CN205371774U - A pneumatic actuator for one -way damping delivery valve - Google Patents
A pneumatic actuator for one -way damping delivery valve Download PDFInfo
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- CN205371774U CN205371774U CN201521106116.XU CN201521106116U CN205371774U CN 205371774 U CN205371774 U CN 205371774U CN 201521106116 U CN201521106116 U CN 201521106116U CN 205371774 U CN205371774 U CN 205371774U
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Abstract
The utility model discloses a pneumatic actuator for one -way damping delivery valve belongs to petrochemical trade catalytic cracking unit technical field. This pneumatic actuator includes: first cylinder, second cylinder, declutch shift shaft, shift fork and cylinder switching -over the control unit, the pole portion of shift fork and the valve shaft fixed connection of one -way damping delivery valve, cylinder switching -over the control unit is used for controlling first cylinder and the switching -over of second cylinder, pneumatic actuator still includes: clutching mechanism, clutching mechanism is the cylinder, and clutching mechanism is last to be provided with the guide way along its lengthwise direction, clutching mechanism's both ends respectively with the piston rod of first cylinder and the piston rod fixed of second cylinder, the declutch shift shaft stretches into the U -shaped opening of shift fork tip and the guide way on the clutching mechanism, the declutch shift shaft can slide in the U -shaped opening and can make linear motion simultaneously in the guide way, this pneumatic actuator can improve the efficiency, and one -way damping delivery valve closes and dies under the assurance accident situation, protects the sealed face of one -way damping delivery valve simultaneously.
Description
Technical field
This utility model relates to petroleum chemical industry catalytic cracking unit technical field, particularly to a kind of pneumatic actuator for one-way damper valve.
Background technology
Being usually provided with one-way damper valve on the main air blower outlet conduit of petroleum chemical industry catalytic cracking unit, when causing pipeline internal medium adverse current when having an accident, one-way damper valve quick closedown is to prevent pipeline internal medium adverse current damage main air blower.The open and close of one-way damper valve rely primarily on the pneumatic actuator supporting with it and complete.
The existing pneumatic actuator for one-way damper valve is two formula pneumatic actuators, mainly includes cylinder, shift fork, shift fork axle, electromagnetic valve and corresponding gas circuit pipe arrangement.The bar portion of shift fork is provided with the through hole for connecting with one-way damper valve valve shaft, and the end of shift fork is additionally provided with the opening of U-shaped.The piston rod of cylinder is vertically connected with cross shift fork axle, the intimate surface contact of the horizontal direction of cross shift fork axle and the U-shaped opening of shift fork and can sliding in the U-shaped opening of shift fork.The piston rod of cylinder drives the valve shaft of one-way damper valve by shift fork, and electromagnetic valve changes the direction of motion of piston rod for controlling cylinder commutation, thus changing the movement locus of valve shaft, it is achieved the open and close of one-way damper valve.Under normal circumstances, the piston rod of cylinder moves along a direction and makes one-way damper valve be in fully open position, and keeps this invariant position；Under accident condition, electromagnetic valve controls cylinder commutation, makes valve rapid-closing.
In realizing process of the present utility model, the design people finds at least to there is problems in that in prior art that existing two formula pneumatic actuators make one-way damper valve be in fully open position under normal circumstances, cause duct pressure loss excessive, cause that catalytic cracking unit efficiency reduces.Simultaneously; when accident occurs, one-way damper valve generally to be closed within 3s, closes with so fast speed and there will be violent mechanical collision, causes one-way damper valve sealing surface of seat to damage; the sealing property causing one-way damper valve is deteriorated, it is impossible to function well as the effect of protection main air blower.
Utility model content
In order to solve above-mentioned technical problem, this utility model provides one can improve device efficiency, and is prevented from one-way damper valve closing process occurring the pneumatic actuator for one-way damper valve of vigorous collision.
