CN105422868A - Pneumatic-control type gas pressure reducer - Google Patents

Abstract

The invention provides a pneumatic-control type pressure reducer and belongs to the technical field of conveying and supplying of high-pressure and intermediate-pressure media. The pneumatic-control type pressure reducer comprises an input cavity, an output cavity, a damping cavity, a control cavity, a throttling assembly, a sensing assembly, an upper valve body, a middle valve body, a lower valve body and an isolation tray. The input cavity is an annular containing cavity defined by the upper valve body, the middle valve body located on the bottom face of the cavity, and the throttling assembly located in the center of the cavity. The output cavity is an annular containing cavity defined by the middle valve body, the isolation tray located on the bottom face of the cavity, and the throttling assembly located on the upper base of the cavity. The damping cavity and the control cavity are defined by the middle valve body, the lower valve body and the isolation tray. The control cavity is used for inflating control gas. The damping cavity is used for inflating output gas with the pressure being reduced. The throttling assembly is used for reducing and stabilizing the pressure of high-pressure gas and isolating the input cavity from the output cavity. The sensing assembly is used for sensing pressure regulating signals and working parameters of the pressure reducer, then transmitting the pressure regulating signals and the working parameters to the throttling assembly and isolating the damping cavity from the control cavity. By means of the pressure reducer, pressure reduction and stabilization of large-flow gas can be achieved rapidly and stably.

Description

A kind of Pneumatic-control type gas pressure reducer

Technical field

The invention belongs to field of aerospace technology, be specifically related to high pressure and middle piezodielectric conveying with provisioning technique field.

Background technique

Decompressor is a kind of modulating valve, and inlet pressure decompression is adjusted to required exit pressure levels by the throttling action of spool by it, and is controlled the stable of the aperture maintenance outlet pressure of spool by the feedback effect of outlet pressure.Visible, the effect of decompressor is reduced pressure by upstream gas pressure and is stabilized on desirable value.In fact, decompressor utilizes the throttle effect of air-flow to realize pressure to regulate.Usually, by there is Choking phenomenon during stenosed section between spool and valve seat in pressurized gas, a part of pressure energy is converted to kinetic energy and obtains very high speed; Air-flow produces eddy current, friction and stagnation after entering output cavity, consumes a large amount of kinetic energy, and after making throttling, pressure reduces.And the motion of spool is directly associated with outlet pressure, once outlet pressure change, spool will move thereupon realize the pressure stabilization function of decompressor.

At present, decompressor is not only widely used in the industries such as oil, gas industry, chemical industry, energy industry, infrastructure construction, also plays an important role at aerospace field.In space flight industry, decompressor is mainly used in ground installation (comprising ground-testing plant), guided missile/carrier rocket and satellite astrovehicle.Wherein, in ground system test, decompressor is mainly used in propellant feed system; In guided missile and rocket, decompressor is mainly used in the pressurization system of motor storage tank; In satellite astrovehicle, decompressor is mainly used in the accurate control of attitude control engine and precise tracking.The gas pressure reducer of practical application has various structures scheme.

Monograph " liquid propellant rocket engine test " (Yuhang Publishing House, 1990,12), " practical valve design handbook " (China Machine Press, 2004,5) etc. describe multiple manually operated type decompressor.Because size is less, this kind of decompressor cannot meet large discharge gas supply requirement.

Monograph " liquid propellant rocket engine test " (Yuhang Publishing House, 1990,12) P68 describes a kind of high-pressure high-flow Pneumatic-control type decompressor, its working principle of labor, but inabundant public technology scheme, and the deliverability of this decompressor under design condition is lower than 5kg/s air.

Master thesis " characteristic research of large discharge decompressor and interior flow field the dynamic simulation " (National University of Defense Technology that claimant instructs, 2007,11) have studied a kind of large discharge Pneumatic-control type gas pressure reducer, the air mass flow that supply is greater than 20kg/s can be stablized under design condition, obtain many results having great importance, but paper only gives decompressor working principle, do not announce its detailed construction.

Always it seems, the gas pressure reducer technological schemes disclosed in source such as documents and materials, design handbook, market product information at present, all cannot meet the demand of separate unit decompressor supply more than 10kg/s air mass flow, and complex structure, reliability is low, and behaviour does and safeguards inconvenience.

Summary of the invention

Object of the present invention will solve existing decompressor cannot realize the technical problem that more than 20MPa pressurized gas that flow is greater than 10kg/s are directly decompressed to below 10MPa state and steady pressure.

