CN101598232B - Electro-hydraulic driver of control valve - Google Patents
Electro-hydraulic driver of control valve Download PDFInfo
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- CN101598232B CN101598232B CN2009100173086A CN200910017308A CN101598232B CN 101598232 B CN101598232 B CN 101598232B CN 2009100173086 A CN2009100173086 A CN 2009100173086A CN 200910017308 A CN200910017308 A CN 200910017308A CN 101598232 B CN101598232 B CN 101598232B
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Abstract
The invention provides an electro-hydraulic driver of a control valve, which comprises a hydraulic driving system, a pressure sensor, a flow sensor, a position sensor and a control unit; wherein, the hydraulic driving system is used for driving a valve core of the control valve and comprises a bidirectional driving cylinder, a directional control valve, a three-position four-way reversing valve, an energy accumulator, a servo motor and a bidirectional gear pump; the pressure sensor and the flow sensor are installed on a fluid output pipeline, are used for detecting the pressure and the flow of the output fluid in the pipeline and are connected with the control unit; the position sensor is used for detecting the valve core position of the control valve to be controlled and is connected with the control unit. The electro-hydraulic driver realizes that hydraulic oil can flow out of an oil outlet cavity and directly enter an oil inlet cavity without passing through an oil tank, and has simple and compact structure; the motor and the oil pump do not need to continuously run but operate intermittently, which can not only save energy but also prolong the service life of the system, thus realizing stable operation for extra-long time and quick response of the control valve with high reliability.
Description
Technical field
The present invention relates to a kind of controlling device of big flow hydrodynamic pressure control, belong to the control valve technical field.
Background technique
The gas turbine generator group that steel mill's circulating generation engineering adopts requires the gas pressure of input stable.Because technology, safety and cost, the voltage stabilizing of coal gas all adopt pneumatic pressure-regulating valve to realize at present.The gas pressure fluctuation is big, can cause serious surge.For preventing surge, pneumatic pressure-regulating valve must be able to respond fast, opens or closes fast.Coke oven and the blast furnace mixed gas delivery volume of importing every gas turbine are bigger, per hour can reach tens thousand of cubic meters.Under so big flow, realize that by common large-scale pneumatic pressure regulator valve pressure stability, the quick response of realization are very difficult, main cause is because dynamic response is slow, hysteresis.Pressure transient is major reason and the hidden danger that causes power generating equipment to be shut down.
Tradition large-scale pressure regulator valve low-response and response lag can not adapt to the pressure stability of gas of high flow rate in the circulating generation engineering.The modulating valve response time depends primarily on actuator.Actuator commonly used has pneumatic and electric actuator.Pneumatic actuator adopts pressurized air or the nitrogen source that is used as power, and yaw stiffness is poor, is unsuitable for response and big actuator fast.Electric actuator is made up of motor, reduction gear box, control box etc., because motor will be through slowing down actuator's speed even also lower than pneumatic actuator.When realizing big thrust, electric actuator is bulky, and the structure of its sealing can produce heat, the Security reduction.The dynamic characteristic and the dynamic response time of actuator's properties influence whole system.The pressure regulator valve response lag then depends primarily on the hysteresis characteristic of system, i.e. the influence in dead band, and friction is one of principal element that influences in the dead band.Common hydraulic driving system is a complex appts that has a bigger fuel tank normally, and motor and oil pump need continuous running, are unfavorable for energy saving.
Summary of the invention
The present invention is directed to problems such as the dynamic response time that has large-scale pressure regulator valve existence now is slow, response lag, the control valve electro-hydraulic driver that a kind of dynamic response time is fast, can eliminate response lag is provided, make it be applicable to the pressure control of big flow fluid.
Control valve electro-hydraulic driver of the present invention comprises hydraulic driving system, pressure transducer, flow transducer, position transducer and control unit:
Hydraulic driving system: the spool that is used for drive control valve, comprise two-way function drive cylinder, position control valve, three position four-way directional control valve, accumulator, actuating motor and double-direction gearpump, double-direction gearpump is connected with actuating motor, actuating motor is connected with control unit, the filler opening of double-direction gearpump is connected with accumulator by one-way valve respectively on the one hand with oil outlet, and accumulator is connected with the two-way function drive cylinder by three position four-way directional control valve again; The filler opening of double-direction gearpump directly is connected with the two-way function drive cylinder by position control valve with oil outlet on the other hand, and the two-way function drive cylinder is installed on the control valve that needs control, and the piston in the two-way function drive cylinder is connected with the spool of control valve; Hydraulic oil directly enters oil suction chamber from going out the oil pocket outflow, and the centre does not need through fuel tank.
Pressure transducer and flow transducer: be installed on the pipeline of fluid output, be used for the pressure and the flow of signal piping output fluid, all be connected with control unit;
Position transducer: be installed in two-way function drive cylinder top, be used to detect the valve element position of the control valve that will control, be connected with control unit.
Described position control valve comprises valve body, piston and taper pin, piston is installed in the endoporus of valve body, respectively be provided with one group of oil inlet and outlet in the both sides of piston on the valve body, be equipped with the taper pin that control port communicates between every group of oil inlet and outlet, be provided with spring between taper pin and the valve interior wall.
Above-mentioned control valve electro-hydraulic driver is set the pressure of pipeline operation and flow etc. by control unit (adopt PLC).When the control valve delivery pressure, when flow increases, the pressure flow sensor feeds back to control unit with the variable signal output of pressure, flow, and the control actuating motor starts double-direction gearpump, the piston that promotes the two-way function drive cylinder moves, and turns the opening degree of control valve down.When the control valve delivery pressure, when flow reduces, the pressure flow sensor feeds back to control unit with the variable signal output of pressure, flow, and the control actuating motor starts double-direction gearpump, the piston that promotes the two-way function drive cylinder moves, and transfers the opening degree of big control valve.Detect the valve element position of the control valve that will control by position transducer.
The present invention drives by electric liquid, and traditional relatively pneumatic actuator and electric actuator have that stroke is big, thrust or characteristics such as moment is big, the response time is fast, highly sensitive, mechanism's compactness.By the automatic controlled hydraulic system of control unit, can bring into play the advantage that electronic control response speed is fast, the hydraulic pressure ouput force is big like this, also can realize the quick response of control valve, improve the reliability of control valve.This control valve electro-hydraulic driver can realize that hydraulic oil directly enters oil suction chamber from going out the oil pocket outflow, and the centre does not need through fuel tank, only needs less fuel tank.The whole control valve electro-hydraulic driver element is few, simple and compact for structure, and cost is low.The motor of hydraulic driving system and oil pump do not need continuous running, and discontinuous operation in energy-conservation, can also prolong the life-span of system, realize ultra-long time stable operation, have high reliability.The present invention is specially adapted to the adjusting control of gas pressure in steel mill's circulating generation engineering, also can be suitable for the adjusting of fluids such as thermal power generation, nuclear power, chemical industry.
Description of drawings
Fig. 1 is a structural principle schematic representation of the present invention.
Fig. 2 is a control principle schematic representation of the present invention.
Fig. 3 is the structural representation of position control valve among the present invention.
Wherein: 1, two-way function drive cylinder, 2, position control valve, 3, three position four-way directional control valve, 4, accumulator, 5, fuel tank, 6, actuating motor, 7, double-direction gearpump, 9, one-way valve, 10, one-way valve, 11, upper piston rod, 12, hydraulic fluid port, 13, lower piston rod, 14, piston, 15, hydraulic fluid port, 16, support, 17, valve body, 18, spool, 19, spring, 20, cover, 21, piston, 22, taper pin, 23, spring, 24, the position control valve body, 25, taper pin.
Embodiment
Control valve electro-hydraulic driver of the present invention comprises hydraulic driving system, pressure transducer, flow transducer, position transducer and control unit, and hydraulic driving part, pressure transducer, flow transducer and position transducer all are connected (referring to Fig. 2) with control unit.
As shown in Figure 1, hydraulic driving system mainly comprises two-way function drive cylinder 1, position control valve 2, three position four-way directional control valve 3, accumulator 4, actuating motor 6 and double-direction gearpump 7, double-direction gearpump 7 is connected with actuating motor 6, by actuating motor 6 control runnings, actuating motor 6 is connected with control unit (PLC).The filler opening of double-direction gearpump 7 is connected with accumulator 4 with one-way valve 10 by one-way valve 9 respectively on the one hand with oil outlet, and accumulator 4 is connected with two-way function drive cylinder 1 by three position four-way directional control valve 3 again; The filler opening of double-direction gearpump 7 directly is connected with two-way function drive cylinder 1 by position control valve 2 with oil outlet on the other hand.Two-way function drive cylinder 1 is fixedly mounted on by support 16 on the valve body 17 of the control valve that needs control, and the piston 14 in the two-way function drive cylinder 1 is connected with the spool 18 of control valve by lower piston rod 13.Accumulator 4 can be fixedly mounted on the housing of two-way function drive cylinder 1.
Actuating motor 6 drives double-direction gearpump 7 and rotates, by fuel tank 5 oil suctions, when double-direction gearpump 7 from left to right during fuel feeding, hydraulic oil passes through one-way valve 9 on the one hand to accumulator 4 fuel feeding, and the hydraulic fluid port A by position control valve 2 enters on the one hand, exports from hydraulic fluid port B, enter the upper chamber of two-way function drive cylinder 1 by hydraulic fluid port 12 through oil pipe, the piston 14 that promotes two-way function drive cylinder 1 is descending, and it is descending that the lower piston rod 13 that is connected piston 14 lower ends promotes the spool 18 of control valves, reduces the valve openings degree.When double-direction gearpump 7 right-to-left fuel feeding, hydraulic oil passes through one-way valve 10 on the one hand to accumulator 4 fuel feeding, hydraulic fluid port C by position control valve 2 enters on the one hand, export from hydraulic fluid port D, enter the lower cavity of two-way function drive cylinder 1 by hydraulic fluid port 15 through oil pipe, the piston 14 that promotes two-way function drive cylinder 1 is up, and the spool 18 of lower piston rod 13 drive control valves is up, increases the valve openings degree.Above two-way function drive cylinder 1, be provided with position transducer, piston 14 upper ends of two-way function drive cylinder 1 are connected with upper piston rod 11, when piston 14 moves up and down, this position transducer detects the displacement distance of upper piston rod 11, and testing result fed back to control unit, this is apart from the opening degree that has reacted control valve, and control unit is according to the working order of feedback signal decision actuating motor 6.
Also can be by accumulator 4 to two-way function drive cylinder 1 fuel feeding, when three position four-way directional control valve 3 was in meta, accumulator 4 was the energy storage state.When three position four-way directional control valve 3 is in right position, accumulator 4 is to the upper chamber fuel feeding of two-way function drive cylinder 1, it is descending fast to promote drive cylinder piston 14, when three position four-way directional control valve 3 is in position, a left side, accumulator 4 promotes drive cylinder piston fast uplink to the lower cavity fuel feeding of two-way function drive cylinder 1.
The structure of position control valve 2 as shown in Figure 3.Comprise valve body 24, piston 21, piston 21 is installed in the endoporus of valve body 24, respectively be provided with one group of oil inlet and outlet in the both sides of piston 21 on the valve body 24, be hydraulic fluid port A and hydraulic fluid port B and hydraulic fluid port C and hydraulic fluid port D, be equipped with the taper pin that control communicates between every group of oil inlet and outlet, i.e. taper pin 22 and taper pin 25, taper pin 25 is installed in the cover 20, be provided with spring 19 in the cover 20, taper pin 22 also is installed in the cover, is provided with spring 23 in this cover.When hydraulic fluid port A oil-feed, promote taper pin 22 pressure springs 23 and move to right, hydraulic fluid port A communicates with hydraulic fluid port B; Promote piston 21 simultaneously and be moved to the left, promote taper pin 25 pressure springs 19 and move to left, hydraulic fluid port C communicates with hydraulic fluid port D.When hydraulic fluid port C oil-feed, promote taper pin 25 pressure springs 19 and move to left, hydraulic fluid port C communicates with hydraulic fluid port D; Promote piston 21 simultaneously and move right, promote taper pin 22 pressure springs 23 and move to right, hydraulic fluid port A communicates with hydraulic fluid port B.
Fig. 2 has provided control principle of the present invention, and control unit adopts programmable controller (PLC).Pressure transducer and flow transducer are installed on the pipeline, are used for the pressure and the flow of signal piping output fluid.Set the pressure of pipeline operation and flow etc. by control unit (PLC), pressure transducer and flow transducer arrive control unit (PLC) with the signal feed back that collects, compare with setting value, according to comparison situation control unit (PLC) control hydraulic driving system the spool aperture of control valve is regulated, with flow and the pressure of stablizing control valve.When the control valve delivery pressure, when flow increases, the pressure flow sensor feeds back to control unit with the variable signal output of pressure, flow, and control actuating motor 6 starts double-direction gearpump 7, the piston 14 that promotes two-way function drive cylinder 1 moves, and turns the opening degree of control valve down.When the control valve delivery pressure, when flow reduces, the pressure flow sensor feeds back to control unit with the variable signal output of pressure, flow, and control actuating motor 6 starts double-direction gearpump 7, the piston 14 that promotes two-way function drive cylinder 1 moves, and transfers the opening degree of big control valve.Above the upper piston rod 11 of two-way function drive cylinder 1, the position transducer that is connected with control unit is installed, detects the valve element position of the control valve that will control by position transducer.In the course of the work, owing to obstruction, wearing and tearing, distortion etc., the working state of control valve can change, and the employing mixing control method makes full use of intelligent control algorithm and use experience is finished intelligent diagnostics.
The present invention adopts Driven by Hydraulic Cylinder control valve spool technology, hydraulic driving system discontinuous operation.When input signal and control valve aperture balance, two-way function drive cylinder 1 quits work, and does not need electric energy to keep this equilibrium position.
The present invention passes through hydraulic driving, and by the automatic controlled hydraulic system of control unit, can bring into play the advantage that electronic control response speed is fast, the hydraulic pressure ouput force is big like this, also can realize the quick response of control valve, improves the reliability of control valve.The hydraulic driving system discontinuous operation in energy-conservation, can also prolong the life-span of system, realizes ultra-long time stable operation, has high reliability.
The present invention also can be provided with tar and stop up intelligent self-diagnosable system, and by detecting pressure, tolerance or the oscillating signal of control valve, whether the diagnosis control valve system exists faults such as tar obstruction, determines reasonably to shut down maintenance opportunity.By detecting pressure, the tolerance of control valve, analyze the state of modulating valve.According to the state of large-scale pressure controlled valve, realize the automatic adjustment of zero point and stroke, optimize response sensitivity, eliminate its influence.
Claims (1)
1. a control valve electro-hydraulic driver comprises hydraulic driving system, pressure transducer, flow transducer, position transducer and control unit, it is characterized in that:
Hydraulic driving system: the spool that is used for drive control valve, comprise two-way function drive cylinder, position control valve, three position four-way directional control valve, accumulator, actuating motor and double-direction gearpump, double-direction gearpump is connected with actuating motor, actuating motor is connected with control unit, the filler opening of double-direction gearpump is connected with accumulator by one-way valve respectively on the one hand with oil outlet, and accumulator is connected with the two-way function drive cylinder by three position four-way directional control valve again; The filler opening of double-direction gearpump directly is connected with the two-way function drive cylinder by position control valve with oil outlet on the other hand, and the two-way function drive cylinder is installed on the control valve that needs control, and the driven plunger in the two-way function drive cylinder is connected with the spool of control valve; Described position control valve comprises valve body, control piston and taper pin, control piston is installed in the endoporus of valve body, respectively be provided with one group of oil inlet and outlet in the both sides of control piston on the valve body, be equipped with the taper pin that this group oil inlet and outlet of control communicates between every group of oil inlet and outlet, be provided with spring between taper pin and the valve interior wall;
Pressure transducer and flow transducer: be installed on the pipeline of fluid output, be used for the pressure and the flow of signal piping output fluid, all be connected with control unit;
Position transducer: be installed in two-way function drive cylinder top, be used to detect the valve element position of the control valve that will control, be connected with control unit.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100173086A CN101598232B (en) | 2009-07-20 | 2009-07-20 | Electro-hydraulic driver of control valve |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100173086A CN101598232B (en) | 2009-07-20 | 2009-07-20 | Electro-hydraulic driver of control valve |
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| CN101598232A CN101598232A (en) | 2009-12-09 |
| CN101598232B true CN101598232B (en) | 2011-01-26 |
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| CN2009100173086A Expired - Fee Related CN101598232B (en) | 2009-07-20 | 2009-07-20 | Electro-hydraulic driver of control valve |
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2009
- 2009-07-20 CN CN2009100173086A patent/CN101598232B/en not_active Expired - Fee Related
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Application publication date: 20091209 Assignee: Yangzhou Hengchun Electronic Co., Ltd. Assignor: Shandong University Contract record no.: 2016320000033 Denomination of invention: Electro-hydraulic driver of control valve Granted publication date: 20110126 License type: Exclusive License Record date: 20160224 |
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