Specifically, including following technical scheme:
A kind of pneumatic actuator for one-way damper valve, described pneumatic actuator includes: the first cylinder, the second cylinder, shift fork axle, shift fork and cylinder commutation control unit；The bar portion of described shift fork is fixing with the valve shaft of described one-way damper valve to be connected；Described cylinder commutation control unit is used for controlling described first cylinder and described second cylinder commutation；Wherein, described pneumatic actuator also includes clutch, described clutch is cylinder, and described clutch is provided with gathering sill along its longitudinally；The two ends of described clutch are fixing with the piston rod of the piston rod of described first cylinder and described second cylinder respectively to be connected；Described shift fork axle stretches into the gathering sill on the U-shaped opening of described shift fork end and described clutch；Described shift fork axle can slide in described U-shaped opening and can be simultaneously for linear motion in described gathering sill.
Further, described pneumatic actuator also includes: damping oil cylinder and anchoring base；Described damping oil cylinder is swing type damping oil cylinder, and the cylinder body of described damping oil cylinder and described anchoring base are articulated and connected, and the bar portion of the piston rod of described damping oil cylinder and described shift fork is articulated and connected.
Further, described cylinder exchange system includes: electromagnetic valve and Pneumatic valve；Electromagnetic valve source of the gas input port is connected with source of the gas, and electromagnetic valve delivery outlet is connected by trachea with Pneumatic valve commutation control mouth；Pneumatic valve source of the gas input port is connected with described source of the gas, and on Pneumatic valve the first delivery outlet and the first cylinder, on interface and the second cylinder, interface connects, Pneumatic valve the second delivery outlet and the first cylinder lower interface and the connection of the second cylinder lower interface；When described one-way damper valve is opened, described electromagnetic valve source of the gas input port and described electromagnetic valve equipped at outlet port are in connected state, described Pneumatic valve source of the gas input port and described Pneumatic valve the second equipped at outlet port are in connected state, and described Pneumatic valve the first delivery outlet and Pneumatic valve first row QI KOU are in connected state；When described one-way damper valve is opened, described electromagnetic valve source of the gas input port and described electromagnetic valve delivery outlet are off, described Pneumatic valve source of the gas input port and described Pneumatic valve the first equipped at outlet port are in connected state, and described Pneumatic valve the second delivery outlet and Pneumatic valve second exhaust port are in connected state.
Further, described cylinder exchange system also includes source of the gas bigeminy part, and described source of the gas bigeminy part one end is connected with described source of the gas, and the other end is connected with described electromagnetic valve source of the gas input port and described Pneumatic valve source of the gas input port.
Further, the two ends of described shift fork axle are additionally provided with circlip.
Further, the bar portion of described shift fork is connected by flat key with the valve shaft of described one-way damper valve.
Further, described clutch is threaded connection with the piston rod of described first cylinder and the piston rod of described second cylinder.
Further, described anchoring base is casing.
The technical scheme that this utility model embodiment provides provides the benefit that:
(1) in the pneumatic actuator that this utility model embodiment provides, adopt the double; two cylinder series design of disengaging type, it is connected by clutch, shift fork axle and shift fork between cylinder and the valve shaft of one-way damper valve, shift fork axle can in the gathering sill of clutch rectilinear motion, and can oppress shift fork drive valve shaft circle；In one-way damper valve opening process, cylinder commutation control unit controls the first cylinder piston rod elongation, second cylinder piston rod shrinks so that clutch vertically moves upward, in this process, the two ends of clutch gathering sill do not contact with shift fork axle, shift fork is without rotating, therefore valve shaft will not be subject to the External Force Acting from pneumatic actuator, valve only relies on the assosting effect of weight on pipeline internal medium pressure and shift fork and opens, its aperture depends on pressure medium and changes in flow rate, i.e. servo-actuated valve opening, avoid duct pressure loss in valve opening process excessive, significantly improve efficiency.When in the one-way damper valve closing process that has an accident, cylinder commutation control unit controls the first cylinder piston rod and shrinks, second cylinder piston rod extends so that clutch moves vertically downwards, when arriving certain position, the upper surface of clutch gathering sill contacts with shift fork axle thus shift fork axle moves downward, shift fork axial compression is compeled shift fork and is rotated, thus driving valve shaft motion to make orifice valve close, play auxiliary and close the effect of valve, and owing to double, two cylinder series design provide bigger output torque, increase closedown moment, ensure that under accident condition, orifice valve shuts and zero leakage.Disclosure satisfy that the pass valve torque demand that heavy caliber orifice valve is bigger, widen the one-way damper valve bore scope matched.