For achieving the above object, the technical solution used in the present invention is as follows:

A kind of Pneumatic-control type decompressor, comprises input cavity 21, output cavity 22, damping cavity 23 and control chamber 24, orifice union, sensory package, upper valve body 2, middle valve body 7 and lower valve body 14, separator 8;

Described input cavity 21 1 by upper valve body 2, be arranged in bottom surface, chamber valve body 7 and be positioned at the ring-shaped chamber that mesotropic orifice union surrounds;

Described output cavity 22 is the ring-shaped chambers surrounded by middle valve body 7, the separator 8 being positioned at bottom surface, chamber and the orifice union that is positioned at chamber upper base;

Described damping cavity 23 and control chamber 24 by middle valve body 7, lower valve body 14 and separator 8 around forming;

Described control chamber 24 controls gas for filling, and damping cavity 23 is for the post-decompression output gas of filling;

Described orifice union is used for the decompression of pressurized gas and voltage stabilizing and Isolation input chamber 21 and output cavity 22;

Described sensory package is sent to orifice union after being used for perception decompressor pressure regulation signal and running parameter, and isolates damping cavity 23 and control chamber 24.

Described upper valve body 2 is the cylindrical body of middle part perforate, the annular chamber in inside machined " M " type cross section, and the suction port 31 processed with side is communicated with; Middle valve body 7 machined the cylindrical body of the annular chamber in " convex " type cross section for inside, be communicated with lateral flow orifices 33.Lower valve body 14 is solid of rotation of inner processing shallow " recessed " type cylindrical cavity, central authorities' processing circular locating openings, sidewall machining control gas port 35 and relief valve port 36.

Described separator 8 is " convex " shape solid of rotation of middle part perforate, is welding as one by bottom edge and middle valve body 7, is upper " convex " die cavity and lower thin cylindrical cavity two-part by " convex " cavity spacer of middle valve body 7; Separator 8 base plate processes damping hole 34, realizes the exchange of gas between output cavity 22 and damping cavity 23.

Described orifice union comprises Returnning spring 3, flap 4, valve seat 5; Valve seat 5 is hollow " convex " shape ring chambers, has seal boss 53, the flap hole 32 that valve seat lateral layout has gas to circulate in chamber; Flap 4 is round cup shape cavitys, flap bottom surface 45 designs seal boss 42, has locating column 44 and positioning pit 43 for installing Returnning spring 3 in chamber; Bottom surface 45 contacts with sensory package, and to start or to close flap 4, on flap 4, uniform flap hole 37 is to realize flap 4 internal and external pressure balance fast;

Described sensory package comprises push rod 6, upper stabilizing spring 9, diaphragm 10, two clamping disks 11, lower stabilizing spring 12, positioning rods 13; Diaphragm 10 is edge's thin discs slightly thicker than middle part, damping cavity 23 and control chamber 24 are isolated and form upper and lower two adjacent pancake cylinder cavity volumes, and upper and lower surface installs the solid of rotation clamping disk 11 of thin patty respectively; The oval mast that push rod 6 is one end conisphere shape, the other end is spherical, cone spheric end contacts with flap 4 bottom surface, the central, circular position matching of spheric end and clamping disk 11; Positioning rod 13 is short cylindrical bars that one end is spherical, one end is plane, and the positioning hole of spheric end and clamping disk 11 adapts, and planar ends is arranged in the circular locating openings of lower valve body 14, and push rod 6 is coaxially installed by the centre pilot hole of separator 8 and separator 8.

Described orifice union should meet,

1, maximum opening hmax, the flap throttling diameter D of flap 4 need meet following relationship,

${\stackrel{\·}{m}}_g=\left\{\begin{array}{cc}{\mathrm{\μ}}_g\mathrm{\π}{\mathrm{Dh}}_{\max }{p}_{10}\sqrt{\frac{2k}{(k-1)\mathrm{RT}}({\left(\frac{p_2}{p_{10}}\right)}^{\frac{2}{k}}-{\left(\frac{p_2}{p_{10}}\right)}^{\frac{k+1}{k}})},& \frac{p_2}{p_{10}}\≤{\mathrm{\σ}}_{\mathrm{cr}};\\ {\mathrm{\μ}}_g\mathrm{\π}{\mathrm{Dh}}_{\max }{p}_{10}\sqrt{\frac{k}{\mathrm{RT}}{\left(\frac{2}{k+1}\right)}^{\frac{k+1}{k-1}}},& \frac{p_2}{p_{10}}>{\mathrm{\σ}}_{\mathrm{cr}}.\end{array}\right.---\left(1\right)$

