Axelson Valve Manual
Disclosed is a relay valve having a valve body with a longitudinal bore having axially spaced apart along its length and extending into the valve bore an inlet, and outlet, an exhaust, and a pilot inlet. A valve stem is slidingly mounted in the valve bore and is movable between a first position in which the inlet is in communication with the outlet and communication from the outlet to the exhaust is blocked, and a second position in which the outlet is in communication with the exhaust and communication from the inlet to the outlet is blocked. A piston is slidingly mounted in the valve bore and is movable with respect to the valve stem. The piston has a longitudinal piston bore and a piston spring is provided for urging the piston toward a closed end of the valve bore. A spool is connected to the stem and is slidingly positioned in the piston bore. The spool is movable with respect to the piston between an open position in which a chamber defined between the piston and the closed end of the bore is in communication with the exhaust and a closed position in which communication between the chamber and the exhaust is blocked and the pilot inlet is in communication with the chamber.
A spool spring is provided for urging the spool toward the open position. What is claimed is: 1. BACKGROUND OF THE INVENTION A.
Field of the Invention The present invention relates to manually operated relay valves of the type used in fluid control systems such as safety systems for oil and gas wells, and more particularly to a relay valve that is relatively easily manually operable to shut in the system and that must be manually returned to service after the system has been shut in. Description of the Prior Art Safety systems for shutting in oil and gas well production lines and other flow lines in the event of unusually high or low pressure conditions are well known. Such systems include a pneumatically or hydraulically actuated safety valve for controlling the fluid flow in the line and sensors or pilot valves for sensing pressure in the flow line and producing a signal when the flow line pressure varies from its intended operating range. The systems include a relay valve which receives pressure from the sensors and supplies fluid pressure to the safety valve actuator. When the sensors signal an abnormal flow line pressure, the relay valve operates to vent the safety valve actuator and allow the safety valve to close. Relay valves typically include some means for preventing the relay from going back into service after it has operated to shut in the safety valve. The preventing means may be either external, as shown for example in McMullan U.S.
3,823,739, or internal, as shown for example in Theriot, et al. 3,877,484, or 3,963,050. A primary shortcoming of the relay valves of the prior art lies in their capacity to be shut in manually.
Relay valves include a relatively large diameter pilot piston that is acted upon by pilot pressure to maintain the relay in its in-service position. If the operator desires to shut in the system manually, he must exert a closing force on the relay equal to the pilot pressure multiplied by the area of the pilot piston. Since the safety valve actuator systems operate at relatively high pressures, it has been necessary in the past to regulate and reduce pilot pressure so that the operator can manually shut in the relay. Regulating the pilot pressure has added complexity to the system and has added a source of system failure. It is therefore an object of the present invention to provide a relay valve that overcomes the shortcomings of the prior art. More particularly, it is an object of the present invention to provide a relay valve that may be manually shut in over a greater range of pilot pressures than was heretofore available. It is a further object of the present invention to provide a relay valve that operates more rapidly to shut in the system in response to a drop in pilot pressure.
SUMMARY OF THE INVENTION Briefly stated, the foregoing and other objects are accomplished by the relay valve of the present invention, which includes a valve body with a longitudinal bore having axially spaced apart along its length an inlet, an outlet, an exhaust, and a pilot inlet. A valve stem is slidingly mounted in the valve bore and is movable between a first or in-service position in which the inlet is in communication with the outlet and communication from the outlet to the exhaust is blocked, and a second, shut in or normal, position in which the outlet is in communication with the exhaust and communication from the exhaust and communication from the inlet to the outlet is blocked. A piston is slidingly mounted in the valve bore and is movable with respect to the stem. The piston has a longitudinal piston bore and defines a chamber in the valve bore between the piston and a closed end of the valve bore. A piston spring is provided for urging the piston toward the closed end of the valve bore.
A spool is connected to the stem and slidingly positioned in the piston bore. The spool is movable with respect to the piston bore between an open position in which the chamber is in communication with the exhaust and communication between the pilot inlet and the chamber is blocked, and a closed position in which communication between the chamber and exhaust is blocked and the pilot inlet is in communication with the chamber.
A spool spring is provided for urging the spool toward its open position. Thus, when the spool is in the closed position, pressure within the chamber acts on the spool and piston to move the stem to or maintain the stem in the first or in-service position. When the spool is in the open position, pressure in the chamber vents to the exhaust and allows the piston and spool to move toward the closed end of the valve bore, which in turn causes the stem to move to the second, shut in or normal, position. Also, when the spool is in the second position, the pilot inlet is isolated from the chamber so that pilot pressure cannot return the stem to the in-service position unless the spool is manually closed.
The stem may be manually operated to move from the first position to the second position by manually opening the spool. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal sectional view of the preferred embodiment of the relay valve of the present invention in the in-service position.
2 is a longitudinal sectional view of the preferred embodiment of the relay valve of the present invention in the shut in or normal position. 3 is a partial longitudinal sectional view of the preferred embodiment of the relay valve of the present invention illustrating the operation of the valve in moving from the in-service position to the shut in position. 4 is a partial longitudinal sectional view of the preferred embodiment of the relay valve of the present invention showing the operation of the valve in moving from the shut in position to the in-service position. DESCRIPTION OF THE PREFERRED EMBODIMENT Referring now to the drawings, and first to FIGS. 1 and 2, the relay valve of the present invention is designated generally by the numeral 11.
