CN105202252A - Drive device of pneumatic proportional valve - Google Patents
Drive device of pneumatic proportional valve Download PDFInfo
- Publication number
- CN105202252A CN105202252A CN201510654592.3A CN201510654592A CN105202252A CN 105202252 A CN105202252 A CN 105202252A CN 201510654592 A CN201510654592 A CN 201510654592A CN 105202252 A CN105202252 A CN 105202252A
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- piston
- valve
- solenoid valve
- air
- end cavity
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
- F16K31/1221—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston one side of the piston being spring-loaded
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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
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
Abstract
The invention discloses a drive device of a pneumatic proportional valve. The drive device is characterized by comprising a compressed air source, an electromagnetic valve, a controller and a cylinder; a piston is arranged in the cylinder and is driven to move up and down through the pressure difference between the two ends of the piston, and the piston is positioned and stays when the stress of the upper end and the lower end is balanced; the compressed air source provides pressure for an upper end cavity and/or a lower end cavity of the piston of the cylinder by opening or closing the electromagnetic valve; the electromagnetic valve is controlled to be opened and closed through PWM signals provided by the controller. By opening and closing the electromagnetic valve, the valve can be accurately and stably controlled at any position of the working stroke, and linearity is high; the number of elements which are used is small, the structure is simple, all the elements which are used are conventional pneumatic elements, and cost is low.
Description
Technical field
The present invention relates to a kind of drive unit of pneumatic proportional valve.Be applicable to field of internal combustion engine.
Background technique
Often adopt to make proportion valve rest on any one neutral position the method controlling spool electromagnet input current in prior art, or realized by the mode of solenoid valve group adjustment suction pressure.
Such as: CN201310010367.7 pneumatic proportional pressure valve, a kind of pneumatic proportional pressure valve, comprises upper shell, lower shell body, and the endoporus of upper shell is provided with main valve plug, and the right-hand member of main valve plug connects the left end of upper valve core; The right-hand member of upper valve core connects proportion electro-magnet; The left end of main valve plug is fixedly installed valve port assembly, and the valve port assembly of main valve plug connects main valve plug spring seat by main valve plug Returnning spring, and main valve plug spring seat is fixedly connected with upper shell by circlip for hole; Be provided with leather cup in lower shell body, between the right side of leather cup and the left side of upper shell, form air pressure control chamber; Be positioned on the lower shell body on the left of leather cup and have working hole, exhaust port and overflow hole; Overflow hole is communicated with working hole with exhaust port respectively; Working hole directly communicates with load, and exhaust port is logical air directly, is provided with spill valve in overflow hole.The spool of pneumatic proportional pressure valve is by solenoid actuated, and proportion electro-magnet receives the input current signal of self-controller, is converted into ouput force; When input current increases, the ouput force of proportion electro-magnet increases, and overcomes the spring force of main valve plug Returnning spring and upper valve core Returnning spring, promotes main valve plug and is moved to the left together with upper valve core, valve port is opened; When input current reduces, proportion electro-magnet ouput force reduces, and upper valve core is first moved right by upper valve core Returnning spring pushing tow, be separated with main valve plug, gas in control chamber is entered air through the loculus of described upper shell, and due to the reduction of power, the valve port opening of main valve plug diminishes, throttle effect is strengthened, make control chamber pressure drop, and leather cup left pressure remains the front force value of electric current reduction, makes both sides there is pressure difference, promotion leather cup moves right, and leather cup no longer seals air outlet hole; Due to the single effect of leather cup, in the process moved right, lip is in tensioner state in the effect of left pressure always, isolated control chamber and working hole, and moves to right due to leather cup, and exhaust port is communicated with working hole, and in load, gas is fast discharged to air; When the gas pressure of load holes drops to certain value, the leather cup left and right sides and load and active chamber gas pressure reach balance again, and initial position got back to by leather cup, and exhaust port is no longer communicated with working hole, and gas is no longer discharged.The program is that pressurized air is connected with a cavity by a proportional electromagnetic valve, the pressure of the control cavity that proportional electromagnetic valve energy is linear, when the pressure of this cavity is greater than load end pressure, pressurized air in cavity will enter load end, thus make the pressure increase of load end, until pressure balance between the two, when the pressure of this cavity is less than load end, the air of load end will enter air, thus make the pressure drop of load end, until pressure balance between the two, the pressure of load end indirectly controls, respond slow, and pneumatic proportional valve complex structure, difficulty of processing is large, price is high.