$4\≤\frac{D}{h_{\max }}\≤20---\left(2\right)$

2, the quantity n of valve seat orifice 32 ₃₂and diameter d ₃₂following relation need be met:

${\stackrel{\·}{m}}_g=\frac{{\mathrm{\μ}}_{32}\mathrm{\π}{p}_{10}}{400000}{\mathrm{\ρ}}_0{\mathrm{un}}_{32}{d}_{32}^2---\left(3\right)$

Wherein: for being flowed into the gas mass flow of output cavity 22 by input cavity 21, unit is kg/s; D is the internal diameter of flap 4 seal boss 42, and unit is m; μ _gfor Ventialtion rate, get μ _g=0.5 ~ 0.70, p ₁₀, p ₂for input cavity 21 stagnation pressure, output cavity 22 pressure, unit is Pa; K is specific heats of gases ratio, R is gas constant, and unit is J/ (kg.K); T is stagnation temperature, and unit is K; it is the critical pressure ratio of gas; μ ₃₂for the flow coefficient of valve seat orifice 32; ρ ₀for gas density under standard atmospheric conditions, unit is kg/m ³; U is gas flow velocity when flowing through valve seat orifice 32, and unit is m/s.

Described inlet hole 31 and exit orifice 33 adopt one or more groups; When one group, inlet hole 31 and exit orifice 33 present 180 degree of layouts; When organizing, uniform layout on the whole, often organizes inlet hole, exit orifice by 180 degree of layouts more.

Effective income of the present invention:

1, decompressor of the present invention adopts " three body four chambeies " structure to make the cavity volume volume such as high pressure air input cavity, the rear output cavity of decompression be easy to increase, import and export size, circulation passage area, can realize the supply of large discharge gas, MAF can reach more than 10kg/s;

2, flowing and mechanical property requirements are considered in " three body four chambeies " structure composition of decompressor of the present invention, and under the smooth and easy prerequisite of guarantee gas flow, decompressor structural mechanical property reliability is high;

3, Optimized Matching sensing assembly performance characteristic parametric scheme, decompressor fast, stably can realize decompression, the voltage stabilizing work of large discharge gas;

4, general structure has single-input single-output interface, orifice union is easy to the features such as inspection, install, maintenance and working service convenient.

Accompanying drawing explanation

Figure 1A is Pneumatic-control type decompressor moulding schematic diagram of the present invention;

Figure 1B is Pneumatic-control type decompressor longitudinal sectional view of the present invention;

Fig. 2 A is orifice union moulding schematic diagram of the present invention;

Fig. 2 B is orifice union longitudinal sectional drawing of the present invention;

Fig. 3 is valve flap structure schematic diagram of the present invention;

Wherein: 1 is valve gap, 2 is upper valve bodies, 3 is Returnning springs, 4 is flaps, 5 is valve seats, 6 is push rods, 7 is middle valve bodies, 8 is separators, 9 is upper stabilizing springs, 11 is clamping disks, 10 is diaphragms, 12 is lower stabilizing springs, 13 is positioning rods, 14 is lower valve bodies, 21 is input cavities, 22 is output cavities 22, 23 is damping cavity 23, 24 is control chambers, 31 is suction ports, 32 is valve seat orifice, 33 is air outlets, 34 is damping holes, 35 is control gas port, 36 is relief valve port, 37 is flap holes, 41 is flap outer surfaces, 42 is seal bosses, 43 is positioning pits, 44 is locating columns, 45 is flap bottom surfaces, 51 is valve seat interior surface, 52 is location anchor rings, 53 is seal bosses, 54 is bottom surfaces, location of valve seat,

Embodiment

The concrete structure of decompressor of the present invention is illustrated below in conjunction with accompanying drawing.

As shown in Figure 1A, 1B, gas pressure reducer of the present invention, has " two three body four chambeies " structural feature, specifically comprises input cavity 21, output cavity 22, damping cavity 23 and control chamber 24; Upper valve body 2, middle valve body 7 and lower valve body 14; Sensory package, orifice union.