(2) pneumatic actuator that this utility model embodiment provides additionally uses swing type damping oil cylinder, it is achieved one-way damper valve closes end buffering, it is to avoid occur in one-way damper valve quick closedown process that violent mechanical collision causes that sealing surface damages.
(3) also cylinder reversing control system having been improved in the pneumatic actuator that this utility model embodiment provides, combine control cylinder commutation by electromagnetic valve and Pneumatic valve.Electromagnetic valve provides pressure signal for Pneumatic valve, and Pneumatic valve controls cylinder commutation, owing to Pneumatic valve has bigger latus rectum, it is possible to avoid the cylinder " creeping " caused in cylinder commutation process because gas flow is not enough.
Accompanying drawing explanation
In order to be illustrated more clearly that the technical scheme in this utility model embodiment, below the accompanying drawing used required during embodiment is described is briefly described, apparently, accompanying drawing in the following describes is only embodiments more of the present utility model, for those of ordinary skill in the art, under the premise not paying creative work, it is also possible to obtain other accompanying drawing according to these accompanying drawings.
The pneumatic actuator that Fig. 1 provides for this utility model embodiment structural representation in normal operation；
The pneumatic actuator that Fig. 2 provides for this utility model embodiment structural representation in the state of accident；
The structural representation of shift fork, shift fork axle and clutch in the pneumatic actuator that Fig. 3 provides for this utility model embodiment；
Fig. 4 is the top view of Fig. 3；
Cylinder commutation control unit connected mode schematic diagram in normal operation in the pneumatic actuator that Fig. 5 provides for this utility model embodiment；
Cylinder commutation control unit connected mode schematic diagram in the state of accident in the pneumatic actuator that Fig. 6 provides for this utility model embodiment；
The structural representation of swing type damping oil cylinder in the pneumatic actuator that Fig. 7 provides for this utility model embodiment.
Accompanying drawing labelling represents respectively:
1, the first cylinder；
2, clutch；21, screwed hole；
3, shift fork axle；4, flat key；5, valve shaft；6, shift fork；
7, damping oil cylinder；71, damping oil cylinder piston rod；72, one-way throttle valve；
8, the second cylinder；9, anchoring base；
10, Pneumatic valve；11, electromagnetic valve；12, source of the gas bigeminy part；13, circlip；
P, source of the gas；
O, Pneumatic valve commutation control mouth；
Interface on 1A, the first cylinder；1B, the first cylinder lower interface；
Interface on 8A, the second cylinder；8B, the second cylinder lower interface；
10P, Pneumatic valve source of the gas input port；
10A, Pneumatic valve the first delivery outlet；10B, Pneumatic valve the second delivery outlet；
10R, Pneumatic valve first row QI KOU；10S, Pneumatic valve second exhaust port；
11P, electromagnetic valve source of the gas input port；
11A, electromagnetic valve delivery outlet；11R, solenoid valve vents mouth.
Detailed description of the invention
For making the technical solution of the utility model and advantage clearly, below in conjunction with accompanying drawing, this utility model embodiment is described in further detail.
This utility model embodiment provides a kind of pneumatic actuator for one-way damper valve, this pneumatic actuator is connected with the valve shaft 5 of one-way damper valve, referring to Fig. 1, and in conjunction with Fig. 2 and Fig. 3, this pneumatic actuator includes: first cylinder the 1, second cylinder 8, shift fork axle 3, shift fork 6 and cylinder commutation control unit；The bar portion of shift fork 6 is fixing with the valve shaft 5 of one-way damper valve to be connected；Cylinder commutation control unit is used for controlling the first cylinder 1 and the second cylinder 8 commutates；Wherein, this pneumatic actuator also includes: clutch 2；Clutch 2 is cylinder, and clutch 2 is provided with gathering sill along its longitudinally；The two ends of clutch 2 are fixing with the piston rod of the piston rod of the first cylinder 1 and the second cylinder 8 respectively to be connected；Shift fork axle 3 stretches into the gathering sill on the U-shaped opening of shift fork 6 end and clutch 2；Shift fork axle 3 can slide in U-shaped opening and can be simultaneously for linear motion in gathering sill.
When one-way damper valve is opened, shift fork 6 rotates under the drive of valve shaft 5, and drives shift fork axle 3 vertically to move upward, and the first cylinder 1 and the commutation of the second cylinder 8 drive clutch 2 vertically to move upward.
When one-way damper valve is closed, first cylinder 1 and the commutation of the second cylinder 8 drive clutch 2 to move vertically downwards, after the end face of the gathering sill of clutch 2 contacts with shift fork axle 3, compressing shift fork axle 3 moves vertically downwards, thus driving shift fork 6 to rotate, shift fork 6 drives valve shaft 5 to rotate.
In the pneumatic actuator that this utility model embodiment provides, adopt the double; two cylinder series design of disengaging type.It is connected by clutch 2, the shift fork axle 3 of " one " font and shift fork 6 between cylinder and the valve shaft 5 of one-way damper valve, shift fork axle 3 can slide and rectilinear motion in the gathering sill of clutch 2 simultaneously in the U-shaped opening of shift fork 6 end, after the piston rod of first cylinder the 1, second cylinder 8 drives clutch 2 rectilinear motion to contact to gathering sill top with shift fork axle 3, shift fork axle 3 is oppressed shift fork 6 and is rotated, thus drive is fixed, with shift fork, the valve shaft 5 being connected and rotated, finally realize one-way damper valve and open and close.And owing to double; two cylinder series design provide bigger output torque, increasing closedown moment, it is ensured that under accident condition, orifice valve shuts and zero leakage.Disclosure satisfy that the pass valve torque demand that heavy caliber orifice valve is bigger, widen the one-way damper valve bore scope matched.Specific works principle is as follows:
Referring to Fig. 1, in one-way damper valve opening process, after the valve plate (not shown) of one-way damper valve is subject to pipeline internal medium pressure effect, driving connected valve shaft 5 to rotate, valve shaft 5 is further driven to connected shift fork 6 and rotates.In shift fork 6 rotation process, penetrating shift fork axle 3 one aspect in its U-shaped opening and do rectilinear motion straight up along the gathering sill of clutch 2, along shift fork 6 end, U-shaped mouth contact plane slides on the other hand.Meanwhile, cylinder commutation control unit controls the piston rod elongation of the first cylinder 1, the second cylinder 8 piston rod shrinks so that clutch 2 vertically moves upward, in this process, two end faces up and down of gathering sill all do not contact with shift fork axle 3, and upper surface is farthest from shift fork axle 3, clutch 2 will not stop the upstroke of shift fork axle 3.As can be seen here, in one-way damper valve opening process, valve shaft 5 will not be subject to the External Force Acting from pneumatic actuator, valve only relies on the assosting effect of the weight (not shown) on pipeline internal medium pressure and shift fork 6 and opens, its aperture depends on pressure medium and changes in flow rate, this process is called servo-actuated valve opening, it is to avoid in valve opening process, duct pressure loss is excessive, significantly improves efficiency.Further, due to the existence of clutch 2, moreover it is possible to protection piston rod, it is to avoid the long-time reciprocating action of piston rod caused because of valve plate (not shown) servo oscillation and abrasion deformation and mechanical performance reduce.
Referring to Fig. 2, when in the one-way damper valve closing process that has an accident, cylinder commutation control unit controls the piston rod contraction of the first cylinder 1, the piston rod of the second cylinder 8 extends so that clutch 2 moves vertically downwards, when arriving certain position, the upper surface of clutch 2 gathering sill contacts thus promoting shift fork axle 3 to move downward with shift fork axle 3, shift fork axle 3 is oppressed shift fork 6 and is rotated, and makes orifice valve close thus driving valve shaft 5 to rotate.It should be noted that, owing to the aperture of one-way damper valve is to be determined by pipeline internal medium pressure and flow, therefore be about to the moment closed at one-way damper valve, its aperture size is unknown, and it is unknown for also allowing for the distance between the upper surface of the gathering sill of clutch 2 and shift fork axle 3.Only after clutch 2 is moved downwardly to certain position.After the upper surface of gathering sill contacts with shift fork axle 3, pneumatic actuator just starts to play the effect cutting out valve, and when the upper surface of gathering sill does not contact with shift fork axle 3, valve plate can be closed under the pass valve moment loading of counter-flow media in pipeline, therefore, this pneumatic actuator plays auxiliary in one-way damper valve closing process and closes the effect of valve.
Further; close in valve process in pneumatic actuator auxiliary; the pass valve moment that in pipeline, counter-flow media causes is relatively big, pneumatic actuator auxiliary closes valve speed; often closing the mechanical collision that the appearance of valve moment is violent; sealing surface is caused to damage; sealing effectiveness is deteriorated, and even cannot cut off adverse current, does not have the effect of protection main air blower.Therefore, the pneumatic actuator that this utility model embodiment provides realizes one-way damper valve also by swing type damping oil cylinder 7 and closes end buffering, it is to avoid one-way damper valve quick closedown process occurring, violent mechanical collision causes that sealing surface damages.The cylinder body of damping oil cylinder 7 and anchoring base 9 are articulated and connected, and the bar portion of the piston rod of damping oil cylinder 7 and shift fork 6 is articulated and connected.While the cylinder body of damping oil cylinder 7 pin joint in anchoring base 9 swings, its piston rod 71 does Direct Travel motion, is starting damping action close to valve closed positions.Referring to Fig. 1 and Fig. 2, when in the one-way damper valve closing process that has an accident, rotation along with shift fork 6, the piston rod 71 of damping oil cylinder 7 is become the vertical state gradually becoming in Fig. 2 by the heeling condition in Fig. 1, the length stretched out is gradually reduced, when it foreshortens to and drives the piston of damping oil cylinder to enter oil cylinder top loculus, damping oil cylinder 7 has started damping action, damping force size changes with load and pendulum angle and changes, avoid damping that traditional Direct Travel oil cylinder constant damping causes excessive or card group, rise sharply thus damping moment when preventing end from cushioning, effectively play cushioning effect, protection sealing surface, extend the service life of single-phase orifice valve.It will be understood by those skilled in the art that, in this utility model embodiment, swing type damping oil cylinder 7 cylinder barrel is up-small and down-big structure, in one-way damper valve closing process, damping oil cylinder 7 swings around anchoring base 9 and piston is progressed into top loculus by big chamber, cylinder barrel bottom, once piston enters top loculus, damping oil cylinder 7 has started damping action；Now, one-way damper valve is close closes, so, this process is referred to as to close valve end buffering.Additionally, damping oil cylinder 7 is also provided with one-way throttle valve 72 (referring to Fig. 7), the damping size of scalable damping oil cylinder 7, reach optimized buffer effect.It is understood that, after the damping size of damping oil cylinder 7 being adjusted to optimum state by one-way throttle valve 72, the damping size of damping oil cylinder 7 is constant, but transferred to vertical gradually by heeling condition owing to closing cylinder piston rod in valve process, so, the component size that piston rod acts on shift fork 6 is also gradually changing, and this change can better adapt to valve plate (not shown) and close the process of valve moment variations, it is prevented that cylinder piston rod is stuck.Meanwhile, valve end is closed but not omnidistance damping also can guarantee that the emergency cut-off time.
Further, conventional electromagnetic valve controls in cylinder commutation process, owing to electromagnetic valve latus rectum is less, its gas flow can not meet the needs of double; two cylinder, therefore, cylinder commutation control unit is also optimized improvement by the pneumatic actuator that this utility model embodiment provides, electromagnetic valve 11 and Pneumatic valve 10 is combined and controls cylinder commutation.Electromagnetic valve 11 provides pressure signal, Pneumatic valve 10 to control cylinder commutation for Pneumatic valve 10.In this utility model embodiment, electromagnetic valve 11 adopts two-position three way magnetic valve, and Pneumatic valve 10 adopts two-position five-way Pneumatic valve.Wherein, electromagnetic valve source of the gas input port 11P is connected with source of the gas P, and electromagnetic valve delivery outlet 11A is connected by trachea with Pneumatic valve commutation control mouth O；Pneumatic valve source of the gas input port 10P is connected with source of the gas P, and on Pneumatic valve the first delivery outlet 10A and the first cylinder, on interface 1A and the second cylinder, interface 8A connects, Pneumatic valve the second delivery outlet 10B and the first cylinder lower interface 1B and the second cylinder lower interface 8B connection.
