CN2246740Y - Electric-control hydraulic driver of driving valve - Google Patents
Electric-control hydraulic driver of driving valve Download PDFInfo
- Publication number
- CN2246740Y CN2246740Y CN 95225000 CN95225000U CN2246740Y CN 2246740 Y CN2246740 Y CN 2246740Y CN 95225000 CN95225000 CN 95225000 CN 95225000 U CN95225000 U CN 95225000U CN 2246740 Y CN2246740 Y CN 2246740Y
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- valve
- oil
- piston
- communicated
- low pressure
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Abstract
The utility model relates to an electric control hydraulic driver for driving a valve, belonging to a liquid pressure actuating mechanism. The utility model is suitable for work under heavy load for process systems, such as pipeline transportation, a coal separating plant, a concentration plant, the chemical industry, etc. In the utility model, a gate plate is hinged with a piston rod of the hydraulic driver, a reversible motor drags a double surface gear pump with an end surface compensating and oil distributing disc to pump oil liquid in a hydraulic cylinder, a piston and the piston rod are pushed to drive the gat plate to move up and down (or backwards and forwards), and a valve is opened or closed. An electrode core which is provided with a polytetrafluoroethylene insulation sleeve is inserted in the hollow hole of the piston rod, and a variable capacitor is formed. The variable capacitor is positioned in the circuit of a displacement sensing electric controller to output current of four to twenty milliamperes as indication for the opening degree for the valve, and a far cavity is realized.
Description
The utility model belongs to liquid pressure actuating mechanism, opens or closes the hydraulic drive of valve under particularly a kind of control heavy duty far away.
At present, set valve in process systems such as big caliber material conveying pipe, coal preparation plant, ore dressing plant and chemical industry, great majority are still using manually, and promptly handwheel drives leading screw and realizes opening or closing of valve, operation inconvenience, require great effort again, can not indicate the aperture and the telecontrol of valve automatically, especially in the winter time under the rugged environment, owing to freeze, the accident that valve is not opened or fitted badly often occurs, what influence was produced normally carries out.Chinese patent on September 25th, 1991 disclosed a kind of patent No. ZL91202647.2, name is called the electrically controlled and hydraulically final controlling element, it is to drag gear pump by motor to pump self fluid in the final controlling element cylinder body, promote cylinder body inner carrier and piston rod to-and-fro motion, the piston rod overhanging end is connected with flashboard, realization is surged and is opened or closed valve, have simple in structure, volume is little, big, the easy to operate advantage of exerting oneself.But, the critical component gear pump of this final controlling element that surges is existing unidirectional oil circuit gear pump, and its suction chamber (low-pressure cavity) and discharge side (hyperbaric chamber) are fixed, in running, internal leakage oil, bearing oil are that the outer drain tap from the pump end cap enters fuel tank, alleviate interior pressure.For making gear pump and final controlling element cylinder chamber constitute sealing, reach the operation of gear pump bidirectional reversible, and the outer drain tap of unidirectional oil circuit gear pump is blocked, cause internal leakage oil not discharge, pressure raises, can only be in underload (less than 2.5 MPas) work down; The axial sealing ring rhegma that pump under heavy duty, often occurs, leakage of oil by force causes the valve paralysis; Because gear pump and final controlling element cylinder body oil circuit seal, when valve opening, in the piston rod retraction cylinder body, fluid is full of the cylinder chamber, because of piston rod occupies certain space in cylinder body, in case during the overhanging throttle down of piston rod, and remaining piston rod space does not have external fluid filling, makes rodless cavity filling fluid not in place, when piston rod is withdrawn again, rodless cavity should be oil-filled to rod chamber, this moment occurs fuel feeding deficiency, the problem that pulling force is not enough; Adopt the sealing of O RunddichtringO between piston and cylinder chamber wall, easily make its rigidity contact, cause rigid damage, produce rod chamber and rodless cavity string liquid, show the pulling force deficiency equally; In addition, measure the electrode cores of the outer sleeving plastic of copper rod of the required capacitive transducer of valve opening, generation distortion influenced by ambient temperature makes position feed back signal gross error occur.
Task of the present utility model is to make improvements at the problems referred to above, and a kind of double-direction gearpump of band edge face compensation oil distribution casing is provided, and drags Y
xThe piston of lip combination seal, and be provided with the automatically controlled hydraulic drive of heatproof electrode cores capacitive transducer, drive opening or closing of valve in order to control far away.
