CA1228582A - Subsea gate valve actuator with external manual override and drift adjustment - Google Patents
Subsea gate valve actuator with external manual override and drift adjustmentInfo
- Publication number
- CA1228582A CA1228582A CA000444865A CA444865A CA1228582A CA 1228582 A CA1228582 A CA 1228582A CA 000444865 A CA000444865 A CA 000444865A CA 444865 A CA444865 A CA 444865A CA 1228582 A CA1228582 A CA 1228582A
- Authority
- CA
- Canada
- Prior art keywords
- stem
- valve
- actuator
- housing
- piston
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 239000012530 fluid Substances 0.000 claims description 8
- 125000006850 spacer group Chemical group 0.000 claims description 6
- 230000008859 change Effects 0.000 claims description 3
- 238000012856 packing Methods 0.000 description 11
- 210000004907 gland Anatomy 0.000 description 10
- 241000191291 Abies alba Species 0.000 description 4
- 235000004507 Abies alba Nutrition 0.000 description 4
- 241000387514 Waldo Species 0.000 description 4
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 230000004888 barrier function Effects 0.000 description 3
- 230000002706 hydrostatic effect Effects 0.000 description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 3
- 230000000712 assembly Effects 0.000 description 2
- 238000000429 assembly Methods 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 238000012544 monitoring process Methods 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 235000009434 Actinidia chinensis Nutrition 0.000 description 1
- 244000298697 Actinidia deliciosa Species 0.000 description 1
- 235000009436 Actinidia deliciosa Nutrition 0.000 description 1
- 241000256856 Vespidae Species 0.000 description 1
- 230000004308 accommodation Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000009428 plumbing Methods 0.000 description 1
- 239000013641 positive control Substances 0.000 description 1
- 238000009877 rendering Methods 0.000 description 1
Classifications
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B34/00—Valve arrangements for boreholes or wells
- E21B34/02—Valve arrangements for boreholes or wells in well heads
- E21B34/04—Valve arrangements for boreholes or wells in well heads in underwater well heads
Landscapes
- Life Sciences & Earth Sciences (AREA)
- Engineering & Computer Science (AREA)
- Geology (AREA)
- Mining & Mineral Resources (AREA)
- Physics & Mathematics (AREA)
- Environmental & Geological Engineering (AREA)
- Fluid Mechanics (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Geochemistry & Mineralogy (AREA)
- Fluid-Driven Valves (AREA)
- Preventing Unauthorised Actuation Of Valves (AREA)
Abstract
Abstract of the Disclosure A hydraulically operated actuator for a sliding gate valve designed for use in a subsea environment. The actuator includes a manual override system that functions independently of the actuator's hydraulic piston and return spring, an externally accessible valve gate drift adjustment, an externally adjustable unstop for the actuator stem, a stem thread assembly that can be manufactured from a material different from the actuator stem to prevent or reduce the possibility of thread galling, a hydraulic control pressure porting system integral with the hydraulic cylinder to minimize space requirements, and a facility for accommodating an optional external electrical stem position indicator package.
Description
Background of the Invention This invention relates to gate valve actuators, and more particularly to hydraulically operated actuators for subset well gate valves.
For some time the oil and gas industry has required hydraulic actuators for operating gate valves on subset well Christmas trees, pipe manifolds, and other w~derwater well apparatus, and such actuators of various designs are in widespread use for this purpose. Preferably, an lo actuator for this type of service would be capable of manual operation in the event of hydraulic power failure, would have provision for external adjustment to compensate for valve gate drift, could be manually operated and adjusted with readily available tools and minimal effort, lo and would be compact in size and functionally reliable.
Summary of the Invention According to an aspect of the invention, a fluid powered actuator for a sliding gate valve comprises a valve body with a flow passage there through, a bonnet I connected to said body a valve gate in said body said valve await havillg a flow passage there through, and a valve stem connected to said gate and extending through said bonnet, said actuator comprises:
a housing with first and second opposed closed ends r fluid cylinder within said housing and having an end portion;
a fluid-powered piston within said cylinder for actuating said valve in an axial direction; an Atari stem connected to slid piston and extending through Roth of said opposed ends, said actuator stem comprising a first stem element extending from said piston thrill said first opposed housing end and terminating ill a means for releasable connecting said actuator stem to said valve stem, a second stem element extending prom sail piston through said cylinder end portion and said second opposed housing end and terminating in a means for rotating suckle second stem element with respect to said first stem element, s-top means on said second stem element cooperating with said second opposed housing end to limit PA
I
-pa-axial movement of said second stem element, and threaded means adjustable interconnecting said first and second stem elements in a end-to-end manner, sail threaded means comprising an externally threaded annular spacer releasable secured to one end of said first stem element and an internally threaded bore in said second element, said spacer and said bore cooperating to cause relative axial movement between said first and second stem elements when said second stem element is rotated with respect to lo said first stem element; means on said valve stem for cooperating with said releasable connecting means on said actuator stem for releasable connecting and disconnecting said actuator stem to said valve stem Chile the valve is under operating pressure; and means or connecting and disconnecting said housing to and from said valve bonnet while the valve is under operating pressure and for adjusting the position ox the valve Nate flow passage relative to the valve body flow passage, said connection and disconnecting means comprising an annular flange body and a sleeve-like collar, said collar connected to the housing by first thread means and connected to said flange body by second thread means, said first and second thread means constituting a differential thread system so that rotation of said collar with respect to said housing and said flange body will change I the axial spacing between the housing and the Lange body and (2) the position ox the valve gate with respect to the valve body and the bonnet.