Referring to Fig. 5, in one-way damper valve opening process, electromagnetic valve 11 obtains electric, and right position is opened, and now, electromagnetic valve source of the gas input port 11P and electromagnetic valve delivery outlet 11A is in connected state.Source of the gas P is divided into two branch roads, and a route electromagnetic valve source of the gas input port 11P enters electromagnetic valve 11 and exported to Pneumatic valve commutation control mouth O by electromagnetic valve delivery outlet 11A, provides pressure signal for Pneumatic valve commutation control mouth O.When Pneumatic valve commutation control mouth O receives pressure signal, right position is opened, and Pneumatic valve source of the gas input port 10P and Pneumatic valve the second delivery outlet 10B is in connected state, and Pneumatic valve the first delivery outlet 10A and Pneumatic valve first row QI KOU 10R is in connected state.Another branch road source of the gas P is entered Pneumatic valve 10 by Pneumatic valve source of the gas input port 10P, it is being divided into two branch roads after being exported by Pneumatic valve the second delivery outlet 10B, the first cylinder 1 and the second cylinder 8 is entered respectively by the first cylinder lower interface 1B and the second cylinder lower interface 8B, promote the piston of the first cylinder 1 and the piston upwards of the second cylinder 8, drive clutch 2 to move upward, make the gathering sill on clutch 2 without influence on the upstroke of shift fork axle 3.
Referring to Fig. 6, under accident condition in check valve closing process, electromagnetic valve 11 dead electricity commutates, and left position is opened, and electromagnetic valve source of the gas input port 11P and electromagnetic valve delivery outlet 11A is off.Source of the gas P cannot be introduced into Pneumatic valve commutation control mouth O and provides pressure signal for it.When Pneumatic valve commutation control mouth O no pressure signal, Pneumatic valve 10 quickly commutates, left position is opened, and Pneumatic valve source of the gas input port 10P and Pneumatic valve the first delivery outlet 10A is in connected state, and Pneumatic valve the second delivery outlet 10B and Pneumatic valve second exhaust port 10S is in connected state.Source of the gas P is entered Pneumatic valve 10 by Pneumatic valve source of the gas input port 10P, it is further divided into two branch roads after being exported by Pneumatic valve the first delivery outlet 10A, respectively by interface 1A on the first cylinder and on the second cylinder interface 8A enter the first cylinder 1 and the second cylinder 8, the piston of the first cylinder 1 and the piston of the second cylinder 8 is promoted to move downward, clutch 2 is driven to move vertically downwards, thus realizing the quick closedown of valve.In first cylinder 1 and the second cylinder 8 cylinder, residual air is emptied by Pneumatic valve second exhaust port 10S.Under above two duty, source of the gas P is all the time from entrance first cylinder 1 of Pneumatic valve 11 and the second cylinder 8, owing to Pneumatic valve 11 has bigger latus rectum, therefore it is entirely capable of meeting flow and the rate request of double; two cylinder from the air-flow of Pneumatic valve 11 output, the cylinder " creeping " caused because of underfed when avoiding the commutation of little bare sizing electro-magnetic valve, even jam.It is not thorough that the application of big orifice Pneumatic valve 11 avoids cylinder commutation, it is ensured that cylinder commutation puts in place rapidly, does not affect the servomechanism process of orifice valve.
Further, in the pneumatic actuator that this utility model embodiment provides, cylinder reversing unit is additionally provided with source of the gas bigeminy part 12, referring to Fig. 1 (or Fig. 2), source of the gas bigeminy part 12 one end is connected with source of the gas P, the other end is connected with electromagnetic valve source of the gas input port 11P and Pneumatic valve source of the gas input port 10P, and source of the gas P is divided into two branch roads to be connected with electromagnetic valve source of the gas input port 11P and Pneumatic valve source of the gas input port 10P respectively after source of the gas bigeminy part 12.
Further, referring to Fig. 3 and in conjunction with Fig. 4, in the pneumatic actuator that this utility model embodiment provides, one end of shift fork 6 is provided with two pieces of fork plates, is respectively arranged with U-shaped opening on two pieces of fork plates.Clutch 2 is between two pieces of fork plates, one end of shift fork axle 3 is penetrated by the U-shaped opening on one of fork plate, passed by the U-shaped opening on another block fork plate after the gathering sill of clutch 2, so that shift fork axle 3 can simultaneously for linear motion along gathering sill and slip in U-shaped opening.The two ends of shift fork axle 3 are additionally provided with circlip for shaft 13, so that shift fork axle 3 axial restraint.
Further, referring to Fig. 3 and in conjunction with Fig. 4, the bar portion of shift fork 6 is connected by flat key 4 with the valve shaft 5 of one-way damper valve.Specifically, in the bar portion of shift fork 6, the position near U-shaped opening offers connecting hole and keyway, connects with flat key 4 after valve shaft 5 is penetrated connecting hole.It will be understood by those skilled in the art that, shift fork 6 is not limited to flat key with the connected mode of the valve shaft 5 of one-way damper valve and is connected, the connected modes such as threaded, interference fit, as long as ensureing that shift fork 6 and valve shaft 5 do not occur to loosen in one-way damper valve opening and closing process.
Further, referring to Fig. 3, in the pneumatic actuator that this utility model embodiment provides, clutch 2 can be cylinder, it is also possible to for the cylinder of other forms such as cuboid.The piston rod of clutch 2 and the first cylinder 1 and the piston rod of the second cylinder 8 can be threaded connection, namely at clutch 2 two ends thread mill drilling 21, it would however also be possible to employ other connected modes commonly used in the art connect.
Further, referring to Fig. 1 (or Fig. 2), in the pneumatic actuator that this utility model embodiment provides, owing to shift fork 6 itself is provided in casing, this casing therefore can be utilized as anchoring base 9.
To sum up, this utility model embodiment with novel catalytic cracking process requirements be according to, rise to point of penetration with refinery device efficiency, to ensure that catalytic unit key equipment safe operation is for target, existing single-phase orifice valve pneumatic actuator is optimized improvement, it is provided that a kind of buffering disengaging type pneumatic actuator.By being connected to clutch between double; two cylinder and stepless switching reaches servo-actuated valve opening and auxiliary closes the effect of valve, changing two formula pneumatic actuators and force the duct pressure loss caused during valve opening excessive, device efficiency improves.And the series connection of double; two cylinder increases pass valve moment, it is ensured that under accident condition, orifice valve shuts and zero leakage.Adopting swing type buffer damping oil cylinder, close in valve process, while oil cylinder swings along pin joint, piston rod does Direct Travel and moves, and in swing process, cylinder damping size changes with angle change.Avoid that damping that Direct Travel oil cylinder constant damping causes is excessive or jam, it is achieved close valve end buffering, protect sealing surface.Adopt big orifice Pneumatic valve to control cylinder commutation, instead of electromagnetic valve in conventional design and control cylinder commutation.Big orifice Pneumatic valve is entirely capable of meeting flow and the rate request of double; two cylinder, it is to avoid the cylinder " creeping " caused because of underfed during little bare sizing electro-magnetic valve commutation.
The above is for only for ease of those skilled in the art and understands the technical solution of the utility model, not in order to limit this utility model.All within spirit of the present utility model and principle, any amendment of making, equivalent replacement, improvement etc., should be included within protection domain of the present utility model.
