CN100445916C - Pressure pneumatic control valve following difference of constant pressure - Google Patents
Pressure pneumatic control valve following difference of constant pressure Download PDFInfo
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- CN100445916C CN100445916C CNB2006101556689A CN200610155668A CN100445916C CN 100445916 C CN100445916 C CN 100445916C CN B2006101556689 A CNB2006101556689 A CN B2006101556689A CN 200610155668 A CN200610155668 A CN 200610155668A CN 100445916 C CN100445916 C CN 100445916C
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Abstract
A pneumatic control valve of fixed pressure-difference and flow-up pressure type is prepared for supplying high pressure air source to entrance of master air supply valve by pneumatic pressure release valve in depressurized way, supplying air to air cavity through throttle of master air supply valve and liquid-controlled air supply check valve for making air cavity be pressurized, exhausting air to ambient by air cavity through liquid-controlled air exhaust valve and master air exhaust valve as well as silencer for making air cavity be depressurized.
Description
Technical field
The present invention relates to the pneumatic control valve of pressure vessel, especially relate to a kind of pressure pneumatic control valve following difference of constant pressure.
Background technology
In the pressure control field of pressure vessel, pressure regulation system commonly used generally adopts pressure electricity feedback, provides signal to air feed electromagnetic switch valve group and exhaust electromagnetic switch valve group through control system, follows the purpose of pressure in the hope of reaching the control cavity volume.The pressure control overshoot that switch control brings is big, precision is low, and cavity volume air pressure is prone to vibration, and poor stability has more increased compressed-air actuated use amount and the air capacity in environment.The other deficiency of automatically controlled pressure regulation system is low, the poor anti jamming capability of functional reliability, and the occasion higher at some reliability requirements is restricted.It is to improve gas cavity volume level pressure difference control ability that fully mechanical Pneumatic pressure with degree of precision, stepless control is followed operation valve, breaks through the various circumscribed inventions of automatically controlled by-pass cock valve group.
Summary of the invention
The object of the present invention is to provide a kind of pressure pneumatic control valve following difference of constant pressure.The level pressure differential pressure that relates to a constant volume gas container or cavity is followed control, by the pneumatic control valve regulation, the pressure of the pressure follow peripheral hardware pressure source of cavity volume is changed, and keeps the pressure reduction of setting constant.Pneumatic control valve of the present invention is general pressure follow control element, can be used for the application scenario of all gases container, chamber pressure adjusting.
The technical solution adopted for the present invention to solve the technical problems is:
Comprise that pressure reduction amplifies pilot stage, air feed main valve, exhaust main valve, hydraulic control air feed stop valve, hydraulic control discharge line valve, reduction valve, safety valve, pneumatic safety valve and pneumatic pressure-release valve; Pressure reduction amplifies pilot stage and connects the peripheral hardware pressure source, the gas cavity volume, fuel tank, the reduction valve outlet, hydraulic control air feed stop valve, the hydraulic control discharge line valve, the sensitive cavity of air feed main valve and exhaust main valve, the oil pressure chamber of air feed main valve and exhaust main valve all is connected with the reduction valve outlet, the entrance and exit of air feed main valve connects pneumatic pressure-release valve outlet and hydraulic control air feed stop valve inlet respectively, the entrance and exit of exhaust main valve connects outlet of hydraulic control discharge line valve and exhaust box respectively, the outlet of hydraulic control air feed stop valve all is connected with the gas cavity volume with the inlet of hydraulic control discharge line valve, the guide of hydraulic control air feed stop valve and hydraulic control discharge line valve controls oil and draws from reduction valve and export, the entrance and exit of pneumatic safety valve connects gas cavity volume and exhaust box respectively, the entrance and exit of pneumatic pressure-release valve connects the inlet of high-pressure air source and air feed main valve respectively, the inlet of reduction valve and safety valve all is connected the control oil sources, the outlet of safety valve, the reduction valve drain tap, guide's oil drain out of hydraulic control air feed stop valve and hydraulic control discharge line valve all is connected with fuel tank.
Described pressure reduction amplifies pilot stage: comprise pressure reduction-force transducer, lever, be connected with the pressure amplification of forming by pressure amplifier stage guiding valve, the resistance of first liquid, the resistance of second liquid, press the chamber to be connected in pressure reduction-force transducer with the gas cavity volume, pressure reduction-force transducer piston rod withstands lever remote branch of a clan point place, and pressure amplifier stage valve core of the spool valve one end of the pressure amplifier stage guiding valve amplifier stage guiding valve that withstands pressure is adjusted a wage scale; Pressure reduction-force transducer is a two rod hydraulic cylinder, pressure reduction-force transducer external pressure chamber and peripheral hardware pressure source joint spring, the leading-off rods of the other end withstands the nearly fulcrum of lever place, open rectangular channel on the pressure amplifier stage valve core of the spool valve, two variable valve ports of pressure amplifier stage guiding valve connect an end of first and second liquid resistance respectively, draw air feed fluid control pressure and exhaust fluid control pressure respectively between valve port and the liquid resistance, oil pressure source is the reduction valve outlet, is connected with the other end and the pressure amplifier stage slide valve spring chamber of the resistance of first and second liquid.