And for example: CN201110205797.5 Pneumatic proportion regulator based on electromagnetic valve array, it comprises main valve body, upper end cap, lower end cap, air inlet electromagnetic valve battle array and electromagnetic valve array of giving vent to anger, be provided with in main valve body and separate mutually independently air cavity, air inlet gas circuit and exhaust gas circuit, main valve body top is provided with pressure transducer and circuit board, and upper end cap is installed on main valve body top pressure transducer, circuit board is accommodated therein; Bottom main valve body, lower end cap is installed; Main valve body left and right sides installs air inlet electromagnetic valve battle array and electromagnetic valve array of giving vent to anger respectively; The first interface, the second interface that are communicated with respectively separately with air inlet gas circuit and air cavity is provided with on front side of main valve body.Air inlet electromagnetic valve battle array comprises the solenoid valve of at least two kinds of latus rectums, two gas port connections of offering on the left of each solenoid valve and main valve body, and one of them gas port is connected with air cavity, and another gas port is connected with air inlet gas circuit; Exhaust solenoid valve battle array comprises the solenoid valve of at least two kinds of latus rectums, two gas port connections of offering on the right side of each solenoid valve and main valve body, and one of them gas port is connected with air cavity, and another gas port is connected with exhaust gas circuit.The program is that the combination of the solenoid valve number opened by air inlet electromagnetic valve group and exhaust solenoid valve group realizes the pressure controlled of pressure chamber, the valve increasing number then air pressure increase that air inlet electromagnetic valve group is opened, the valve increasing number then air pressure reduction that exhaust solenoid valve group is opened, it is complicated that this mode needs to use a lot of electromagnetic valve structures, and to the poor linearity that air pressure controls.
Summary of the invention
The object of the invention is to provide that a kind of structure is simple, the linearity good for the defect of above-mentioned prior art, the drive unit of the pneumatic proportional valve of fast response time and method for driving.
The present invention for achieving the above object, adopts following technological scheme:
A drive unit for pneumatic proportional valve, is characterized in that: this device comprises source of compressed air, solenoid valve, controller and cylinder; Have piston in described cylinder, the pressure differential that described piston is subject to piston two ends is up and down, upper and lower two ends stress balance, and piston location stops; Described source of compressed air provides pressure by solenoid valve break-make to the upper end cavity of cylinder piston and/or lower end cavity; Described controller provides pwm signal to control described solenoid valve break-make.
A kind of mode: be provided with Compress Spring below described piston, provides power upwards to piston; Described solenoid valve is two-position three way magnetic valve, has I, II two kind of working state, under controller pwm signal controls, carry out state switching; During working state I, the pressurized air that source of compressed air provides enters the upper end cavity of cylinder piston after solenoid valve, and it is descending that driven plunger overcomes Compress Spring elastic force; During working state II, the pressurized air in the upper end cavity of cylinder piston enters the lower end cavity of cylinder piston and enters air after solenoid valve, and described Compress Spring elastic force driven plunger is up.
Preferred: the pressurized air of described source of compressed air enters the upper end cavity of cylinder piston again after one-way valve through solenoid valve; Pressurized air in the upper end cavity of described cylinder piston is divided into two-way again through solenoid valve after one-way valve, and a road enters the lower end cavity of cylinder piston after throttle valve, and another road enters air after one-way valve.
Another kind of form: described solenoid valve is two five-way electromagnetic valves, has I, II two kind of working state, under controller pwm signal controls, carry out state switching; During working state I, the pressurized air that source of compressed air provides enters the upper end cavity of cylinder piston after solenoid valve, and the air in the lower end cavity of cylinder piston enters air after solenoid valve, the pressure differential descent of piston at piston two ends; During working state II, the pressurized air that source of compressed air provides enters the lower end cavity of cylinder piston after solenoid valve, and the air in the upper end cavity of cylinder piston enters air after solenoid valve, the pressure differential piston stroking upward at piston two ends.
Preferred: the pressurized air that described source of compressed air provides enters upper end cavity or the lower end cavity of cylinder piston again after one-way valve through solenoid valve; Upper end cavity and the lower end cavity compressed air of described cylinder piston enter air again through solenoid valve after one-way valve He after throttle valve.