Its technological scheme is as follows:
Drive the automatically controlled hydraulic drive of valve, the flashboard 21 of overhanging end hinge valve that comprises the metallic piston bar 3 of hydraulic drive, the end in addition of metallic piston bar stretches in the hydraulic cylinder 17, and connect firmly mutually with piston 5, the cylinder chamber of piston front portion is a rodless cavity 6, the rear portion is a rod chamber 16, it is characterized in that the outer rim of piston is provided with Y
xLip combined seal ring 15 contacts with the chamber wall of cylinder body 17, rodless cavity is communicated with the oil pipe 12 that moves ahead by fuel sucking pipe 10 and is communicated with a port of the double-direction gearpump 14 of band edge face compensation oil distribution casing 25, rod chamber is communicated with by the port in addition of back row oil pipe 4 with the double-direction gearpump of band edge face compensation oil distribution casing, the main shaft of double-direction gearpump 14 links to each other with reversing motor 11 by coupling drive 13, the poly-tetrafluoride alkene electrode cores 7 of copper rod overcoat that occupies rodless cavity and connect firmly on bonnet 9 is inserted in the hollow hole of metallic piston bar, constitute variable condenser, metallic piston bar 3, copper rod overcoat polytetrafluoroethylene electrode core 7 is electrically connected with the electric pneumatic converter 8 of displacement sensor electrical-controller.
Adopt technique scheme, because gear pump is provided with the end-face compensate oil distribution casing, makes and leak the suction chamber that fluid returns pump, the oil pressure of pump is normal, eliminates to leak and the damage and crack problem, improves pumping pressure; The piston outer rim is established Y
xThe lip combined seal ring contacts with casing wall, and sealing is strict, has prevented string leakage of oil liquid between rodless cavity and rod chamber, has improved that piston rod pushes away, pulling force; Establish fuel sucking pipe in the rodless cavity, in case the vertical use of hydraulic drive when the rodless cavity liquid level descends, is stretched into below the liquid level with fuel sucking pipe, it is oil-filled to rod chamber to do as usual, and has improved the pulling force of piston rod; Teflon has dielectric constant stability, and the electrode cores with its outer variable condenser that is enclosed within on the copper rod to be constituted reaches piston rod displacement and electric capacity linear relationship, accurately shows the aperture of valve.Working properly under 16 MPa heavy dutys through the advance copy model utility.
Be described in detail the utility model structure and mode of execution below in conjunction with accompanying drawing.
Fig. 1 represents to drive the automatically controlled hydraulic drive structure sectional view of valve
Fig. 2 presentation graphs 1 label 25 end-face compensate oil distribution casing amplification views.
Fig. 3 presentation graphs 2 along A to view.
Fig. 4 presentation graphs 2 is along the B-B sectional view.
Fig. 5 represents displacement sensor electrical-controller circuit.
Automatically controlled hydraulic drive as the represented driving valve of Fig. 1 comprises valve body 22, inserts the flashboard 21 of valve body, and wear-resisting lining 23 is set on the hole wall of the flowing hole of valve body, and an end of flashboard is hinged with the overhanging end of articulated elements 19 with metallic piston bar 3.Hydraulic drive is connected with valve body by valve body bearing support 20, adpting flange 18.Said hydraulic drive comprises hydraulic cylinder 17, connects firmly a front cover 2 at the front end of hydraulic cylinder, and metallic piston bar overhanging end wore front cover, and with Y
x1 sealing of lip combined seal ring; The last rapids that occupies the metallic piston bar in the hydraulic cylinder connects firmly a piston 5, and this piston outer rim is established Y
xLip combined seal ring 15 and cylinder wall contact seal; The cylinder chamber of piston front portion is a rodless cavity 6, and the fluid of this rodless cavity is communicated with the oil pipe 12 that moves ahead by fuel sucking pipe 10 and is communicated with double-direction gearpump 14 1 ports (suction port or exhaust port); The piston rear portion is a rod chamber 16, and the fluid of this rod chamber is communicated with the port (exhaust port or suction port) in addition of double-direction gearpump by back row oil pipe 4; Double-direction gearpump links to each other with reversing motor 11 by coupling drive 13.The end face of double-direction gearpump 14 is provided with an end-face compensate oil distribution casing 25, as Fig. 2,3,4 is represented, on the end-face compensate oil distribution casing, be provided with high pressure (or low pressure) the district runner 26 that communicates with gear pump, low pressure (or high pressure) district's runner 27 and high low pressure transition zone 28, in the high low pressure transition zone and near one side of zone of high pressure, bore several left bank oilholes 29, several right oil drainage holes 30 are bored on one side near low pressure area, general every district is 3 holes, left bank oilhole and right one-way valve 31 holes connect, right oil drainage hole and left one-way valve 32 holes connect, and leak oilhole 33 and left one-way valve, right one-way valve is communicated with; When left bank oilhole 29 is in the zone of high pressure, when right oil drainage hole 30 was in low pressure area, right one-way valve 31 was closed, and leaked oil and bearing oil through leaking oilhole 33 inflows and opening left one-way valve 32, flowed back to the suction chamber of pump through right oil drainage hole 30; When left bank oilhole 29 is in low pressure area, when right oil drainage hole 30 is in the zone of high pressure, left closed check valve, leak oil and bearing oil and flow into and open right one-way valve through leaking oilhole, flow back to the suction chamber of pump through the left bank oilhole, eliminate the interior pressure that leaks, alleviates pump thus, improve pumping pressure.Occupy rodless cavity and connect firmly electrode cores 7 (Fig. 1) on bonnet 9, constituted by copper rod overcoat insulation teflon cover, teflon has the stable performance of dielectric constant, this electrode cores 7 is inserted in the hollow hole of metallic piston bar 3, constitute variable condenser, this variable condenser places the circuit of the electric pneumatic converter 8 that Fig. 5 represents, is equivalent to variable capacitance C
x, wherein a point and metallic piston bar Electricity Federation, b point and electrode cores 7 Electricity Federations are because variable capacitance amount C
xVery little, be the interference of avoiding going between, the circuit board of its electric pneumatic converter 8 is installed in the bonnet of hydraulic drive.