The present invention as embodied in a hydraulic operated vale valve actuator has one or more of the above features. Such an actuator can include an externally adjustable valve vale drift adjustment system, a manual override system that does not exercise the hydraulic piston or its return spin at any time during I the manual override operation, thereby requiring the application of only minimal actuation torque ho the diver, and what does not introduce a potential leak path to control pressure fluid during said override cycle, an externally adjustable unstop for the actuator stem that A
5~3f~
-2b-can be used instead of the backseat between the valve stem and bonnet, and a separate and readily replaceable thread assembly for the actuator stem that offers reduced lo /
I
5~3Z
manufacturing costs and less potential for thread galling during the actuator's service life.
The actuator has a high spring load-to-actuation piston area ratio with multiple control ports for more rapid response to command control pressure. Should the control pressure fail the spring automatically and quickly returns the piston to its "valve closed" position, thereby providing effective fail-safe closed protection to the fluid conduit in which the valve is installed.
In its preferred form the actuator also includes a hydraulic control pressure porting system that is integral to the cylinder to minimize external plumbing requirements and the overall length and diameter of the actuator. A
manifolding hydraulic distribution system for the control pressure porting assures positive distribution of fluid to the cylinder during actuation, and minimizes the number of fabricated parts in the system.
In its preferred form the actuator further includes an ambient pressure compensation porting system on eke backside of the piston and piston cylinder to almost equalize the pressure in the static non-operating mode control pressure porting system caused by hydrostatic hydraulic head from sea level to the installed subset valve. This compensation system assures that the actuator is only operated to the open position by a positive control pressure command from the surface control system, and not by hydrostatic head pressure in the control pressure porting system.
The preferred form of actuator additionally includes an accommodation for an externally mounted electrical position indication package for monitoring the position of the actuator stem and, ultimately, the valve gate to which the stem is connected. Provision for manually monitoring the stem and gate positions, from outside the actuator also is present in the preferred embodiment in a form that is readily accessible to a diver.
Brief Description of the Drawings Figure 1 is a diagrammatic side elevation of a subset well completion system, showing valve actuators incorporating the present invention in functional position on gate valves of a subset Christmas tree.
Figure 2 is a central longitudinal section, on an enlarged scale, of a valve actuator that includes the features of the present invention.
Description of the Preferred Embodime_ As diagrammatically represented in Figure l, valve actuators 8 embodying the present invention are especially suitable for use on subset well completion apparatus 10 to open and close gate valves 12 located in the Christmas tree 14 that is tnounted on the subset Waldo assembly 16. The illustrated Waldo assembly 16 typically includes a Waldo housing 18, a tree connector 20 securing the crew 14 to the housing 18, and a permanent guide base 22 surrounding and secured to the housing 18 and associated Waldo components 24 by support struts 26. The actuators 8 are operated by hydraulic pressure conducted from a suitable source (not shown) through hydraulic lines (not shown), and the pressure is applied to the actuator pistons through internal passages in the actuator as described below.
Referring to Figure 2, the preferred embodiment of the present invention is illustrated in one of the valve actuators 8 that is shown attached to the bonnet 30 of one of the gate valves 12 by a plurality of screws 31. The actuator 8 broadly comprises a housing 32 secured to a main body 34 by threads 36, a flange body 38 connected to the main body 34 by a flange body collar 40, a stem assembly 41 comprising an outer or manual override stem 42 and an inner or actuation cylinder stem 44, a sleeve-type lo hydraulic cylinder 46 secured by threads 48 to the main body 34, a cylinder cap 50 secured by. threads 52 and a set screw 53 to the cylinder 46, a piston 54 mounted on the inner stem 44 within the cylinder 46, and a piston-return coil spring 56 surrounding the cylinder 46 and extending between the main body 34 and a spring compression hub 58 that surrounds the outer stem 42.
The outer end of the housing 32; i.e., the right hand end as viewed in Fig. 2, has a central opening into which is threaded a packing gland 60, and threaded onto the outer end of the packing gland is an end cap 62 with a central opening aye. The outer stem 42 extends through the packing gland 60 and into the end cap 62, preferably terminating within the central opening aye when the stem is in its "valve closed" position shown in Fig 2. Between a radial flange aye of the packing gland 60 and the adjacent end face of the actuator housing 32 is a spacer ring 63 that is removed to facilitate further threading of the gland into the housing to provide a stop for the actuator stem, as will be more fully explained later. An annular static seal 64 I
so provides fluid-tight integrity between the gland 60 and the housing 32, and annular dynamic seals 66 provide a fluid barrier between the gland and the actuator's outer stem 42.
The outer stem 42 has a radially enlarged area or flange aye located within a central bore aye of the hub 58, and a pair of bearing assemblies 68, 70, located on opposite sides of the flange aye, provide relative rotation support between the stem 42 and the hub 58. A retainer ring 72 holds the bearing assembly 70 in position against the stem flange aye.
The outer stem 42 is connected to the inner stem 44 by moans of a stem adjustment screw 74 that is secured to the end of the inner stem by a cap screw 76. The inner end ox the stem adjustment screw 74 has a central transverse tongue aye that cooperates with a matins groove aye in the adjacent end of the inner stem 44 to prevent relative rotation between the screw 74 and the stem 44 when properly assembled as shown. The adjustment screw 74 and the adjacent portion of the inner stem 44 reside in a central threaded bore 42b in the outer stem 42, and external threads on the screw 74 cooperate with the threads in the bore 42b to axially change the location ox the screw in the bore, and thus the axial position of the inner stem 44 with respect to the outer stem 42, when the outer stem is rotated will respect Jo the inner stem.
