CN101634862B - Control method of opening of large flow throttle valve for water - Google Patents
Control method of opening of large flow throttle valve for water Download PDFInfo
- Publication number
- CN101634862B CN101634862B CN2009100440142A CN200910044014A CN101634862B CN 101634862 B CN101634862 B CN 101634862B CN 2009100440142 A CN2009100440142 A CN 2009100440142A CN 200910044014 A CN200910044014 A CN 200910044014A CN 101634862 B CN101634862 B CN 101634862B
- Authority
- CN
- China
- Prior art keywords
- water
- valve
- throttle valve
- opening
- large flow
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 77
- 238000000034 method Methods 0.000 title claims abstract description 50
- 230000008569 process Effects 0.000 claims abstract description 17
- 230000001105 regulatory effect Effects 0.000 claims abstract description 5
- 230000010355 oscillation Effects 0.000 claims description 13
- 230000004044 response Effects 0.000 claims description 12
- 238000013341 scale-up Methods 0.000 claims description 10
- 230000033001 locomotion Effects 0.000 claims description 9
- 230000010354 integration Effects 0.000 claims description 5
- 230000008901 benefit Effects 0.000 abstract description 2
- 230000001276 controlling effect Effects 0.000 abstract 1
- 238000009434 installation Methods 0.000 abstract 1
- 238000005516 engineering process Methods 0.000 description 14
- 238000001125 extrusion Methods 0.000 description 12
- 238000006073 displacement reaction Methods 0.000 description 10
- 239000012530 fluid Substances 0.000 description 7
- 238000002474 experimental method Methods 0.000 description 6
- 230000033228 biological regulation Effects 0.000 description 4
- 230000008859 change Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 4
- 230000009467 reduction Effects 0.000 description 4
- 238000006243 chemical reaction Methods 0.000 description 3
- 238000001514 detection method Methods 0.000 description 3
- 239000002609 medium Substances 0.000 description 3
- 238000011160 research Methods 0.000 description 3
- 238000004891 communication Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 239000000839 emulsion Substances 0.000 description 2
- 238000012544 monitoring process Methods 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 238000004088 simulation Methods 0.000 description 2
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- 239000004411 aluminium Substances 0.000 description 1
- 239000012736 aqueous medium Substances 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000011217 control strategy Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 210000004907 gland Anatomy 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000003672 processing method Methods 0.000 description 1
- 238000003908 quality control method Methods 0.000 description 1
- 210000000664 rectum Anatomy 0.000 description 1
- 238000005070 sampling Methods 0.000 description 1
- 239000013535 sea water Substances 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 239000008399 tap water Substances 0.000 description 1
- 235000020679 tap water Nutrition 0.000 description 1
- 230000009466 transformation Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Images
Landscapes
- Servomotors (AREA)
- Feedback Control In General (AREA)
Abstract
The invention provides a control method of the opening of a large flow throttle valve for water. The control method is characterized in that the position of a piston rod in a proportional servo oil cylinder is controlled by regulating input current of a pilot electro-hydraulic proportional flow valve, and the piston rod drives a valve core of the large flow throttle valve for water to move, thus ultimately controlling the opening of the large flow throttle valve for water; the piston rod is fixedly connected with the valve core of the throttle valve for water by screw threads; an unsymmetrical closed loop PID control method is employed in the control process, input is a given opening value of the large flow throttle valve for water, feedback is the actually detected opening value of the large flow throttle valve for water, the difference e (t) between the given opening value of the large flow throttle valve for water and the actually detected opening value of the large flow throttle valve for water is input into a PID controller, and the PID controller outputs current signals to the pilot electro-hydraulic proportional flow valve. The method has the advantages of high control precision, convenient installation and operation, strong practicability and high reliability.
Description
Technical field
The invention belongs to the integrated control of mechanical electronic hydraulic field, specifically be a kind of control method of opening of large flow throttle valve for water, be applied to based in the oil pressure control system of electro-hydraulic proportion reversing valve with the spool position of the big flow water valve of accurate control, thereby control the overcurrent flow of big flow water valve.
Background technology
Extruding is one of most important pressure processing method, and large-size extruder is an imperative equipment in the industry such as present space flight, aviation, traffic, telecommunications, boats and ships, and it is one of important symbol of the industrialization degree of a country and economy, military capability of the country.
Extrusion speed is a technological parameter that needs strict control in the aluminium extrusion process, and factors such as the composition of extrusion speed and institute's extrusion section bar, cross sectional shape, extrusion ratio are closely related.Extrusion speed is too high or too low all can be made the production efficiency reduction even extruding work can't be carried out.In addition, from the angle of extrusion process, extrusion speed must be relatively stable in extrusion process, and the fluctuation of extrusion speed will cause product surface ripple to occur, influences quality of item.At present, the speed control technology of large-size extruder mainly contains frequency conversion drive volumetric speed control mode, variable output pump volumetric speed control mode, electro-hydraulic proportion cartridge valve mode of speed regulation, but these modes of speed regulation all only are fit to be applied to oil pressure control or technology is immature at home.
The required working fluid scale of construction of huge hydropress is huge, considers many-sided factors such as economy, pollution, and hydraulic fluid is selected emulsion for use, because leakage rate is big, and emulsion expense height, the existing many water consumption substitutions of driving medium.Therefore the huge hydropress of China generally still is a water pressure engine, and at present, external water hydraulic Study on Technology makes substantial progress.The attrition and attack of the quality control of aqueous medium, element and system control, and new material, new technology, new control technology are fully reflected in the development of existing water hydraulic element and system.Now, the water hydraulic element supply of minority series has been arranged on the world market, shown in table 1.1, pressure mainly contains five kinds of grades such as 10MPa, 14MPa, 21MPa, 32MPa, 40MPa.But in general, existing water hydraulic element overall performance and oil pressure element differ bigger, and price is also very expensive.
The market availability of table 1.1 water hydraulic operation valve
The water hydraulic technical research of China also starts to walk.Colleges and universities such as the Central China University of Science and Technology and Zhejiang University have carried out this Study on Technology work now.The research of the two has their own characteristics each.Central China University of Science and Technology's research emphatically is the water hydraulic technology of medium with the seawater, and main application fields is conceived to naval equipment; It is the correlation technique of medium that Zhejiang University then focuses on the tap water, and application is civilian.But up to the present, the water hydraulic technology has just entered the phase one of practical application, with computing machine the water throttling valve is realized that precise figures control will be an important development direction of water hydraulic technology.
The original throttling valve of 125MN extruder adopts direct current generator to drive worm and gear, drives transmission levers with nut screw pair mechanism after speed reduction unit slows down, thus control throttling valve spool aperture, Control Flow indirectly.Because original system employing selsyn servo-actuated and driving-chain are long, the poor stability of valve, there is drift in displacement of valve rod.And total system is an open cycle system, and control accuracy is not high, and the production efficiency of control accuracy and press urgently has much room for improvement.
Summary of the invention
The object of the present invention is to provide a kind of control method of opening of large flow throttle valve for water, be applied to the High Accuracy Control of the big flow water throttling valve valve openings degree of large-size extruder.
For achieving the above object, technical scheme of the present invention is:
A kind of control method of opening of large flow throttle valve for water, it is characterized in that, position by piston rod in the input current control ratio servo-cylinder of regulating guide's electro-hydraulic proportional flow valve, piston rod and water throttling valve spool are fixedly connected, thereby directly drive the valve core movement of big flow water throttling valve by the motion of piston rod, the final accurate control that realizes the opening degree of big flow water throttling valve;
Adopt the PID control method of closed loop asymmetric in the control procedure, input quantity is given opening of large flow throttle valve for water value, feedback quantity is the opening of large flow throttle valve for water value of detected reality, the poor e (t) of the given opening of large flow throttle valve for water value and the opening of large flow throttle valve for water value of detected reality is input in the PID controller, and PID controller output current signal is given guide's electro-hydraulic proportional flow valve.
Described PID controller adopts asymmetry parameter, and concrete parameter tuning process is:
If K
P1, K
I1, K
D1And K
P2, K
I2, K
D2Be e (t) ratio when getting positive and negative respectively, integration, derivative constant; K
P1, K
I1, K
D1Parameter tuning method is: the dead band value of setting PID control is 0.05mm, but adopts Ya Ge-Ni scholar's method, at first puts K
D1=K
I1=0, independent resize ratio COEFFICIENT K, this moment, controller just was a proportional controller, by in supervisory system, the setting opening value of throttling valve being made as greater than throttling valve actual aperture degree value, even e (t)＞0, increase system proportional coefficient K then until system's starting oscillation, record scale-up factor K at this moment is Km
1, K then
P1, K
I1, K
D1Parameter is calculated as follows:
K
P1＝0.6K
m1 ω in the formula
mBe oscillation frequency; (when putting K
D1=K
I1=0 o'clock, system adopted a proportional component control, K exactly
P1, K, Km
1Be the scale-up factor of hereinafter mentioning, K is the general name of scale-up factor, and KM1 begins to shake scale-up factor constantly, and KP1 is for multiply by KM1 the scale-up factor that is used for PID control after 0.6)
K
P2, K
I2, K
D2Parameter tuning method is: the dead band value of setting PID control is 0.05mm, but adopts Ya Ge-Ni scholar's method, at first puts K
D2=K
I2=0, this moment, controller was a proportional controller, by in supervisory system, the setting opening value of throttling valve being made as less than throttling valve actual aperture degree value, even e (t)＜0, increase system proportional coefficient K then until system's starting oscillation, make system be in negative step response, the scaling up coefficient is until system's starting oscillation then, and record scale-up factor at this moment is Km
2, K
P2, K
I2, K
D2Parameter is calculated as follows:
K
P2＝0.6K
m2 ω in the formula
mBe oscillation frequency.
Use the big flow water throttle valve control system of this method, comprise big flow water throttling valve and fluid power system thereof, status signal detection system, PLC control system, host computer real-time monitoring system, and adopt the industrial field bus technology to realize the totally digitilized communication height of system signal.
What described system adopted is directly numeral input, and simulation rod figure regulates and numeral shows the mode of operation that combines.Before the precise figures amount input that can realize throttling valve is set opening degree and detected actual aperture degree (digital quantity input) and the valve, (this signal is used to the setting opening degree that reference is provided to downstream pressure, be the analog quantity input) combination, realization is to the accurate closed-loop control of the digitizing of throttling valve valve core opening degree, and its control accuracy is at 0.1mm.
Described big flow water throttle valve control system, the displacement detecting scope of throttling valve spool is 0～60mm, at its asymmetric dynamic characteristic in spool rising and decline process, in order in rising and decline process, all to obtain short adjustment time and low overshoot, in control system, throttling valve opening and closing process is provided with different parameters by experiment, it is adopted the asymmetric dynamic parameter regulation, adopt the Ziegler-Nichols (method of Ya Ge-Ni Keshifa), it is carried out parameter tuning (process of adjusting is seen specific embodiments in detail), thereby make throttling valve in the opening and closing process, all have comparatively ideal dynamic perfromance, learn that by experiment throttling valve is in opening process, its response time is 0.6s, non-overshoot almost, adopt the asymmetric dynamic parameter to be provided with and adjusting, solving throttling valve can different problem in the dynamic perfromance of the process spool of opening and closing.
Described big flow water throttle valve control system detects the valve core opening degree shift value by digital high precision magnetostrictive displacement sensor.
Described big flow water throttle valve control system is characterized in that, adopts pressure sensor is gathered pressure reduction before and after the throttling valve simultaneously, and this pressure reduction has certain reference role to the throttle valve opening setting value.
Described big flow water throttle valve control system is characterized in that, adopts Profibus industrial field bus technology to realize the totally digitilized communication of system's detection signal, control signal.
The accurate control mode of a kind of big flow water throttling valve, it is characterized in that by regulating the input current of guide proportion reversal valve, the position of piston rod in the accurate control ratio servo-cylinder, drive big flow water throttling valve valve core movement by piston rod again, thereby accurately control the position of this valve core, finally realize the accurate control of its flow.
Described big flow water throttling valve, the liquid flow point by water inlet is a two-way, the runner that forms between spool and the valve cup of leading up to is communicated with water delivering orifice.Another road is communicated with water throttling valve epicoele by the pipeline on the valve body, with the opening pressure of balance valve core.
Between spool and the valve cup, all directly seal between spool and the gland, efficiently solve the problem that the water throttling valve leaks with O-ring seal.Water throttling valve spool upper end links to each other with the in-oil cylinder piston rod of proportional servo by being threaded, and directly drives water throttling valve valve core movement by the motion of piston rod.The magnetic stretching displacement transducer is installed on piston rod.
Advantage of the present invention and effect:
The present invention has designed a kind of big latus rectum, big flow water throttling valve accuracy control method, this method is applied on the control system transformation project of 125MN extruder, be used to control extrusion speed, project is passed through to check and accept in March, 2008 smoothly, the production practice over one year operation shows, throttling valve overcurrent flow is linear approximate relationship with the variation of valve port opening, explanation fluctuations in discharge in whole range of adjustment is even, the trace adjusting function is good, throttling valve spool aperture dynamic response characteristic curve such as Fig. 5, horizontal ordinate among the figure is sampling time (s), as shown in Figure 5 the throttling valve spool displacement to the response time of pilot valve core step signal about 0.6s, non-overshoot almost, control accuracy is at 0.1mm.Efficiently solve this press originally because of the production efficiency that factors such as extrusion speed instability, poor controllability cause is low, hang down problem die life.
Description of drawings
Fig. 1 is water throttling valve and accessory structure synoptic diagram thereof;
Fig. 1 label declaration:
1, valve seat 2, remove working cylinder 3, spool 4, proportional cylinder
5, piston rod 6, displacement of valve rod pick-up unit 7, first control port
8, second control port 9, from water under high pressure
Fig. 2 is electric control structure figure;
Fig. 3 is big flow water throttling valve spool position control block diagram;
Fig. 4 is big flow water throttling valve fluid power system hydraulic schematic diagram;
Fig. 4 label declaration:
10, throttling oil pump 11, DN40 guide's electro-hydraulic proportional flow valve
12, DN80 guide's electro-hydraulic proportional flow valve 13, high-pressure water pipeline 14, upstream pressure detect table 15, DN40 water throttling valve 16, DN40 proportional cylinder 17, DN80 water throttling valve
18, DN80 proportional cylinder 19, downstream pressure detect table 20, main control divider 21, main working cylinder
22, moved cross beam
Fig. 5 is the dynamic response curve figure in the actual application of big flow water throttling valve spool in opening process.
Embodiment
Embodiment 1:
Fig. 2 has described the big flow water of the present invention throttle valve control system and has formed structure, comprising big flow water throttling valve and fluid power system thereof, status signal detection system, PLC control system, host computer (touch-screen) real-time monitoring system.
The operator can accurately set the throttling valve opening degree with the digital quantity form on host computer (touch-screen) supervisory system, and can regulate continuously it by simulating excellent figure according to actual conditions, also can monitor in real time by supervisory system detect throttling valve actual aperture degree (digital quantity input) by the magnetic stretching displacement transducer, to set opening degree and actual aperture degree by the PLC program and obtain a signal difference after relatively, with this signal difference input pid function block, a curtage signal that obtains behind the passing ratio amplifier, go to control the flow and the direction of guide's electro-hydraulic proportional valve again by this electric signal, by the definite direction of passing through the fluid of pilot valve of the direction of signal difference, determine the size of pilot valve fluid flow by the signal extent, in Fig. 4, when pilot valve (12) (has been mentioned two water valves of DN40 and DN80 among Fig. 4, be used for sectional-regulated speed, the present invention studies the water throttling valve of DN80, water valve for DN40 does not describe in detail) the right side electromagnet gets when electric, guide's control is by entering proportional cylinder by second control port (seeing 8 in the accompanying drawing 1), make on the piston rod and move, water throttling valve spool upper end links to each other with the in-oil cylinder piston rod of proportional servo by being threaded, motion by piston rod directly drives water throttling valve valve core movement, therefore, when pilot valve right side electromagnet gets when electric, move on the water throttling valve spool, the throttling valve opening degree increases, and the valve through-current capacity increases.
Thereby the throttling valve spool position is realized accurate closed-loop control, and its control block diagram as shown in Figure 3.[displacement transducer be used for side valve core opening degree value]
Gordian technique of the present invention is how to obtain the input electrical signal of guide's electro-hydraulic proportional valve, it is by actual aperture degree and given opening degree difference gained behind pid function block and proportional amplifier again that the front has been mentioned, so the parameter setting to pid function block is a gordian technique of the present invention, because throttling valve spool and other follow-up unit self gravitation and spool, between piston rod and the counterpart with the influence of friction force, throttling valve can be different in the dynamic perfromance of the process spool of opening and closing, promptly this system is an asymmetric dynamic system, at this feature, in control system, throttling valve opening and closing process is provided with different parameters by experiment.
The value of PID controller parameter is for short response time t is provided
SWith low overshoot M
S, but corresponding positive and negative step response is different, this point conforms with normal logic.The problem of Chu Xianing is the moment of how determining when needing the controller parameter exchange thus.DYa (t)/dt (Ya (t) is meant throttling valve actual aperture degree here) can be the standard of a reference.But, because the Dead Time of equipment dYa (t) response can cause the delay of dYa (t)/dt reaction.Just because of this, the value of control system in the previous parameter of timing period just depended in the conversion of controller parameter value.So, just may increase the uncertainty of control system running.
The change of Ya (t) directly affects the value of e (t) (e (t) is for setting the difference of opening degree and actual aperture degree).Therefore, the performance of e (t) can be considered as the indicator of control system state, and as e (t) when changing, controlled variable also should change.According to this thinking, be positive and negative at e (t), under the different situation of each parameter value, the algorithm of PID control can be represented with following formula:
K
p(t)＝K
p1，K
i(τ)＝K
i1，K
d(t)＝K
d1，|e(t)≥0 (1)
K
p(t)＝K
p2，K
i(τ)＝K
i2，K
d(t)＝K
d2，|e(t)＜0
K wherein
P1, K
I1, K
D1And K
P2, K
I2, K
D2For e (t) gets ratio when positive and negative, integration, derivative constant.t
0Initial point for the formula timing.As e (t) when symbol changes, ratio, integration, three constants of differential also can change separately.Therefore, ratio, integration, differential are not real constants, but in formula (1), change in time.
In the ordinary course of things, getting positive and negatively for e (t), is different based on the PID controller of formula (1) algorithm to the influence of equipment, that is to say that this PID controller is asymmetric.
The parameter adjustment process is as follows:
1) requiring the dead band value of setting pid control function piece according to system accuracy is 0.05mm.
2) adopt the Ziegler-Nichols method, at first put K
D1=K
I1=0, this moment, system was that a PID controller just is a proportional controller, by in supervisory system, the setting opening value of throttling valve being made as greater than throttling valve actual aperture degree value, even e (t)＞0, increase system proportional coefficient K then until system's starting oscillation, record scale-up factor K at this moment is Km
1, K
P1, K
I1, K
D1Parameter is calculated as follows:
K
P1＝0.6K
m1
In the formula, Km
1K value during for system's starting oscillation; ω
mBe oscillation frequency, by experiment, the Km of system when drawing the throttling valve unlatching
1=15, ω
m=4 π rad/s, using the Z-N equation then [is K
P=0.6K
m ] obtain parameter.:
K
P1＝9，K
i1＝36，K
d1＝0.6；
Under this parameter regulation, open aperture real response performance graph by the throttling valve of reading in the host computer and see Fig. 5, as can be seen, throttling valve spool displacement simulation curve as can be known the throttling valve spool displacement to response time of pilot valve core step signal about 0.6s, owing in real system, adopted asymmetric PID control strategy to make the basic non-overshoot of system.
Equally throttling valve is adopted same parameter adjustment method in closing closed procedure, promptly use Ziegler-Nichols experimental technique (Ya Ge-Ni Keshifa), at first put K
D2=K
I2=0, by in supervisory system, the setting opening value of throttling valve being made as less than throttling valve actual aperture degree value, even e (t)＜0, increase system proportional coefficient K then until system's starting oscillation, make system be in negative step response, the scaling up coefficient is until system's starting oscillation then, and record scale-up factor at this moment is Km
2, K
P2, K
I2, K
D2Parameter is calculated as follows:
K
P2＝0.6K
m2
By experiment, the K value K of throttling valve when system begins stable oscillation stationary vibration to occur when closing
M2=13, ω
m=4 π rad/s get according to the Ziegler-Nichols equation again:
K
P2＝8，K
i2＝32，K
d2＝0.8。
Claims (2)
1. the control method of an opening of large flow throttle valve for water, it is characterized in that, position by piston rod in the input current control ratio servo-cylinder of regulating guide's electro-hydraulic proportional flow valve, piston rod and water throttling valve spool are fixedly connected, thereby directly drive the valve core movement of big flow water throttling valve by the motion of piston rod, the final accurate control that realizes the opening degree of big flow water throttling valve;
Adopt the PID control method of closed loop asymmetric in the control procedure, input quantity is given opening of large flow throttle valve for water value, feedback quantity is the opening of large flow throttle valve for water value of detected reality, the poor e (t) of the given opening of large flow throttle valve for water value and the opening of large flow throttle valve for water value of detected reality is input in the PID controller, and PID controller output current signal is given guide's electro-hydraulic proportional flow valve.
2. the control method of opening of large flow throttle valve for water according to claim 1 is characterized in that, described PID controller adopts asymmetry parameter, and concrete parameter tuning process is:
If K
P1, K
I1, K
D1And K
P2, K
I2, K
D2Be e (t) ratio when getting positive and negative respectively, integration, derivative constant;
K
P1, K
I1, K
D1Parameter tuning method is: the dead band value of setting PID control is 0.05mm, but adopts Ya Ge-Ni scholar's method, at first puts K
D1=K
I1=0, independent resize ratio COEFFICIENT K, this moment, controller just was a proportional controller, by in supervisory system, given opening of large flow throttle valve for water value being made as greater than throttling valve actual aperture degree value, even e (t)＞0, increase system proportional coefficient K then until system's starting oscillation, record scale-up factor K at this moment is Km
1, K then
P1, K
I1, K
D1Parameter is calculated as follows:
K
P1=0.6K
M1 
ω in the formula
M1Be K
P1, K
I1, K
D1Oscillation frequency during parameter tuning;
K
P2, K
I2, K
D2Parameter tuning method is: the dead band value of setting PID control is 0.05mm, but adopts Ya Ge-Ni scholar's method, at first puts K
D2=K
I2=0, this moment, controller was a proportional controller, by in supervisory system, the setting opening value of throttling valve being made as less than throttling valve actual aperture degree value, even e (t)＜0, increase system proportional coefficient K then until system's starting oscillation, make system be in negative step response, record scale-up factor at this moment is Km
2, K
P2, K
I2, K
D2Parameter is calculated as follows:
K
P2=0.6K
M2 
ω in the formula
M2Be K
P2, K
I2, K
D2Oscillation frequency during parameter tuning.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100440142A CN101634862B (en) | 2009-07-31 | 2009-07-31 | Control method of opening of large flow throttle valve for water |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100440142A CN101634862B (en) | 2009-07-31 | 2009-07-31 | Control method of opening of large flow throttle valve for water |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101634862A CN101634862A (en) | 2010-01-27 |
| CN101634862B true CN101634862B (en) | 2011-05-04 |
Family
ID=41594073
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009100440142A Expired - Fee Related CN101634862B (en) | 2009-07-31 | 2009-07-31 | Control method of opening of large flow throttle valve for water |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN101634862B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102536954A (en) * | 2011-12-24 | 2012-07-04 | 大连交通大学 | Piston-type multi-stage hydraulic cylinder control system |
| CN103605312A (en) * | 2013-10-12 | 2014-02-26 | 楚天科技股份有限公司 | Servo closed loop control system for pressure-plunger oil cylinder of freeze dryer slab |
Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102541098B (en) * | 2012-01-10 | 2013-08-07 | 江苏科技大学 | Electric liquid linear displacement servo system |
| CN104088842B (en) * | 2014-06-30 | 2016-05-11 | 武汉船用机械有限责任公司 | Automatic identification and compensation method and the system in a kind of proportional direction valve control dead band |
| US10317304B2 (en) * | 2014-12-23 | 2019-06-11 | Scs Concept S.R.L. | Screwdriver test bench |
| RS58241B1 (en) | 2014-12-23 | 2019-03-29 | Scs Concept S R L | Screwdriver test bench with improved braking system |
| CN104847715B (en) * | 2015-04-23 | 2017-01-25 | 中南大学 | Control method for asymmetric electric-hydraulic proportional system based on model transferring |
| CN105706864A (en) * | 2015-09-18 | 2016-06-29 | 薛杨 | Pump and valve integrated single-motor double-acting pressure flow precise control valve for flower watering |
| CN107191154B (en) * | 2016-03-15 | 2020-07-31 | 中国石油化工股份有限公司 | Wellhead back pressure regulating method and device |
| CN105824781A (en) * | 2016-04-06 | 2016-08-03 | 北方民族大学 | Method and system for acquiring PID (Proportion Integration Differentiation) self-tuning parameter of positioner |