Relay valve 11 includes a valve body 13 having a longitudinal valve bore 15 therethrough. Valve bore 15 includes an open first end 17 and a second end 19 that is closed by an end cap 21. An O-ring seal 22 is provided to seal between end 19 and end cap 21. Valve bore 14 includes a first sealing bore portion 23 generally adjacent open end 17 and an enlarged diameter second sealing bore portion 25 generally adjacent second end 19. Valve body 13 includes a plurality of axially spaced apart radially extending ports communicating with valve bore 15. The ports include an inlet 27, an outlet 29, an exhaust 31, and a pilot inlet 33.
A valve stem 35 is axially movably positioned in valve bore 15 and is movable to perform the valving functions among inlet 27, outlet 29, and exhaust 31. An O-ring seal 37 is carried by stem 35 to sealingly engage first sealing bore portion 23 of valve bore 15 between inlet 27 and first end 17 of valve bore 15.
A first cup seal 39 is carried by valve stem 35 to sealingly engage first sealing bore portion 23 of valve bore 15 to isolate outlet 29 from inlet 27 when relay valve 11 is in the shut in or normal position, as shown in FIG. First cup seal 39 is positioned to reside in a radially enlarged portion 41 of valve bore 15 when valve stem 35 is in the in-service position to communicate inlet 27 with outlet 29, as shown in FIG.
A second cup seal 43 is carried by valve stem 35 generally between outlet 29 and exhaust 31. Second cup seal 43 is positioned to sealingly engage first sealing bore 23 of valve bore 15 to isolate exhaust 31 from outlet 29 when valve stem 35 is in the in-service position, as shown in FIG. Second cup seal 43 is disposed in a radially enlarged portion 45 of valve bore 15 to communicate outlet 29 with exhaust 31 when valve stem 35 is in the normal or shut in position, as shown in FIG. Thus, when valve stem 35 is in the in-service position, as shown in FIG. 1, inlet 27 is communicated with outlet 29 and exhaust 31 is isolated from outlet 29. Conversely, when valve stem 35 is in the normal or shut in position, inlet 27 is isolated from outlet 29 and outlet 29 is communicated with exhaust 31. Since cup seals generate greater frictional forces than do O-rings, first sealing bore portion 23 of valve bore 15 below inlet 27, which is engaged by cup seals 39 and 43, may have a slightly larger diameter than the portion of first sealing bore portion 23 above inlet 27, which is engaged by O-ring 37.
Thus, the slightly greater frictional force generated by the cup seals is balanced by a slightly greater pressure force acting on the cup seals. The increase in diameter of first sealing bore portion 23 is selected so that the pressure and frictional forces are preferably balanced so that pressure at inlet 27 causes no movement of valve stem 35.
Valve stem 35 includes a handle or knob 47 so that valve stem 35 may be easily manipulated between its in-service and shut in or normal positions. The movement of valve stem 35 between its in-service and shut in or normal positions is operated and controlled by a piston and spool assembly designated generally by the numeral 49. Piston and spool assembly 49 include a piston 51 axially movably positioned in second sealing bore portion 25 of valve bore 15. Piston 51 cooperates with second sealing bore portion 25 and end cap 21 to form a chamber 53. A first piston seal 55 is carried by piston 51 in sealing engagement with second sealing bore portion 25 of valve bore 15 to isolate exhaust 31 from pilot inlet 33.
A second piston seal 57 is carried by piston 51 in sealing engagement with second sealing bore portion 25 of valve bore 15 to isolate pilot inlet 33 from chamber 53. First piston seal 55 and second piston seal 57 have equal and opposed effective areas so that pressure from pilot inlet 33 in the space between piston seals 55 and 57 produces no net force on piston 51.
Piston 51 includes a longitudinal piston bore 59. A radially extending first passage 61 is formed in piston 51 to communicate piston bore 59 with the space between piston seals 55 and 57. A generally longitudinally extending second passage 63 is formed in piston 51 to communicate piston bore 59 with chamber 53. A piston spring 65 is disposed in the radially enlarged portion 45 of valve bore 15 intermediate first sealing bore portion 23 and second sealing bore portion 25 to urge piston 51 toward second end 19 and end cap 21.
Piston and spool assembly 49 includes a spool 67 connected to valve stem 35 and axially movably positioned in piston bore 59. Spool 67 carries a first spool seal 69 in sealing engagement with piston bore 59 to isolate first passage 61 of piston 51 from chamber 53. Spool 67 also carries a second spool seal 71 in sealing engagement with piston bore 59. Second spool seal 71 is movable with spool 67 between a closed position, as shown in FIG.
1, wherein passages 61 and 63 are communicated with each other through piston bore 59 and passage 63 is isolated from exhaust 31, and an open position, as shown in FIG. 2, in which passages 61 and 63 are isolated from each other and passage 63 is communicated with exhaust 31. Piston 51 includes a plurality of ports 73 to provide a flow path from passage 63 to exhaust 31. A spool spring 75 is positioned between piston 51 and spool 67 to urge spool 67 toward its open position. When spool 67 is in the closed position, pressure from pilot inlet 33 communicates with chamber 53 through first passageway 61, piston bore 59 between spool seals 69 and 71, and second passage 63.
Spool seals 69 and 71 have equal and opposed effective areas such that the pressure therebetween applies no net force to move spool 67. Pressure in chamber 53 acts to urge spool 67 axially with respect to piston 51 to compress spool spring 75 and engage spool 67 with a stop 77 in piston bore 59. Pressure in chamber 53 also acts to urge piston 51 axially in second sealing bore portion 25 of valve bore 15 to compress piston spring 65.
The force acting on piston spring 65 is equal to the pressure in chamber 53 multiplied by the combined effective areas of piston 51 and spool 67. The pressure in chamber 53 acts on the effective area of spool 67 to move and maintain valve stem 35 in the in-service position. When spool 67 is in the open position, as shown in FIG. 2, chamber 53 is isolated from pilot inlet 33.
Pressure at pilot inlet 33 acts only between piston seals 55 and 57 and spool seals 69 and 71. Since piston seals 55 and 57, on the one hand, and spool seals 69 and 71, on the other, have equal and opposed respective effective areas, pressure at pilot inlet 33 has no tendency to move either piston 51 or spool 67. Thus, valve stem 35 cannot be returned from the normal or shut in position to the in-service position unless valve stem 35 is manually pulled out to move spool 67 to the closed position. When stem 35 is in the shut in or normal position, piston 51 abuts a stop 81 formed by end cap 21 which limits the axial movement of piston 51 while allowing spool 67 to be fully open. Referring to FIG.
4, there is illustrated the condition of relay valve 11 at the instant that spool 67 is moved to the closed position when stem 35 is otherwise in the normal or shut in position. Spool spring 75 has been compressed slightly and spool seal 71 has moved about the inlet 79 to second spool passage 63. Since spool spring 75 produces a smaller force than piston spring 65, piston 51 remains fully against the stop 81 formed by end cap 21. The pilot fluid at pilot inlet 33 begins to flow through passages 61 and 63 to pressurize chamber 53.
Immediately after the instant depicted in FIG. 4, pressure in chamber 53 acts to urge spool 67 against stop 77. With spool 67 in the closed position, pressure acts on spool 67 and piston 51 to urge them outwardly, thereby moving stem 35 to the inservice position, as shown in FIG. Piston 51 preferably includes a plurality of standoffs 85 to prevent piston 51 from sticking to upper stop 83. Referring to FIG. 3, there is illustrated the condition of relay valve 11 at the instant that spool 67 has moved to the open position, either by the manipulation of stem 35 or by a decrease in pressure at pilot inlet 33. The force required to move spool 67 to the open position is equal only to the pressure in chamber 53 multiplied by the effective area of spool 67, which is substantially less than the effective area of piston 51.
Thus, in the case of manipulation of stem 35, a relatively small force may be applied to stem 35 to move spool 67 to the open position and thereby manually shut in relay valve 11. Spool spring 75 is selected to provide an opening force on spool 67 that is less than the force generated by the normally expected pressure at pilot inlet 33 but greater than some reduced pressure so that when pilot pressure drops below a selected value, spool 67 opens. Thus, upon a drop in pilot pressure, spool 67 moves quickly to the open position, simultaneously blocking communication between pilot inlet 33 and chamber 53 and allowing communication between chamber 53 and exhaust 31.
3, spool seal 71 has shifted to simultaneously isolate passage 61 from passage 63 and communicate chamber 53 with exhaust 31, thus allowing pressure to bleed from chamber 53. As pressure bleeds from chamber 53, spring 65 urges piston 51 toward end cap 21 and stem 35 moves to the normal or shut in position, as shown in FIG. When spool 67 is open, pressure in chamber 53 can act on neither spool 67 nor piston 51. Thus, when spool 67 opens, either because of manipulation of stem 35 or because of a drop in pilot pressure, stem 35 moves quickly and positively to the normal or shut in position under the force of piston spring 65. Spool spring 75 maintains spool 67 in the open position. When stem 35 is in the normal or shut in position, a return of pilot pressure will not move stem 35 back to the in-service position. Stem 35 may be returned to the in-service position only by manually closing spool 67.
Relay valve 11 is particularly adapted for use in oil and gas well safety systems. In such systems, a source of valve actuator operating fluid, which may be either pneumatic or hydraulic, is connected to inlet 27 and outlet 29 is connected to the valve actuator. The system sensors are connected to pilot inlet 33 in the manner known to those skilled in the art.
Since relay valve 11 may be operated manually to shut in with substantially less force than is required with heretofore existing relays, pilot pressure does not have to be regulated and the same source may be used for both actuator pressure and pilot pressure. Further modifications and alternative embodiments of the apparatus of this invention will be apparent to those skilled in the art in view of this description. Accordingly, this description is to be construed as illustrative only and is for the purpose of teaching those skilled in the art the manner of carrying out the invention. It is to be understood that the form of the invention herewith shown and described is to be taken as the presently preferred embodiment. Various changes may be made in the shape, size, and arrangement of parts. For example, equivalent elements or materials may be substituted for those illustrated and described herein, parts may be reversed, and certain features of the invention may be utilized independently of the use of other features, all as would be apparent to one skilled in the art after having the benefit of this description of the invention.