When reversing motor 11 drive double-direction gearpumps 14 are rotated counterclockwise, double-direction gearpump pumps to rodless cavity 6 with the fluid of rod chamber 16 by back row oil pipe 4, piston 5 will promote metallic piston bar 3 and flashboard 21 reaches (or moving down), this moment, electrode cores was motionless relatively, along with the reach of metallic piston bar, metallic piston bar and electrode cores relative area reduce, Capacity C
xReduce gradually, flashboard cuts out when being reduced to minimum value; Otherwise, when reversing motor drive double-direction gearpump turns clockwise, double-direction gearpump pumps to rod chamber with the fluid of rodless cavity 6 by the fuel sucking pipe 10 and the oil pipe 12 that moves ahead, piston will move (or on move) after will spurring metallic piston bar and flashboard, metallic piston bar and electrode cores relative area increase, Capacity C
xIncrease gradually, flashboard is all opened when increasing to maximum value.
The displacement sensor electrical-controller circuit that Fig. 5 represents, it is that above said metallic piston bar and flashboard mechanical displacement are converted to electrical signal, in order to the indication and the hydraulic drive position feed back signal of valve opening.It is made up of electric pneumatic converter 8 circuit and amplification change-over circuit 24.
The electric pneumatic converter circuit comprises with T
1For the vibrator circuit of core with T
2Change-over circuit formation for core.Transformer secondary L in vibrator circuit
2Output voltage under just going up when negative, with upper half after straight capacitor C
5, C
4With variable capacitance C
xCharging voltage series connection, produce T
2Base current i
g, through T
2Amplify and output half-wave current I
cObviously, when the metallic piston bar bounces back, go deep into length lengthening in the hollow hole of metallic piston bar along with electrode cores 7 in cylinder body 17, relative area increases, variable capacitance amount C
xIncrease, with T
2Base current i
bIncrease the output current I of electric pneumatic converter
cAlso increase; Otherwise, when the metallic piston bar extends outside cylinder body, output current I
cWith variable capacitance amount C
xReduce and reduce.Half-wave current I
cBehind the input change-over circuit 24, by potentiometer RP
2Be converted into voltage signal V
c, and by being the differential amplifier circuit of core with amplifier F, with zeroing voltage V
zAfter subtracting each other amplification, by with T
3For 4～20 milliamperes of current signals of the constant current output element outputting standard of core, by resistance R
12The negative feedback links of forming in order to improve the temperature stability of circuit, reduces temperature drift.Will adjust to valve opening indication and hydraulic drive metallic piston bar position feed back signal before use, its method is: metallic piston bar and flashboard reach (or moving down), when reaching the valve Close All, regulate potentiometer RP
2, make its T
3Output also shows 20 milliamperes on ammeter A; When moving (or on move) behind metallic piston bar and the flashboard and reaching valve and all open, regulate potentiometer RP
3, make its T
3Output also shows 4 milliamperes on ammeter A.This signal code has the [constant characteristic, in order to control far away.
Claims (2)
1, drives the automatically controlled hydraulic drive of valve, the flashboard 21 of overhanging end hinge valve that comprises the metallic piston bar 3 of hydraulic drive, the end in addition of metallic piston bar stretches in the hydraulic cylinder 17, and connect firmly mutually with piston 5, the cylinder chamber of piston front portion is a rodless cavity 6, the rear portion is a rod chamber 16, it is characterized in that the outer rim of piston is established Y
xLip combined seal ring 15 contacts with cylinder body 17 chamber walls, rodless cavity is communicated with the oil pipe 12 that moves ahead by fuel sucking pipe 10 and is communicated with a port of the double-direction gearpump 14 of band edge face compensation oil distribution casing 25, rod chamber is communicated with by the port in addition of back row oil pipe 4 with the double-direction gearpump of band edge face compensation oil distribution casing, the main shaft of double-direction gearpump 14 links to each other with reversing motor 11 by coupling drive 13, the electrode cores 7 that occupies rodless cavity and connect firmly the copper rod overcoat teflon on bonnet 9 is inserted in the hollow hole of metallic piston bars and is constituted variable condenser, metallic piston bar 3, electrode cores 7 is electrically connected with the electric pneumatic converter 8 of displacement sensor electrical-controller.