Claims (8)
1., for a pneumatic actuator for one-way damper valve, described pneumatic actuator includes: the first cylinder (1), the second cylinder (8), shift fork axle (3), shift fork (6) and cylinder commutation control unit；
The bar portion of described shift fork (6) is fixing with the valve shaft (5) of described one-way damper valve to be connected；
Described cylinder commutation control unit is used for controlling described first cylinder (1) and described second cylinder (8) commutation；
It is characterized in that,
Described pneumatic actuator also includes: clutch (2)；
Described clutch (2) is cylinder, and described clutch is provided with gathering sill along its longitudinally on (2)；The two ends of described clutch (2) are fixing with the piston rod of the piston rod of described first cylinder (1) and described second cylinder (8) respectively to be connected；
Described shift fork axle (3) stretches into the gathering sill on the U-shaped opening of described shift fork (6) end and described clutch (2)；Described shift fork axle (3) can be slided in described U-shaped opening and can be simultaneously for linear motion in described gathering sill.
2. pneumatic actuator according to claim 1, it is characterised in that described pneumatic actuator also includes: damping oil cylinder (7) and anchoring base (9)；
Described damping oil cylinder (7) is swing type damping oil cylinder, the cylinder body of described damping oil cylinder (7) and described anchoring base (9) are articulated and connected, and the bar portion of the piston rod of described damping oil cylinder (7) and described shift fork (6) is articulated and connected.
3. pneumatic actuator according to claim 1, it is characterised in that described cylinder commutation control unit includes: electromagnetic valve (11) and Pneumatic valve (10)；
Electromagnetic valve source of the gas input port (11P) is connected with source of the gas (P), and electromagnetic valve delivery outlet (11A) is connected by trachea with Pneumatic valve commutation control mouth (O)；
Pneumatic valve source of the gas input port (10P) is connected with described source of the gas (P), Pneumatic valve the first delivery outlet (10A) and interface (1A) on the first cylinder and on the second cylinder interface (8A) be connected, Pneumatic valve the second delivery outlet (10B) is connected with the first cylinder lower interface (1B) and the second cylinder lower interface (8B)；
When described one-way damper valve is opened, described electromagnetic valve source of the gas input port (11P) and described electromagnetic valve delivery outlet (11A) are in connected state, described Pneumatic valve source of the gas input port (10P) and described Pneumatic valve the second delivery outlet (10B) are in connected state, and described Pneumatic valve the first delivery outlet (10A) and Pneumatic valve first row QI KOU (10R) are in connected state；
When described one-way damper valve is closed, described electromagnetic valve source of the gas input port (11P) and described electromagnetic valve delivery outlet (11A) are off, described Pneumatic valve source of the gas input port (10P) and described Pneumatic valve the first delivery outlet (10A) are in connected state, and described Pneumatic valve the second delivery outlet (10B) and Pneumatic valve second exhaust port (10S) are in connected state.
4. pneumatic actuator according to claim 3, it is characterized in that, described cylinder exchange system also includes source of the gas bigeminy part (12), described source of the gas bigeminy part (12) one end is connected with described source of the gas (P), and the other end is connected with described electromagnetic valve source of the gas input port (11P) and described Pneumatic valve source of the gas input port (10P).
5. pneumatic actuator according to claim 1, it is characterised in that the two ends of described shift fork axle (3) are additionally provided with circlip (13).
6. pneumatic actuator according to claim 1, it is characterised in that the bar portion of described shift fork (6) is connected by flat key (4) with the valve shaft (5) of described one-way damper valve.
7. pneumatic actuator according to claim 1, it is characterised in that described clutch (2) is threaded connection with the piston rod of described first cylinder (1) and the piston rod of described second cylinder (8).
8. pneumatic actuator according to claim 1, it is characterised in that described anchoring base (9) is casing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201521106116.XU CN205371774U (en) | 2015-12-26 | 2015-12-26 | A pneumatic actuator for one -way damping delivery valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201521106116.XU CN205371774U (en) | 2015-12-26 | 2015-12-26 | A pneumatic actuator for one -way damping delivery valve |
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| CN205371774U true CN205371774U (en) | 2016-07-06 |
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| CN201521106116.XU Active CN205371774U (en) | 2015-12-26 | 2015-12-26 | A pneumatic actuator for one -way damping delivery valve |
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