The outer stem 42 extends through a central bore in the cylinder cap 50 and is sealed in a fluid-ti~ht manner thereto by annular dynamic seals to. Between the inner end of the outer stem 42 and the piston 54 is an annular bushing 80 to prevent galling of the adjacent piston face by the stem 42 when the stem is rotated with respect to the icier stem 44 into the position shown in Fig. 2. When in that position the outer stem 42 holds the piston 54 against an annular shoulder 44b on the inner stem 44, and when the actuator is operated by hydraulic pressure the piston 54, inner stem 44 and outer stem 42 translate in unison. Annular seals 82 assure a ~luid-tight barrier between the piston and the inner stem.
When the actuator 8 is functionally connected to a gate valve the actuator's inner stem 44 is connected to the valve's bonnet stem 84 by suitable means such as the T-slot arrangement shown in Fig. 2, so that when the actuator is operated the stems 44, 84 translate in unison. The other end portion of the valve bonnet stem 84 includes an annular beveled shoulder aye that cooperates with an annular beveled backseat surface aye on the valve bonnet 30 to establish a metal-to-metal seal between the stem So and the bonnet when the valve is closed as shown in Fig. 2. An annular packing 86, held in place in the bonnet 30 by a packing retainer nut 88, provides a dynamic seal between the bonnet and the bonnet stem 84, and annular dynamic seals 90 provide a ~luid-tight barrier between the stem 84 and the packing nut 88. The packing nut 88 is sealed to the bonnet 30 by an annular seal element 92, and an annular seal 94 provides fluid-tight integrity between the bonnet and the actuator main body 34.
Hydraulic Operation The valve actuator 8 is designed for h~draulîc operation but is provided with manual override capability when required. When operated hydraulically, control pressure is introduced through one or more ports 96 Sony one shown) and conducted by an annular manifold 98 to and through a plurality of circumferential spaced longitudinal passageways 100 in the wall of the cylinder 46 into an annular chamber 102 between the piston 54 and the cylinder cap 50. Annular seals 104 between the piston and the cylinder and 106 between the cylinder cap and the cylinder cooperate with the seals 78, I to confine actuation control pressure to the chamber 102, whereby in response to this pressure the piston, the actuator stem assembly 41 and the valve bonnet stem 84 translate in unison Jo the left as viewed in Fig. 2, unseating the bonnet stem shoulder aye from the bonnet backseat aye and translating the valve gate (not show) into its open position.
Pressure compensation for the actuator 8 Jo ease its operation at deep sea depths is provided by an external compensator (not shown) that is functionally connected to one or more ports 108 only one shown in the actuator main body 34. Compensated oil pressure entering port 108 is conducted by a passageway 110 into an annular chamber 112 in the cylinder 46 and in front of the piston 54, and also by a passageway 114 into the spring housing 32. This pressure compensation precludes external hydrosc~tic pressure from crushing the housing 32 and rendering the actuator inoperable.
The actuator sprint 56 functions to automatically close the valve whenever control pressure is lost or removed from the backside of the piston 54. The spring I provides so a force sufficient -to rapidly overcome the hydrostatic head of the control pressure column situated above the water surface; i . 2 ., platform control room height above the water. Since the above-describea pressure compensation system eliminates the effect of the ambient water pressure on the actuator, which pressure can be vex great depending upon the depth at which the actuator is located, the size of the spring 56 required to close the valve is substantially less than if such pressure compensation were absent.
When the actuator is hydraulically operated by control pressure command the outer stem 42 moves from its illustrated "valve closed" position towards the valve bonnet 30, carrying with it the spring compression hub 58 and the bearing assemblies 68, 70. This movement of the hub 58 compresses the actuator spring 56 which remains compressed as long as the valve remains open This movement of the outer stem 42 also results in relocation of -the stem's outer end face 42c, so that the position of I the stem, and thus the position of the valve gate, can be manually ascertained from the outside of the actuator through the end cap opening aye.
Manual Override Operation the present invention provides manual override I operation of the valve operator 3, even under valve operating pressure or hydraulic system control pressure, by removing the end cap 62, installing a wheel crank 116 fig. I on the outer stem I and then rotating the stem.
As the stem 42 rotates the stem adjustment screw 74 is forced to the let (Fig. 2); i.e., towards the valve hornet 30, thereby translating the inner stem 44, the bonnet stem 34, and the valve gate __ _ _ I_ _ !
I' (not shown) to the left to open the valve. During this valve opening rotation the operation resultant forces from the stems 44 and 84 and the valve Nate are reacted through the bearing assembly 70 by the stem 42, and the bearing assembly 70 is reacted by the packing gland 60.
It should be noted that the manual override feature of the present invention enables the stems 44 and 84, and of course, also the valve gate, to translate without exercising the piston 54, the spring 56 or the spring compression hub 58. Because of this, significantly less torque is required to manually open the valve, and thus an important advantage is achieved as compared with operation requiring spring compression.
When using the manual override to close the valve from its open position, the stem 42 is rotated by the wheel crank 116 in the opposite direction. This rotation causes the stem adjustment screw 74 to move to the right; i.e., towards the packing land 60, thereby pulling the stems 44 and 84 and thy valve gate in the same direction, and resulting in closing the valve. During this valve-closing rotation the operation resultant forces from the valve Nate and the stems 84 and 44 are reacted through bearing assembly 68 by the stem 42. Also during this valve-closing the bearing assembly 68 is reacted by the spring compre~ion hub 58, and the hub it reacted by the sprint 56.
It should be noted that the retainer ring 72, which retains the bearing assembly 70 on the outer stem 42, is required for normal hydraulic operation of eke actuator when the stem 42, hub 58 and spring 56 cycle forward and aft ~.22~2 many times during normal actuation of a subset valve by control pressure command.
External Adjustments The present invention further provides for externally adjusting the position of the valve gate to which the actuator 8 is connected.
External adjustment of valve gate drift is accomplished by rotating the flange collar 40 either clockwise or counter clock-wise. The collar 40 has two sets of internal threads aye, 40b, one right-hand and the other left-hand, that engage external threads on the flange body 38 and the main body 34.
Relative rotation of the bodies 38, 34 is prevented by an anti-rotation key 118 that resides in opposed kiwi slots in the adjacent body surfaces. Accordingly, rotation of eke collar 40 either draws the main body 34 and the housing 32 towards the flange body 38 or forces them away from the body 38, thereby changing the position of the bonnet stem By and the actuator's inner stem 44 with respect to the actuator cylinder 46, and thus changing the drift; i.e., the valve gate position with respect to the valve body/bonnet/ actuator assembly.
External stop adjustment for the stems 42l 44, 84 and the valve gate is accomplished by rotation of the packing gland 60. Thus, if it is desired to stop closing ulovement of these stems and the Nate before the stem shoulder aye backseat on the bonnet surface aye, the frangible spacer ring 63 is knocked out and the gland 60 is threaded further into the housing 32 until its axial position stops the movement at the desire point.
so The ability to achieve these two adjustments from outside the actuator offers significant cost savings in assembly adjustment, both in the shop and in the field, as well as adjustment when in a subset location.
Valve Gate Position Indication As discussed above, the present invention facilitates determination of the position of the valve gate by viewing or feeling/measuring the relative position of the outer stem 42 to the end cap 62. A fully extended stem indicates the valve gate is closed, and of course a fully retracted stem indicates the valve gate is in its open position.
The invention also envisions determination of the valve gate position by electrical means, such as by an external electrical sensor (not shown) mounted on the end cap 62. Using a permanently magnetized stem 42, the proper sensor can determine the presence (valve closed position) of the stem or the non-presence (valve open position) thereof, and send an appropriate signal to the control room on the surface platform (not shown).
It should further be noted that although the above-described valve actuator is intended for use on gate valves on subset well completion Christmas trees and/or manifolds, the actuator also has utility on shore where remote operation of gate valves is required. Thus the adjustment features described above offer an economic advantage where valve adjustments are required in the field, either on land or subset.
Although the best mode contemplated for carrying out the present invention has been herein shown and described, 5~3~
it will be apparent that modification and variation may be made without departing from what is regarded to be the subject matter of the invention.
For some time the oil and gas industry has required hydraulic actuators for operating gate valves on subset well Christmas trees, pipe manifolds, and other w~derwater well apparatus, and such actuators of various designs are in widespread use for this purpose. Preferably, an lo actuator for this type of service would be capable of manual operation in the event of hydraulic power failure, would have provision for external adjustment to compensate for valve gate drift, could be manually operated and adjusted with readily available tools and minimal effort, lo and would be compact in size and functionally reliable.
Summary of the Invention According to an aspect of the invention, a fluid powered actuator for a sliding gate valve comprises a valve body with a flow passage there through, a bonnet I connected to said body a valve gate in said body said valve await havillg a flow passage there through, and a valve stem connected to said gate and extending through said bonnet, said actuator comprises:
a housing with first and second opposed closed ends r fluid cylinder within said housing and having an end portion;
a fluid-powered piston within said cylinder for actuating said valve in an axial direction; an Atari stem connected to slid piston and extending through Roth of said opposed ends, said actuator stem comprising a first stem element extending from said piston thrill said first opposed housing end and terminating ill a means for releasable connecting said actuator stem to said valve stem, a second stem element extending prom sail piston through said cylinder end portion and said second opposed housing end and terminating in a means for rotating suckle second stem element with respect to said first stem element, s-top means on said second stem element cooperating with said second opposed housing end to limit PA
I
-pa-axial movement of said second stem element, and threaded means adjustable interconnecting said first and second stem elements in a end-to-end manner, sail threaded means comprising an externally threaded annular spacer releasable secured to one end of said first stem element and an internally threaded bore in said second element, said spacer and said bore cooperating to cause relative axial movement between said first and second stem elements when said second stem element is rotated with respect to lo said first stem element; means on said valve stem for cooperating with said releasable connecting means on said actuator stem for releasable connecting and disconnecting said actuator stem to said valve stem Chile the valve is under operating pressure; and means or connecting and disconnecting said housing to and from said valve bonnet while the valve is under operating pressure and for adjusting the position ox the valve Nate flow passage relative to the valve body flow passage, said connection and disconnecting means comprising an annular flange body and a sleeve-like collar, said collar connected to the housing by first thread means and connected to said flange body by second thread means, said first and second thread means constituting a differential thread system so that rotation of said collar with respect to said housing and said flange body will change I the axial spacing between the housing and the Lange body and (2) the position ox the valve gate with respect to the valve body and the bonnet.
The present invention as embodied in a hydraulic operated vale valve actuator has one or more of the above features. Such an actuator can include an externally adjustable valve vale drift adjustment system, a manual override system that does not exercise the hydraulic piston or its return spin at any time during I the manual override operation, thereby requiring the application of only minimal actuation torque ho the diver, and what does not introduce a potential leak path to control pressure fluid during said override cycle, an externally adjustable unstop for the actuator stem that A
5~3f~
-2b-can be used instead of the backseat between the valve stem and bonnet, and a separate and readily replaceable thread assembly for the actuator stem that offers reduced lo /
I
5~3Z
manufacturing costs and less potential for thread galling during the actuator's service life.
The actuator has a high spring load-to-actuation piston area ratio with multiple control ports for more rapid response to command control pressure. Should the control pressure fail the spring automatically and quickly returns the piston to its "valve closed" position, thereby providing effective fail-safe closed protection to the fluid conduit in which the valve is installed.
In its preferred form the actuator also includes a hydraulic control pressure porting system that is integral to the cylinder to minimize external plumbing requirements and the overall length and diameter of the actuator. A
manifolding hydraulic distribution system for the control pressure porting assures positive distribution of fluid to the cylinder during actuation, and minimizes the number of fabricated parts in the system.
In its preferred form the actuator further includes an ambient pressure compensation porting system on eke backside of the piston and piston cylinder to almost equalize the pressure in the static non-operating mode control pressure porting system caused by hydrostatic hydraulic head from sea level to the installed subset valve. This compensation system assures that the actuator is only operated to the open position by a positive control pressure command from the surface control system, and not by hydrostatic head pressure in the control pressure porting system.
The preferred form of actuator additionally includes an accommodation for an externally mounted electrical position indication package for monitoring the position of the actuator stem and, ultimately, the valve gate to which the stem is connected. Provision for manually monitoring the stem and gate positions, from outside the actuator also is present in the preferred embodiment in a form that is readily accessible to a diver.
Brief Description of the Drawings Figure 1 is a diagrammatic side elevation of a subset well completion system, showing valve actuators incorporating the present invention in functional position on gate valves of a subset Christmas tree.
Figure 2 is a central longitudinal section, on an enlarged scale, of a valve actuator that includes the features of the present invention.
Description of the Preferred Embodime_ As diagrammatically represented in Figure l, valve actuators 8 embodying the present invention are especially suitable for use on subset well completion apparatus 10 to open and close gate valves 12 located in the Christmas tree 14 that is tnounted on the subset Waldo assembly 16. The illustrated Waldo assembly 16 typically includes a Waldo housing 18, a tree connector 20 securing the crew 14 to the housing 18, and a permanent guide base 22 surrounding and secured to the housing 18 and associated Waldo components 24 by support struts 26. The actuators 8 are operated by hydraulic pressure conducted from a suitable source (not shown) through hydraulic lines (not shown), and the pressure is applied to the actuator pistons through internal passages in the actuator as described below.
Referring to Figure 2, the preferred embodiment of the present invention is illustrated in one of the valve actuators 8 that is shown attached to the bonnet 30 of one of the gate valves 12 by a plurality of screws 31. The actuator 8 broadly comprises a housing 32 secured to a main body 34 by threads 36, a flange body 38 connected to the main body 34 by a flange body collar 40, a stem assembly 41 comprising an outer or manual override stem 42 and an inner or actuation cylinder stem 44, a sleeve-type lo hydraulic cylinder 46 secured by threads 48 to the main body 34, a cylinder cap 50 secured by. threads 52 and a set screw 53 to the cylinder 46, a piston 54 mounted on the inner stem 44 within the cylinder 46, and a piston-return coil spring 56 surrounding the cylinder 46 and extending between the main body 34 and a spring compression hub 58 that surrounds the outer stem 42.
The outer end of the housing 32; i.e., the right hand end as viewed in Fig. 2, has a central opening into which is threaded a packing gland 60, and threaded onto the outer end of the packing gland is an end cap 62 with a central opening aye. The outer stem 42 extends through the packing gland 60 and into the end cap 62, preferably terminating within the central opening aye when the stem is in its "valve closed" position shown in Fig 2. Between a radial flange aye of the packing gland 60 and the adjacent end face of the actuator housing 32 is a spacer ring 63 that is removed to facilitate further threading of the gland into the housing to provide a stop for the actuator stem, as will be more fully explained later. An annular static seal 64 I
so provides fluid-tight integrity between the gland 60 and the housing 32, and annular dynamic seals 66 provide a fluid barrier between the gland and the actuator's outer stem 42.
The outer stem 42 has a radially enlarged area or flange aye located within a central bore aye of the hub 58, and a pair of bearing assemblies 68, 70, located on opposite sides of the flange aye, provide relative rotation support between the stem 42 and the hub 58. A retainer ring 72 holds the bearing assembly 70 in position against the stem flange aye.
The outer stem 42 is connected to the inner stem 44 by moans of a stem adjustment screw 74 that is secured to the end of the inner stem by a cap screw 76. The inner end ox the stem adjustment screw 74 has a central transverse tongue aye that cooperates with a matins groove aye in the adjacent end of the inner stem 44 to prevent relative rotation between the screw 74 and the stem 44 when properly assembled as shown. The adjustment screw 74 and the adjacent portion of the inner stem 44 reside in a central threaded bore 42b in the outer stem 42, and external threads on the screw 74 cooperate with the threads in the bore 42b to axially change the location ox the screw in the bore, and thus the axial position of the inner stem 44 with respect to the outer stem 42, when the outer stem is rotated will respect Jo the inner stem.