Input cavity 21 1 by upper valve body 2, be arranged in bottom surface, chamber valve body 7 and be positioned at the ring-shaped chamber that mesotropic orifice union surrounds.Upper valve body 2 is the cylindrical body of middle part perforate on the whole, adopts the stainless steel and other metal materials of high strength to make, and the annular chamber in inside machined " M " type cross section, the suction port 31 processed with side is communicated with." M " type cross section scheme of input cavity 21, can meet valve body structure reliability simultaneously, valve seat 5 locates and multiple demands of big-flow high-pressure gas smooth outflow.Entrance hole diameter: D ₃₁=40 ~ 100mm.Input cavity 21 and output cavity 22 are isolated by orifice union

Output cavity 22 is the ring-shaped chambers surrounded by middle valve body 7, the separator 8 being positioned at bottom surface, chamber and the orifice union that is positioned at chamber upper base, and chamber central authorities are provided with push rod 6.Middle valve body 7 is the cylindrical body of middle part perforate on the whole, adopts the stainless steel and other metal materials of high strength to make, and the annular chamber in inside machined " convex " type cross section, the air outlet 33 processed with side is communicated with.Outlet aperture: D ₃₃=50 ~ 150mm.

One group of inlet hole 31/ exit orifice 33 can be adopted or organize inlet hole/exit orifice more.When one group, inlet hole 31, exit orifice 33 present 180 degree of layouts; When inlet hole, exit orifice are organized in employing more, uniform layout on the whole, often organizes inlet hole, exit orifice by 180 degree of layouts.

Damping cavity 23 and control chamber 24, be by middle valve body 7, lower valve body 14 and separator 8 around, upper and lower two adjacent pancake cylinder cavity volumes of being isolated by diaphragm 10, clamping disk 11, upper stabilizing spring 9, lower stabilizing spring 12, push rod 6 and positioning rod 13 have been installed in chamber respectively.Lower valve body 14 is solid of rotation that an inside machined shallow " recessed " type cylindrical cavity, adopts the stainless steel and other metal materials of high strength to make, and central authorities' processing circular locating openings, sidewall machined and controls gas port 35 and relief valve port 36.

Separator 8 is middle part perforate " convex " shape solid of rotation, the stainless steel and other metal materials of high strength is adopted to make, being welded as a whole by bottom edge and middle valve body 7, is upper " convex " die cavity and lower thin cylindrical cavity two-part by " convex " cavity spacer of middle valve body 7.Separator 8 base plate machined damping hole 34, realize the function of carrying out gas exchanges between output cavity 22 and damping cavity 23.Damping hole is according to academic dissertation master thesis " characteristic research of large discharge decompressor and interior flow field the dynamic simulation " (National University of Defense Technology, 2007,11) result of study and decompressor design parameter are determined, hole count 3 ~ 6, aperture 2 ~ 6mm.Separator 8 base plate lower surface is uniformly distributed along the circumference 3 ~ 6 and goes up the circular locating openings of stabilizing springs 9, and its position, size should meet the demand of the balance keeping upper stabilizing spring 9 and diaphragm 10.

As shown in Fig. 2 A, 2B, be made up of Returnning spring 3, flap 4, valve seat 5 orifice union of the present invention.Valve seat 5 is hollow " convex " shape ring chambers, and by the less materials processing of hardness, such as brass etc., there is seal boss 53 in the flap hole 32 that the lateral layout of valve seat 5 has gas to circulate in chamber, require to polish processing, surface roughness reaches 0.1 grade.Valve seat interior surface 51 requirement on machining accuracy is high, and surface roughness should reach 0.4 ~ 0.8 grade and require high with seal boss 53 perpendicularity.Flap 4 is round cup shape cavitys, adopts the metallic material larger than valve seat 5 material hardness to make, such as stainless steel etc.Outer surface 41 is split into multiple region, and to reduce friction area when moving, surface roughness requirements reaches 0.4 ~ 0.8 grade.The bottom surface design seal boss 42 of flap 4, surface requirements polishes processing, and surface roughness reaches 0.1 grade.Seal boss 42 surface requires high with outer surface 41 perpendicularity.In chamber, Design Orientation post 44 and positioning pit 43 are for installing Returnning spring 3.Bottom surface 45 contacts with decompressor sensing mechanism, to start or to close flap 4.On flap 4, uniform flap hole 37 is to realize flap 4 internal and external pressure balance fast.Returnning spring 3 adopts spring steel to make, and performance characteristic parameter designing is carried out with reference to General valve method, and the coefficient of stiffiness gets k ₃=15 ~ 40N/mm.

Maximum opening hmax, the flap throttling diameter D of flap 4 meet following relation:

${\stackrel{\·}{m}}_g=\left\{\begin{array}{cc}{\mathrm{\μ}}_g\mathrm{\π}{\mathrm{Dh}}_{\max }{p}_{10}\sqrt{\frac{2k}{(k-1)\mathrm{RT}}({\left(\frac{p_2}{p_{10}}\right)}^{\frac{2}{k}}-{\left(\frac{p_2}{p_{10}}\right)}^{\frac{k+1}{k}})},& \frac{p_2}{p_{10}}\≤{\mathrm{\σ}}_{\mathrm{cr}};\\ {\mathrm{\μ}}_g\mathrm{\π}{\mathrm{Dh}}_{\max }{p}_{10}\sqrt{\frac{k}{\mathrm{RT}}{\left(\frac{2}{k+1}\right)}^{\frac{k+1}{k-1}}},& \frac{p_2}{p_{10}}>{\mathrm{\σ}}_{\mathrm{cr}}.\end{array}\right.---\left(1\right)$

$4\≤\frac{D}{h_{\max }}\≤20---\left(2\right)$

Wherein: for being flowed into the gas mass flow of output cavity 22 by input cavity 21, unit is kg/s; D is the internal diameter of flap 4 seal boss 42, and unit is m; μ _gfor Ventialtion rate, get μ _g=0.7 ~ 0.90, p ₁₀, p ₂for pressurized gas stagnation pressure, delivery pressure after spool, unit is Pa; K is specific heats of gases ratio, R is gas constant, and unit is J/ (kg.K), T is stagnation temperature, and unit is K; it is the critical pressure ratio of gas.Valve core diameter's scope is 30-70mm.

The quantity n of valve seat orifice 32 ₃₂and diameter d ₃₂meet following relation:

${\stackrel{\·}{m}}_g=\frac{{\mathrm{\μ}}_{32}\mathrm{\π}{p}_{10}}{400000}{\mathrm{\ρ}}_0{\mathrm{un}}_{32}{d}_{32}^2---\left(3\right)$

Wherein: μ ₃₂for the flow coefficient of valve seat orifice 32, get μ ₃₂span is 0.5 ~ 0.7, ρ ₀for gas density under standard atmospheric conditions, flow velocity during unit to be kg/m3, u be gas flows through valve seat orifice 32, gets u=20 ~ 50m/s.Valve seat orifice 32 diameter d ₃₂choose between 15-25mm, n ₃₂span be 8-16.

Flap hole 37 quantity n ₃₇and diameter d ₃₇choose in following value according to practical structures: n ₃₇span be 8-16, d ₃₇span be 2-4mm.

During decompressor general assembly, the bottom surface, location 54 of valve seat 5 coordinates with the dimple-shaped mountion plate at middle valve body 7, upper valve body 2 and valve seat 5 coaxial cooperation, and valve body 7 in simultaneously compressing downwards also plays auxiliary pressuring action to the location anchor ring 52 of valve seat 5.Valve gap 1 compresses Returnning spring 3, is fixedly mounted on upper valve body 2.According to valve universal method, realize valve seat 5 and upper valve body 2, valve seat 5 and middle valve body 7 simultaneously, seal between upper valve body 2 and middle valve body 7.

Orifice union is the executive module realizing high pressure air reducing, voltage stabilizing, is the core component of decompressor function.During decompressor work, by the relative movement between flap 4 and valve seat 5, orifice union plays the effect controlling pressurized gas and circulated by input cavity 21 to output cavity 22 or disconnect, and by the lifting aperture h of flap 4 relative to valve seat 5, decides the gas flow flowing into output cavity 22.

Sensory package comprises the parts such as push rod 6, upper stabilizing spring 9, diaphragm 10, clamping disk 11, lower stabilizing spring 12, positioning rod 13.Diaphragm 10 is one, and by rubber or metal elasticity good thin discs, edge is slightly thicker than middle part, is convenient to install and location.Clamping disk 11 is thin patty solid of rotation that metal material processing becomes, one of them bottom surface, a circumference uniform distribution 3-6 coil component spring positioning hole, and its position, size should meet the demand that location, keep-spring and diaphragm 10 balance.The oval mast that push rod 6 one end is conisphere shape, the other end is spherical, hardness is adopted to make higher than the material of flap 4, as 1Cr17Ni2 etc., cone spheric end contacts with flap 4 bottom surface, the central, circular position matching of spheric end and clamping disk 11, when length should ensure initially to install, two ends contact adjacent positioned face, not load just.Positioning rod 13 is that one end is spherical, the short cylindrical bar of a Transverse plane, and the positioning hole of spheric end and clamping disk 11 adapts, and planar ends is positioned in the circular locating openings of lower valve body 14, adopts hardness to make higher than the material of clamping disk 11.The performance characteristic parameter designing of the elastic members such as upper stabilizing spring 9, diaphragm 10 and lower stabilizing spring 12 is carried out with reference to General valve method, upper stabilizing spring 9 coefficient of stiffiness k ₉=2 ~ 6N/mm, lower stabilizing spring 12 coefficient of stiffiness k ₁₂=1.5 ~ 5N/mm, and k ₉>=k ₁₂.

Sensory package is pressure regulation signal, the running parameters such as perception decompressor pilot pressure, delivery pressure, and is communicated to the key component of orifice union.Sensory package is arranged on the inner and adjacent component of damping cavity 23, control chamber 24, its working procedure and two chamber internal states closely related.The comparative result of damping cavity 23 and control chamber 24 internal pressure, will be passed to orifice union, be controlled the working procedure of decompressor by the sensory package perception being core parts with diaphragm 10.

Diaphragm 10 is fixed to clamp by middle valve body 7 and lower valve body 14 and is arranged between damping cavity 23 and control chamber 24.Control chamber 24 controls gas for filling, and damping cavity 23 is for the post-decompression output gas of filling, and both comparison signals make decompressor normally work for driving motion of membrane.Therefore the excellent sealing between damping cavity 23 and control chamber 24 and isolation must be ensured.Except diaphragm, other parts of sensory package are all in contact condition with adjacent component, can relative movement.Clamping disk 11 is installed on diaphragm about 10 both sides respectively, to protect the structure of diaphragm 10.Push rod 6 is coaxially installed by the centre pilot hole of separator 8 and separator 8, its upper-end contact flap 4 bottom surface.The position of upper clamping disk 11, is determined by the center positioning hole on clamping disk 11, push rod 6 and separator 8 pilot hole.The position of lower clamping disk 11, is determined by the center positioning hole on the center positioning hole on clamping disk 11, positioning rod 13 and lower valve body 14.Meanwhile, install stabilizing spring 9 upper clamping disk 11 is corresponding with between separator 8, between lower clamping disk 11 with lower valve body 14 corresponding install under stabilizing spring 12, to maintain diaphragm applied force balance, keep equilibrium position.Relief valve port 36 and air outlet 33 are connected to safety valve simultaneously, to ensure output gas pressure not higher than control atmospheric pressure.

All closure size, structure all can comparator valve handbook, determine according to decompressor designing requirement.

When in control chamber 24, nothing controls gas, decompressor of the present invention is in off working state.Now, if be filled with pressurized gas in input cavity 21, gas can pass through the valve seat orifice 32 on valve seat 5, the flap hole 37 on flap 4, enters flap 4 inner, the pressure to flap 4 will be increased outside the elastic force of Returnning spring 3, make valve seat 5 and flap 4 fit tightlier, seal better.If without gas in input cavity 21, then the elastic force of Returnning spring 3 can make flap 4 be pressed on valve seat 5, avoids moving element in decompressor to be in free state.

Decompressor working procedure of the present invention comprises 3 kinds of situations.

1, pressure regulation working procedure

In input cavity 21, be filled with pressurized gas, and air outlet 33 is closed or when being connected to a closed end by pipeline, can carry out pressure regulation operation to decompressor.

Pass into control chamber 24 the control gas that pressure is pc by controlling gas import 35.Before inflation, output cavity 22, damping cavity 23 and control chamber 24 internal pressure are barometric pressure.

After inflation, first control chamber 24 pressure raises, make to produce pressure reduction between control chamber 24 and damping cavity 23, when reaching sufficiently high pressure power, clamping disk 11 and diaphragm 10 start upwards to be out of shape, to move, drive push rod 6 that flap 4 is upwards risen, form the gap of certain aperture between flap 4 and valve seat 5, input cavity 21 is communicated with output cavity 22.Pressurized gas are inflated to output cavity 22 by input cavity 21, and the pressure in input cavity 21 starts to raise, and gas is begun through air outlet 33 and outwards flows out, inflated to damping cavity 23 by damping hole 37.

Because air outlet 33 is closed, lasting inflation makes output cavity 22 pressure durations raise, damping cavity 23 pressure p z also increases, now clamping disk 11 and diaphragm 10 are subject to increasing downward active force, when pz reaches certain value, clamping disk 11 and diaphragm 10 start to move downward, resile, and flap 4 is return under the elastic force effect of Returnning spring 3, put until set back completely, input cavity 21 and output cavity 22 respacing.Output cavity 22 and damping cavity 23 pressure reach stable, and balance with control chamber 24 internal pressure, and pressure regulation process terminates.

Visible, the effect of pressure regulation process makes to be full of the low-pressure gas balanced each other with control chamber 24 internal pressure in output cavity 22.

2, air feed working procedure

In input cavity 21, be filled with pressurized gas, and when completing decompressor pressure regulation process, air supplying operation can be carried out by decompressor.

Open the downstream pipe valve be connected with air outlet 33, in output cavity 22, gas suddenly outwardly, pressure declines suddenly, damping cavity 23 pressure declines thereupon, the stress balance of sensory package is destroyed, and is subject to power upwards, flap 4 lifting, aperture between formation and valve seat 5, input cavity 21 pressurized gas flow into output cavity, and output cavity 22 and damping cavity 22 pressure are gone up.

Along with output cavity 22 pressure recover increases, flap 4 will move downward and return along with sensory package, and the flow flowing into output cavity 22 reduces, and output cavity 22, damping cavity 23 pressure reduce, and flap 4 seating velocity slows down.When on sensory package during stress balance, flap 4 will be stabilized in a fixing aperture, now by decompressor will to downstream gas without interruption.Due to inertia and hesitation, before flap 4 is really stabilized in an aperture, can first repeatedly vibrate repeatedly at equilibrium position place, correspondingly, output cavity 22 pressure, damping cavity 23 pressure, sensory package position etc., also have fuctuation within a narrow range.

So far, decompressor achieves decompression, voltage stabilizing and the function continued to the required pressed gas of downstream supply.

When downstream valve closing, because input cavity 21 is to output cavity 22 aeration, output cavity 22 pressure can increase, thus makes sensory package, flap 4 etc. start restorative return, and final flap 4 is adjacent to completely, seals with valve seat 5, decompressor end-of-job.

3, pressure leak process

After decompressor end-of-job, by the emptying control chamber internal pressure of pressure relief opening 35, its pressure is made to reduce to barometric pressure.Now, due to output cavity, the effect of damping cavity internal pressure, sensory package moves down.Safety valve now starts, and output cavity internal pressure is emptying by safety valve.

Claims (9)

1. a Pneumatic-control type decompressor, is characterized in that: comprise input cavity (21), output cavity (22), damping cavity (23) and control chamber (24), orifice union, sensory package, upper valve body (2), middle valve body (7) and lower valve body (14), separator (8);

Described input cavity (21) be one by upper valve body (2), be arranged in bottom surface, chamber valve body (7) and be positioned at the ring-shaped chamber that mesotropic orifice union surrounds;

Described output cavity (22) is a ring-shaped chamber surrounded by middle valve body (7), the separator (8) being positioned at bottom surface, chamber and the orifice union that is positioned at chamber upper base;

Described damping cavity (23) and control chamber (24) by middle valve body (7), lower valve body (14) and separator (8) around forming;

Described control chamber (24) controls gas for filling, and damping cavity (23) is for the post-decompression output gas of filling;

Described orifice union is used for the decompression of pressurized gas and voltage stabilizing and Isolation input chamber (21) and output cavity (22);

Described sensory package is sent to orifice union after being used for perception decompressor pressure regulation signal and running parameter, and isolates damping cavity (23) and control chamber (24).

2. a kind of Pneumatic-control type decompressor as claimed in claim 1, is characterized in that: the cylindrical body that described upper valve body (2) is middle part perforate, and the annular chamber in inside machined " M " type cross section, the suction port processed with side (31) is communicated with.

3. a kind of Pneumatic-control type decompressor as claimed in claim 2, is characterized in that: described middle valve body (7) machined the cylindrical body of the annular chamber in " convex " type cross section for inside, be communicated with lateral flow orifices (33).

4. a kind of Pneumatic-control type decompressor as claimed in claim 3, it is characterized in that: described lower valve body (14) is the solid of rotation of inner processing shallow " recessed " type cylindrical cavity, central authorities processing a circular locating openings, sidewall machining control gas port (35) and relief valve port (36).

5. a kind of Pneumatic-control type decompressor as claimed in claim 4, it is characterized in that: " convex " shape solid of rotation that described separator (8) is middle part perforate, being welding as one by bottom edge and middle valve body (7), is upper " convex " die cavity and lower thin cylindrical cavity two-part by " convex " cavity spacer of middle valve body (7); Separator (8) base plate is processed damping hole (34), realize the exchange of gas between output cavity (22) and damping cavity (23).

