CN101660554A - Fully hydraulic servo dynamic balance exhaust head control system - Google Patents
Fully hydraulic servo dynamic balance exhaust head control system Download PDFInfo
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- CN101660554A CN101660554A CN200910023836A CN200910023836A CN101660554A CN 101660554 A CN101660554 A CN 101660554A CN 200910023836 A CN200910023836 A CN 200910023836A CN 200910023836 A CN200910023836 A CN 200910023836A CN 101660554 A CN101660554 A CN 101660554A
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Abstract
The invention relates to the exhaust head control of a steel pipe hydrostatical testing machine in the hydraulic servo control technology, in particular to a fully hydraulic servo dynamic balance exhaust head control system, at least comprising an exhaust head displacement sensor, a test water pressure sensor, a control mechanism and an oil cylinder mechanism. The fully hydraulic servo dynamic balance exhaust head control system is characterized in that the movement of an exhaust head between a sealing working position and loading and unloading positions in a steel pipe is realized through thecontrol mechanism to control the oil cylinder mechanism according to position signals provided by the exhaust head displacement sensor; signals of the test water pressure sensor and balance oil cylinder pressure sensor of the oil cylinder mechanism are detected through the control mechanism; and the acting force of pressure test water borne by the exhaust head during pressure test is dynamicallybalanced in real time; and the position change of the exhaust head during pressure test is controlled according to the real-time position signals provided by the exhaust head displacement sensor. Theinvention provides the fully hydraulic servo dynamic balance exhaust head control system with fast response speed, high control accuracy, safe and reliable performance, low equipment failure rate andsafe and convenient maintenance and operation.
Description
Technical field
The present invention relates to the exhaust head control, particularly fully hydraulic servo dynamic balance exhaust head control system of the steel pipe hydrostatic tester of Hydraulic Servo Control Technology.
Background technique
The exhaust head of steel pipe hydrostatic tester is a vitals of steel pipe hydrostatic tester, its main function is: 1. according to tested outer diameter of steel pipes specification, corresponding Pressure test mould and pressure testing special sealing ring are installed, are realized the sealing of tested steel pipe exhaust head end test water; 2. be installed on the action of the outlet valve on the exhaust head by control, realize that air is in time got rid of in the tested steel pipe, guarantee that the filling of pressure testing water fully reaches pressure testing process safety and carries out.
Exhaust head must move forward and backward between steel pipe material loading discharging position and pressure testing position along tested steel pipe length direction, so that tested steel pipe material loading discharging and satisfy the needs of different length steel tube pressure-measuring, realizes that steel tube pressure-measuring process high-efficiency and continuous carries out.
Moving of existing steel pipe hydrostatic tester exhaust head generally adopted oil hydraulic motor or motoring screw-nut body to realize, and born the active force of pressure testing process testing water to exhaust head by feed screw nut.The deformation of the rapid change of test water pressure and pressure testing process steel pipe very easily causes leading screw and nut locking, in case this kind phenomenon occurs, high-potting water in the not only tested steel pipe can't safe unloading pressure, and the leading screw and the nut of throwing off locking are very difficult, can't realize the safety in production and convenient maintenance of steel pipe hydrostatic tester.
In view of this kind situation, up-to-date steel pipe hydrostatic tester exhaust head moves uses hydraulic oil cylinder driving instead, but the oil cylinder in the new equipment only is used to realize exhaust head moving between steel pipe material loading discharging position and the seal operation position.In the steel tube pressure-measuring process,, rely on the elastic deformation force of fluid airtight in the oil cylinder to come the active force of blance test water, do any control and no longer the physical location of exhaust head is changed to exhaust head by cutting off the advancing of oil cylinder, oil outlet passage.Because oil cylinder and advance, oil outlet passage can't reach positive confinement, and may be mixed with air in the oil cylinder, this will cause the pressure testing equilibrant deficiency that early stage, oil cylinder provided, exhaust head yielding phenomenon by a relatively large margin appears, aggravated the relative friction between steel pipe and pressure testing special sealing ring, reduce the working life of seal ring, increased plant maintenance and cost of production.Make a concession when serious even the pressure testing seal ring can occur when exhaust head and throw off tested steel pipe and cause industrial accident.