The outer stem 42 extends through a central bore in the cylinder cap 50 and is sealed in a fluid-ti~ht manner thereto by annular dynamic seals to. Between the inner end of the outer stem 42 and the piston 54 is an annular bushing 80 to prevent galling of the adjacent piston face by the stem 42 when the stem is rotated with respect to the icier stem 44 into the position shown in Fig. 2. When in that position the outer stem 42 holds the piston 54 against an annular shoulder 44b on the inner stem 44, and when the actuator is operated by hydraulic pressure the piston 54, inner stem 44 and outer stem 42 translate in unison. Annular seals 82 assure a ~luid-tight barrier between the piston and the inner stem.
When the actuator 8 is functionally connected to a gate valve the actuator's inner stem 44 is connected to the valve's bonnet stem 84 by suitable means such as the T-slot arrangement shown in Fig. 2, so that when the actuator is operated the stems 44, 84 translate in unison. The other end portion of the valve bonnet stem 84 includes an annular beveled shoulder aye that cooperates with an annular beveled backseat surface aye on the valve bonnet 30 to establish a metal-to-metal seal between the stem So and the bonnet when the valve is closed as shown in Fig. 2. An annular packing 86, held in place in the bonnet 30 by a packing retainer nut 88, provides a dynamic seal between the bonnet and the bonnet stem 84, and annular dynamic seals 90 provide a ~luid-tight barrier between the stem 84 and the packing nut 88. The packing nut 88 is sealed to the bonnet 30 by an annular seal element 92, and an annular seal 94 provides fluid-tight integrity between the bonnet and the actuator main body 34.
Hydraulic Operation The valve actuator 8 is designed for h~draulîc operation but is provided with manual override capability when required. When operated hydraulically, control pressure is introduced through one or more ports 96 Sony one shown) and conducted by an annular manifold 98 to and through a plurality of circumferential spaced longitudinal passageways 100 in the wall of the cylinder 46 into an annular chamber 102 between the piston 54 and the cylinder cap 50. Annular seals 104 between the piston and the cylinder and 106 between the cylinder cap and the cylinder cooperate with the seals 78, I to confine actuation control pressure to the chamber 102, whereby in response to this pressure the piston, the actuator stem assembly 41 and the valve bonnet stem 84 translate in unison Jo the left as viewed in Fig. 2, unseating the bonnet stem shoulder aye from the bonnet backseat aye and translating the valve gate (not show) into its open position.
Pressure compensation for the actuator 8 Jo ease its operation at deep sea depths is provided by an external compensator (not shown) that is functionally connected to one or more ports 108 only one shown in the actuator main body 34. Compensated oil pressure entering port 108 is conducted by a passageway 110 into an annular chamber 112 in the cylinder 46 and in front of the piston 54, and also by a passageway 114 into the spring housing 32. This pressure compensation precludes external hydrosc~tic pressure from crushing the housing 32 and rendering the actuator inoperable.
The actuator sprint 56 functions to automatically close the valve whenever control pressure is lost or removed from the backside of the piston 54. The spring I provides so a force sufficient -to rapidly overcome the hydrostatic head of the control pressure column situated above the water surface; i . 2 ., platform control room height above the water. Since the above-describea pressure compensation system eliminates the effect of the ambient water pressure on the actuator, which pressure can be vex great depending upon the depth at which the actuator is located, the size of the spring 56 required to close the valve is substantially less than if such pressure compensation were absent.
When the actuator is hydraulically operated by control pressure command the outer stem 42 moves from its illustrated "valve closed" position towards the valve bonnet 30, carrying with it the spring compression hub 58 and the bearing assemblies 68, 70. This movement of the hub 58 compresses the actuator spring 56 which remains compressed as long as the valve remains open This movement of the outer stem 42 also results in relocation of -the stem's outer end face 42c, so that the position of I the stem, and thus the position of the valve gate, can be manually ascertained from the outside of the actuator through the end cap opening aye.
Manual Override Operation the present invention provides manual override I operation of the valve operator 3, even under valve operating pressure or hydraulic system control pressure, by removing the end cap 62, installing a wheel crank 116 fig. I on the outer stem I and then rotating the stem.
As the stem 42 rotates the stem adjustment screw 74 is forced to the let (Fig. 2); i.e., towards the valve hornet 30, thereby translating the inner stem 44, the bonnet stem 34, and the valve gate __ _ _ I_ _ !
I' (not shown) to the left to open the valve. During this valve opening rotation the operation resultant forces from the stems 44 and 84 and the valve Nate are reacted through the bearing assembly 70 by the stem 42, and the bearing assembly 70 is reacted by the packing gland 60.
It should be noted that the manual override feature of the present invention enables the stems 44 and 84, and of course, also the valve gate, to translate without exercising the piston 54, the spring 56 or the spring compression hub 58. Because of this, significantly less torque is required to manually open the valve, and thus an important advantage is achieved as compared with operation requiring spring compression.
When using the manual override to close the valve from its open position, the stem 42 is rotated by the wheel crank 116 in the opposite direction. This rotation causes the stem adjustment screw 74 to move to the right; i.e., towards the packing land 60, thereby pulling the stems 44 and 84 and thy valve gate in the same direction, and resulting in closing the valve. During this valve-closing rotation the operation resultant forces from the valve Nate and the stems 84 and 44 are reacted through bearing assembly 68 by the stem 42. Also during this valve-closing the bearing assembly 68 is reacted by the spring compre~ion hub 58, and the hub it reacted by the sprint 56.