Described air feed main valve and exhaust main valve: oil pressure source is connected air feed main valve oil pressure chamber and exhaust main valve oil pressure chamber, the air feed valve core of main valve is stepped, open triangular groove, big end connects air feed main valve regulating spring, small end connects air feed main valve returning spring, the air feed main valve sensitive cavity at air feed main valve regulating spring place is introduced the air feed fluid control pressure, and throttle orifice connects the outlet of pneumatic pressure-release valve, and air feed main valve air cavity connects the inlet of hydraulic control air feed stop valve; The exhaust valve core of main valve is opened rectangular channel, two ends connect exhaust main valve regulating spring and exhaust main valve returning spring respectively, the exhaust main valve sensitive cavity at exhaust main valve regulating spring place is introduced the exhaust fluid control pressure, and throttle orifice connects the outlet of hydraulic control discharge line valve, and exhaust main valve air cavity connects exhaust box; For the exhaust main valve work dead band is set all, and can by adjust air feed main valve regulating spring, exhaust main valve regulating spring is regulated, air feed valve core of main valve, exhaust valve core of main valve clearance seal respectively and between the valve pocket of air feed main valve, exhaust main valve.
Described hydraulic control air feed stop valve, the hydraulic control discharge line valve: hydraulic control air feed stop valve comprises hydraulic control air feed stop valve pilot stage valve core of the spool valve, hydraulic control air feed stop valve pilot stage regulating spring, the drain resistance of hydraulic control air feed stop valve elder generation, hydraulic control air feed stop valve main valve plug, hydraulic control air feed stop valve main valve returning spring; The hydraulic control discharge line valve comprises hydraulic control discharge line valve pilot stage valve core of the spool valve, hydraulic control discharge line valve pilot stage regulating spring, the drain resistance of hydraulic control discharge line valve elder generation, hydraulic control discharge line valve main valve plug, hydraulic control discharge line valve main valve returning spring; Oil pressure source connects the pilot stage throttle orifice and the hydraulic control air feed stop valve main valve sensitive cavity of hydraulic control air feed stop valve by the drain resistance of hydraulic control air feed stop valve elder generation, and the drain resistance of hydraulic control air feed stop valve elder generation is formed Type B hydraulic pressure half-bridge with the pilot stage of hydraulic control air feed stop valve; Oil pressure source connects the pilot stage throttle orifice and the hydraulic control discharge line valve main valve sensitive cavity of hydraulic control discharge line valve by the drain resistance of hydraulic control discharge line valve elder generation, and the drain resistance of hydraulic control discharge line valve elder generation is also formed Type B hydraulic pressure half-bridge with the pilot stage of hydraulic control discharge line valve; Hydraulic control air feed stop valve pilot stage guiding valve low-pressure cavity all is connected with fuel tank with spring cavity with spring cavity, hydraulic control discharge line valve pilot stage guiding valve low-pressure cavity, hydraulic control air feed stop valve pilot stage guiding valve sensitive cavity is introduced the air feed fluid control pressure, and hydraulic control discharge line valve pilot stage guiding valve sensitive cavity is introduced the exhaust fluid control pressure; Hydraulic control air feed stop valve pilot stage valve core of the spool valve withstands hydraulic control air feed stop valve pilot stage regulating spring, hydraulic control air feed stop valve main valve plug withstands hydraulic control air feed stop valve main valve returning spring and is pressed on the main valve valve seat of hydraulic control air feed stop valve, hydraulic control air feed stop valve main valve import air cavity is connected the outlet and the gas cavity volume of air feed main valve respectively with the outlet air cavity, hydraulic control discharge line valve pilot stage valve core of the spool valve withstands hydraulic control discharge line valve pilot stage regulating spring, hydraulic control discharge line valve main valve plug withstands hydraulic control discharge line valve main valve returning spring and is pressed on the main valve valve seat of hydraulic control discharge line valve, and hydraulic control discharge line valve main valve import air cavity is connected the inlet of gas cavity volume and exhaust main valve respectively with the outlet air cavity.
Pressure pneumatic control valve following difference of constant pressure of the present invention is used full hydraulic control principle and is improved functional reliability, stability and antijamming capability, comprises that pressure reduction amplifies pilot stage, air feed main valve, exhaust main valve, hydraulic control by air valve, reduction valve, safety valve etc.Pressure reduction amplifies pilot stage pressure reduction conversion between peripheral hardware pressure source and the gas cavity volume is enlarged into certain pressure, drives the open and close for the exhaust main valve.The size of the corresponding pressure reduction departure of the aperture of main valve valve port, and certain dead band is set, oscillation-damped and improve antijamming capability reduces pressurized air use amount and air capacity, can realize that accurate level pressure difference controls automatically.
Pneumatic control valve of the present invention directly is converted to the pressure reduction between peripheral hardware pressure source and the gas cavity volume power output by pressure reduction-force transducer that pressure reduction amplifies pilot stage, amplify through lever, the valve core of the spool valve that promotes the pressure amplifier stage moves, and the displacement size is relevant with the pressure reduction departure.When pressure reduction bias free or departure were very little, valve core of the spool valve was in meta, and valve port is closed.This guiding valve has two control limits, is equivalent to two variable liquid resistances, forms for, exhaust gas drive Type B half-bridge with two immobile liquids resistances respectively.The corresponding guiding valve air feed of pressure reduction overgauge drives the throttle orifice aperture, and deviation is big more, and valve port opening is big more, and air feed drives the half-bridge output pressure and reduces many more.The corresponding guiding valve exhaust gas drive of pressure reduction minus deviation throttle orifice aperture, same deviation is big more, and exhaust gas drive half-bridge output pressure reduces also many more.For the displacement of exhaust gas drive pressure control main valve valve core of the spool valve, and then control valve port opening and supply exhaust throttle flow resistance size.The pressure reduction departure for exhaust main valve valve port opening by hydraulic control driving pressure correspondence, promptly increase along with the increase of pressure reduction departure for extraction flow, and corresponding dead band is set, the dead band size can be preset by changing for the initial tension of spring of exhaust main valve.For reducing friction, reduce hysteresis and improve the linearity, adopt clearance seal between the spool of main valve guiding valve and the valve pocket, use for exhaust and prevent the leakage that dead zone range is interior by operation valve.Be connected with the gas cavity volume by operation valve for exhaust, respectively in outlet of air feed main valve and exhaust main valve porch, its fluid control pressure can provide by amplifying bridge circuit for exhaust gas drive pressure, and also can amplify pilot stage by the pressure reduction positive feedback provides.Amplifying bridge circuit for exhaust gas drive pressure forms by the immobile liquid resistance with for exhaust gas drive pressure signal amplifier stage.The driving pressure amplified signal level is corresponding sets the dead band for exhaust gas drive pressure, opens valve port when promptly the pressure reduction departure surpasses dead zone range.This amplifier stage has bigger area of passage gradient, and the immobile liquid resistance is also bigger, and the output pressure of the Type B half-bridge of Zu Chenging can reduce rapidly at the critical value place that surpasses dead zone range thus, plays the effect of high-speed switch control.Pilot stage and pressure reduction are amplified in the pressure reduction positive feedback, and to amplify pilot stage similar, and difference is that valve core of the spool valve two ends sensitive cavity introduced confession exhaust gas drive pressure.The air feed driving pressure is introduced left chamber, and exhaust gas drive pressure is introduced right chamber.When pressure reduction positively biased residual quantity surpasses dead zone range, spool moves to left and enters right position, and when the air feed driving pressure reduced, because the spool that reduces of left cavity pressure continues to move to left, valve port was opened rapidly greatly, after be subjected to the spring force balance.When the positively biased residual quantity reduced to get back to dead zone range, the spool aperture that moves to right reduced, and the air feed driving pressure increases and continues to promote spool and move to right, and gets back to meta up to close port.Action situation when pressure reduction generation negative bias residual quantity enters the reduction of position, left side generation exhaust gas drive pressure is identical with position, the right side.
When peripheral hardware pressure source pressure change or gas cavity volume pressure since duty change when causing fluctuation, if the pressure reduction departure surpasses the dead zone range of setting, then the pilot stage of operation valve is regulated for the exhaust main valve and is produced corresponding air feed or exhaust action, adjust gas container or cavity internal pressure, pressure reduction is come back in the safe range dead band of setting.Hydraulic control ends the skew that air valve prevents dead zone range interior internal leakage causing cavity volume air pressure, and reduction valve, safety valve play a part auxiliary.
The beneficial effect that the present invention has is:
(1) is different from by electric feedback transducer detected pressures, pressure reduction, the electric-control system for exhaust electromagnetic switch valve group is handled and operated to control module, pressure pneumatic control valve following difference of constant pressure of the present invention is used full hydraulic control principle, work under the full machine performance, improve control accuracy, functional reliability, stability and the antijamming capability of valve, reduced compressed-air actuated use amount and the air capacity in environment.
(2) use pressure reduction to amplify pilot stage, the pressure reduction between cavity volume air pressure and the peripheral hardware pressure directly is converted to pressure after the amplification, drive confession exhaust main valve, overcome the difficulty that the small pressure difference departure is not enough to drive big flow throttling main valve.The pressure of the gain amplifier of pressure reduction departure and stable hydraulic oil sources is relevant with the gain of the Type B half-bridge of pressure amplifier stage, and amplifying power is strong, and the degree of accuracy height is regulated flexibly.
(3) for the displacement of exhaust gas drive pressure control main valve valve core of the spool valve, and then the control valve port opening, exhaust throttle flow resistance size promptly supplied.Increase along with the increase of pressure reduction departure for extraction flow, effectively raise the precision and the stability of pressure follow control.Corresponding pressure reduction departure can be provided with certain confession exhaust dead band, the dead band size can be set flexibly by changing for the initial tension of spring of exhaust main valve, eliminate the pressure oscillation of following in the control procedure, reduced compressed-air actuated use amount and the air capacity in environment.
(4) the pressure chamber both sides bearing area that links to each other with the gas cavity volume of air feed main valve guiding valve does not wait, valve port opening is increased with the pressure of gas cavity volume, weakened of the influence of gas cavity volume pressure to the air feed volumetric flow rate, make the air feed volumetric flow rate basic only relevant, and do not change fluctuation and the deviation that produces greatly with gas cavity volume pressure with the pressure reduction departure.
(5) clearance seal between confession, exhaust main valve valve core of the spool valve and the valve pocket for pneumatic relatively poor lubricating ability, has reduced friction force greatly, has reduced the flow hysteresis and has improved the linearity.
(6) application by operation valve, prevents the skew of dead zone range interior internal leakage causing gas container or chamber pressure for exhaust.The controlled pressure of fluid-controlled cut-off valve can provide by amplifying bridge circuit for exhaust gas drive pressure, also can amplify pilot stage by the pressure reduction positive feedback provides, stop valve is opened rapidly when the pressure reduction departure exceeds the dead zone range critical value, got back to the dead band critical value in departure and close rapidly when following.
(7) the pressure follow operation valve of all-hydraulic control is integrated in the various functions of original automatically controlled regulating system on the one deck valve group, has reduced system cost, compact conformation, and taking up room reduces greatly.
Pneumatic control valve of the present invention is general pressure follow control element, can be used for the application scenario of all gases container, chamber pressure adjusting.
Description of drawings
Fig. 1 is the circuit theory figure of pressure pneumatic control valve following difference of constant pressure of the present invention;
Fig. 2 amplifies the work circuit theory figure of pilot stage for the pressure reduction of pneumatic control valve of the present invention;
Fig. 3 is the work circuit theory figure for the exhaust main valve of the present invention;
Fig. 4 is the work circuit theory figure of fluid-controlled cut-off valve of the present invention.