Disclosed is a pressure controller for sensing changes in a service pressure and controlling a control pressure in response to such changes. The pressure controller includes a valve body having a control inlet and a bleed outlet with a passage therebetween. A valve seat is positioned in the passage and a valve member is reciprocatingly mounted in the valve body for movement between a closed position in engagement with the valve seat and an open position out of engagement with the valve seat.
The controller includes a releasable latch for latching the valve member in the closed position. The controller includes a release mechanism for releasing the latch in response to changes in service pressure to allow the valve member to move to the open position. What is claimed is: 1.
BACKGROUND OF THE INVENTION The present invention relates generally to the field of systems and apparatus for controlling the flow of fluid through flowlines in response to changes in service pressure within the flowlines, and more particularly, to a pressure controller that is adapted to sense changes in service pressure and control a control pressure in response to such changes, wherein the control and sense functions are independent of each other and wherein the control function is capable of operating at very high pressures. DESCRIPTION OF THE PRIOR ART In the past, various systems have been developed to control the flow the fluid through a flowline when the pressure in the flowline is less than or greater than a predetermined maximum or minimum.
One such system, which is described in U.S. 3,043,331, includes a control system that supplies pressurized fluid to an actuator that holds a valve inserted in the flowline in a normally open position. A pair of pilot valves is connected to the system and adapted to sense pressure and vent the control system when the line pressure is greater than or less than the maximum or minimum. The venting of the control system causes the actuator to allow the safety valve to close. An example of a pilot valve adapted for use in such a system is disclosed in U.S. The pilot valve includes a valve body having spaced apart inlet, outlet, and bleed ports that communicate with a bore.
The valve includes a spool slidingly mounted in the bore and having spaced apart O-ring type seals. The spool is movable between a first position in which the inlet and outlet ports are communicated and the bleed port is blocked and a second position in which the outlet and bleed ports are communicated but the inlet port is blocked. The spool is urged in one direction by a spring and in the other direction by a piston which is exposed to service pressure.
Axelson Relief Valve Manual
Most sensors or pilot valves of the type described above are adapted to control only low pressures. Accordingly, in order to control higher pressures, there have been developed systems that include interfacing valves to control high pressures. Such interfacing valves are commonly called relays, and systems including such relays are disclosed, for example, in U.S. 3,877,484, U.S. 3,963,050, and U.S. Such relays are pressure operated three-way block and bleed valves that are adapted to shift when they receive a signal from a sensor or pilot valve. Additional relay type valves are disclosed, for example, in U.S.
3,823,739, U.S. 4,073,466, and U.S.
One shortcoming of all of the above described valves and systems is in that they all include a spool, or the like, which moves longitudinally in a bore and which forms seals by means of O-rings or the like. The O-ring seals frictionally engage the bores of the valves and the magnitude of the frictional engagement is substantially directly proportional to the pressure differential on either side of the O-ring. In high pressure applications, O-ring friction affects greatly the reliability and repeatability of the valve. Thus, such valves are best suited to relatively low pressure application.
And additional, but related shortcoming of such valves is in that O-rings have a tendency to extrude and fail in high pressure applications. Alternative pilot valve arrangements are disclosed in related U.S. 4,017,053, 4,026,326, and in U.S. All of those three patents disclose two-way, bleed-only, pilot valves that are operated by a longitudinally movable cam. The pilot valve of the U.S. 4,017,053 and 4,026,326 operate by pressure a three-way block and bleed relay.
It is an object of the present invention to provide a pressure controller that overcomes the shortcomings of the prior art. More specifically, it is an object of the present invention to provide a pressure controller that is reliable and repeatable at high pressures. It is a further object of the present invention to provide a pressure controller that eliminates the need for separate sensors and relays and associated sources of separate control and instrument pressure.
It is a further object of the present invention to provide a pressure controller that includes built in manual override functions. It is a further object of the present invention to provide a pressure controller that may be reset only manually and which will not reset automatically.
Axelson Valve Pilot
SUMMARY OF THE INVENTION The foregoing and other objects are accomplished by the pressure controller of the present invention. In its broadest aspect, the pressure controller of the present invention includes a valve body having a control inlet and bleed outlet. A valve seat is positioned in a passage between the control inlet and the bleed outlet. A valve member is reciprocally mounted in the valve body for movement between a closed position in engagement with the valve seat to block communication between the control inlet and the bleed outlet and an open position out of engagement with the valve seat. Means are provided for releasably latching the valve member in the closed position. Means are also provided for releasing the latch means in response to a change in service pressure to allow the valve member to move to the opened position. The latch means includes a detent recess formed in the valve body.
A detent is movably carried with the valve member and a trigger is provided for urging the detent into engagement with the detent recess when the valve member is in the closed position. Pressure generated forces tending to urge the valve member out of engagement with the seat are transmitted from the valve member to the valve body by the engagement of the detent with the detent recess. The release means of the present invention includes an instrument body mounted adjacent the valve body.
A piston is reciprocatingly mounted in the instrument body and is exposed to service pressure received in the instrument body through a sense inlet. An operator is longitudinally movably mounted in the instrument body for movement with the piston. A spring is provided for urging the operator and piston in the direction opposite the force due to the service pressure acting on the piston. The operator includes a cam portion that engages a cam follower that is operably connected with the trigger of the latch means. When service pressure varies from its intended range, the operator moves longitudinally, thereby causing the cam portion to move the cam follower and trigger.
Movement of the trigger allows the detent to become disengaged from the detent recess in the valve body. With the detent so disengaged, pressure forces move the valve member to the open position. Means are provided for resetting or reclosing the valve member. Preferably, the resetting or reclosing means includes a reset yoke that is operable from exterior of the valve and instrument bodies. The reset yoke is engageable with the valve member to urge the valve member into engagement with the seat.
If the service pressure is within the desired range, the trigger will operate to urge the detent into engagement with the detent recess. Means are also provided for manually opening the valve when the service pressure is within the desired range. Preferably, the opening means includes a trip yoke having a portion extending exterior of the valve and instrument bodies and a portion engageable with the trigger. In another aspect of the present invention, the pressure controller may include a control outlet in communication with the passage between the valve seat and the control inlet. In such embodiment, the pressure controller includes a second valve seat positioned in the passageway between the control inlet and the control outlet and a second valve member reciprocatingly mounted in the passage for movement between a closed position and engagement with the second valve seat to block communication between the control inlet and the control outlet and an open position out of engagement with the second valve seat to allow communication between the control inlet and the control outlet. In such embodiment, the pressure controller includes means for holding the second valve member in the open position when the first recited valve member is in the closed position and for allowing the second member to move the closed position when the first valve member moves to the open position.
Such embodiment thereby provides a three-way block and bleed arrangement in that when the first valve member is closed, thereby blocking communication to the bleed outlet, the second valve member is open, thereby allowing communication from the control inlet to the control outlet. On the other hand, when the first valve member is open and the second valve member is closed, communication from the control inlet to the control outlet is blocked, but communication from the control outlet to the bleed outlet is allowed. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a schematic view showing a system embodying the pressure controller of the present invention in comparison with system of the prior art. 2 is side section view of a two way, bleed only, embodiment of the pressure controller of the present invention. 3 is a sectional view taken along line 3-3 of FIG. 4 is a fragmentary sectional view similar to FIG.
2 with the valve of the pressure controller of the present invention in the open position. 5 is a sectional view similar to FIG. 3 with the valve of the pressure controller of the present invention in the open position. 6 is a sectional view similar to FIG. 5 showing the valve of the pressure controller of the present invention moved manually to the closed positioned, but with service pressure outside the desired range.
7 is a sectional view similar to FIG. 6, but with the service pressure within the desired range. 8 is a sectional view of a three-way block and bleed embodiment of the pressure controller of the present invention. 9 is a fragmentary sectional view of the embodiment of FIG. 8 in the bleed position. 10 is a sectional view of an alternative embodiment of the three-way block and bleed embodiment of the present invention.
11 is a fragmentary sectional view of the embodiment of FIG. 10 in the bleed position. 12 is a sectional view of a high-low three-way block and bleed embodiment of the pressure controller of the present invention. DESCRIPTION OF THE PREFERRED EMBODIMENT Referring now to the drawings, a subsurface safety system including a pressure controller of the present invention is illustrated schematically and compared with a system of the prior art. The subsurface safety system includes a subsurface safety valve included in a string of tubing 13 in the well bore 15 at some point below the surface. A packer 17 is provided for packing off the annulus exterior of tubing string 13. Subsurface safety vavles of the type of subsurface safety valve 11 are commercially available and generally well known.
Axelson Relief Valve Manuals
Subsurface safety valve 11 is held in the open position by high pressure hydraulic fluid supplied thereto through a line 19. Hydraulic fluid is supplied to line 19 by a control system, which is adapted to sense the pressure of the fluid flowing out of the well through tubing 13 and maintain the supply of hydraulic pressure to subsurface safety valve 11 as long as the pressure is above a predetermined minimum or below a predetermined maximum. If the pressure varies from the predetermined range, then the control system is adapted to relieve the hydraulic pressure supplied to subsurface safety valve 11 and allow it to close. A typical control system of the prior art is enclosed in dashed lines in FIG. The prior art system includes a high pressure hydraulic supply 21 and a low pressure pneumatic instrument supply 23.
High pressure hydraulic control supply 21 supplies hydraulic fluid to subsurface safety valve 11 through a relay 25. Instrument pressure is supplied to relay 25 by low pressure instrument supply 23 through a high pressure sensor 27 and a low pressure sensor 29. Sensors 27 and 29 are connected to receive tubing pressure through a manifold system 31. As long as tubing pressure remains within the predetermined pressure range, sensors 27 and 29 remain in the inservice position to supply instrument pressure to relay 25. If, however, tubing pressure varies outside the predetermined range, then sensor 27 or sensor 29 will shift and bleed instrument pressure from relay 25, whereupon relay 25 will shift to bleed hydraulic pressure from subsurface safety valve 11, which will allow subsurface safety valve 11 to close. Relays of the type of relay 25 normally have a manual override feature, which allows subsurface safety valve 11 to be closed manually, and a lockout and manual reset feature, which prevents relay 25 from automatically returning to the reset position after it has tripped. A control system which includes the pressure controller of the present invention is designated generally by the numeral 33.
Control system 33 includes a high pressure hydraulic control supply 35 which supplies high pressure hydraulic fluid to subsurface safety valve 11 through a pressure controller 37. As will be explained in detail hereinafter in connection with the embodiments of the invention disclosed in FIGS. 8-12, pressure controller 37 is adapted for connection to receive and sense tubing pressure and to relieve controlled pressure from subsurface safety valve 11 when tubing pressure is either too high or too low. It is readily apparent that the control system that includes pressure controller 37 of the present invention is much simpler than that of the prior art in that is does not include separate instrument and control supplies or separate sensors and relays. Referring now to FIG. 2, one embodiment of the pressure controller of the present invention is designated generally by the numeral 39. The embodiment of FIG.
2 is a high or low, two-way bleed-only hydraulic controller. Pressure controller 39 includes a valve body 41 having a control inlet 43 and a bleed outlet 45.
Control inlet 43 and bleed outlet 45 are intercommunicated by a passageway 47 which, when pressure controller 39 is in service, is closed by a valve designated generally by the numeral 49. Valve 49 includes a seat 51 and a valve member 53. Seat 51 is formed at the inner end of a tubular member 55 which is sealingly slidingly mounted within valve body 41. Preferably, the sliding seal is provided by a cup type seal shown schematically at 57. Tubular member 55 is biased inwardly toward valve member 53 by a spring 59 which is held in valve body 41 by a spring retainer 61.
Additionally, pressure forces received at control inlet 43 act to urge tubular portion 55 inwardly to firmly engage seat 51 with valve member 53. Valve member 53 includes a relatively large diameter tubular detent carrier 63 which is slidingly sealingly mounted within valve body 41. The sliding seal is preferably accomplished by an O-ring 65. The diameter of detent carrier 63 is substantially greater than the diameter of valve member 53 within seat 51.
Thus, when valve member 53 becomes unseated, the forces acting on valve member 53 are multiplied to drive valve member 53 forcefully to the open position. Valve member 53 is releasably latched in the closed position by a latch designated generally by the numeral 67. Latch 67 includes detent carrier 63 which has therein a plurality of detent apertures 69. Each detent aperture 69 carries a detent ball 71. Detent balls 71 are radially inwardly and outwardly movable in detent apertures 69.
Valve body 41 includes an annular detent recess 73 which is adapted to receive detent balls 71 when valve member 53 is in the closed position. Detent balls 71 are held into detent recess 73 by a spool-shaped trigger 75. Trigger 75 includes a radially outwardly facing shoulder 77 which engages detent balls 71 into detent recess 73. Trigger 75 is biased axially upwardly against a stop bar 79 by a spring 81. When trigger 75 is in contact with stop bar 79, shoulder 77 registers with detent recess 73 to latch valve member 53 closed.
Pressure forces tending to open valve member 43 are transmitted through detent carrier 63 and detent balls 71 into detent recess 73. Latch 67 is released to allow valve 49 to open by means of release means designated generally by the numeral 83. Release means 83 includes an instrument body 85 which includes a service inlet 87. Service inlet 87 communicates service pressure to a cylindrical chamber 89 within instrument body 85.
Chamber 89 has slidingly sealingly mounted therein a piston 91 that is acted on by service pressure. Release means 83 includes an elongated cylindrical operator 93 longitudinally slidingly mounted within instrument body 85. Operator 93 includes a first end 95 that abuts piston 91 and a second end 97. Second end 97 abuts a spring pad 99 which compresses a spring 101 within a spring chamber formed at one end of instrument body 85. Spring chamber 103 is formed by a cap 105 that is threadedly engaged with the exterior of instrument body 85 so as to be axially movable to vary the compression of spring 101. Operator 93 includes a cam portion 107 intermediate ends 95 and 97.
Cam portion 107 includes a reduced diameter portion 109 and a conical camming surface 111. A cam follower 113 is axially slidingly mounted through stop bar 79 and includes a conical portion 115 which engages cam portion 107 of operator 93 and a shoulder 117 which engages trigger 75. Spring 101 biases operator 93 leftward as shown in FIG. 2 against the force generated by service pressure acting on piston 91. The embodiment shown in FIG.
2 acts as a low sensor in that as long as service pressure remains above a predetermined minimum piston 91 and operator 93 wil remain in the position shown in FIG. If, however, service pressure drops below the predetermined minimum, the force of spring 101 will urge operator 93 and piston 95 leftward. Such leftward movement of operator 95 will be transmitted to caming surface 11 to cam follower 113 and cause cam follower 113 to move axially downwardly. Such axially downward movement of cam follower 113 is transmitted to trigger 75, which in turn moves shoulder 77 axially out of register with detent balls 71. With shoulder 77 so moved, detent balls 71 are no longer restrained against radial movement and are free to move radially inwardly into a recess 119 in trigger 75. Such inward movement of detent balls 71 allows valve member 53 to move axially upwardly into engagement with a stop ring 121 to the open position, as shown in FIG.
While the embodiment shown in FIG. 2 operates as a low sensor, it will be recognized that pressure controller 39 may operate as a high sensor by reversing the ends of operator 93 such that end 97 abuts piston 91 and end 95 abuts spring pad 99. Referring now specifically to FIG. 3, means are provided for manually manipulating valve member 53 and trigger 75 exterior of valve body 41 and instrument body 85.
More specifically, a reset yoke 123 is provided for manipulating valve member 53 and a trip yoke 125 is provided for manipulating trigger 75. Reset yoke 123 includes a tubular upper portion 127 and a pair of depending legs 129.
Tubular portion 127 extends generally outwardly of instrument body 85 and is mounted within a nut 131 threadedly engaged with instrument body 85 for movement inwardly and outwardly thereof. A hand wheel 133 is connected to nut 131 so that nut 131 may be more readily rotated to move reset yoke 123 inwardly. Legs 129 of reset yoke 123 generally straddle operator 93 and extend into valve body 41 to contact stop ring 121. When valve member 53 is in the open position, as shown in FIG.
5, inward movement of reset yoke 123 moves valve member 53 toward the closed position. Trip yoke 125 likewise includes a cylindrical upper portion 135 and a pair of downwardly depending legs 137. Upper portion 135 of trip yoke 125 is slidingly mounted within tubular portion 127 of reset yoke 123. A spring 139 is positioned to bias trip yoke 125 axially downwardly with respect to reset yoke 123 to urge legs 137 into engagement with trigger 75. Spring 139 is selected to be weaker than spring 81 so as not to cause inadvertent tripping of latch 67.
If, however, it is desired to manually cause valve member 53 to move to the open position, the outwardly extending end 141 of trip yoke 125 may be pushed inwardly, thereby to move trigger 75 out of engagement with detent balls 71. Referring now to FIGS. 5-7, there is shown the sequence of returning valve member 53 from the open position to the closed position. 5, valve member 53 is open and service pressure is outside the predetermined range. Accordingly, cam follower 113 is shown urged axially downwardly by cam surface 111 and is in engagement with the maximum outside diameter of operator 93. It will be noted that upper portion 135 of trip yoke 125 includes an upper indicator mark 143 and an axially spaced apart lower indicator mark 145. When pressure controller 39 is in service, as shown for example in FIG.
3, upper indictor mark 143 is substantially even with the end of reset yoke 123. Since trip yoke 125 is urged continually into engagement with trigger 75, trip yoke 125 provides an indication of the position of trigger 75. Thus, in FIG. 5, upper indicator mark 143 is within reset yoke 123, thereby to indicate that latch 67 has tripped and service pressure is outside the predetermined range.
Referring now to FIG. 6, handwheel 133 and reset yoke 123 are shown in the axially inward position with valve member 53 thereby moved to the closed position. However, operator 93 is still in the out of service position. Thus, trigger 75 is prevented from moving axially outwardly into registry with detent recess 73 and latch 67 will not reset. The condition depicted in FIG.
6 is externally indicated by reference to the end of trip yoke 125, wherein the outer end of reset yoke 123 is approximately midway between upper indicator mark 143 and lower indicator mark 145. 7, handwheel 133 and reset yoke 123 are again in the inward position with valve member 53 closed.
However, operator 93 has returned to the in service position thereby allowing cam follower 113 and trigger 75 to be urged upwardly by spring 81. Outwardly facing shoulder 77 of trigger 75 is thus in registry with detent recess 73 thereby urging detent balls 71 radially outwardly into engagement therewith. The position of trigger 75 is indicated by the exposure of both upper indicator mark 143 and lower indicator mark 145 of trip yoke 125. Outward movement of handwheel 133 and reset yoke 123 returns pressure controller 39 to the in service position as shown, for example, in FIG. Referring now to FIGS.
8 and 9, there is shown a preferred embodiment of the pressure controller of the present invention as a high or low three-way block and bleed hydraulic controller. The latch and release means of the embodiment of FIGS., 8 and 9 are substantially the same as those described above. However, the embodiment of FIGS. 8 and 9 includes a valve body 41a that includes, in addition to a control inlet 43a and a bleed outlet 45a, a control outlet 147. Valve body 41a includes a passage 47a that intercommunicates control inlet 43a with control outlet 147 and bleed outlet 45a. A second valve seat 149 is positioned in passageway 47a between control inlet 43a and control outlet 147.
A second valve member, which in the embodiment of FIGS. 8 and 9 is a ball 151, is positioned in passageway 47a and is adapted to close by seating on second valve seat 149. Ball 151 is retained by a spring-loaded ball retainer 153 having a plurality of flow passages therethrough. Tubular member 55a includes a downwardly extending rod or stinger 155. Stinger 155 extends through second seat 149 and into contact with ball 151. When valve member 53a is closed, as shown in FIG.