It should be noted that the retainer ring 72, which retains the bearing assembly 70 on the outer stem 42, is required for normal hydraulic operation of eke actuator when the stem 42, hub 58 and spring 56 cycle forward and aft ~.22~2 many times during normal actuation of a subset valve by control pressure command.
External Adjustments The present invention further provides for externally adjusting the position of the valve gate to which the actuator 8 is connected.
External adjustment of valve gate drift is accomplished by rotating the flange collar 40 either clockwise or counter clock-wise. The collar 40 has two sets of internal threads aye, 40b, one right-hand and the other left-hand, that engage external threads on the flange body 38 and the main body 34.
Relative rotation of the bodies 38, 34 is prevented by an anti-rotation key 118 that resides in opposed kiwi slots in the adjacent body surfaces. Accordingly, rotation of eke collar 40 either draws the main body 34 and the housing 32 towards the flange body 38 or forces them away from the body 38, thereby changing the position of the bonnet stem By and the actuator's inner stem 44 with respect to the actuator cylinder 46, and thus changing the drift; i.e., the valve gate position with respect to the valve body/bonnet/ actuator assembly.
External stop adjustment for the stems 42l 44, 84 and the valve gate is accomplished by rotation of the packing gland 60. Thus, if it is desired to stop closing ulovement of these stems and the Nate before the stem shoulder aye backseat on the bonnet surface aye, the frangible spacer ring 63 is knocked out and the gland 60 is threaded further into the housing 32 until its axial position stops the movement at the desire point.
so The ability to achieve these two adjustments from outside the actuator offers significant cost savings in assembly adjustment, both in the shop and in the field, as well as adjustment when in a subset location.
Valve Gate Position Indication As discussed above, the present invention facilitates determination of the position of the valve gate by viewing or feeling/measuring the relative position of the outer stem 42 to the end cap 62. A fully extended stem indicates the valve gate is closed, and of course a fully retracted stem indicates the valve gate is in its open position.
The invention also envisions determination of the valve gate position by electrical means, such as by an external electrical sensor (not shown) mounted on the end cap 62. Using a permanently magnetized stem 42, the proper sensor can determine the presence (valve closed position) of the stem or the non-presence (valve open position) thereof, and send an appropriate signal to the control room on the surface platform (not shown).
It should further be noted that although the above-described valve actuator is intended for use on gate valves on subset well completion Christmas trees and/or manifolds, the actuator also has utility on shore where remote operation of gate valves is required. Thus the adjustment features described above offer an economic advantage where valve adjustments are required in the field, either on land or subset.
Although the best mode contemplated for carrying out the present invention has been herein shown and described, 5~3~
it will be apparent that modification and variation may be made without departing from what is regarded to be the subject matter of the invention.
Claims (5)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A fluid powered actuator for a sliding gate valve comprising a valve body with a flow passage therethrough, a bonnet connected to said body, a valve gate in said body, said valve gate having a flow passage therethrough, and a valve stem connected to said gate and extending through said bonnet, said actuator comprising:
a housing with first and second opposed closed ends;
a fluid cylinder within said housing and having an end portion;
a fluid-powered piston within said cylinder for actuating said valve in an axial direction;
an actuator stem connected to said piston and extending through both of said opposed ends, said actuator stem comprising a first stem element extending from said piston through said first opposed housing end and terminating in a means for releasably connecting said actuator stem to said valve stem, a second stem element extending from said piston through said cylinder end portion and said second opposed housing end and terminating in a means for rotating said second stem element with respect to said first stem element, stop means on said second stem element cooperating with said second opposed housing end to limit axial movement of said second stem element, and threaded means adjustably interconnecting said first and second stem elements in a end-to-end manner, said threaded means comprising an externally threaded annular spacer releasably secured to one end of said first stem element and an internally threaded bore in said second element, said spacer and said bore cooperating to cause relative axial movement between said first and second stem elements when said second stem element is rotated with respect to said first stem element;
means on said valve stem for cooperating with said releasably connecting means on said actuator stem for releasably connecting and disconnecting said actuator stem to said valve stem while the valve is under operating pressure; and means for connecting and disconnecting said housing to and from said valve bonnet while the valve is under operating pressure and for adjusting the position of the valve gate flow passage relative to the valve body flow passage, said connecting and disconnecting means comprising an annular flange body and a sleeve-like collar, said collar connected to the housing by first thread means and connected to said flange body by second thread means, said first and second thread means constituting a differential thread system so that rotation of said collar with respect to said housing and said flange body will change (1) the axial spacing between the housing and the flange body and (2) the position of the valve gate with respect to the valve body and the bonnet.
a housing with first and second opposed closed ends;
a fluid cylinder within said housing and having an end portion;
a fluid-powered piston within said cylinder for actuating said valve in an axial direction;
an actuator stem connected to said piston and extending through both of said opposed ends, said actuator stem comprising a first stem element extending from said piston through said first opposed housing end and terminating in a means for releasably connecting said actuator stem to said valve stem, a second stem element extending from said piston through said cylinder end portion and said second opposed housing end and terminating in a means for rotating said second stem element with respect to said first stem element, stop means on said second stem element cooperating with said second opposed housing end to limit axial movement of said second stem element, and threaded means adjustably interconnecting said first and second stem elements in a end-to-end manner, said threaded means comprising an externally threaded annular spacer releasably secured to one end of said first stem element and an internally threaded bore in said second element, said spacer and said bore cooperating to cause relative axial movement between said first and second stem elements when said second stem element is rotated with respect to said first stem element;
means on said valve stem for cooperating with said releasably connecting means on said actuator stem for releasably connecting and disconnecting said actuator stem to said valve stem while the valve is under operating pressure; and means for connecting and disconnecting said housing to and from said valve bonnet while the valve is under operating pressure and for adjusting the position of the valve gate flow passage relative to the valve body flow passage, said connecting and disconnecting means comprising an annular flange body and a sleeve-like collar, said collar connected to the housing by first thread means and connected to said flange body by second thread means, said first and second thread means constituting a differential thread system so that rotation of said collar with respect to said housing and said flange body will change (1) the axial spacing between the housing and the flange body and (2) the position of the valve gate with respect to the valve body and the bonnet.