6. a kind of Pneumatic-control type decompressor as described in one of claim 1-4, is characterized in that: described orifice union comprises Returnning spring (3), flap (4), valve seat (5); Valve seat (5) is hollow " convex " shape ring chamber, has seal boss (53), the flap hole (32) that valve seat lateral layout has gas to circulate in chamber; Flap (4) is a round cup shape cavity, flap bottom surface (45) designing seal boss (42), having locating column (44) and positioning pit (43) in chamber for installing Returnning spring (3); Bottom surface (45) contacts with sensory package, and to start or to close flap (4), the upper uniform flap hole (37) of flap (4) is to realize flap (4) internal and external pressure balance fast.

7. a kind of Pneumatic-control type decompressor as claimed in claim 6, is characterized in that: described sensory package comprises push rod (6), upper stabilizing spring (9), diaphragm (10), two clamping disks (11), lower stabilizing spring (12), positioning rod (13); Diaphragm (10) is edge's thin discs slightly thicker than middle part, damping cavity (23) and control chamber (24) isolation are formed upper and lower two adjacent pancake cylinder cavity volumes, and upper and lower surface installs the solid of rotation clamping disk (11) of thin patty respectively; The oval mast that push rod (6) is one end conisphere shape, the other end is spherical, cone spheric end contacts with flap (4) bottom surface, the central, circular position matching of spheric end and clamping disk (11); Positioning rod (13) is the short cylindrical bar that one end is spherical, one end is plane, the positioning hole of spheric end and clamping disk (11) adapts, planar ends is arranged in the circular locating openings of lower valve body (14), and push rod (6) is coaxially installed by the centre pilot hole of separator (8) and separator (8).

8. a kind of Pneumatic-control type decompressor as claimed in claim 7, is characterized in that: described orifice union should meet,

1), the maximum opening hmax of flap (4), flap throttling diameter D need meet following relationship,

${\stackrel{\·}{m}}_g=\left\{\begin{array}{cc}{\mathrm{\μ}}_g\mathrm{\πD}{h}_{\max }{p}_{10}\sqrt{\frac{2k}{(k-1)\mathrm{RT}}({\left(\frac{p_2}{p_{10}}\right)}^{\frac{2}{k}}-{\left(\frac{p_2}{p_{10}}\right)}^{\frac{k+1}{k}})},& \frac{p_2}{p_{10}}\≤{\mathrm{\σ}}_{\mathrm{cr}};\\ {\mathrm{\μ}}_g\mathrm{\πD}{h}_{\max }{p}_{10}\sqrt{\frac{k}{\mathrm{RT}}{\left(\frac{2}{k+1}\right)}^{\frac{k+1}{k-1}}},& \frac{p_2}{p_{10}}>{\mathrm{\σ}}_{\mathrm{cr}}.\end{array}\right.---\left(1\right)$

$4\≤\frac{D}{h_{\max }}\≤20---\left(2\right)$

2) the quantity n of valve seat orifice (32) ₃₂and diameter d ₃₂following relation need be met:

${\stackrel{\·}{m}}_g=\frac{{\mathrm{\μ}}_{32}\mathrm{\π}{p}_{10}}{400000}{\mathrm{\ρ}}_0{\mathrm{un}}_{32}{d}_{32}^2---\left(3\right)$

Wherein: for being flowed into the gas mass flow of output cavity (22) by input cavity (21), unit is kg/s; D is the internal diameter of flap (4) seal boss (42), and unit is m; μ _gfor Ventialtion rate, get μ _g=0.5 ~ 0.70, p ₁₀, p ₂for input cavity (21) stagnation pressure, output cavity (22) pressure, unit is Pa; K is specific heats of gases ratio, R is gas constant, and unit is J/ (kg.K); T is stagnation temperature, and unit is K; it is the critical pressure ratio of gas; μ ₃₂for the flow coefficient of valve seat orifice (32); ρ ₀for gas density under standard atmospheric conditions, unit is kg/m ³; U is gas flow velocity when flowing through valve seat orifice (32), and unit is m/s.

9. a kind of Pneumatic-control type decompressor as claimed in claim 8, is characterized in that: described inlet hole (31) and exit orifice (33) adopt one or more groups; When one group, inlet hole (31) and exit orifice (33) present 180 degree of layouts; When organizing, uniform layout on the whole, often organizes inlet hole, exit orifice by 180 degree of layouts more.