8, tubular portion 55a and stinger 155 are urged downwardly to hold ball 151 off seat 149. Thus, in FIG.
8, there is communication between control inlet 43a and control outlet 147, but bleed outlet 45a is blocked. However, as shown in FIG. 9, when valve member 53a is in the open position, tubular portion 55a and stinger 155 move upwardly to allow ball 151 to seat on seat 149. Thus, in FIG.
9, control inlet 43a is blocked, but control outlet 147 and bleed outlet 45a are communicated. Referring now to FIGS. 10 and 11, there is shown an alternative embodiment of the present invention which is adapted for use as a high or low three-way pneumatic controller.
Again, the latch and release means of the embodiment of FIGS. 10 and 11 are substantially the same as those described above. However, the valving in valve body 41b is different.
Valve body 41b includes a control inlet 43b, a control outlet 147a and a bleed outlet 45b. A first valve seat 49a is defined by a cylindrical bore about passage 47b between control outlet 147a and bleed outlet 45b.
A second valve seat 149a is defined by a cylindrical bore between control inlet 43b and control outlet 147a. The first valve member of the embodiment of FIGS. 10 and 11 is formed by a seal 157 mounted on a rod 159 connected to detent carrier 63a. The second valve member is formed by a seal 161 positioned on rod 159. Seals 157 and 161 are spaced axially apart such that when seal 157 is sealingly engaged with first seat 49a, second seal 161 is positioned in a radially enlarged bore 163 between control inlet 43b and second valve seat 149, as shown in FIG. Thus, when the embodiment of FIGS.
10 and 11 is in service, there is communication between control inlet 43b and control outlet 147a, but bleed outlet 45b is blocked. However, as shown in FIG. 11, when the controller moves out of service, detent carrier 63a moves axially upwardly such that second seal 161 engages second seat 149a and first seal 157 moves out of engagement with first seat 49a, thereby to block control inlet 43b and communicate control outlet 149a with bleed outlet 45b.
Referring now to FIG. 12, there is shown a further alternative embodiment of the present invention which functions as a high and low three-way block and bleed hydraulic pressure controller. The operation of the valves within valve body 41c is substantially the same as that of the embodiment of FIGS.
8 and 9, in that latch means 67 is substantially the same as that described above. However, the release means of FIG. 12 is adapted to release latch 67 if service pressure is either high or low. The release means of the embodiment of FIG.
12 includes an instrument body 85a mounted adjacent to valve body 41c. Instrument body 85a includes a service inlet 87a which is adapted to receive and supply service pressure to a chamber 89a. A piston 91a is slidingly sealingly mounted in chamber 89a and is exposed to service pressure. An operator 93a is longitudinally slidingly mounted within instrument body 85a. A first end 95a of operator 93a abuts piston 91a and a second end 97a of operator 93a extends into a spring chamber 103a of instrument body 85a and into engagement with a spring pad 99a.
A main spring 165 is compressed between a cap 105a that is threadedly engaged with instrument body 85a and spring pad 99a. The force of spring 165 tends to urge spring pad 99a and operator 93a leftwards against the force generated by service pressure acting on piston 91a. The embodiment of FIG. 12 also includes a secondary spring pad 167 which includes a plurality of legs 169. Legs 169 extend axially through passageways in spring pad 99a into abutment with a stop surface 171 in spring chamber 103a. A secondary or high spring 173 is compressed between secondary spring pad 167 and a second spring adjustment screw 175 threadedly engaged in the end of cap 105a. Secondary spring 173 is adapted together with main spring 165 to oppose rightward movement of operator 93a and piston 91a.
The compression of main spring 165 may be varied by adjusting the axial position of cap 105a with respect to instrument body 85a and the compression of secondary spring 173 may be adjusted by varying the axial position of secondary spring adjustment screw 175 with respect to cap 105a. Operator 93a includes intermediate ends 95a and 97a a cam portion designated generally by the numeral 177. Cam portion 177 includes opposed conical caming surfaces 179 and 181. When the controller of FIG. 12 is inservice, cam follower 113 resides between caming surfaces 179 and 181. If service pressure within chamber 89a falls below a preselected minimum, main spring 165 urges spring pad 99a and operator 93a leftward thereby causing caming surface 179 to urge cam follower 113 axially to release latch 67.
If, on the other hand, service pressure within chamber 89aexceeds the predetermined maximum, piston 91a urges operator 93a rightward, thereby to move spring pad 99a and secondary spring pad 167 to compress springs 165 and 173, respectively. In such event, caming surface 181 urges cam follower 113 axially, again to release latch 67. From the foregoing it will be seen that this invention is one well adapted to attain all of the ends and objects hereinabove set forth, together with other advantages which are obvious and which are inherent to the apparatus.
It will be understood that certain features and subcombinations are of utility and may be employed with reference to other features and subcombinations. This is contemplated by and is within the scope of the claims. As many possible embodiments may be made of the invention without departing from the scope thereof, it is to be understood that all matter herein set forth or shown in the accompany drawings is to be interpreted as illustrative and not in a limiting sense.