2. An actuator according to claim 1 wherein the first and second thread means are of opposite hand.
3. An actuator according to claim 1 wherein the actuator stem includes manual override means for manually operating the actuator without advancing the piston.
4. An actuator according to claim 3 including means for biasing the piston and the actuator stem in one axial direction, and wherein the manual override means functions without exercising said biasing means.
5. An actuator according to claim 4 wherein the biasing means comprises a coil spring enclosed within the housing.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US45695783A | 1983-01-10 | 1983-01-10 | |
| US456,957 | 1983-01-10 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1228582A true CA1228582A (en) | 1987-10-27 |
Family
ID=23814832
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000444865A Expired CA1228582A (en) | 1983-01-10 | 1984-01-06 | Subsea gate valve actuator with external manual override and drift adjustment |
Country Status (6)
| Country | Link |
|---|---|
| BR (1) | BR8400108A (en) |
| CA (1) | CA1228582A (en) |
| GB (1) | GB2133472B (en) |
| MX (1) | MX158221A (en) |
| NO (1) | NO160873C (en) |
| SG (1) | SG61486G (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3606148C2 (en) * | 1986-02-26 | 1994-11-17 | Bbc Brown Boveri & Cie | Spring-mounted suspension of a control piston |
| US4809733A (en) * | 1987-04-22 | 1989-03-07 | National-Oilwell | Fail-safe gate valve with separated actuators |
| US6536740B2 (en) * | 2001-03-29 | 2003-03-25 | Cooper Cameron Corporation | Disconnected piston for a valve actuator |
| GB2596540B (en) * | 2020-06-30 | 2023-02-01 | Aker Solutions As | Actuator and associated methods |
| NO20220828A1 (en) | 2022-07-26 | 2024-01-29 | Fmc Kongsberg Subsea As | Subsea valve actuator assembly |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1604339A (en) * | 1977-05-31 | 1981-12-09 | Baker Int Corp | Quick disengaging valve actuator |
-
1984
- 1984-01-06 CA CA000444865A patent/CA1228582A/en not_active Expired
- 1984-01-09 MX MX199990A patent/MX158221A/en unknown
- 1984-01-09 NO NO840062A patent/NO160873C/en unknown
- 1984-01-09 GB GB08400446A patent/GB2133472B/en not_active Expired
- 1984-01-10 BR BR8400108A patent/BR8400108A/en unknown
-
1986
- 1986-07-11 SG SG614/86A patent/SG61486G/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| GB2133472A (en) | 1984-07-25 |
| SG61486G (en) | 1987-03-27 |
| MX158221A (en) | 1989-01-16 |
| GB2133472B (en) | 1986-05-21 |
| NO160873C (en) | 1989-06-07 |
| GB8400446D0 (en) | 1984-02-08 |
| NO160873B (en) | 1989-02-27 |
| NO840062L (en) | 1984-07-11 |
| BR8400108A (en) | 1984-08-14 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4650151A (en) | Subsea gate valve actuator with external manual override and drift adjustment | |
| US4809733A (en) | Fail-safe gate valve with separated actuators | |
| US7108006B2 (en) | Subsea actuator assemblies and methods for extending the water depth capabilities of subsea actuator assemblies | |
| CA1273328A (en) | Dual stage hydraulic actuator for expanding gate valve | |
| US6041804A (en) | Subsea valve actuator and method | |
| US4294284A (en) | Fail-safe, non-pressure locking gate valve | |
| US7523916B2 (en) | Fail-safe gate valve | |
| US3379405A (en) | Valve | |
| US4230299A (en) | Pressure balanced gate valve having selective actuator systems | |
| US5287879A (en) | Hydraulically energized wireline blowout preventer | |
| US4436279A (en) | Stem connection for gate valve | |
| US5415378A (en) | Valve assembly | |
| US4877217A (en) | Fail-safe blowout preventer | |
| US3086745A (en) | Hydraulic operator for reciprocating gate valves | |
| US4635901A (en) | Position indicator for valves | |
| US6050541A (en) | Pneumatic valve actuator assembly | |
| GB2216237A (en) | Gate valve with hydraulic actuator | |
| US6345668B1 (en) | Tubing hanger having an integral valve gate | |
| US4795171A (en) | Self-pressurized shaft or closure seal | |
| CA1228582A (en) | Subsea gate valve actuator with external manual override and drift adjustment | |
| US6536740B2 (en) | Disconnected piston for a valve actuator | |
| US3538938A (en) | Automatic sealant sealed valves | |
| US4795128A (en) | Gate type kelly cock valve | |
| GB2276209A (en) | Electrohydraulic valve actuator | |
| US3570804A (en) | Hydraulic valve operator having manual override mechanism |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |