Patent Document

BACKGROUND OF THE INVENTION 
     1. Field of the Invention 
     The present invention is in the field of storm chokes for closing oil well production lines or pipelines in the event of a break or sudden increase in fluid pressure. 
     In production lines from oil wells or in pipelines conducting materials from one location to another, a break in the conduit obviously results in loss of considerable fluid and in many instances it is difficult or impossible to cut off flow and serious damage and loss result. A particularly dangerous situation exists in offshore oil production facilities wherein high seas or other marine events often rupture a production line, thus causing spillage of oil in the surrounding waters and such spillage not only contaminates the water but presents an extremely serious fire hazard. In the event of such an occurrence, it has been heretofore extremely difficult to stem flow from the well. 
     2. General Background 
     The present invention provides an improved, extremely simple automatic valve that can be placed in a production line or pipeline. The strom choke valve of the present invention comprises an upper and lower valve housing; an upper seat mated into the top of the upper valve housing and a lower seat mated at the connection between the upper and lower valve housings, thereby connecting the lower and upper valve housings; upper and lower valve members mounted onto a longitudinally extending axle having a longitudinal axis substantially coincidental with the longitudinal axis of the upper and lower valve housings and mounted for reciprocal movement therein, the upper and lower valve members thereby being movable for seating engagement with the upper and lower valve seats, respectively; the upper valve member is fixedly mounted to the axle relative to inclined vanes that cause the valve member and the entire axle and the lower valve member to rotate during fluid flow in the production line or pipeline. 
     Sufficient background has now been afforded to discuss the improvements of the present invention over the prior art, particularly U.S. Pat. No. 3,714,957. The improvements are as follows: 
     1. The inclined vanes which are mounted to the upper valve member are not subject to closure by fluid flow through the production line, as in U.S. Pat. No. 3,714,957, but rather, the vanes can only be adjusted to variable open positions and can only be closed by means of a vane adjustment nut circumferentially mounted on the axle, below the vanes, the axle being calibrated so that the operator can preset the degree of opening of the vanes in order to allow a specified amount of fluid flow past the vanes, and if this fluid flow is exceeded, the vanes cause the upper and lower valve members and the entire axle to rotate, and exert a lifting force on the upper valve member, and if the fluid flow is increased enough, the vane rotates more rapidly and a greater lifting force is applied to the upper valve member, thereby causing the entire axle and the upper and lower valve members mounted thereto to rise within the upper and lower valve housings, so that the upper and lower valve members are pulled into seating engagement with the upper and lower valve seats, respectively, and thus, automatically close the pipe against further or continued flow therethrough; 
     2. A lower seal housing having a lower shaft rotatably mounted therein, the lower shaft being mated on its top to the lower end of the lower valve member, the top of the seal housing communicating with the bottom surface of the lower valve member, thereby defining the lowermost movement of the lower valve member; a compression spring circumferentially mounted to the lower portion of the lower shaft at the bottom of the seal housing, and the lower shaft is secured within the seal housing by a lower bushing and an upper bushing, O-ring seals, and a lock ring and washer; 
     3. A plug having breather vents in its lower portion is mated at its top end with the lower end of the seal housing, thereby fluidly sealing the seal housing; the seal housing is secured within the lower valve housing by means of spiders or support fins being welded to the outer surface of the seal housing and the inner surface of the lower valve housing; 
     4. The weight of the upper and lower valve members downwardly biases the compression spring mounted to the lower shaft within the seal housing, and this bias can only be reversed by increased fluid flow velocity which causes the inclined vanes mounted to the upper valve member to rotate, thereby exerting a lifting force on the upper valve member and thus, the vanes, the axle, and the lower valve member, and this lifting action is further enhanced by the decompression of the compression spring and the resultant upward movement of the lower shaft and the lower valve member mounted thereto, and thus, the upper axle and the upper valve member, ultimately resulting in the seating engagement of the upper valve member and the lower valve member with the upper and lower valve seats, respectively, thus automatically closing the pipe or production line against further or continued flow therethrough. 
     The invention disclosed herein contemplates forms for employment in vertical production lines or in horizontal production lines. 
     Many other objects and advantages of the present invention will become apparent from the following detailed description taken in conjunction with the accompanying drawings. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     FIG. 1 is an elevational, cross-sectional view of the present invention employed within a vertical production line. 
     FIG. 2 is an elevational, cross-sectional view of the present invention in isolation. 
     FIG. 3 is an isolated, elevational cross-sectional view of the upper solid member of the present invention with the top frusto-conical solid member therein inserted. 
     FIG. 4 is a fragmentary view of the upper part of the apparatus of the present invention. 
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
     Referring now to FIG. 1, numeral 2 indicates a generally vertically extending oil well production line, which may be a well casing or a separate pipe therein, the apparatus of the present invention, indicated generally by numeral 4, being depicted mounted therein. Referring now to FIG. 2, there can be seen the apparatus of the present invention, indicated generally by the numeral 4, in isolation (i.e. not mounted within the production line), wherein the present invention comprises, from top to bottom, an upper valve housing 6 and a lower valve housing 8, connected together by internal, lower collar 10 having an annular valve seat 11; an upper collar 12 having a larger upper bore 14 and a lower, annular valve seat 16, is mated with the machine-threads provided in the top end of the upper valve housing 6; an upper shaft 18, or upper axle 18, mounted on its lower end to a lower, solid head member 20 having a substantially conical top portion 21, and mated on its upper end to an upper, solid head member 22, such as by set screw 24 (head member 22 hereinafter referred to as upper valve member 22); a substantially conical, solid head member 26 having a lower threaded stud 28 which is mated into a machine-threaded central bore 30 provided in upper valve member 22 for receiving same; a pair of generally semi-circular vanes 32 pivotally mounted on upper valve member 22 by means of a pivot pin 34, which extends through upper valve member 22 and through upwardly extending ears 36 on the vanes 32. Upper valve member 22 is provided with a pair of diametrically spaced bores 38 terminating at their lower ends in smaller openings 40 through which shanks 42 of slidable thrust plugs 44 slidably extend. The shanks 42 are positioned to bear at their lower ends on the upper surfaces of their respective vanes 32, each at a position laterally displaced from the pivot pin 34. Within each bore 38 is a compression spring 46, bearing at its lower end on the thrust plug 44, held under compression by an adjustable threaded plug 48 threaded into the upper end of the bore 38. Thus, plugs 48 may be preset or pre-adjusted to provide the desired valve of compression force stored in springs 46 and thus predetermine the torque applied by shanks 42 to the vanes 32, which torque normally holds vanes 32 in the tilted or oblique position shown in FIGS. 1 and 2. In the preferred embodiment of the present invention, adjustable threaded plug 48 is preset or pre-adjusted to provide a compression force to springs 46 which makes vanes 32 non-responsive to any amount of upward fluid pressure, the degree of the tilt of the vanes 32 being solely adjustable by means of vane adjustment nut 52 which is provided with internal threads to mate with the machine-threaded portion 54 of upper axle 18 below upper valve member 22. The degree of the tilt of the vanes 32 regulates the amount of fluid allowed to flow therepast. The machine-threaded portion 54 of upper axle 18 is calibrated to indicate the amount of fluid which would be allowed to flow past the vanes 32 at the particular setting selected. In the preferred embodiment, the machine-threaded portion 54 of upper axle 18 is calibrated with two separate sets of markings for indicating the flow which would be permitted past vanes 32, for the various settings of the vane adjustment nut 52, one set of markings representing the calibration for natural gas flow and the other set of markings representing calibration for crude oil flow. As is further apparent from FIG. 4, the downwardly facing area of each vane 32 is considerably greater on one side of the pivot pin 34 than the area of that vane on the other side of pivot pin 34. Thus, any upward fluid pressure applied to the lower surfaces of the vanes 32 will apply a net torque thereto in direction tending to rotate each vane about the pivot pin 34 in opposition to the torque provided by the compression springs 46. 
     Referring again to FIG. 2, a lower, reciprocable shaft 56, or lower axle 56, is provided with machine-threads at its top end for mating a machine-threaded, lower, central bore 94 provided through lower valve member 20. Lower shaft 56 extends through and is journalled in O-ring seals 57, 58 and bushings 60, 61 within seal housing 63 whereby it is rotatable therein and axially movable therethrough. Seal housing 63 is affixed within lower valve housing 8 by means of fins 85 or spiders 85 being welded, for example, to the inner wall of lower valve housing 8 and the outer surface of seal housing 63. A compression spring 72 surrounds the lower shaft 56 from a point substantially downstream from bushing 61, in the preferred embodiment, downwardly to a point substantially near the lower end of lower shaft 56. Compression spring 72 is retained onto shaft 56 by means of washer 65, and one or more spring retainer nuts 66, 67. Plug-in 74 is inserted into the bottom end of seal housing 63, thereby fluidly sealing seal housing 63, thereby preventing fluid flow therethrough except through breather vents 75, 76 which permit the intake and exhaust of fluid. 
     In operation, the upper valve housing 6 and the lower valve housing 8 are inserted into the oil well production line 2, the larger upper bore 14 of upper collar 12 being threaded for mating an adaptor (not shown) which engages a down hole lock (not shown) within the bore of production line 2, thereby securing upper valve housing 6 and lower housing 8 within the bore of production line 2. O-rings 88, 90 ensure a fluid seal between the upper and lower valve housings 6, 8 and the oil well production line 2. When production fluid is flowing upwardly into conduit 2, that flow of fluid past the tilted vanes 32 will apply an upward fluid pressure to the lower surfaces of the vanes, thereby applying a net torque thereto in a direction tending to rotate each vane about the pivot pin 34 in opposition to the torque provided by the compression springs 46 thereby ensuring that vanes 32 remain in their preselected tilted position and only a certain amount of fluid passes between the vanes and the inner walls of upper valve housing 6. It will also be obvious that the rotation of tilted vanes 32 will cause the upper axle 18 and the upper valve member 22 and lower valve member 20 mounted thereto, and lower shaft 56, to also rotate. The vane adjustment nut 52 is manually, or otherwise, adjusted to the desired setting to allow a preselected amount of fluid flow past the vanes 32 and through the upper valve housing 6 and therethrough through the production line 2. Some of the fluid flowing through the production line 2 upwardly into the lower valve housing 8 will enter through breather vents 75, 76 of plug-in 74 to prevent buoyancy of plug-in 74, which would cause an undue increased velocity of fluid flow, thereby resulting in malfunctioning of the device. Any increase in fluid flow beyond the amount of fluid flow desired to be allowed past vanes 32 as is predetermined by preselecting the setting of vane adjustment nut 52, will cause an increased rotation of vanes, 32, thereby creating a rotating/lifting force on vanes 32, thereby causing the upper axle 18, upper valve member 22, the lower valve member 20, and the lower shaft 56, to simultaneously rotate and be lifted and ultimately head member 26 of upper valve member 22 will engage its seating surface 16, and top portion 21 of lower valve member 20 will engage its seating surface 11, thereby stopping all flow of fluid through lower valve housing 8 and upper valve housing 6. The above described lifting/rotating action is enhanced by the action of compression spring 72; in its normal state, spring 72 tends to hold the valve open, it is decompressed as best shown in FIG. 1 with its lower end bearing on bushing 60 and its upper end pushing against bushing 61 therefore, any lifting of the upper valve member 22 and the lower valve member 20 causes a commensurate compression of compression spring 72, thereby upwardly urging lower shaft 56, lower valve member 20, upper axle 18, and upper valve member 22. Thusly, compression spring 72 enhances the rotating/lifting action caused by an increased velocity of fluid flow past vanes 32, thereby substantially lessening the time gap between the point at which the velocity of fluid flow exceeds the maximum allowable flow according to the setting of the vane adjustment nut 52, and the seating of the head member 26 of upper valve member 22 with its valve seat 16 and the seating of top portion 21 of lower valve member 20 with its valve seat 11, thereby preventing a potentially damgerous situation in the event that the production line 2 may rupture or break, or in the event of a sudden surge of high pressure in the production line it is important to note that breather vents 75, 76 serve as pressure equilization means to permitting a flow of oil or gas into the interior of chamber 63, which houses spring 72, since chamber 63 is sealed against the flow operating valve head members 20, 22 and vanes 32. The provision of two valve members and the provision of a spring-action lower shaft are major improvements over the prior art, as they facilitate a more effective, and quicker action sealing means to prevent the flow of fluid through the valve, thereby preventing potentially dangerous situations, either subsurface or at the surface. Note that when the fluid flow is decreased below the preselected maximum level, the lowermost movement of lower valve member 20 is defined by the upper surface of seal housing 63. 
     While specific embodiment of the present invention has been shown and described, the same is merely illustrative of the principles involved and other forms will be obvious to those skilled in the art, within the scope of the appended claims.

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