Summary of the invention
The purpose of this invention is to provide that a kind of speed of response is fast, control accuracy is high, performance is safe and reliable, the fully hydraulic servo dynamic balance exhaust head control system that equipment failure rate is low, housekeeping operation is safe and simple.
The object of the present invention is achieved like this, fully hydraulic servo dynamic balance exhaust head control system, at least comprise exhaust head displacement transducer, test water pressure transducer, control mechanism and oil cylinder mechanism, it is characterized in that: the position signal that provides according to the exhaust head displacement transducer, by control mechanism the control of oil cylinder mechanism is realized exhaust head mobile between putting with the upper and lower material level of steel pipe in the seal operation position; Detect the balancing cylinder pressure sensor signal of test water pressure sensor signal and oil cylinder mechanism by control mechanism; In real time dynamic balance exhaust head is at the active force of the suffered pressure testing water of pressure testing process, and according to the real time position signal that the exhaust head displacement transducer provides, the change in location of exhaust head in the pressure testing process controlled.
Two the piston type idle runnings that comprise described oil cylinder mechanism move oil cylinder, plunger type balancing cylinder and fuel tank, and two piston type idle runnings move oil cylinder and realize that the idle running of exhaust head moves, and a plunger type balancing cylinder is realized the transient equiliblium control of exhaust head; Two piston type idle runnings move the left and right sides that oil cylinder is distributed in the plunger type balancing cylinder; The piston type idle running moves the side that oil cylinder and plunger type balancing cylinder are arranged in exhaust head.
Described oil cylinder mechanism also can adopt a piston type idle running to move and balancing cylinder and fuel tank, move and the piston cavity and the rod end chamber of balancing cylinder all have the balancing cylinder pressure transducer in the piston type idle running, by the exhaust head position sensor signal, control system control exhaust head realizes that idle running moves, by signal and the test water pressure sensor signal that the balancing cylinder pressure transducer provides, realize its dynamic stress balance and positioning control.
Described control mechanism comprises high pressure oil pump, servovalve or high frequency sound Proportional valve, liquid-filling valve and PLC or computer; The return opening of servovalve or high frequency sound Proportional valve connects fuel tank, and an actuator port connects the plunger cavity of plunger type balancing cylinder; The low pressure port of liquid-filling valve connects the plunger cavity of fuel tank, high-pressure mouth connection plunger type balancing cylinder; The high pressure oil pump inlet port connects fuel tank, oil outlet is connected with the oil-feed port of servovalve or high frequency sound Proportional valve; PLC or computer are connected with the circuit control system of high pressure oil pump, servovalve or high frequency sound Proportional valve and liquid-filling valve.
Described oil cylinder mechanism comprises that a piston type idle running moves and balancing cylinder and fuel tank; Described control mechanism comprises high pressure oil pump, servovalve or high frequency sound Proportional valve and PLC or computer, the return opening of servovalve or high frequency sound Proportional valve is connected with fuel tank, and two-way control port connects respectively that the piston type idle running moves and the piston cavity and the rod end chamber of balancing cylinder; The high pressure oil pump inlet port connects fuel tank, and the high pressure oil outlet is connected with the oil-feed port of servovalve or high frequency sound Proportional valve; PLC or computer are connected with the circuit control system of high pressure oil pump, servovalve or high frequency sound Proportional valve.
Described piston type idle running moves the concrete parameter of oil cylinder: piston diameter is 125mm; Diameter of piston rod is 90mm; Oil cylinder stroke is 1800mm.
The concrete parameter of described plunger type balancing cylinder is: plunger diameter is 400mm; Oil cylinder stroke is 1800mm.