2, according to the described hydraulic drive of claim 1, it is characterized in that the end-face compensate oil distribution casing is provided with zone of high pressure runner 26, low pressure area runner 27 and high low pressure transition zone 28, in the high low pressure transition zone and near one side of zone of high pressure, bore several left bank oilholes 29, some right oil drainage holes 30 are bored on one side near low pressure area, left bank oil connects with right one-way valve 31 holes, right oil drainage hole and left one-way valve 32 holes connect, and leak oilhole 33 and are communicated with left one-way valve, right one-way valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 95225000 CN2246740Y (en) | 1995-10-20 | 1995-10-20 | Electric-control hydraulic driver of driving valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 95225000 CN2246740Y (en) | 1995-10-20 | 1995-10-20 | Electric-control hydraulic driver of driving valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2246740Y true CN2246740Y (en) | 1997-02-05 |
Family
ID=33871587
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 95225000 Expired - Fee Related CN2246740Y (en) | 1995-10-20 | 1995-10-20 | Electric-control hydraulic driver of driving valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2246740Y (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101761492A (en) * | 2010-03-16 | 2010-06-30 | 潘正平 | Two-door pump valve |
| CN102245948A (en) * | 2008-12-11 | 2011-11-16 | 阿尔法拉瓦尔股份有限公司 | Valve actuator |
| CN102829152A (en) * | 2012-09-15 | 2012-12-19 | 浙江理工大学 | Turn flow type hydraulic limited slip differential |
| CN104197074A (en) * | 2014-08-21 | 2014-12-10 | 山东大学 | Integrated type electro-hydraulic drive regulating valve and control method |
| CN104847952A (en) * | 2014-02-17 | 2015-08-19 | 张民良 | Tray piston type swing driving machine capable of mechanically driving a piston to act on fluid load |
| CN109027368A (en) * | 2018-09-04 | 2018-12-18 | 桐城市立行电子科技有限公司 | A kind of on-off control valve for tail gas clean-up in vehicle gas circuit |
| CN109027369A (en) * | 2018-09-04 | 2018-12-18 | 桐城市立行电子科技有限公司 | It is a kind of for controlling the valve of gas path on-off in vehicle |
| CN109027367A (en) * | 2018-09-04 | 2018-12-18 | 桐城市立行电子科技有限公司 | A kind of vehicle gas path on-off control valve |
-
1995
- 1995-10-20 CN CN 95225000 patent/CN2246740Y/en not_active Expired - Fee Related
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102245948A (en) * | 2008-12-11 | 2011-11-16 | 阿尔法拉瓦尔股份有限公司 | Valve actuator |
| CN102245948B (en) * | 2008-12-11 | 2014-03-05 | 阿尔法拉瓦尔股份有限公司 | Valve actuator |
| US8960219B2 (en) | 2008-12-11 | 2015-02-24 | Alfa Laval Corporate Ab | Valve actuator |
| CN101761492A (en) * | 2010-03-16 | 2010-06-30 | 潘正平 | Two-door pump valve |
| CN102829152A (en) * | 2012-09-15 | 2012-12-19 | 浙江理工大学 | Turn flow type hydraulic limited slip differential |
| CN102829152B (en) * | 2012-09-15 | 2016-08-17 | 浙江理工大学 | A kind of reverse-flow type hydraulic limited slip differential |
| CN104847952A (en) * | 2014-02-17 | 2015-08-19 | 张民良 | Tray piston type swing driving machine capable of mechanically driving a piston to act on fluid load |
| CN104847952B (en) * | 2014-02-17 | 2017-10-10 | 张民良 | Mechanical Driven piston effect waves driving machine in the pallet piston type of fluid load |
| CN104197074A (en) * | 2014-08-21 | 2014-12-10 | 山东大学 | Integrated type electro-hydraulic drive regulating valve and control method |
| CN109027368A (en) * | 2018-09-04 | 2018-12-18 | 桐城市立行电子科技有限公司 | A kind of on-off control valve for tail gas clean-up in vehicle gas circuit |
| CN109027369A (en) * | 2018-09-04 | 2018-12-18 | 桐城市立行电子科技有限公司 | It is a kind of for controlling the valve of gas path on-off in vehicle |
| CN109027367A (en) * | 2018-09-04 | 2018-12-18 | 桐城市立行电子科技有限公司 | A kind of vehicle gas path on-off control valve |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |