlet and outlet valves V6 and V7 are adjusted, the flange cover (DN350)9 on the vent is closed, and the flange cover (DN200) of the reserved interface on the pipeline between the integrated orifice plate flowmeter (LT-LG)8 and the air inlet and outlet valve V5 is closed. The orifice flowmeter is connected with a signal line and a power line, the inlet valve and the outlet valve are opened, and the valve opening of the inlet valve and the valve opening of the outlet valve are consistent. And (3) starting the fan, inflating the pipeline, opening the orifice plate flowmeter and the stainless steel three-valve group balance intake and exhaust valve, slowly opening the intake and exhaust valve at the high-low pressure end of the orifice plate, and closing the stainless steel three-intake and exhaust valve group balance intake and exhaust valve after the fluid passes through the flowmeter.
2. And adjusting the air inlet and outlet valves V6 or V7, testing the flow value Q of the orifice plate flowmeter at different opening degrees, recording P-Q data and comparing the P-Q data with a calibrated value. When the deviation is not more than 1%, the orifice plate flowmeter is considered to be in an accurate state.
3. And starting the test after the orifice plate flowmeter is calibrated, closing the air inlet and outlet valve V5, and opening the test air inlet and outlet valve after the test air inlet and outlet valve is installed at the exhaust test position. The gas passes through the rectifying net and the orifice plate flowmeter and then to the intake and exhaust valve to be tested, and the exhaust volume is measured.
4. And adjusting the fan, and recording data when the inlet pressure P value of the air inlet and exhaust valve reaches the pressure to be measured. (if the flow needs to be reduced, the air inlet and exhaust valves V6 and V7 are adjusted, the air inlet and exhaust valve V7 is roughly adjusted, and the air inlet and exhaust valve V6 is finely adjusted). Intake and exhaust valve actuation was observed and P, Q values were recorded.
5. If the inlet pressure P value of the air inlet and exhaust valve fluctuates sharply, the flow Q value tends to be stable; or the throttle plug is blown up (the exhaust sound becomes sharp, the throttle plug collides with the small bell and makes a sound), the large amount of exhaust is considered to reach the critical value, and corresponding data is recorded at the moment. Otherwise, the flow of the fan is continuously increased, and the actions are repeated until the throttle plug is blown up.
6. The throttle plug is blown up, and a large amount of exhaust is finished, and micro-exhaust is carried out at the moment. And in the micro-discharge process, the floating ball is blown up, the throttling plug falls, the flow Q value is reduced, and the pressure P value is increased. The corresponding data is recorded. And after micro-discharging is finished, the floating ball falls, the pressure P is reduced, the flow Q is increased, and the next exhaust cycle is started.
7. And (5) closing the Roots blower 1 after the test is finished.
Exhaust gas Performance test results
The invention mainly aims to improve the air intake and exhaust capacity of an air intake and exhaust valve, and the main index for measuring the air intake and exhaust capacity of the exhaust valve is an air intake and exhaust flow coefficient, which is defined as: the ratio of the actual air intake and exhaust amount to the theoretical air intake and exhaust amount is calculated by applying the mathematical model below based on different pressure difference conditions inside and outside a pipe in a pressure water delivery system, and calculating the theoretical exhaust coefficient of the air intake and exhaust process of an air intake and exhaust valve by adopting the exhaust amount of an FGP type composite high-speed air intake and exhaust valve with the caliber of 150mm given by the current domestic specification 'composite high-speed air intake and exhaust valve (CJ/T19-1513'); based on the measured variable cross-section displacement, the actual exhaust coefficient of the variable cross-section intake/exhaust valve is calculated, and the result is shown in table 1. The theoretical displacement of the DN150 intake and exhaust valve and the displacement and the exhaust coefficient thereof are shown in the graph 7, and the theoretical displacement and the exhaust coefficient thereof are shown in the graph 8.
TABLE 1 theoretical and normative values of air displacement of air inlet and outlet valves
As can be seen from fig. 6 and 7, the calculated value of the exhaust flow of the intake and exhaust valve, the value given by the specification and the intake and exhaust threshold value of the variable cross-section are compared under the same differential pressure, and the larger the differential pressure between the inside and the outside of the pipe is, the larger the difference between the calculated value and the measured value is. In order to make the air displacement of the air inlet and outlet valve closer to the actual value in the water hammer simulation calculation, an air inlet and outlet flow coefficient is introduced into the model. From Table 1, it can be seen that the difference between the internal and external pressure difference of the intake and exhaust valves is different, and the exhaust coefficient is different, which is a dynamic coefficient.
The above disclosure is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the scope of the present invention, therefore, the present invention is not limited by the appended claims. It is to be understood that the above description is intended to be illustrative, and not restrictive. For example, the above-described embodiments (and/or aspects thereof) may be used in combination with each other. In addition, many modifications may be made to adapt a particular situation or material to the teachings of the invention without departing from its scope. Many other embodiments and modifications within the scope and spirit of the claims will be apparent to those of skill in the art from reading the foregoing description.
Claims (8)
1. An implementation method for improving the exhaust capacity of an intake and exhaust valve is characterized in that a streamline mathematical model of the intake and exhaust valve is established based on the mechanism research of gas state parameters; for each water supply system, theoretical air intake and exhaust amount calculation is carried out according to a streamline mathematical model of an air intake and exhaust valve, the model and specification of a conventional air intake and exhaust valve are determined according to specification, and an exhaust flow coefficient is calculated; recording and calculating the actual displacement of the selected air inlet and outlet valves based on an air outlet performance test platform; designing a variable cross-section intake and exhaust valve with an intake and exhaust flow passage of the same specification being streamline, installing the variable cross-section intake and exhaust valve on an exhaust performance test platform, and recording, testing and calculating the actual exhaust volume and the exhaust flow coefficient of the variable cross-section intake and exhaust valve with the intake and exhaust flow passage being streamline based on the exhaust performance test platform; under the condition of finishing the same air displacement, the variable cross-section air inlet and outlet valve is selected to have a smaller caliber;
the streamline mathematical model of the intake and exhaust valve is as follows:
when in use
When the concentration of the metal oxide is less than 1.892,
wherein:
is the true mass flow of air in the tube through the exhaust outlet of the intake and exhaust valve, CdThe intake and exhaust flow coefficient is the relationship between the real mass flow and the theoretical mass flow of the air in the pipe passing through the exhaust outlet of the intake and exhaust valve during the exhaust period,
the absolute pressure of air in the pipe is shown, and Av is the section of an exhaust outlet of the air inlet and exhaust valve; r is a gas constant, TaIs the temperature in the tube in degrees kelvin,
is atmospheric absolute pressure;
when in use
When the concentration of the active carbon is more than 1.892,
according to the streamline mathematical model of the air inlet and outlet valve, the air inlet and outlet capacity is closely related to the air inlet and outlet flow coefficient, and the air inlet and outlet capacity is improved by adopting an air flow channel of the air inlet and outlet valve;
establishing a flow control equation of an air flow passage of the air inlet/outlet valve:
the method comprises the following steps of establishing a mass conservation equation, a flow conservation equation and an energy conservation equation according to a continuous medium control equation, considering the compressibility and turbulence characteristics of air, further comprising a gas state equation and a characteristic line equation of turbulent flow, neglecting masonry force and heat source influence based on a Cartesian coordinate system, and performing dimensionless processing, wherein the conservation form of a three-dimensional continuous medium control equation is as follows:
in the formula: q is a conservative value; E. f, G is the throughput; subscript v is the viscous flux, expressed as follows:
in the formula: ρ is the gas density; u, v and w are flow velocities in x, y and z directions; e is the internal energy per unit mass; p is the pressure intensity; q is the energy flux; reIs Reynolds number; tau is the stress tensor and is equal to the sum of laminar and turbulent shear stresses; the shear stress in each direction is as follows:
in the formula:
laminar shear stress;
is turbulent shear stress; k is the turbulence energy;
the energy flux due to heat conduction is formulated as follows:
in the formula: mu.slIs the molecular viscosity coefficient; mu.stA turbulent flow viscosity coefficient; pr (Pr) oflIs the prandtl number; pr (Pr) oftIs the turbulent flow prandtl number; t is the temperature; gamma is the gas specific heat ratio; ma∞The mach number of the incoming flow;
in order to simulate the streamline characteristics of the air inlet and exhaust channel of the variable-section air inlet and exhaust valve, an RNG k-epsilon model is adopted for data processing.
2. The method for improving the exhaust capability of the intake and exhaust valve according to claim 1, wherein the variable cross-section intake and exhaust valve comprises a large-orifice intake and exhaust device with low-pressure and large-amount intake and exhaust functions, and a buffer device with functions of preventing impact water hammer and closing water hammer, wherein the bottom of the large-orifice intake and exhaust device is connected with the buffer device.
3. The method for improving the exhaust capability of an air intake and exhaust valve according to claim 2, wherein the large-orifice air intake and exhaust device comprises a large-orifice air intake and exhaust valve body of an exhaust flow passage with a cross section formed by a small group, a large group and a small group into a full diameter, any flow cross section area of the exhaust flow passage is not smaller than the specification area of the valve, the flow passage in the valve body is streamline, a floating ball capable of moving up and down is arranged in the large-orifice air intake and exhaust valve body, a floating ball tray is arranged at the bottom of the large-orifice air intake and exhaust valve body, a valve seat is arranged at the top outlet of the large-orifice air intake and exhaust valve body, and a gland.
4. The method for improving the exhaust capability of an air intake and exhaust valve according to claim 3, wherein the valve seat is a sealing structure combining a copper alloy seal and a rubber seal.
5. The method as claimed in claim 3, wherein the floating ball is a smooth spherical free floating ball.
6. The method for improving the exhaust capability of an air inlet and exhaust valve according to claim 2, wherein the buffer device comprises a buffer valve body with a small-large-small cross section, a buffer plate is arranged in the buffer valve body, a connecting pipe is arranged at the top of the buffer valve body, a water hammer preventing valve flap is sleeved on the connecting pipe, and the upper end of the connecting pipe is connected with the part of the valve body between the large-hole air inlet and exhaust device and the buffer device.
7. The method as claimed in claim 1, wherein the exhaust performance testing platform comprises a roots blower, a noise elimination device, a pressure release valve, a first pressure transmitter, a rectifying device, a temperature sensor, a differential pressure transmitter, an integrated orifice plate flowmeter, an air inlet/outlet valve V1, a V2, a V3, a V4, a V5, a V6 and a V7, the air inlet/outlet valve V1 is connected with an air inlet of the roots blower through an air inlet pipe, an air outlet of the roots blower is connected with an air inlet of the noise elimination device, an air outlet of the noise elimination device is connected with a first pipeline, the pressure release valve, the air inlet/outlet valve V2, the rectifying device and the integrated orifice plate flowmeter are sequentially arranged on the first pipeline from near to far from the noise elimination device, a vent hole and a flange cover for closing the vent hole are arranged on the pipeline between the pressure release valve and the air inlet/outlet valve V2, the flange, one end of the air inlet and exhaust valve V3 is communicated with the part of the first pipeline between the air inlet and exhaust valve V2 and the rectifying device, the other end of the air inlet and exhaust valve V3 is connected with one end of the first flange reducer, the other end of the first flange reducer is connected with the first air suction test valve through the first vertical pipe, the first vertical pipe is connected with a first pressure transmitter, the part of the first pipeline between the air inlet and exhaust valve V2 and the air inlet and exhaust valve V3 is communicated with a branch pipe leading to atmosphere, the branch pipe is provided with an air inlet and exhaust valve V6 and an air inlet and exhaust valve V7 in parallel, one end of the air inlet and exhaust valve V5 is connected with the first pipeline, the other end of the first pipeline is connected with one end of the second flange reducer through a flange, the other end of the second flange reducer is connected with the second air suction test valve through the second vertical pipe, the second vertical pipe is connected with a second pressure transmitter, a temperature sensor is arranged on the pipeline between the, still be equipped with differential pressure transmitter on the pipeline of integral type orifice plate flowmeter both sides, be provided with on the pipeline between integral type orifice plate flowmeter and the air inlet and exhaust valve V5 and reserve the interface and be used for sealing the blind flange of this reservation interface, air inlet and exhaust valve V4's one end is connected on the pipeline between integral type orifice plate flowmeter and air inlet and exhaust valve V5, air inlet and exhaust valve V4's the other end is connected with the one end of second pipeline, the other end of second pipeline passes through the one end connection of third flange reducing pipe, the other end of third flange reducing pipe passes through connecting pipe and air intake-tube connection.
8. The method for improving the exhaust capability of an air inlet/outlet valve is characterized in that the air inlet of the silencing device is connected with the air outlet of the Roots blower through an elastic joint.
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| CN112991625B (en) * | 2021-05-19 | 2021-07-27 | 天津赛恩能源技术股份有限公司 | Matrix type valve control water meter system and valve control method thereof |
| CN113483946B (en) * | 2021-06-01 | 2023-04-28 | 广西防城港核电有限公司 | Water filling and exhausting system and method for differential pressure transmitter |
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| CN102401155A (en) * | 2011-08-30 | 2012-04-04 | 深圳市华力大机电技术有限公司 | Air valve set with four functions for waterproof hammer |
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| CN207999538U (en) * | 2018-01-31 | 2018-10-23 | 杨玉明 | Three-level exhaust, waterproof plektron air valve |
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| CN102401155A (en) * | 2011-08-30 | 2012-04-04 | 深圳市华力大机电技术有限公司 | Air valve set with four functions for waterproof hammer |
| CN104405904A (en) * | 2014-10-17 | 2015-03-11 | 北京航天益森风洞工程技术有限公司 | Large-caliber pressure regulating valve |
| CN207999538U (en) * | 2018-01-31 | 2018-10-23 | 杨玉明 | Three-level exhaust, waterproof plektron air valve |
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