Described stressed control of the real-time dynamic balance exhaust head of balancing cylinder pressure sensor signal by control mechanism detection test water pressure sensor signal and oil cylinder mechanism is:
According to detected test water pressure, electric PLC or computer calculate the oil liquid pressure (p in the required plunger type balancing cylinder automatically
Required), and the balancing cylinder actual pressure value (p that this required pressure and balancing cylinder pressure transducer are detected
Actual) compare, the difference of supposing these two force value is Δ p=p
Actual-p
Required
When Δ p=0, electric PLC or computer will be kept the openings of sizes of servovalve or high frequency sound Proportional valve and the state of a control of oily flow path direction by control unit, the state that keeps plunger type balancing cylinder actual pressure value to equate with required force value;
When Δ p＞0, the actual pressure value that is the plunger type balancing cylinder is greater than required force value, electric PLC or computer will reduce the openings of sizes of servovalve or high frequency sound Proportional valve or change oily flow path direction by control unit this moment, reduce fuel feeding by servovalve or high frequency sound Proportional valve to the plunger type balancing cylinder, or the part fluid that has more in the plunger type balancing cylinder flow back to fuel tank, reduce the actual oil liquid pressure in the plunger type balancing cylinder, actual oil liquid pressure in the plunger type balancing cylinder is equated, i.e. Δ p=0 with required pressure;
When Δ p＜0, the actual pressure value that is the plunger type balancing cylinder is less than required force value, electric PLC or computer will increase the openings of sizes of servovalve or high frequency sound Proportional valve or change oily flow path direction by control unit this moment, increase fuel feeding by servovalve or high frequency sound Proportional valve to the plunger type balancing cylinder, improve the actual oil liquid pressure in the plunger type balancing cylinder, actual oil liquid pressure in the plunger type balancing cylinder is equated, i.e. Δ p=0 with required pressure.
Advantage of the present invention is: by the variation of dynamic balance exhaust head because of variation in water pressure in the tested steel pipe and caused force-bearing situation of steel pipe deformation and position, control tested steel pipe exhaust head end high pressure water sealing and be within the scope of setting with the steel pipe relative position, the working life of assurance exhaust head end high pressure water sealing and the safety of steel pipe hydrostatic testing process are carried out.The characteristics of this system are the control technique advanced persons, system response time is fast, performance is safe and reliable.The most outstanding advantage is that equipment failure rate is low, housekeeping operation is safe and simple.
Description of drawings
The invention will be further described below in conjunction with embodiment's accompanying drawing
Fig. 1 is the embodiment of the invention 1 structural representation;
Fig. 2 is the embodiment of the invention 2 structural representations.
Among the figure: 1, fuel tank; 2, high pressure oil pump; 3, servovalve or high frequency sound Proportional valve; 4, test water pressure transducer; 5, exhaust head displacement transducer; 6, balancing cylinder pressure transducer; 7, liquid-filling valve; 8, exhaust head; 9, plunger type balancing cylinder; 10, the piston type idle running moves oil cylinder; 11, the piston type idle running moves and balancing cylinder.
Embodiment
Fully hydraulic servo dynamic balance exhaust head control system, at least comprise exhaust head displacement transducer 5, test water pressure transducer 4, control mechanism and oil cylinder mechanism, the position signal that provides according to exhaust head displacement transducer 5 is realized exhaust head 8 mobile between putting with the upper and lower material level of steel pipe in the seal operation position by control mechanism to the control of oil cylinder mechanism; Detect balancing cylinder pressure transducer 6 signals of test water pressure transducer 4 signals and oil cylinder mechanism by control mechanism; In real time dynamic balance exhaust head 8 is at the active force of the suffered pressure testing water of pressure testing process, and according to the real time position signal that exhaust head displacement transducer 5 provides, the change in location of exhaust head 8 in the pressure testing process controlled.
As shown in Figure 1, two the piston type idle runnings that comprise oil cylinder mechanism move oil cylinder 10, a plunger type balancing cylinder 9 and a fuel tank 1, two piston type idle runnings move oil cylinder 10 and realize that the idle running of exhaust head 8 moves, and a plunger type balancing cylinder 9 is realized the transient equiliblium control of exhaust head 8; Two piston type idle runnings move the left and right sides that oil cylinder 10 is distributed in plunger type balancing cylinder 9; The piston type idle running moves the side that oil cylinder 10 and plunger type balancing cylinder 9 are arranged in exhaust head 8.
Two piston type idle runnings of control mechanism control move the idle running of oil cylinder 10 realization exhaust heads 8 and advance, retreat and stop; In the exhaust head 8 idle running moving process, liquid-filling valve 7 is in open mode, realize that the fluid in the fuel tank 1 flows to plunger type balancing cylinder 9 fast, or the fluid in the plunger type balancing cylinder 9 flows back to fuel tank 1 fast.After exhaust head 8 arrived the seal operation positions, two piston type idle runnings moved 10 pairs of exhaust heads 8 of oil cylinder any control action that do not recur, and liquid-filling valve 7 also is in closed condition simultaneously.The stress balance position of exhaust head 8 is realized by high pressure oil pump 2 control servovalves or 9 effects of 3 pairs of plunger type balancing cylinders of high frequency sound Proportional valve fully.
In the steel tube pressure-measuring process, the openings of sizes of servovalve or high frequency sound Proportional valve 3 and oily flow path direction are controlled by electric control unit, according to the fuel feeding that increases, keeps or reduce plunger type balancing cylinder 9, or the unnecessary fluid in the plunger type balancing cylinder 9 are flow back to fuel tank, exhaust head 8 advances, retreats and stop in the realization steel pipe hydrostatic testing process, the balance of control exhaust head 8 force-bearing situations guarantees that the position of exhaust head 8 is within the scope of setting.
Test water pressure transducer 4 is fixed on the passage of test water, detects the pressure size of test water in the tested steel pipe in real time.On exhaust head 8, be fixed with exhaust head displacement transducer 5, be used for detecting in real time the displacement of exhaust head 8.In the steel pipe hydrostatic testing process, owing to be subjected to the effect of test water power to the right in the tested steel pipe, produce movement tendency to the right when exhaust head 8.The size of this active force to the right and movement tendency change with the pressure size of test water.Make 9 pairs of exhaust heads of plunger type balancing cylinder 8 timely " synchronously " that an active force left that adapts with the test water active force is provided, the size of this active force and " synchronously " property (being speed of response) that provides will determine the relative displacement between exhaust head 8 and the tested steel pipe.The size of the active force that 9 pairs of exhaust heads 8 of plunger type balancing cylinder provide depends on the size of plunger type balancing cylinder 9 inner fluid pressure and the dimensional parameters of oil cylinder.Plunger type balancing cylinder 9 is equipped with balancing cylinder pressure transducer 6, is used to detect the actual oil liquid pressure size (p in the plunger type balancing cylinder 9
Actual).
According to detected test water pressure, electric PLC or computer calculate the oil liquid pressure (p in the required plunger type balancing cylinder 9 automatically
Required), and the balancing cylinder actual pressure value (p that this required pressure and compensating cylinder pressure transducer 6 are detected
Actual) compare, the difference of supposing these two force value is Δ p=p
Actual-p
Required
When Δ p=0, electric PLC or computer will be kept the openings of sizes of servovalve or high frequency sound Proportional valve 3 and the state of a control of oily flow path direction by control unit, the state that keeps plunger type balancing cylinder 9 actual pressure value to equate with required force value.
When Δ p＞0, promptly the actual pressure value of plunger type balancing cylinder 9 is greater than required force value.Electric PLC or computer will reduce the openings of sizes of servovalve or high frequency sound Proportional valve 3 or change oily flow path direction by control unit this moment, the fuel feeding that reduces plunger type balancing cylinder 9 by servovalve or high frequency sound Proportional valve 3, or the part fluid that has more in the plunger type balancing cylinder 9 flow back to fuel tank, reduce the actual oil liquid pressure in the plunger type balancing cylinder 9, actual oil liquid pressure in the plunger type balancing cylinder 9 is equated, i.e. Δ p=0 with required pressure.
When Δ p＜0, promptly the actual pressure value of plunger type balancing cylinder 9 is less than required force value.Electric PLC or computer will increase the openings of sizes of servovalve or high frequency sound Proportional valve 3 or change oily flow path direction by control unit this moment, the fuel feeding that increases plunger type balancing cylinder 9 by servovalve or high frequency sound Proportional valve 3, improve the actual oil liquid pressure in the plunger type balancing cylinder 9, actual oil liquid pressure in the plunger type balancing cylinder 9 is equated, i.e. Δ p=0 with required pressure.
Because system detects and organ action execution can't reach absolute " synchronously ", also be the active force of 9 pairs of exhaust heads of plunger type balancing cylinder can't absolute synchronization in the active force of test water to exhaust head 8, add actual size and detect error, exhaust head 8 always produces and moves with respect to the position of tested steel pipe.This relative position amount of movement Δ s can detect by the exhaust head displacement transducer 5 that is fixed on the exhaust head 8.
Electric PLC or computer move size and direction according to exhaust head displacement transducer 5 detected exhaust heads 8 with respect to the position of tested steel pipe, be the numerical value of Δ s and positive and negative, openings of sizes by control servovalve or high frequency sound Proportional valve 3 or change oily flow path direction, control exhaust head 8 are done and made Δ s is zero move.And then the control exhaust head is within the scope of setting in the displacement of whole pressure testing process with respect to tested steel pipe.When fortuitous event appears in the pressure testing process, when exhaust head meets or exceeds a certain limiting value of setting with respect to the displacement of tested steel pipe, control system will be reported to the police automatically and be interrupted steel tube pressure-measuring, prevent that exhaust head 8 from deviating from from tested steel pipe, guarantee equipment operator and equipment self safety.
As shown in Figure 2, providing exhaust head 8 driving oil cylinder is structural representations of plunger type balancing cylinder 9, as different from Example 1: exhaust head 8 adopts a piston type idle running to move and balancing cylinder 11 realizes that its idle running moves, and moves and balancing cylinder 11 realization its dynamic stress balance and positioning control by this piston type idle running.The piston type idle running of exhaust head 8 transient equiliblium control moves and balancing cylinder 11 no liquid-filling valves 7, but is provided with balancing cylinder pressure transducer 6 in its piston cavity and rod end chamber; Servovalve or high frequency sound Proportional valve 3 two-way output are altogether moved with the piston type idle running respectively and the piston cavity and the rod end chamber of balancing cylinder 11 are connected.
When exhaust head 8 idle runnings moved, 3 pairs of piston type idle runnings of servovalve or high frequency sound Proportional valve moved and balancing cylinder 11 does not start to control making usefulness.The piston type idle running is moved and the control of balancing cylinder 11 by general controls element (not shown among Fig. 2), realize that the idle running of exhaust head 8 is advanced, retreated and stops.After exhaust head 8 arrives the seal operation position, in the whole pressure testing process of steel pipe, electric PLC or computer will stop the piston type idle running is moved and the control of balancing cylinder 11 by control unit, and the stress balance of this graduated discharge head 8 and positioning control are moved by high pressure oil pump 2, servovalve or high frequency sound Proportional valve 3, piston type idle running and realization such as balancing cylinder 11 fully.
In the steel tube pressure-measuring process, the openings of sizes of servovalve or high frequency sound Proportional valve 3 and oily flow path direction are controlled by control unit by electric PLC or computer, according to the piston type idle running being moved and the piston cavity of balancing cylinder 11 and rod end chamber carry out fuel feeding or oil extraction control, exhaust head 8 advances, retreats and stop in the realization steel pipe hydrostatic testing process, the balance of control exhaust head 8 force-bearing situations guarantees that the position of exhaust head 8 is within the scope of setting.
Among the present invention, plunger type balancing cylinder 9, piston type idle running move oil cylinder 10, the piston type idle running moves and balancing cylinder 11 design or select for use and should follow following principle:
1) plunger type balancing cylinder 9, piston type idle running move oil cylinder 10 and the piston type idle running moves and the stroke of balancing cylinder 11 should satisfy with batch tested steel pipe extreme length difference and steel pipe feed discharging required along the steel pipe length direction apart from sum.
2) the piston type idle running 10 strength that can provide of oil cylinder are provided should be able to drive exhaust head 8 and does idle running along tested steel pipe length direction and move, and should satisfy required travelling speed.
3) the piston type idle running moves and 11 idle runnings that can provide of balancing cylinder move strength and should be able to drive exhaust head 8 and do idle running along tested steel pipe length direction and move, and should satisfy required travelling speed.
4) the maximum transient equiliblium power that plunger type balancing cylinder 9 and piston type idle running move and 11 of balancing cylinders can provide to exhaust head 8, should determine that to 8 peak powers that can produce of exhaust head this peak power depends on that equipment tries steel pipe specifications parameter and test pressure numerical value according to test water in the tested steel pipe.
The piston type idle running moves oil cylinder 10 concrete parameters: 1. piston diameter: Ф 125mm; 2. diameter of piston rod: Φ 90mm; 3. oil cylinder stroke: S=1800mm.
Plunger type balancing cylinder 9 concrete parameters are: 1. plunger diameter: Ф 400mm; 2. oil cylinder stroke: S=1800mm.
Claims (8)
1, fully hydraulic servo dynamic balance exhaust head control system, at least comprise exhaust head displacement transducer (5), test water pressure transducer (4), control mechanism and oil cylinder mechanism, it is characterized in that: the position signal that provides according to exhaust head displacement transducer (5), by control mechanism the control of oil cylinder mechanism is realized exhaust head (8) mobile between putting with the upper and lower material level of steel pipe in the seal operation position; Detect balancing cylinder pressure transducer (6) signal of test water pressure transducer (4) signal and oil cylinder mechanism by control mechanism; In real time dynamic balance exhaust head (8) is at the active force of the suffered pressure testing water of pressure testing process, and according to the real time position signal that exhaust head displacement transducer (5) provides, the change in location of exhaust head (8) in the pressure testing process controlled.
2, fully hydraulic servo dynamic balance exhaust head control system according to claim 1, it is characterized in that: described oil cylinder mechanism comprises that two piston type idle runnings move oil cylinder (10), a plunger type balancing cylinder (9) and fuel tank (1), two piston type idle runnings move oil cylinder (10) and realize that the idle running of exhaust head (8) moves, and a plunger type balancing cylinder (9) is realized the transient equiliblium control of exhaust head (8); Two piston type idle runnings move the left and right sides that oil cylinder (10) is distributed in plunger type balancing cylinder (9); The piston type idle running moves the side that oil cylinder (10) and plunger type balancing cylinder (9) are arranged in exhaust head (8).
3, fully hydraulic servo dynamic balance exhaust head control system according to claim 1, it is characterized in that: described oil cylinder mechanism also can adopt a piston type idle running to move and balancing cylinder (11) and fuel tank (1), move and the piston cavity and the rod end chamber of balancing cylinder (11) all have balancing cylinder pressure transducer (6) in the piston type idle running, by exhaust head (8) position sensor signal, control system control exhaust head (8) realizes that idle running moves, by signal and test water pressure transducer (4) signal that balancing cylinder pressure transducer (6) provides, realize its dynamic stress balance and positioning control.
4, fully hydraulic servo dynamic balance exhaust head control system according to claim 1 is characterized in that: described control mechanism comprises high pressure oil pump (2), servovalve or high frequency sound Proportional valve (3), liquid-filling valve (7) and PLC or computer; The return opening of servovalve or high frequency sound Proportional valve (3) connects fuel tank (1), and an actuator port connects the plunger cavity of plunger type balancing cylinder (9); The low pressure port of liquid-filling valve (7) connects the plunger cavity of fuel tank (1), high-pressure mouth connection plunger type balancing cylinder (9); High pressure oil pump (2) inlet port connects fuel tank (1), oil outlet is connected with the oil-feed port of servovalve or high frequency sound Proportional valve (3); PLC or computer are connected with the circuit control system of high pressure oil pump (2), servovalve or high frequency sound Proportional valve (3) and liquid-filling valve (7).
5, fully hydraulic servo dynamic balance exhaust head control system according to claim 1 is characterized in that: described oil cylinder mechanism comprises that a piston type idle running moves and balancing cylinder (11) and fuel tank (1); Described control mechanism comprises high pressure oil pump (2), servovalve or high frequency sound Proportional valve (3) and PLC or computer, the return opening of servovalve or high frequency sound Proportional valve (3) is connected with fuel tank (1), and two-way control port connects respectively that the piston type idle running moves and the piston cavity and the rod end chamber of balancing cylinder (11); High pressure oil pump (2) inlet port connects fuel tank (1), and the high pressure oil outlet is connected with the oil-feed port of servovalve or high frequency sound Proportional valve (3); PLC or computer are connected with the circuit control system of high pressure oil pump (2), servovalve or high frequency sound Proportional valve (3).
6, fully hydraulic servo dynamic balance exhaust head control system according to claim 2 is characterized in that: described piston type idle running moves the concrete parameter of oil cylinder (10) and is: piston diameter is 125mm; Diameter of piston rod is 90mm; Oil cylinder stroke is 1800mm.
7, fully hydraulic servo dynamic balance exhaust head control system according to claim 2 is characterized in that: the concrete parameter of described plunger type balancing cylinder (9) is: plunger diameter is 400mm; Oil cylinder stroke is 1800mm.
8, fully hydraulic servo dynamic balance exhaust head control system according to claim 1 is characterized in that: described stressed control of the real-time dynamic balance exhaust head of balancing cylinder pressure transducer (6) signal by control mechanism detection test water pressure transducer (4) signal and oil cylinder mechanism is:
According to detected test water pressure, electric PLC or computer calculate the oil liquid pressure (p in the required plunger type balancing cylinder (9) automatically
Required), and the balancing cylinder actual pressure value (p that this required pressure and balancing cylinder pressure transducer (6) are detected
Actual) compare, the difference of supposing these two force value is Δ p=p
Actual-p
Required
When Δ p=0, electric PLC or computer will be kept servovalve or the openings of sizes of high frequency sound Proportional valve (3) and the state of a control of oily flow path direction by control unit, the state that keeps plunger type balancing cylinder (9) actual pressure value to equate with required force value;
When Δ p＞0, the actual pressure value that is plunger type balancing cylinder (9) is greater than required force value, electric PLC or computer will reduce the openings of sizes of servovalve or high frequency sound Proportional valve (3) or change oily flow path direction by control unit this moment, reduce fuel feeding by servovalve or high frequency sound Proportional valve (3) to plunger type balancing cylinder (9), or the part fluid that has more in the plunger type balancing cylinder (9) flow back to fuel tank, reduce the actual oil liquid pressure in the plunger type balancing cylinder (9), actual oil liquid pressure in the plunger type balancing cylinder (9) is equated, i.e. Δ p=0 with required pressure;
When Δ p＜0, the actual pressure value that is plunger type balancing cylinder (9) is less than required force value, electric PLC or computer will increase the openings of sizes of servovalve or high frequency sound Proportional valve (3) or change oily flow path direction by control unit this moment, increase fuel feeding by servovalve or high frequency sound Proportional valve (3) to plunger type balancing cylinder (9), improve the actual oil liquid pressure in the plunger type balancing cylinder (9), actual oil liquid pressure in the plunger type balancing cylinder (9) is equated, i.e. Δ p=0 with required pressure.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910023836A CN101660554A (en) | 2009-09-09 | 2009-09-09 | Fully hydraulic servo dynamic balance exhaust head control system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910023836A CN101660554A (en) | 2009-09-09 | 2009-09-09 | Fully hydraulic servo dynamic balance exhaust head control system |
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| CN101660554A true CN101660554A (en) | 2010-03-03 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103527533A (en) * | 2013-10-24 | 2014-01-22 | 中冶辽宁德龙钢管有限公司 | Device and solution for preventing top oil tank of hydrostatic pressure testing machine from oil injection |
-
2009
- 2009-09-09 CN CN200910023836A patent/CN101660554A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103527533A (en) * | 2013-10-24 | 2014-01-22 | 中冶辽宁德龙钢管有限公司 | Device and solution for preventing top oil tank of hydrostatic pressure testing machine from oil injection |
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Application publication date: 20100303 |