CN201513398U - Full hydraulic servo balance exhaust head control device - Google Patents
Full hydraulic servo balance exhaust head control device Download PDFInfo
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- CN201513398U CN201513398U CN200920309948XU CN200920309948U CN201513398U CN 201513398 U CN201513398 U CN 201513398U CN 200920309948X U CN200920309948X U CN 200920309948XU CN 200920309948 U CN200920309948 U CN 200920309948U CN 201513398 U CN201513398 U CN 201513398U
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- exhaust head
- oil cylinder
- plunger
- cylinder
- oil
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Abstract
The utility model relates to the exhaust head control of a steel pipe water pressure tester in the hydraulic servo control technology, in particular to a full hydraulic servo dynamic exhaust head control device, which comprises an exhaust head displacement sensor, a water pressure sensor for tests, a control mechanism and an oil cylinder mechanism, and is characterized in that the oil cylinder mechanism is composed of two piston type idle stroke moving oil cylinders, a plunger type balance oily cylinder and an oil tank, the idle stroke movement of an exhaust head can be realized through the two piston type idle stroke moving oil cylinders, the dynamic balance control of the exhaust head can be realized through the plunger balance oil cylinder, the two piston idle stroke moving oil cylinders are arranged on the left side and the right side of the plunger balance oil cylinder, and the piston idle stroke moving oil cylinders and the plunger type balance oil cylinder are both arranged on one side of the exhaust head. The utility model provides a full hydraulic servo balance exhaust head control device with fast response speed, high control precision, safe and reliable performance, low device fault rate and safe and simple maintenance operation.
Description
Technical field
The utility model relates to the exhaust head control, particularly fully hydraulic servo dynamic balance exhaust head control gear 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 utility model provides 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 gear that equipment failure rate is low, housekeeping operation is safe and simple.
The purpose of this utility model is to realize like this, the fully hydraulic servo dynamic balance exhaust head control gear, at least comprise exhaust head displacement transducer, test water pressure transducer, control mechanism and oil cylinder mechanism, it is characterized in that: described oil cylinder mechanism comprises that two piston type idle runnings move oil cylinder, plunger type balancing cylinder and fuel tank, 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 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 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.
The utility model has the advantages that: 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 utility model is described in further detail below in conjunction with embodiment's accompanying drawing
Fig. 1 is the utility model embodiment 1 structural representation.
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.
Embodiment
As shown in Figure 1, at least comprise exhaust head displacement transducer 5, test water pressure transducer 4, control mechanism and oil cylinder mechanism, 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 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.
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 the plunger cavity that 1, one actuator port of fuel tank connects 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 ports connect 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.
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.
The piston type idle running moves oil cylinder 10 concrete parameters: 1. piston diameter: Φ 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: Φ 400mm; 2. oil cylinder stroke: S=1800mm.
Claims (4)
1. fully hydraulic servo dynamic balance exhaust head control gear, at least comprise exhaust head displacement transducer (5), test water pressure transducer (4), control mechanism and oil cylinder mechanism, 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).
2. fully hydraulic servo dynamic balance exhaust head control gear 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).
3. fully hydraulic servo dynamic balance exhaust head control gear according to claim 1 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.
4. fully hydraulic servo dynamic balance exhaust head control gear according to claim 1 is characterized in that: the concrete parameter of described plunger type balancing cylinder (9) is: plunger diameter is 400mm; Oil cylinder stroke is 1800mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200920309948XU CN201513398U (en) | 2009-09-09 | 2009-09-09 | Full hydraulic servo balance exhaust head control device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200920309948XU CN201513398U (en) | 2009-09-09 | 2009-09-09 | Full hydraulic servo balance exhaust head control device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201513398U true CN201513398U (en) | 2010-06-23 |
Family
ID=42484806
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200920309948XU Expired - Lifetime CN201513398U (en) | 2009-09-09 | 2009-09-09 | Full hydraulic servo balance exhaust head control device |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201513398U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103233929A (en) * | 2013-04-27 | 2013-08-07 | 甘肃蓝科石化高新装备股份有限公司 | Four-column guiding type pressurizing device of hydrostatic testing machine |
| CN104613032A (en) * | 2015-02-06 | 2015-05-13 | 济南邦威仪器有限公司 | Irregularity self-adaptive loading device |
-
2009
- 2009-09-09 CN CN200920309948XU patent/CN201513398U/en not_active Expired - Lifetime
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103233929A (en) * | 2013-04-27 | 2013-08-07 | 甘肃蓝科石化高新装备股份有限公司 | Four-column guiding type pressurizing device of hydrostatic testing machine |
| CN104613032A (en) * | 2015-02-06 | 2015-05-13 | 济南邦威仪器有限公司 | Irregularity self-adaptive loading device |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C56 | Change in the name or address of the patentee | ||
| CP01 | Change in the name or title of a patent holder |
Address after: 710032 Shaanxi city in Xi'an province Xin Jiamiao East yuan Road No. 209 Xi'an Heavy Machinery Research Institute Patentee after: China National Heavy Machinery Research Institute Co., Ltd. Address before: 710032 Shaanxi city in Xi'an province Xin Jiamiao East yuan Road No. 209 Xi'an Heavy Machinery Research Institute Patentee before: China National Heavy Machinery Research Institute Co., Ltd. |
|
| CX01 | Expiry of patent term |
Granted publication date: 20100623 |
|
| CX01 | Expiry of patent term |