The method that the dutyfactor value of the pwm signal of above-mentioned controller is regulated by PID controls.
The piston of above-mentioned cylinder is fixed with inductor, the shell of described cylinder is fixed with position transducer, described position transducer exports corresponding signal to controller according to the position of inductor, and controller is formulated control strategy according to the position signal obtained and target position signal and controlled described solenoid valve.
Good effect of the present invention is: by the break-make of solenoid valve, can by any position of control precise and stable for valve in working stroke, and the linearity is good; The few structure of number of elements used is simple, and element used is Conventional pneumatic element entirely, and cost is low.
Accompanying drawing explanation
Fig. 1 is the structural representation of one embodiment of the present invention.
Fig. 2 is Fig. 1 arrangement works state I schematic diagram.
Fig. 3 is Fig. 1 arrangement works state II schematic diagram.
Fig. 4 is the structural representation of another embodiment of the present invention.
Fig. 5 is Fig. 4 arrangement works state I schematic diagram.
Fig. 6 is Fig. 4 arrangement works state II schematic diagram.
Embodiment
Embodiment 1:
As Figure 1-3, described solenoid valve 13 has I, II two kinds of working staties, there is P, A, T tri-passages, wherein passage A is connected with passage 17, passage P is connected with one-way valve 15, passage T is connected with one-way valve 2, one-way valve 15 is in source of compressed air 1 downstream, one-way valve 2 is in passage T downstream, one-way valve 14 is in one-way valve 2 downstream, throttle valve 3 is in one-way valve 2 downstream one-way valve 14 upstream, described solenoid valve 13 can be Double-coil type also can be single line ring type, the each coil of Double-coil type controls a working state, if with Double-coil type, two coils adopt complementary SC sigmal control, control signal directly controls one of them coil, another one coil is controlled after reverse process, single line ring type coil electricity only controls from a state to another state, get back to original state then coil blackout realized by spring, if by single line ring type, control signal directly controls this coil.Cylinder 19 is single-acting cylinder, and the descending of piston 20 is power-actuated by the effect of air pressure, and up is power-actuated by spring.The piston 20 of described cylinder 19 is fixed with inductor 29, the shell of described cylinder 19 is fixed with position transducer 30, described position transducer 30 can export corresponding signal to controller 4 according to the position of inductor 29, controller 4 is formulated control strategy according to the position signal obtained and target position signal and is controlled described solenoid valve 13, makes described piston 9 move to target location quickly and accurately and be stabilized in target location.Described spring 23 is except possessing the back to zero position effect of valve when driving effect also possesses system stalls.
Fig. 2,3 is the schematic diagram of two kinds of working staties of solenoid valve 13.As shown in Figure 2, when described solenoid valve 13 works in working state I, described one-way valve 15 is opened, and passage P communicates with passage A, and air enters in cavity 18 by one-way valve 15, passage P, passage A, passage 17; The spring force that air pressure in cavity 18 makes piston 20 overcome spring 23 moves down, air in cavity 21 will produce certain air pressure under the effect of piston 20, one-way valve 14 is opened under gas pressure, and the air in cavity 21 is entered in air by throttle valve 3, one-way valve 14.As shown in Figure 3, when described solenoid valve 13 works in working state II, passage T communicates with passage A, piston 20 moves up under the spring-force driven dual of spring 23, negative pressure is formed in cavity 21, air pressure simultaneously in cavity 18 makes one-way valve 2 open, and the portion of air in cavity 18 enters in cavity 21 by passage 17, passage A, passage T, one-way valve 2, throttle valve 3, passage 24; Due in working order I time cavity 18 are logical high-pressure airs, after switching to working state II, air in cavity 18 can enter in the pipeline of one-way valve 14 anode, make the air pressure of anode higher than negative terminal, one-way valve 14 will be opened, and the portion of air in cavity 18 will be entered in air by passage 17, passage A, passage T, one-way valve 2, one-way valve 14.
Switch between I, II two states fast with pwm signal Controlling solenoid valve 13, and when the periodic quantity switched and air forward flow through one-way valve 2, one-way valve 14, one-way valve 15 they open needed for time match, to reach effect below:
When solenoid valve 13 switches to working state I from working state II, passage T closes, one-way valve 2 two ends do not have the pressure reduction of forward, one-way valve 2 is closed, the pressure reduction that one-way valve 15 is subject to forward will be opened, but open and need a period of time, even and if one-way valve 15 unlatching has a small amount of pressurized air to enter cavity 18, in the state that one-way valve 14 is not opened, air in cavity 21 can be certain to the descending generation of piston 20 inhibition, although the pressure reduction that now one-way valve 14 is subject to forward has the trend of unlatching, but its unlatching needs the regular hour, at one-way valve 15, 14 also do not open or open solenoid valve 13 soon just switches to working state II from working state I, when solenoid valve 13 switches to working state II from working state I, passage P closes, one-way valve 15,14 two ends do not have the pressure reduction of forward, they will be closed, the pressure reduction that now one-way valve 2 is subject to forward has the trend of unlatching, but open and need a period of time, also do not open or open solenoid valve 13 soon at one-way valve 2 and just switch to working state I from working state II again.
By that controlling method above can make the air of turnover cavity 18 seldom and also turnover gas hocket, air inflow is equal with gas output, and the pressure of cavity 18 maintains to be stablized, and piston 20 is stabilized in fixed position.Regulate the dutycycle of pwm signal, the air pressure of cavity 18 is regulated between atmospheric pressure and the air pressure of source of compressed air 1, thus the arbitrary target position regulation of the position of piston 20 in working stroke can be made.
The effect of throttle valve 3 be the speed of piston 20 movement is met the demands while the pwm signal Controlling solenoid valve 13 of more large period can be adopted to improve its reliability.Cancel one-way valve 15 source of compressed air 1 directly and passage P communicate, or cancel throttle valve 3, one-way valve 2 negative terminal and one-way valve 14 anode is direct and passage 24 communicates all belongs to this preferred version.
Embodiment 2:
Fig. 4 shows the principle schematic of described invention.Solenoid valve 13 is two five-way electromagnetic valves, have I, II two kinds of working staties, P, A, B, R, S five passages, wherein passage A is connected with passage 6, channel B is connected with passage 12, passage P is connected with one-way valve 15, passage R is connected with one-way valve 2, passage S is connected with one-way valve 14, one-way valve 15 is in source of compressed air 1 downstream, one-way valve 2 is in passage R downstream, one-way valve 14 is in passage S downstream, throttle valve 3 is at one-way valve 2, 14 downstreams, described solenoid valve 13 can be Double-coil type also can be single line ring type, the each coil of Double-coil type controls a working state, if with Double-coil type, two coils adopt complementary SC sigmal control, control signal directly controls one of them coil, another one coil is controlled after reverse process, single line ring type coil electricity only controls from a state to another state, get back to original state then coil blackout realized by spring, if by single line ring type, control signal directly controls this coil.Cylinder 7 is double-acting cylinder, and the uplink and downlink of piston 9 all drive by air pressure.The piston 9 of described cylinder 7 is fixed with inductor 29, the shell of described cylinder 7 is fixed with position transducer 30, described position transducer 30 can export corresponding signal to controller 4 according to the position of inductor 29, controller 4 is formulated control strategy according to the position signal obtained and target position signal and is controlled described solenoid valve 13, makes described piston 9 move to target location quickly and accurately and be stabilized in target location.The spring force of spring 31 is very little, only realizes the return effect of valve during system stalls, and does not work to drive valve, if valve itself has returning device spring 31 to cancel.
Fig. 5,6 is the schematic diagram of two kinds of working staties of solenoid valve 13, when described solenoid valve 13 works in working state II, described one-way valve 15 is opened, and described passage P communicates with channel B, and pressurized air enters in cavity 10 by one-way valve 15, passage P, channel B, passage 12; Passage R communicates with passage A, and open under the gas pressure of described one-way valve 2 in cavity 8, the air in cavity 8 enters in air by passage 6, passage A, passage R, one-way valve 2, throttle valve 3, and piston 9 is up.When described solenoid valve 13 works in working state I, described one-way valve 15 is opened, and passage P communicates with passage A, and pressurized air enters in cavity 8 by one-way valve 15, passage P, passage A, passage 6; Passage S communicates with channel B, and open under the gas pressure of described one-way valve 14 in cavity 10, the air in cavity 10 enters in air by passage 12, channel B, passage S, one-way valve 14, throttle valve 3, and piston 9 is descending.
When the position of described piston 9 is greater than the first threshold values far from the distance of target location, described solenoid valve 13 switching signal controls, and make solenoid valve 13 be operated in working state I or working state II, piston 9 moves to target location fast.When described piston 9 position far from the distance of target location be less than the first threshold values be greater than the second threshold values time, described solenoid valve 13 pwm signal that the cycle is period 1 value controls, solenoid valve 13 is switched between I and working state II in working order, switching cycle equals period 1 value, dutycycle is equal with the dutycycle of pwm signal, the mode that the dutycycle of pwm signal adopts PID to regulate controls, and piston 9 to move to target location with speed faster and is unlikely to accommodative excess simultaneously.When the position of described piston 9 is less than the second threshold values far from the distance of target location, described solenoid valve 13 pwm signal that the cycle is second week time value controls, solenoid valve 13 is switched between I and working state II in working order, switching cycle equals second week time value, dutycycle is equal with the dutycycle of pwm signal, the mode that the dutycycle of pwm signal adopts PID to regulate controls, when described second week time value and air forward flow through described one-way valve 2, one-way valve 14, one-way valve 15 they open needed for time match the effect that reaches below:
When solenoid valve 13 switches to working state II from working state I, the two ends of one-way valve 14 do not have the pressure reduction of forward, one-way valve 14 will be closed, and the anode of one-way valve 2 communicates with cavity 8 and will to open under differential pressure action, but open and need a period of time, also do not open or open solenoid valve 13 soon at one-way valve 2 and just switch to working state I from working state II, therefore little air is only had to discharge from cavity 8, situation when solenoid valve 13 switches to working state I from working state II too, little air is only had to discharge from cavity 10, cavity 8 and the pressure reduction both cavity 10 remain stable, piston 9 is stabilized in target location.
The effect of throttle valve 3 be the speed of piston 9 movement is met the demands while the pwm signal Controlling solenoid valve 13 of more large period can be adopted to improve its reliability.Cancel one-way valve 15 source of compressed air 1 directly and passage P communicate, or cancel throttle valve 3, one-way valve 2,14 negative terminal directly leads to air and all belongs to this preferred version.
Claims (7)
1. a drive unit for pneumatic proportional valve, is characterized in that: this device comprises source of compressed air, solenoid valve, controller and cylinder; Have piston in described cylinder, the pressure differential that described piston is subject to piston two ends is up and down, upper and lower two ends stress balance, and piston location stops; Described source of compressed air provides pressure by solenoid valve break-make to the upper end cavity of cylinder piston and/or lower end cavity; Described controller provides pwm signal to control described solenoid valve break-make.
2. the drive unit of pneumatic proportional valve according to claim 1, is characterized in that: be provided with Compress Spring below described piston, provides power upwards to piston; Described solenoid valve is two-bit triplet solenoid valve, has I, II two kind of working state, under controller pwm signal controls, carry out state switching; During working state I, the pressurized air that source of compressed air provides enters the upper end cavity of cylinder piston after solenoid valve, and it is descending that driven plunger overcomes Compress Spring elastic force; During working state II, the pressurized air in the upper end cavity of cylinder piston enters the lower end cavity of cylinder piston and enters air after solenoid valve, and described Compress Spring elastic force driven plunger is up.
3. the drive unit of pneumatic proportional valve according to claim 2, is characterized in that: the pressurized air of described source of compressed air enters the upper end cavity of cylinder piston again after one-way valve through solenoid valve; Pressurized air in the upper end cavity of described cylinder piston is divided into two-way again through solenoid valve after one-way valve, and a road enters the lower end cavity of cylinder piston after throttle valve, and another road enters air after one-way valve.
4. the drive unit of pneumatic proportional valve according to claim 1, is characterized in that: described solenoid valve is two five-way electromagnetic valves, has I, II two kind of working state, under controller pwm signal controls, carry out state switching; During working state I, the pressurized air that source of compressed air provides enters the upper end cavity of cylinder piston after solenoid valve, and the air in the lower end cavity of cylinder piston enters air after solenoid valve, the pressure differential descent of piston at piston two ends; During working state II, the pressurized air that source of compressed air provides enters the lower end cavity of cylinder piston after solenoid valve, and the air in the upper end cavity of cylinder piston enters air after solenoid valve, the pressure differential piston stroking upward at piston two ends.
5. the drive unit of pneumatic proportional valve according to claim 4, is characterized in that: the pressurized air that described source of compressed air provides enters upper end cavity or the lower end cavity of cylinder piston again after one-way valve through solenoid valve; Upper end cavity and the lower end cavity compressed air of described cylinder piston enter air again through solenoid valve after one-way valve He after throttle valve.
6. the drive unit of the pneumatic proportional valve according to any one of claim 1-5, is characterized in that: the method that the dutyfactor value of the pwm signal of described controller is regulated by PID controls.
7. the drive unit of the pneumatic proportional valve according to any one of claim 1-5, it is characterized in that: the piston of described cylinder is fixed with inductor, the shell of described cylinder is fixed with position transducer, described position transducer exports corresponding signal to controller according to the position of inductor, and controller is formulated control strategy according to the position signal obtained and target position signal and controlled described solenoid valve.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201510654592.3A CN105202252B (en) | 2015-10-12 | 2015-10-12 | A kind of driving device of pneumatic proportional valve |
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| CN201510654592.3A CN105202252B (en) | 2015-10-12 | 2015-10-12 | A kind of driving device of pneumatic proportional valve |
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| CN105202252B CN105202252B (en) | 2018-06-19 |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN107136561A (en) * | 2017-06-17 | 2017-09-08 | 常德烟草机械有限责任公司 | The glue cooling device and cooling means of a kind of cork paper |
| CN108644454A (en) * | 2018-07-26 | 2018-10-12 | 大连亨利测控仪表工程有限公司 | A kind of electrical integrated control system of adjustment type pneumatic actuator |
| CN108691840A (en) * | 2017-03-31 | 2018-10-23 | 住友重机械工业株式会社 | Position control, fluid pressure drive device |
| CN108980343A (en) * | 2017-07-01 | 2018-12-11 | 董润 | Automatically control the automatic gear shift apparatus and its working method of vehicle shift |
| CN109343492A (en) * | 2018-11-08 | 2019-02-15 | 郭浩 | Two-wire system Process Control System protective device |
| CN109424382A (en) * | 2017-09-04 | 2019-03-05 | 北京汽车动力总成有限公司 | A kind of dynamic air gate control device and automobile |
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| TWI749178B (en) * | 2017-03-31 | 2021-12-11 | 日商住友重機械工業股份有限公司 | Position control device, hydraulic drive device |
| CN108691840A (en) * | 2017-03-31 | 2018-10-23 | 住友重机械工业株式会社 | Position control, fluid pressure drive device |
| CN107136561B (en) * | 2017-06-17 | 2018-03-06 | 常德烟草机械有限责任公司 | The glue cooling device and cooling means of a kind of cork paper |
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| CN109424382A (en) * | 2017-09-04 | 2019-03-05 | 北京汽车动力总成有限公司 | A kind of dynamic air gate control device and automobile |
| CN109424382B (en) * | 2017-09-04 | 2023-08-22 | 北京汽车动力总成有限公司 | Power valve control device and automobile |
| CN108644454A (en) * | 2018-07-26 | 2018-10-12 | 大连亨利测控仪表工程有限公司 | A kind of electrical integrated control system of adjustment type pneumatic actuator |
| CN108644454B (en) * | 2018-07-26 | 2024-03-15 | 大连亨利测控仪表工程有限公司 | Electrical integrated control system for adjusting type pneumatic actuating mechanism |
| CN109343492A (en) * | 2018-11-08 | 2019-02-15 | 郭浩 | Two-wire system Process Control System protective device |
| CN109343492B (en) * | 2018-11-08 | 2021-02-12 | 郭浩 | Two-wire system process control system protection device |
| CN112303258A (en) * | 2020-10-31 | 2021-02-02 | 张家港市金秋环保科技有限公司 | Ventilation valve and use method thereof |
| CN112303258B (en) * | 2020-10-31 | 2022-11-11 | 张家港市金秋环保科技有限公司 | Ventilation valve and use method thereof |
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|---|---|
| CN105202252B (en) | 2018-06-19 |
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