| CN106556676A (en) * | 2016-10-27 | 2017-04-05 | 中法渤海地质服务有限公司 | A kind of detection means and detection method for multi-channel gas |
| CN107143549A (en) * | 2017-05-25 | 2017-09-08 | 广东伟业铝厂集团有限公司 | A kind of servo-control system based on extruding production technology |
| CN107102538A (en) * | 2017-06-21 | 2017-08-29 | 利穗科技(苏州)有限公司 | A kind of flow correction method matched somebody with somebody in liquid layer analysis system |
| CN108195574B (en) * | 2017-12-27 | 2019-12-10 | 浙江工业大学 | control valve position abnormal oscillation experimental method |
-
2009
- 2009-07-31 CN CN2009100440142A patent/CN101634862B/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102536954A (en) * | 2011-12-24 | 2012-07-04 | 大连交通大学 | Piston-type multi-stage hydraulic cylinder control system |
| CN103605312A (en) * | 2013-10-12 | 2014-02-26 | 楚天科技股份有限公司 | Servo closed loop control system for pressure-plunger oil cylinder of freeze dryer slab |
| CN103605312B (en) * | 2013-10-12 | 2016-04-13 | 楚天科技股份有限公司 | The servo closed control system of freeze dryer flaggy tamponade oil cylinder |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101634862A (en) | 2010-01-27 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101634862B (en) | Control method of opening of large flow throttle valve for water | |
| CN105700347B (en) | A kind of hydraulic motor default capabilities tracking and controlling method containing Hysteresis compensation | |
| CN201225264Y (en) | Clearance stepless adjusting device of piston reciprocating compressor | |
| CN109595223B (en) | Control method of asymmetric electro-hydraulic proportional system based on precise modeling of proportional valve | |
| CN104483111B (en) | All-hydraulic steering gear test system | |
| CN209244950U (en) | Double valve control cylinder mode position synchronization control devices | |
| CN107542727B (en) | A kind of slide valve pair hydraulic detection device and its detection method | |
| CN102886917B (en) | Hydraulic servo control system for efficiently improving pressing precision of powder-forming hydraulic machine | |
| CN104179740A (en) | Loading method of double-jacking-cylinder structure and hydraulic system of double-jacking-cylinder structure | |
| CN101773947A (en) | Digital hydraulic extruder speed control system and method | |
| CN204594548U (en) | A kind of wide range tandem piston formula liquid flow standard device | |
| CN202091298U (en) | Bulk flow and high frequency response electrohydraulic vibrating device based on parallel connection of servo valves | |
| Wang et al. | Performance improvement of a two-stage proportional valve with internal hydraulic position feedback | |
| CN102380569A (en) | Control method for setting constant speed, constant strain and variable strain process pressing curve | |
| CN102519669B (en) | Pressure fluctuation calibrating device of pressure or differential pressure sensor and calibrating method thereof | |
| CN104949283A (en) | Air valve adjusting method and system for controlling air volume | |
| CN117167510B (en) | Regulating valve and flow regulating system | |
| RU2542254C2 (en) | Variable flow rate control by linear pump | |
| CN103008608A (en) | Pressure boost adjusting device and method based on on-line control of die-casting machine | |
| CN109695598B (en) | Water hydraulic motor rotating speed control system and method | |
| CN101908287A (en) | Experimental facility for demonstrating dynamic characteristics of integration variable process | |
| CN116007716A (en) | Measuring device and measuring method for high-stability tiny liquid flow source | |
| CN106884831A (en) | A kind of hydraulic circuit of solid-liquid engine calibrated in situ power source | |
| CN113533135B (en) | Flow control method based on non-Newtonian fluid rheological property test system | |
| CN103344373A (en) | Method for carrying out pressure fluctuation calibration on pressure sensor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20110504 |