Among the figure: A. pressure reduction amplifies pilot stage, 1. pressure reduction-force transducer, 1-1. pressure reduction-force transducer piston rod, 1-A. pressure reduction-force transducer external pressure chamber, 1-B. press the chamber in pressure reduction-force transducer, 2. regulations and parameters, 3. pressure amplifier stage guiding valve, 3-1. pressure amplifier stage valve core of the spool valve, 3-2. pressure amplifier stage guiding valve regulating spring, 3-A. pressure amplifier stage slide valve spring chamber, 4. first liquid resistance, 5. second liquid resistance, 6. air feed main valve, 6-1. air feed main valve regulating spring, 6-2. air feed valve core of main valve, 6-3. air feed main valve returning spring, 6-A. air feed main valve sensitive cavity, 6-B. air feed main valve air cavity, 6-C. air feed main valve oil pressure chamber, 7. exhaust main valve, 7-1. exhaust main valve regulating spring, 7-2. exhaust valve core of main valve, 7-3. exhaust main valve returning spring, 7-A. exhaust main valve sensitive cavity, 7-B. exhaust main valve air cavity, 7-C. exhaust main valve oil pressure chamber, 8. hydraulic control air feed stop valve, 8-1. hydraulic control air feed stop valve pilot stage valve core of the spool valve, 8-2. hydraulic control air feed stop valve pilot stage regulating spring, 8-3. hydraulic control air feed stop valve elder generation drain resistance, 8-4. hydraulic control air feed stop valve main valve plug, 8-5. hydraulic control air feed stop valve main valve returning spring, 8-A. hydraulic control air feed stop valve pilot stage guiding valve sensitive cavity, 8-B. hydraulic control air feed stop valve pilot stage guiding valve low-pressure cavity, 8-C. hydraulic control air feed stop valve pilot stage slide valve spring chamber, 8-D. hydraulic control air feed stop valve main valve sensitive cavity, 8-E. hydraulic control air feed stop valve main valve import air cavity, 8-F. hydraulic control air feed stop valve main valve outlet air cavity, 9. hydraulic control discharge line valve, 9-1. hydraulic control discharge line valve pilot stage valve core of the spool valve, 9-2. hydraulic control discharge line valve pilot stage regulating spring, 9-3. hydraulic control discharge line valve elder generation drain resistance, 9-4. hydraulic control discharge line valve main valve plug, 9-5. hydraulic control discharge line valve main valve returning spring, 9-A. hydraulic control discharge line valve pilot stage guiding valve sensitive cavity, 9-B. hydraulic control discharge line valve pilot stage guiding valve low-pressure cavity, 9-C. hydraulic control discharge line valve pilot stage slide valve spring chamber, 9-D. hydraulic control discharge line valve main valve sensitive cavity, 9-E. hydraulic control discharge line valve main valve import air cavity, 9-F. hydraulic control discharge line valve main valve outlet air cavity, 10. pneumatic safety valve, 11. pneumatic pressure-release valves, 12. reduction valve, 13. safety valve, 14. the control oil sources, 15. fuel tanks, 16. high-pressure air source, 17. peripheral hardware pressure source, 18. the gas cavity volume, 19. exhaust boxs, 20. air feed fluid control pressures, 21. the exhaust fluid control pressure, 22. oil pressure source.
Embodiment
With reference to Fig. 1, pressure pneumatic control valve following difference of constant pressure of the present invention comprises that the pressure reduction of being made up of pressure reduction-force transducer 1, lever 2, pressure amplifier stage guiding valve 3, first liquid resistance, 4 and second liquid resistance 5 amplifies pilot stage A, air feed main valve 6, exhaust main valve 7, hydraulic control air feed stop valve 8, hydraulic control discharge line valve 9, reduction valve 12, safety valve 13, pneumatic safety valve 10, pneumatic pressure-release valve 11.This pneumatic control valve amplifies pilot stage A by pressure reduction the little departure of pressure reduction between peripheral hardware pressure source 17 and the gas cavity volume 18 is enlarged into bigger fluid control pressure, the corresponding air feed fluid control pressure 20 of positively biased residual quantity, the corresponding exhaust fluid control pressure 21 of negative bias residual quantity is introduced air feed main valve and exhaust main valve sensitive cavity 6-A, 7-A respectively.When the pressure of variation of peripheral hardware pressure source 17 pressure or gas cavity volume 18 causes fluctuation owing to duty changes, if the pressure reduction departure surpasses the dead zone range of setting for exhaust main valve regulating spring 6-1,7-1, pressure reduction amplify pilot stage A output for exhaust fluid control pressure 20 and 21 respectively control produce accordingly to gas cavity volume 18 air feed or through the action of exhaust box 19 exhausts for exhaust main valve 6 and 7, adjust the pressure of gas cavity volume 18, the pressure reduction between peripheral hardware pressure source 17 and the gas cavity volume 18 is come back in the safe range of setting.The air feed source of the gas of pressure pneumatic control valve following difference of constant pressure is a high-pressure air source 16, after pneumatic pressure-release valve 11 decompression with certain pressure, by hydraulic control air feed stop valve 8, air feed main valve 6 to gas cavity volume 18 air feed.Control oil sources 14 provides the hydraulic control oil pressure through reduction valve 12 to this pneumatic control valve, and control oil is last, and all oil return is to fuel tank 15, and safety valve 13 is used to protect the hydraulic control oil circuit.
With reference to Fig. 2, the principle of work that the pressure reduction of pressure pneumatic control valve following difference of constant pressure of the present invention amplifies pilot stage A is: pressure reduction-force transducer 1 is equivalent to a two rod hydraulic cylinder, the peripheral hardware pressure source 17 and the pressure of gas cavity volume 18 introduced respectively press chamber 1-B in pressure reduction-force transducer external pressure chamber 1-A and the pressure reduction-force transducer and act on pressure reduction-force transducer piston rod 1-1, output corresponding the power of pressure reduction between peripheral hardware pressure source 17 and gas cavity volume 18 pressure, and by lever 2 amplifications.The pressure amplifier stage is made up of pressure amplifier stage guiding valve 3, first liquid resistance 4 and second liquid resistance 5, the power of lever 2 outputs is converted into compares the much bigger confession exhaust fluid control pressure 20 and 21 of pressure reduction departure.Pressure amplifier stage guiding valve 3 is equivalent to the 3-position-3-way valve, has two control limits, forms two Type B half-bridges with first liquid resistance, 4 and second liquid resistance 5 respectively.The big I of first liquid resistance, 4 and second liquid resistance 5 is by the initialization adjustment.When the pressure reduction between peripheral hardware pressure source 17 and gas cavity volume 18 pressure increased, when promptly setting pressure reduction relatively and having the positively biased residual quantity, the power output of lever 2 increased, and promoted pressure amplifier stage valve core of the spool valve 3-1 compression pressure amplifier stage guiding valve regulating spring 3-2.Drive the rectangle throttling channel on the pressure amplifier stage valve core of the spool valve 3-1, and throttle orifice is plus lap, sets certain dead band thus.Pressure reduction positively biased residual quantity increases to a certain degree, pressure amplifier stage guiding valve 3 is opened with first liquid resistance, 4 throttle orifices that link to each other, and according to hydraulic pressure half-bridge principle, air feed fluid control pressure 20 reduces, decrease is relevant with valve port opening, and air feed fluid control pressure 20 is used to control air feed main valve 6.Equally, when the pressure reduction between peripheral hardware pressure source 17 and the gas cavity volume 18 reduces, lever 2 power outputs reduce, and pressure amplifier stage valve core of the spool valve 3-1 moves right under oil pressure source 22 pressure that cause pressure amplifier stage slide valve spring chamber 3-A and pressure amplifier stage guiding valve regulating spring 3-2 effect.Pressure reduction is reduced to a certain degree, and pressure amplifier stage guiding valve 3 is opened with second liquid resistance, 5 throttle orifices that link to each other, and exhaust fluid control pressure 21 reduces, and decrease is same relevant with valve port opening, and exhaust fluid control pressure 21 is used to control exhaust main valve 7.So, the positive and negative deviation amount for exhaust fluid control pressure 20 and the corresponding pressure reduction of 21 difference of pressure amplifier stage output, and because the driving pressure size can be set by oil pressure source 22, suitably the pressure of big oil pressure source 22 can make the enough big gain that has the relative pressure departure for exhaust fluid control pressure 20,21.Like this, amplify pilot stage A by pressure reduction, with the pressure reduction between gas cavity volume 18 and the peripheral hardware pressure source 17 directly be converted to after the amplification for exhaust fluid control pressure 20,21, control is for exhaust main valve 6,7, overcome the difficulty that the small pressure difference departure is not enough to drive the pneumatic main valve of big flow throttling.The gain amplifier of pressure reduction departure can be by the pressure of oil pressure source 22 and the gain setting of pressure amplifier stage Type B half-bridge, and amplifying power is strong, and the degree of accuracy height is regulated flexible.
With reference to Fig. 3, air feed fluid control pressure 20 and exhaust fluid control pressure 21 that pressure reduction amplifies pilot stage A cause respectively for exhaust main valve sensitive cavity 6-A and 7-A, and control is for the keying and the aperture size of exhaust main valve 6,7.Introduce oil pressure source 22 pressure respectively for exhaust main valve oil pressure chamber 6-C, 7-C, balance each other with supplying exhaust fluid control pressure 20,21 and spring force.Air feed main valve air cavity 6-B both sides bearing area does not wait, the valve port opening that makes air feed main valve 6 increases with the pressure of gas cavity volume 18, can weaken of the influence of gas cavity volume 18 pressure like this to the air feed volumetric flow rate, make the air feed volumetric flow rate approximate only relevant, and do not change fluctuation and the deviation that produces greatly with gas cavity volume 18 pressure with the pressure reduction departure.Open triangular groove on the air feed valve core of main valve 6-2, the area of passage of corresponding little aperture is littler, has further weakened the influence that gas cavity volume 18 pressure change, and then opens rectangular channel on the exhaust valve core of main valve 7-2.When the pressure reduction of peripheral hardware pressure source 17 and gas cavity volume 18 is in setting value, supply the initial value of exhaust fluid control pressure 20 and 21 to equal oil pressure source 22 pressure.Air feed valve core of main valve 6-2 is balance under the oil pressure source 22 pressure effects of gas cavity volume 18 pressure of the air feed fluid control pressure 20 of the spring force of air feed main valve regulating spring 6-1, air feed main valve returning spring 6-3, air feed main valve sensitive cavity 6-A, air feed main valve air cavity 6-B, air feed main valve oil pressure chamber 6-C, exhaust valve core of main valve 7-2 is balance under the oil pressure source 22 pressure effects of the exhaust fluid control pressure 21 of the spring force of exhaust main valve regulating spring 7-1, exhaust main valve returning spring 7-3, exhaust main valve sensitive cavity 7-A, exhaust main valve oil pressure chamber 7-C, and valve port is plus lap.Size for exhaust main valve 6,7 valve port covering amounts promptly supplies exhaust throttle dead band size, can set by the pretightning force of air feed main valve regulating spring 6-1 and exhaust main valve regulating spring 7-1.For the setting in the dead band of exhaust main valve 6,7, can effectively eliminate the pressure oscillation of following in the control procedure, reduce high-pressure air source 16 compressed-air actuated use amounts and through the air capacity of exhaust box 19 in environment.When the pressure reduction of peripheral hardware pressure source 17 and gas cavity volume 18 increases and positively biased residual quantity when surpassing pressure reduction and amplifying pilot stage A dead band, exhaust fluid control pressure 21 is constant, and air feed fluid control pressure 20 reduces, and decrease is corresponding with the positively biased residual quantity.At this moment, exhaust main valve 7 is failure to actuate, and air feed valve core of main valve 6-2 is owing to move on the reducing of air feed fluid control pressure 20.If pressure reduction positively biased residual quantity increases to above air feed main valve 6 dead zone ranges, valve port is opened, the size of the aperture of air feed main valve 6 and air feed fluid control pressure 20, and promptly pressure reduction positively biased residual quantity size is corresponding.When pressure reduction reduces and negative bias residual quantity when surpassing pressure reduction and amplifying pilot stage A dead band, air feed fluid control pressure 20 is constant, and exhaust fluid control pressure 21 reduces, and decrease is corresponding with the negative bias residual quantity.At this moment, air feed main valve 6 is failure to actuate, and exhaust valve core of main valve 7-2 is owing to move on the reducing of exhaust fluid control pressure 21.If pressure reduction negative bias residual quantity increases to above exhaust main valve 7 dead zone ranges, valve port is opened, the size of the aperture of exhaust main valve 7 and exhaust fluid control pressure 21, and promptly pressure reduction negative bias residual quantity size is corresponding.Thus, for changing that exhaust main valve 6,7 is regulated, effectively raise the precision and the stability of pressure follow control for the variation of extraction flow with pressure reduction positive and negative deviation amount.
For clearance seal between exhaust main valve 6 and 7 valve core of the spool valve and the valve pocket, reducing friction, and then reduce for the exhaust throttle flow hysteresis and the raising linearity.Use hydraulic control air feed stop valve 8 and be connected with gas cavity volume 18,, prevent to supply in the dead zone range exhaust main valve 6 and 7 internal leakages to cause the skew of gas cavity volume 18 pressure respectively in air feed main valve 6 outlet and exhaust main valve 7 porch with hydraulic control discharge line valve 9.
With reference to Fig. 4, to hydraulic control air feed stop valve 8, air feed fluid control pressure 20 is introduced hydraulic control air feed stop valve pilot stage guiding valve sensitive cavity 8-A, and with the spring force balance of hydraulic control air feed stop valve pilot stage regulating spring 8-2, initial pilot stage throttle orifice is plus lap.When air feed fluid control pressure 20 reduces with the increase of pressure reduction positively biased residual quantity, hydraulic control air feed stop valve pilot stage regulating spring 8-2 decrement reduces, hydraulic control air feed stop valve pilot stage valve core of the spool valve 8-1 moves to right, after surpassing the covering dead band, valve port is opened, and hydraulic control air feed stop valve 8 pilot stage throttle orifices are Quanzhou type, the area of passage gradient is big, and the drain resistance 8-3 of hydraulic control air feed stop valve elder generation is big liquid resistance, therefore the Type B half-bridge of the forming pressure that leads to hydraulic control air feed stop valve main valve sensitive cavity 8-D reduces rapidly, plays the effect of high-speed switch control.Hydraulic control air feed stop valve main valve plug 8-4 is at hydraulic control air feed stop valve main valve sensitive cavity 8-D original pressure, i.e. under the oil pressure source 22 pressure effects, compression hydraulic control air feed stop valve main valve returning spring 8-5 closes primary valve.When hydraulic control air feed stop valve main valve sensitive cavity 8-D pressure reduces rapidly, hydraulic control air feed stop valve main valve plug 8-4 lifts rapidly, hydraulic control air feed stop valve main valve import air cavity 8-E is communicated with hydraulic control air feed stop valve main valve outlet air cavity 8-F, will carry out the control of throttling air feed by air feed main valve 6 afterwards.Same, to hydraulic control discharge line valve 9, exhaust fluid control pressure 21 is introduced hydraulic control discharge line valve pilot stage guiding valve sensitive cavity 9-A, with the spring force balance of hydraulic control discharge line valve pilot stage regulating spring 9-2, initially also is plus lap.When exhaust fluid control pressure 21 reduces with the increase of pressure reduction negative bias residual quantity, the decrement of hydraulic control discharge line valve pilot stage regulating spring 9-2 reduces, hydraulic control discharge line valve pilot stage valve core of the spool valve 9-1 moves to left, after surpassing the covering dead band, valve port is opened, its area of passage gradient is big and the drain resistance 9-3 of hydraulic control discharge line valve elder generation is big liquid resistance, and the pressure that the half-bridge bridge circuit leads to hydraulic control discharge line valve main valve sensitive cavity 9-D also reduces rapidly.Hydraulic control discharge line valve main valve plug 9-4 is under the effect of hydraulic control discharge line valve main valve sensitive cavity 9-D original pressure, and compression hydraulic control discharge line valve main valve returning spring 9-5 closes primary valve.When hydraulic control discharge line valve main valve sensitive cavity 9-D pressure reduces rapidly, hydraulic control discharge line valve main valve plug 9-4 lifts rapidly, hydraulic control discharge line valve main valve import air cavity 9-E is communicated with hydraulic control discharge line valve main valve outlet air cavity 9-F, will carry out throttling exhaust control by exhaust main valve 7 afterwards.Hydraulic control air feed stop valve 8 and hydraulic control discharge line valve 9 amplify bridge circuit by pilot stage fluid control pressure separately provides the switching mode controlled pressure, realized when the pressure reduction departure exceeds the dead zone range critical value, opening rapidly primary valve, departure get back to that the dead band critical value closes rapidly when following for exhaust by function.
Pressure pneumatic control valve following difference of constant pressure of the present invention, use full hydraulic control principle, work under the full machine performance, improved control accuracy, functional reliability, stability and the antijamming capability of valve, reduced compressed-air actuated use amount and the air capacity in environment.This valve is integrated in the various functions of original automatically controlled regulating system on the one deck valve group, has reduced system cost, compact conformation, and taking up room reduces greatly.By the adjusting of pneumatic control valve of the present invention, the pressure of the pressure follow peripheral hardware pressure source 17 of gas cavity volume 18 is changed, or when gas cavity volume 18 pressure cause fluctuation, deviation because of duty changes, keep the pressure reduction of setting constant.
Claims (3)
1. pressure pneumatic control valve following difference of constant pressure, it is characterized in that comprising that pressure reduction amplifies pilot stage (A), air feed main valve (6), exhaust main valve (7), hydraulic control air feed stop valve (8), hydraulic control discharge line valve (9), reduction valve (12), safety valve (13), pneumatic safety valve (10) and pneumatic pressure-release valve (11); Pressure reduction amplifies pilot stage (A) and connects peripheral hardware pressure source (17), gas cavity volume (18), fuel tank (15), reduction valve (12) outlet, hydraulic control air feed stop valve (8), hydraulic control discharge line valve (9), the sensitive cavity of air feed main valve (6) and exhaust main valve (7), the oil pressure chamber of air feed main valve (6) and exhaust main valve (7) all is connected with reduction valve (12) outlet, the entrance and exit of air feed main valve (6) connects pneumatic pressure-release valve (11) outlet and hydraulic control air feed stop valve (8) inlet respectively, the entrance and exit of exhaust main valve (7) connects hydraulic control discharge line valve (9) outlet and exhaust box (19) respectively, the inlet of the outlet of hydraulic control air feed stop valve (8) and hydraulic control discharge line valve (9) all is connected with gas cavity volume (18), the guide of hydraulic control air feed stop valve (8) and hydraulic control discharge line valve (9) controls oil and draws from reduction valve (12) and export, the entrance and exit of pneumatic safety valve (10) connects gas cavity volume (18) and exhaust box (19) respectively, the entrance and exit of pneumatic pressure-release valve (11) connects the inlet of high-pressure air source (16) and air feed main valve (6) respectively, the inlet of reduction valve (12) and safety valve (13) all is connected control oil sources (14), the outlet of safety valve (13), reduction valve (12) drain tap, guide's oil drain out of hydraulic control air feed stop valve (8) and hydraulic control discharge line valve (9) all is connected with fuel tank (15);
Described pressure reduction amplifies pilot stage (A): comprise pressure reduction-force transducer (1), lever (2) and the pressure amplifier stage of being made up of pressure amplifier stage guiding valve (3), first liquid resistance (4), second liquid resistance (5); Pressure reduction-force transducer (1) is a two rod hydraulic cylinder, pressure reduction-force transducer external pressure chamber (1-A) is connected with peripheral hardware pressure source (17), press chamber (1-B) to be connected in pressure reduction-force transducer with gas cavity volume (18), pressure reduction-force transducer piston rod (1-1) withstands lever (2) remote branch of a clan point place, pressure amplifier stage valve core of the spool valve (3-1) end of pressure amplifier stage guiding valve (3) the amplifier stage guiding valve regulating spring (3-2) that withstands pressure, the leading-off rods of the other end withstands the nearly fulcrum place of lever (2), open rectangular channel on the pressure amplifier stage valve core of the spool valve (3-1), two variable valve ports of pressure amplifier stage guiding valve (3) connect first and second liquid resistance (4 respectively, 5) a end, draw air feed fluid control pressure (20) and exhaust fluid control pressure (21) respectively between valve port and the liquid resistance, oil pressure source (22) is reduction valve (12) outlet, with first and second liquid resistance (4,5) the other end and pressure amplifier stage slide valve spring chamber (3-A) connect.
2. pressure pneumatic control valve following difference of constant pressure according to claim 1, it is characterized in that described air feed main valve (6) and exhaust main valve (7): oil pressure source (22) is connected air feed main valve oil pressure chamber (6-C) and exhaust main valve oil pressure chamber (7-C), air feed valve core of main valve (6-2) is stepped, open triangular groove, big end connects air feed main valve regulating spring (6-1), small end connects air feed main valve returning spring (6-3), the air feed main valve sensitive cavity (6-A) at air feed main valve regulating spring (6-1) place is introduced air feed fluid control pressure (20), throttle orifice connects the outlet of pneumatic pressure-release valve (11), and air feed main valve air cavity (6-B) connects the inlet of hydraulic control air feed stop valve (8); Exhaust valve core of main valve (7-2) is opened rectangular channel, two ends connect exhaust main valve regulating spring (7-1) and exhaust main valve returning spring (7-3) respectively, the exhaust main valve sensitive cavity (7-A) at exhaust main valve regulating spring (7-1) place is introduced exhaust fluid control pressure (21), throttle orifice connects the outlet of hydraulic control discharge line valve (9), and exhaust main valve air cavity (7-B) connects exhaust box (19); Confession, exhaust main valve (6,7) all are provided with the work dead band, and by adjust air feed main valve regulating spring (6-1), exhaust main valve regulating spring (7-1) is regulated, air feed valve core of main valve (6-2), exhaust valve core of main valve (7-2) clearance seal respectively and between the valve pocket of air feed main valve (6), exhaust main valve (7).
3. pressure pneumatic control valve following difference of constant pressure according to claim 1, it is characterized in that described hydraulic control air feed stop valve (8), hydraulic control discharge line valve (9): hydraulic control air feed stop valve (8) comprises hydraulic control air feed stop valve pilot stage valve core of the spool valve (8-1), hydraulic control air feed stop valve pilot stage regulating spring (8-2), hydraulic control air feed stop valve elder generation drain resistance (8-3), hydraulic control air feed stop valve main valve plug (8-4), hydraulic control air feed stop valve main valve returning spring (8-5); Hydraulic control discharge line valve (9) comprises hydraulic control discharge line valve pilot stage valve core of the spool valve (9-1), hydraulic control discharge line valve pilot stage regulating spring (9-2), hydraulic control discharge line valve elder generation drain resistance (9-3), hydraulic control discharge line valve main valve plug (9-4), hydraulic control discharge line valve main valve returning spring (9-5); Oil pressure source (22) is by hydraulic control air feed stop valve elder generation's drain resistance (8-3), the pilot stage throttle orifice and the hydraulic control air feed stop valve main valve sensitive cavity (8-D) that connect hydraulic control air feed stop valve (8), hydraulic control air feed stop valve elder generation's drain resistance (8-3) is formed Type B hydraulic pressure half-bridge with the pilot stage of hydraulic control air feed stop valve (8); Oil pressure source (22) is by hydraulic control discharge line valve elder generation's drain resistance (9-3), the pilot stage throttle orifice and the hydraulic control discharge line valve main valve sensitive cavity (9-D) that connect hydraulic control discharge line valve (9), hydraulic control discharge line valve elder generation's drain resistance (9-3) is also formed Type B hydraulic pressure half-bridge with the pilot stage of hydraulic control discharge line valve (9); Hydraulic control air feed stop valve pilot stage guiding valve low-pressure cavity (8-B) all is connected with fuel tank (15) with spring cavity (8-C), hydraulic control discharge line valve pilot stage guiding valve low-pressure cavity (9-B) and spring cavity (9-C), hydraulic control air feed stop valve pilot stage guiding valve sensitive cavity (8-A) is introduced air feed fluid control pressure (20), and hydraulic control discharge line valve pilot stage guiding valve sensitive cavity (9-A) is introduced exhaust fluid control pressure (21); Hydraulic control air feed stop valve pilot stage valve core of the spool valve (8-1) withstands hydraulic control air feed stop valve pilot stage regulating spring (8-2), hydraulic control air feed stop valve main valve plug (8-4) withstands on the main valve valve seat that hydraulic control air feed stop valve main valve returning spring (8-5) is pressed in hydraulic control air feed stop valve (8), hydraulic control air feed stop valve main valve import air cavity (8-E) is connected the outlet and the gas cavity volume (18) of air feed main valve (6) respectively with outlet air cavity (8-F), hydraulic control discharge line valve pilot stage valve core of the spool valve (9-1) withstands hydraulic control discharge line valve pilot stage regulating spring (9-2), hydraulic control discharge line valve main valve plug (9-4) withstands on the main valve valve seat that hydraulic control discharge line valve main valve returning spring (9-5) is pressed in hydraulic control discharge line valve (9), and hydraulic control discharge line valve main valve import air cavity (9-E) and outlet air cavity (9-F) are connected the inlet of gas cavity volume (18) and exhaust main valve (7) respectively.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2006101556689A CN100445916C (en) | 2006-12-30 | 2006-12-30 | Pressure pneumatic control valve following difference of constant pressure |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2006101556689A CN100445916C (en) | 2006-12-30 | 2006-12-30 | Pressure pneumatic control valve following difference of constant pressure |
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| Publication Number | Publication Date |
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| CN101004615A CN101004615A (en) | 2007-07-25 |
| CN100445916C true CN100445916C (en) | 2008-12-24 |
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| CNB2006101556689A Expired - Fee Related CN100445916C (en) | 2006-12-30 | 2006-12-30 | Pressure pneumatic control valve following difference of constant pressure |
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| JP6650471B2 (en) * | 2016-01-29 | 2020-02-19 | 株式会社小松製作所 | Spool valve device for hydraulic cylinder |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5586575A (en) * | 1993-06-22 | 1996-12-24 | Nuovopignone- Industrie Meccaniche E Fonderia S.P.A. | Electropneumatic converter with solenoid valve control |
| JP2004360770A (en) * | 2003-06-04 | 2004-12-24 | Fujikura Rubber Ltd | Electric-to-pneumatic conversion type pneumatic regulator |
| CN1623129A (en) * | 2002-01-28 | 2005-06-01 | 图尔和安德森公司 | Apparatus for control of differential pressure in a heating and cooling system |
| CN1796783A (en) * | 2004-12-28 | 2006-07-05 | 株式会社Tgk | Control valve in variable displacement compressor |
| CN200993263Y (en) * | 2006-12-30 | 2007-12-19 | 浙江大学 | Constant pressure difference tracking pressure pneumatic control valve |
-
2006
- 2006-12-30 CN CNB2006101556689A patent/CN100445916C/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5586575A (en) * | 1993-06-22 | 1996-12-24 | Nuovopignone- Industrie Meccaniche E Fonderia S.P.A. | Electropneumatic converter with solenoid valve control |
| CN1623129A (en) * | 2002-01-28 | 2005-06-01 | 图尔和安德森公司 | Apparatus for control of differential pressure in a heating and cooling system |
| JP2004360770A (en) * | 2003-06-04 | 2004-12-24 | Fujikura Rubber Ltd | Electric-to-pneumatic conversion type pneumatic regulator |
| CN1796783A (en) * | 2004-12-28 | 2006-07-05 | 株式会社Tgk | Control valve in variable displacement compressor |
| CN200993263Y (en) * | 2006-12-30 | 2007-12-19 | 浙江大学 | Constant pressure difference tracking pressure pneumatic control valve |
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