MXPA99009020A - Safety excess flow valve system with adjustable closing flow rate settings - Google Patents

Abstract

The present invention relates to an excess flow valve system having a sliding poppet (11) within a chamber with an orifice at one end, wherein the closing flow rate settings can be adjusted. Precise adjustments can be made externally by turning a threaded member extending through the valve, which causes a retainer (37), threadably located on the member, to move laterally within the chamber. This movement causes an angled surface on the retainer to engage and slide in relation to a similarly angled surface on the poppet. As the poppet is urged toward the retainer by a coiled spring (25), the poppet is moved longitudinally within the chamber, either toward or away from the orifice. Turning the threaded member enables the maximum travel distance of the poppet, and therefore, the threshold flow rate of the valve, to be precisely set. Additional means for broadening the range of settings, without replacing the spring or changing the orifice size, can also be provided, such as spacers to change the spring tension and multiple phase settings on the valve housing.

Description

SAFETY VALVE SYSTEM FOR EXCESS FLOW WITH ADJUSTABLE FLOW CLOSURE POSITIONS BACKGROUND OF THE INVENTION I. Field of the Invention The present invention relates in general to the field of excess flow valves used to regulate and prevent excess flow of the liquid or gas passing through them. More specifically, the present invention relates to excess flow valves that prevent the flow of fluid or gas through a conduit if its velocity exceeds a predetermined threshold level.

II. Related Art Description The use of excess flow valves is absolutely standard in the gas industry. These valves are commonly used in gas conveyor systems. The mission of these valves is to regulate the flow of gas, vapor or fluid that passes through them, limiting their speed to a predetermined maximum value. If the flow speed exceeds the predetermined level, which indicates a malfunction condition or dangerous situation, such as in the case of damage or rupture of a hose, spout or fitting, the valve P888 will automatically interrupt the flow of fluid or gas automatically for the purpose of avoiding excessive discharge of the substance transported. Typically, a gas supply system comprises a gas pipe or pipe, or other source of high pressure gas, connected directly or through a pipe, or a similar gas distribution means, to a regulating unit. The regulating unit supplies the gas at low pressure to its final destination, for example, a kitchen. The excess flow valve is usually placed on the low pressure end of the regulating unit. The mission of the excess flow valve is to interrupt the gas supply in the event of a failure in the pressure regulator, or in any of the connection parts such as hoses or pipes. A typical excess flow valve comprises a sliding rod inside a chamber capable of closing an opening present therein, thus preventing the flow of fluid or gas. A spring is generally used for the purpose of moving the rod into its opening position under which it is separated from the opening. As the flow velocity reaches or exceeds the maximum velocity, such as for example the speed allowed by the size of the opening and / or the spring tension, the increase in pressure differential makes P888 that the rod slides in the direction of the opening, against the tension exerted by the spring, for the purposes of regulating or closing the valve. The difficulty with standard excess flow valves, however, is that they can not be adjusted and therefore it is impossible to use them under situations in which fluid or gas supply pressures and flow velocity thresholds they may vary, without replacing them. Certain types of externally adjustable valve systems have been used in the past for the purpose of allowing systems to adapt to different speeds and flow pressures without having to replace the critical components each time a regulation is made. This adjustment capability is intended to alleviate the difficulty of having to replace internal components, such as the spring, or modify the size of the opening, whenever different speeds and flow pressures are present. These adjustable valve systems, however, have not been entirely satisfactory since they have not been specifically designed to provide a wide range of adjustments, nor to allow valves to be precisely fixed in circumstances under which sensitivity to changes may be required. of pressure.

P888 U.S. Patent 3,807,442, issued to Summer et al., Discloses an excess flow valve that enjoys a limited adjustment capacity (the 'Summer patent'). The Summer patent provides a check valve for excess flow comprising a rod element and a retainer element with external adjustment capability. The distance between the rod element and an orifice determines the flow area for the fluid passing through the valve. Varying the flow area, the pressure differential established by the fluid flow is inversely modified (ie, as the flow area decreases, the pressure differential increases). In -one mode, the Summer patent uses a cam element which, when turned, adjusts the distance between its rod and a hole. The ability to adjust the distance, however, is limited by the preselected settings on the cam member, ie uneven surfaces. That is, for a specific application, the interruption speed determined by the cam element could be much greater than the combined requirements of the appliances connected to the gas pipeline, which could allow a substantially dangerous flow without the valve being operated. . The valve is also not compatible with the various levels of flow velocity that might be needed.

P888 Another type of externally adjustable valve, called a speed fuse for a hydraulic pipe, is illustrated in U.S. Patent 4,383,549, issued to Maldavs (the 'Maldavs patent'). The Maldavs fuse comprises a rod valve system with a set screw that extends into an internal shielded body. The armored body helps to divert the flow of fluid from the body of the rod so that only the head of the rod is exposed thereto. The internal components of the armored body also help to dampen the movement of the rod so that it does not react quickly to slight changes in the pressure of the pipe, such as those created by overloading brief peaks. A set screw used in conjunction with a damped rod usually does not provide great sensitivity to changes in flow pressure. In view of the limitations of the prior art, the excess flow valves disclosed in the Summer and Maldavs patents, and others similar, only enjoy a limited or rudimentary adjustment capacity. In the case of Summers, for example, the sensitivity of the valve depends on the limited threshold levels of predetermined flow velocity, while in the case of Maldavs, the adjustment screw moves laterally and rotates against a P888 disc with freely rotating rod which makes the task of establishing precise adjustments difficult. These excess flow valves also do not enjoy a wide range of regulation. As a result, an excess flow valve that is sensitive to virtually any flow rate threshold is needed. On the other hand, the flow rate threshold for these excess flow valves should be easily adjustable for the purposes of adapting them to various fluid or gas pressures.

Stpaz-Rio OF THE INVENTION The present invention provides an excess flow rate valve system and a method for regulating the flow of fluid, vapor or gas passing through it. According to the present invention, the valve can be adjusted to operate under a wide range of flow rates. The system is designed to interrupt the flow of fluid, vapor or gas if its speed exceeds a predetermined value (the "Threshold Speed"). The system responds to virtually any "Threshold Speed", through which it adapts to a wide range of gas or fluid pressures. At the same time, the valve is precisely adjusted within the regulation range so that it can be applied virtually to any application, such as low pressure installations, in the P888 ~ which might require great sensitivity to pressure changes. On the other hand, the system interrupts the flow of fluid or gas in case a pipe, hose or fuel pipe is broken as a result of a catastrophe, for example, an earthquake, flood, explosion, etc. In this case, the excess flow valve system interrupts the supply of fluid or gas almost completely, with the exception of a minimum allowable back pressure. The valve system will not restore the flow of fluid or gas until the break in the pipe, hose or fuel pipe is repaired. The preferred embodiment of the present invention relates to an excess flow valve that prevents the flow of a gas, for example natural gas, and other vapors, through a conduit if its speed exceeds the predetermined threshold level. Although the valve can be used with fluids, the preferred embodiment is specifically designed to prevent excess flow of natural gas and / or liquid petroleum gas vapors through a similar low pressure gas transport pipe or medium in the case of a leak or catastrophic failure. The preferred valve comprises a sliding rod within a chamber that can be actuated to cause closure of an orifice when the flow rate exceeds the predetermined threshold. The hole allows the passage of gas from one end to the other. A coil spring is used to push the rod out of the hole when the flow velocities are lower than the excess level. An adjustment mechanism is intended to establish the maximum distance of displacement of the rod relative to the hole. By precisely controlling the position of the adjustment mechanism, it is possible to adjust the threshold level accurately without having to change the tension of the spring, modify the dimension of the hole, etc. At the same time, the ability to repeat the operation of the valve is provided. The adjustment mechanism comprises a threaded element that extends through the chamber and an adjustment cam located thereon. The threaded element is externally adjustable and preferably perpendicular to the direction of longitudinal movement of the rod. The cam is located on the threaded element and can be displaced laterally with respect to the chamber and longitudinally relative to the threaded element. The cam has an angled clutch surface which can be displaced against a similar angled clutch surface located on top of the rod. By turning the threaded element and moving the cam laterally, consequently, the clutch surface of the cam slides against the clutch surface of the rod, and, by virtue of the spring that moves the rod towards the cam, it will move towards the orifice will be separated from it. The pressure applied by the spring pushes the clutch surface of the rod towards the clutch surface of the cam, thus, the cam interrupts the movement of the rod and determines the maximum distance of displacement thereof. The spring holds the rod disc in its open position against the cam until the flow velocity exceeds the threshold level, in which case the increase in pressure differential will exert its action causing the rod to move to its closed position . The precise control of the maximum displacement distance of the rod in relation to the orifice, that is to say the Threshold Speed, allows the valve to be practically infinitely adjustable within its operating range and highly sensitive to changes in the flow velocity and differential of pressure from one part of the system to the other. Likewise, in the preferred embodiment, the valve is configured to substantially limit the rotation of the rod with respect to the cam, thereby helping to maintain the clutch surfaces angled with respect to each other, with unidirectional displacement capacity and in parallel each. The upper part of the rod also has supporting arms that extend towards the walls of the chamber for the purposes of stabilizing it during an adjustment, that is, when the threaded element is rotated, lateral pressure is exerted on the upper part of the rod. , while at the same time it slides longitudinally inside the chamber. In addition to the adjustment mechanism described above, other features make it possible to extend the possible range of threshold levels. First, it is possible to provide spacers for the purposes of adjusting the compression distance of the spring for the displacement distances between the rod and the hole. Secondly, the threaded element can be adapted in order to place it in different fixed positions located in the valve housing in such a way that the distance between the adjustment mechanism and the hole can be modified. These preselected positions allow the adjustment mechanism to be placed closer or farther from the bore, thereby expanding the range of potential threshold velocities. The length of the rod can also be modified in order to expand the range if necessary. The valve also contemplates the use of an inadequate tamper-proof breakable plug to cover the head of the threaded element once the adjustment has been made. Once the threaded element is rotated, and after the P888 corresponding settings to set the flow rate threshold, the cap can be used in order to cover the head and avoid unauthorized adjustments.

BRIEF DESCRIPTION OF THE DRAWINGS The above aspects together with other aspects, advantages and characteristics of the present invention will become more apparent from the Detailed Description section of the invention presented together with the following drawings, wherein; Figure 1 illustrates a longitudinal cross-section of an exemplary embodiment of the excess flow valve body used in the present invention; Figure 2 illustrates a longitudinal cross section of an exemplary configuration of the excess flow valve of the present invention in its open position, corresponding to that illustrated in Figure 3; Figure 3 illustrates a longitudinal cross section of an exemplary configuration of the excess flow valve of the present invention in its closed position, corresponding to that illustrated in Figure 2; Figures 4a, 4b and 4c illustrate a view P888 upper, lateral and lower, respectively, of an exemplary configuration of the rod with an angled clutch surface and the support arms used in the excess flow valve of the present invention; Figures 5a, 5b and 5c illustrate an end, top and side view, respectively, of an exemplary configuration of an adjustment cam with an angled clutch surface used in the excess flow valve of the present invention; Figures 6a and bb illustrate a side view and a terminal view, respectively, of an exemplary configuration of a threaded element used in the excess flow valve of the present invention; Figure 7a illustrates a cross-sectional view of an exemplary configuration of a lid with a perforation on the valve body with a breakable plug used in the excess flow valve of the present invention; Figure 7b illustrates a cross-sectional view of an exemplary configuration of a sealing cap used in the excess flow valve of the present invention; Figures 8a and 8b illustrate spacers of different widths that can be used in the valve P888 of excess flow of the present invention; Figure 9 illustrates an exemplary system having multiple positions with a long rod and a threaded element in the upper position, used in the excess flow valve of the present invention; Figure 10 illustrates an exemplary system having multiple positions with a long rod, a threaded element in the upper position, and a spacer, used in the excess flow valve of the present invention; Figure 11 illustrates an exemplary system having multiple positions with a long rod, a threaded element in the upper position, and two spacers, used in the excess flow valve of the present invention; Figure 12 illustrates an exemplary system having multiple positions with a short rod and a threaded element in the central position, used in the excess flow valve of the present invention; Figure 13 illustrates an exemplary system having multiple positions with a short rod, a threaded element in the central position, and a spacer, used in the excess flow valve of the present invention; and Figure 14 illustrates an exemplary system P888 having multiple positions with a short rod and a threaded element in the lower position, used in the excess flow valve of the present invention.

DETAILED DESCRIPTION OF THE INVENTION With reference to the drawings, the present invention provides an excess flow valve system and a method for regulating the flow of fluid, vapor or gas passing through it. In the first modality, the valve system comprises a housing body 1 in a single chamber, as illustrated in Figure 1, which has an upper end 2 and a lower end 3, wherein in the internal part of the housing body there is a chamber 4 with a hole in one end. The orifice 5 is formed in a narrow portion 7 of the housing body 1 through which the fluid or gas can pass from one end 2 to the other 3. The narrow portion 7 has a receiving sector 8 adjacent to the widest portion 9. of the chamber 4 receiving the seat of the rod 15, as will be explained hereinafter. The body 1 is preferably externally threaded on each end 2 and 3 in such a way that it can be fixed to a system of threaded pipes, such as those used in gas distribution systems. The body 1 has an opening or perforation 10 through which a threaded element 31, such as P888 illustrated in Figure 6a, can be inserted laterally in the chamber. In other embodiments, it is possible to provide multiple perforations 10, as will be discussed, for the purposes of locating the threaded element 31 relative to the body 1 to be changed. Directly on the opposite side of the chamber 4, on the inner wall of the widest portion 9, as illustrated in Figure 1, a notch 29 is seen corresponding to the core 10 so that the threaded element 31 can extend to through the chamber 4 and enter it for the purposes of securing the element against both sides of the body 1. It should be noted that it is possible to implement other means of fastening the threaded element 31, which fall within the scope of the present invention . The housing body 1 is preferably made of a strong, rigid, hermetic material such as steel, a composite material, hardened plastic, etc., and can be manufactured by conventional techniques. Inside the chamber 4, as illustrated in Figures 2 and 3, there is a sliding rod 11 and a helical spring 25 extending in longitudinal direction with respect to the axis of the body 1 of the housing. The rod 11 and the spring 25 are preferably oriented inside the chamber 4, preferably with the spring on the outside, near the perimeter P888 of the camera, while the rod extends relatively inside the spring. The inner wall of the chamber 4 is preferably cylindrical for the purpose of allowing the rod as the spring to slide unhindered. The spring 25 is preferably located in the chamber 4 such that its lower end 30 is compressed against the narrow portion 7 of the chamber 4 and its upper end 28 extends towards the upper part of the rod 14. The upper end 28 of the spring 25 preferably cooperates with the upper part of the rod 14, thus the spring pushes the rod 11 of the hole 5. The spring may be a conventional one, for example, metallic, and may be provided with precalibrated tension, as is known in the technique. The rod 11 is designed to slide inside the chamber 4, preferably inside the spring 25. The rod 11, illustrated in Figures 4a, 4b and 4c, preferably has a lower portion 12 in the form of a flange with four fins 16 that a valve seat 15 prepared to seal the hole 5, an elongated portion 13 in the form of an axis, and an upper part 14 of the rod extend from it. The lower portion 12 in the form of a flange is adapted to be inserted into the hole 5 and positioned relative to the chamber in such a way that the rod 11 can move in the P888 longitudinal guided by the fins 16. The seat 15 of the rod is located on top of the flange-shaped portion 12 and preferably substantially conforms to the receiving portion 8 such that, under the closed position, according to to Figure 3, the rod seat 15 will seal the hole 5. The spaces 18 between the fins 16, as illustrated in Figure 4c, as well as the distance between the rod seat 15 and the receiving portion 8 of the hole, cooperate in determining the flow area through which the fluid or gas can pass from one end 2 to the other 3. The size of the hole 5, as well as the flow area 18 between the fins 16, are accordingly carefully calibrated in order to provide the appropriate amount of flow. Above the seat 15 is the shaft portion 13 which is preferably relatively thin for the purpose of reducing the total weight of the rod such that gravity does not substantially affect the performance of the valve. Along the axis it is possible to place ribs 24 in order to add rigidity, if any. By lengthening or shortening the portion 13 in the form of an axis, or other portions of the rod, it may be longer or shorter for the purposes of adjusting the flow rate threshold when this is necessary. The upper part 14 of the rod has one or P888 plus support arms 19, as illustrated in Figures 4a-4c. The support arms 19 preferably extend outwardly and laterally for the purpose of providing the necessary support to the rod 11 with respect to the wall of the chamber. The support arms 19, in conjunction with the fins 16 of the lower portion 12 in the form of a flange, allow the rod 11 to slide substantially in the longitudinal direction along the axis of the housing body 1. The support arms 19 further reinforce the rod against lateral pressure that can be applied to the upper portion 14 of the rod when the valve is adjusted. Preferably at least four support arms 19 are provided, or the necessary number of them in order to provide the necessary support in all directions within the 'cylindrical wall of the chamber 4. The spaces 26 between the support arms 19 must also provide a sufficient flow area, ie, greater than the flow area of the hole 5, so that this portion of the chamber does not control the Valve flow rate. This also applies to the rest of the components of the valve placed collectively inside the chamber 4. As long as the arms 19 extend far enough to the wall of the chamber for the purposes of obtaining lateral support, these extend , preferably, a little P888 inside the camera, for the purpose of reducing friction between the arms 19 and the interior of the camera. The upper part 14 of the rod, with the support arms 19, retains the upper end 28 of the spring 25, either directly, as illustrated in Figures 2 and 3, or together with a retaining ring, or spacer, placed between the spring t the upper part 14 of the rod. Preferably, on the upper portion 14 of the rod is the angled clutch surface 17 of the rod. The clutch surface 17 preferably has the same inclination as the clutch surface 39 of the cam, located on the adjustment cam 37 illustrated in Figures 5a-5c. The location of the clutch surface 17 between two support arms 19 on the upper portion 14 of the rod enables the clutch surface 39 of the cam to slide relative to the clutch surface 17 of the rod, fitting between the two. support arms, at the same time, the rotation between both clutch surfaces 17 and 39 is limited. The width 20 between the two support arms 19 is preferably slightly greater than the width of the clutch surface 39 of the cam, so , that the relative rotation of the surfaces 17 and 39, and the rod 11 and the cam 37, respectively, to which they are connected, P888 is substantially restricted. The rotation of the rod 11 with respect to the cam 37 is limited such that the clutch surfaces 17 and 39 will remain parallel to each other and will slide unidirectionally during the adjustments, whereby adjustments can be made with precision. It is evident that it is possible to place similar support guides on the cam 37 and other portions of the valve to limit the relative rotation between the rod 11 and the cam 37, as well as other means of limiting the rotation of the rod, for example , guides can also be used along the chamber or hole. Through the perforation 10 of the body 1, as illustrated in Figures 2 and 3, the threaded element 31 is located. The threaded element 31, according to Figures 6a-6b, is preferably constituted by an axis or bolt with a external thread 33 extending at least along part of its length. The shaft has a head 35 at one end 34 and ends at the other end 36. When it is inserted into the body 1, the terminal end 36 is inserted into the notch 29 located on the side of the chamber 4 opposite the bore 10, so that the threaded portion 33 of the shaft extends laterally through the chamber 4, the element 31 being supported by the body 1. The head 35 is located such P888 that can be accessed through piercing 10 from the outside of the body. The head 35 is preferably alien, although a screw head, hexagonal or otherwise, may be used for the purpose of allowing the threaded element 31 to be rotated inside the chamber 4. Located on the threaded element 31, as illustrated Figure 3, is the cam 37. The cam 37, according to Figures 5a-5c, has a threaded bore 41 that can rotate with respect to the threaded portion 33 of the element 31. When the element 31 is rotated, the The cam moves longitudinally thereon and, as illustrated in Figure 3, laterally with respect to the chamber 4. The clutch surface of the cam 39 extends from the holding portion, and is oriented and adapted to contact and slide in parallel to the clutch surface 17 of the rod substantially along the same inclined plane 60, according to Figure 3. The angle of the two surfaces 17 and 39 and the inclined plane 60 is preferably approximate. at 45 degrees, however it is possible to use any angle through which a relative displacement of the two surfaces in normal directions relative to each other is achieved. When the threaded element 31 is rotated and the cam 37 moves laterally, the two clutch surfaces slide together, and the spring P888 25 pushed to the rod 11 towards the cam 37, the sliding of both clutch surfaces 17 and 39 causes the first one of them and the rod 11 to move in the longitudinal direction, either approaching or moving away from the hole 5. Since the cam limits the upward displacement of the rod, the adjustment thereof in the manner described sets the maximum distance of displacement of the rod relative to the hole 5. Both the rod 11, with its upper portion 14, and the cam 37, can be made virtually from any resistant and resilient material, although preferably a compound of the Delrin M. Reg. type, marketed by Dupont, is preferably used, for example. The material will preferably withstand extreme changes in temperature and humidity whereby the two clutch surfaces 17 and 39 will wear out evenly, sliding with relative ease and low friction. It is also convenient that the material be light so that the displacement of the rod 11 is only nominally affected by the orientation of the valve. The rod 11 and the element 31 can be manufactured by any conventional method, such as, for example, injection molding. A sealing cap 45 sealing the perforation 10, as illustrated in Figure 7a. Preferably P888 has an external thread 46 which matches the internal thread of the perforation 10, so that when the cover 45 is inserted into it, once it is clamped, it configures a seal. The cover 45 is adapted with a cavity 47 adjacent to which the head 35 can be placed where the lid cooperates in the fixing of the threaded element 31 inside the chamber, preventing the element 31 from sliding but allowing it to rotate. In the preferred embodiment, an access hole 49 is provided through the cover 45 so that the head 35 of the threaded element 31 can be rotated externally, ie, from outside the body 1. Within the cavity 47 of the cover 45 a bushing 50, illustrated in Figure 9, is preferably placed for the purpose of preventing leakage of fluid or gas from the chamber 4 through the access hole 49. The access hole 49 preferably has a thread such as that a breakable screw 51 can be inserted therein to prevent the implementation of unauthorized adjustments of the threaded element 31. The pitch of the threads 52 and 53 of the screw 51 and the access hole 49, respectively, will preferably be breakable, manufactured in such a way that a standard screw can be inserted. The screw 51 has an independent head 55, for example, a screw head, alien, hexagonal, etc., which is adapted to be rotated using any P888 conventional medium. The head 55 is supported by a thin shank 56 that can be split once the valve is adjusted and the screw is inserted. The separators 57, 59 and 61, according to Figures 8a and 8b, are intended to extend the spectrum of speed thresholds. The spacers are preferably annular in shape that agree with the shape of the spring, although the possibility of using spacers that adopt virtually any shape is evident. In the chamber adjacent the spring, it is possible to insert one or more spacers, either on the upper end 28, or lower 30, or both. The separators facilitate the adjustment of the flow velocity threshold by compressing the spring and adjusting its tension for any distance of displacement of the rod. Figures 10, 11 and 13 illustrate examples that refer to the way in which the spacers are inserted in the chamber with respect to the spring. The separators 57, 59 and 61 can come in different widths according to the desired Threshold Velocity spectra. In your case it is possible to use the desired number of separators. According to another embodiment of the present invention, illustrated in Figures 9-14, the system may be constituted by a multi-phase excess flow valve. The structure and operation of this system Valve P888 are similar to the case of the first modality, with the difference that it enjoys a wider spectrum of Threshold Speed. As substantially illustrated in Figures 9-14, a three phase housing design 70 is presented which implements the multiple phase flow overflow valve system. According to the design of three-phase housing, three positions 63, 64 and 65 are provided axially displaced for the threaded element 31. The physical dimensions of other components of the valve system can be adjusted for the purpose of allowing the introduction of the element 31 in one of the new positions. For each of the positions it is possible to use the same helical spring 25 of pre-calibrated tension, or different springs for the effects of covering a broad spectrum of Threshold Speed. Each of the positions comprises a perforation 10 and an associated notch 29, as illustrated in Figures 9-14, similar to those used in the first embodiment. Each position 63, 64 and 65 is at a predetermined distance from the hole 5 in order to expand the spectrum of speed thresholds. The unused positions can be sealed by the use of threaded plugs 67, as illustrated in Figure 7b, for the purpose of preventing any leakage of fluid or gas from the body 1. In conjunction with the fine adjustments that can be made by means of P888 of the adjustment mechanism, the multi-phase design valve system can be used to encompass virtually any Threshold Speed spectrum. Although the illustrations show only three positions, the possibility of implementing 2, 4, 5 or more positions according to the spectrum of flow rates and the fineness of the required adjustment will be noted. In its opening position, the valve system regulates the flow of fluid or gas coming from one area on one end 2 in the direction of another area located at the opposite end 3. To adjust the valve, rotating the threaded element 31 with the head 35, the cam 37 can be laterally displaced in the direction transverse to the flow orientation or to the longitudinal axis of the valve body 1. The clutch surface of the cam 39, as discussed, is designed to slide relative to the clutch surface of the rod 17 along the inclined plane 60. In the embodiment illustrated in Figures 2 and 3, the lateral displacement of the cam 37 along the element 31, separating from the sealing cap 45, allows the rod 11 moves upwards in response to the pressure of the spring 25, whereby the distance between the seat 15 of the rod and the hole 5 is increased. Consequently, the pressure differential created or through hole 5 decreases, P888 by increasing the Threshold Speed under which the valve system will interrupt the passage of fluid or gas. On the other hand, the displacement of the cam 37 towards the sealing cap 45 causes the rod 11 to move in a downward direction, thus decreasing the distance between the seat 15 of the rod and the hole 5. Consequently, the pressure differential created through the hole 5 increases, decreasing the Threshold Speed (Of course, the ramp-like structure of the inclined plane 60 could be inverted, so that the displacement towards the sealing cap 45 can increase the Threshold Speed instead to decrease it). Through this unique design, the valve system can be adapted to operate at virtually any Threshold Speed. In practice, the system can be used to regulate the flow of gas entering a house from an external gas source. First, the maximum gas consumption rate for the house is determined (the speed at which all gas-powered appliances are turned on). Then the Threshold Speed is set at the desired level, for example, a value approximately 10% higher than the maximum consumption speed. This task is preferably performed by a professional by using a flow meter. Consequently, if the maximum consumption speed is P888 established in 100,000 BTUs (British Caloric Units) (105.50 MJ), then the Threshold Speed is set at approximately 110,000 BTUs (116.05 MJ) by adjusting a pre-calibrated threaded element 31. If the flow velocity exceeds the Threshold Speed, the rod moves against the spring 25 in the direction of the hole 5, so that the seat 15 of the rod exerts pressure against the receiving portion 8, causing the valve system to interrupt the supply of gas to the house, thus avoiding a possible catastrophe. Using the design of the present invention, the valve system can be regulated to operate at any Threshold Speed with a virtually infinite adjustment capacity. Figure 2 illustrates a cross-sectional view of an exemplary configuration of the excess flow valve system under its open position, while Figure 3 is a view of the same valve from a direction normal to the cross section of the valve. Figure 2 in its closed position. As it slides in an upward or downward direction, the rod 11 is guided by the two or more guide fins 16 and / or the support arms 19. The support arms 19 on the upper part of the disk with rod 14 guarantee the sliding length of the rod inside the body 1 of the housing during its movement towards P888 up or down. The support arms 19 help to stabilize the rod during adjustments. In addition, since excessive lateral pressure on the upper portion 14 of the rod can cause the arms 19 to become stuck against the wall of the chamber 4, when regulating the valve care must be taken to release the rod by turning the element in the opposite direction Threaded 31 slightly before final adjustment. The rod 11 is pushed against the cam 37, as illustrated in Figure 2, which limits its ascent within the chamber 4 and when the Threshold Speed is exceeded, the rod 11 quickly separates from the cam 37 and slides in the direction of the hole 5, so that the seat 15 of the rod seals the valve, as illustrated in Figure 3. With reference to Figures 9-14, the valve system herein can be used to expand on Significantly, the range of potential velocity thresholds. For example, according to a modality that has been tested and put into practice, the spectrum of flow velocity thresholds for natural gas can range from approximately 30,000 to 1.5 million BTUs (31.65 and 1582.58 MJ). Below are illustrated the possible ranges that can be achieved with a single valve housing body, using spacers of different sizes and rods, and phase positions P888 multiple. In each of these examples a single pre-calibrated tension spring is used, with a three-phase housing body 1, in combination with an adjustment mechanism whose clutch surfaces are at 45 degrees. In each of the cases presented, the precision settings are practically infinite within the operating ranges without the need to replace the spring, modify the size of the hole, etc. System No. 1: The system illustrated in Figure 9 uses a standard size rod 11 with the threaded element 31 in the upper position 63. The operating spectrum using the adjustment mechanism of the present invention on this system ranges from approximately 31,000 to 593,000 BTUs (32.70 and 625.64 MJ) for natural gas, and between approximately 47,000 and 944,000 BTUs (49.58 and 995.97 MJ) for liquid petroleum. System No. 2: The system illustrated in Figure 10 utilizes a standard size rod 11 with a spacer 61 of .300 inches wide (0.762 cm wide) and the threaded element 31 in the upper position 63. The operating spectrum employing the adjustment mechanism of the present invention on this system ranges from approximately 39,000 to 916,000 BTUs (41.14 and 966.43 MJ) for natural gas, and between approximately 61,000 and 1,457,000 BTUs (64.35 and 1537.21 MJ) for liquid oil P888 System No. 3: The system illustrated in Figure 11 uses a standard size rod 11 with two spacers 59 and 61 (of .200 and .300 inches wide, respectively) (0.508 and 0.762 cm wide, respectively) and the threaded element 31 in the upper position 63. The spectrum operative using the adjustment mechanism of the present invention on this system ranges from approximately 52,000 to 793,000 BTUs (54.86 and 836.65 MJ) for natural gas, and between approximately 82,000 and 1,26,000 BTUs (86.51 and 1331, 48 MJ) for liquid petroleum. System No. 4: The system illustrated in Figure 12 uses a shorter rod 69 with the threaded element 31 in the middle position 64. The operating spectrum using the adjustment mechanism of the present invention on this system ranges from approximately 75,000 to 980,000 BTUs (79.12 and 1033.95 MJ) for natural gas, and between approximately 119,000 and 1,561,000 BTUs (125.55 and 1646.94 MJ) for liquid petroleum. "System No. 5: The system illustrated in the Figure 13 uses a shorter rod 69 with a spacer 57 (of .100 inches wide) (0.254 cm wide) and the threaded element 31 in the middle position 64. The operating spectrum using the adjustment mechanism of the present invention on this system ranges between approximately 36,000 and P888 877,000 BTUs (37.98 and 925.28 MJ) for natural gas, and between approximately 57,000 and 1,395,000 (60.13 and 1471.80 MJ); for liquid oil. System No. 6: The system illustrated in Figure 14 uses a shorter rod 69 with the threaded element 31 in the lower position 65. The operating range using the adjustment mechanism of the present invention on this system ranges from about 54,000 to 851,000 BTUs (56.97 and 897.5 MJ) for natural gas, and between approximately 86,000 and 1,354,000 BTUs (90.73 and 1428.54 MJ) for liquid petroleum. With the valve systems described above, it is very likely that the Threshold Velocity spectrum is sufficient for most applications that use natural gas or liquid petroleum gas. Consequently, a single valve system in which the positions can be adjusted in the field according to a wide possible spectrum, without having to modify the size of the housing body 1, the size of the hole 5, or the tension of the spring 25, can be applied in numerous applications in which the pressures of the fluid or gas supply vary. The positions can be invalidated and recovered since the clutch surfaces typically wear out evenly. On the other hand, it should be noted that when other applications require a P888 distinct spectrum of threshold velocity, the above threshold spectra can be further modified by changing the position of the threaded element 31, the length of the rod 11, and / or the size and number of the separators. In your case, the range of movement of the adjustment mechanism can also be regulated. Instead of having to replace the spring or modify the size of the hole for the purposes of adjusting the Threshold Speed as in standard valves, it is possible to implement one or more of the aforementioned adjustment procedures. For example, using a single valve housing body, it is possible to add one or more spacers for the purposes of adjusting the effective tension of the spring in order to modify the spectrum of possible Threshold Speeds. Likewise, and in order to extend the range of Threshold Speeds, it is possible to use multiple phase positions that adapt to any housing body size. On the other hand, it is possible to change the rod itself to adjust its distance of travel and therefore the Threshold Speed. Then the valve is regulated at the precise Threshold Speed by means of the adjustment mechanism by turning the threaded element 31 to a predetermined position, for example, at a specific BTUs (MJ) level.

P888 Likewise, tests have been carried out using flow meters that show the sensitivity of the positions of the adjustment mechanism. For example, a pipe of approximately 54 feet (16.46) with 3/4 inch (1.90 cm) pipes was subjected to a test, which was supplied with air, simulating natural gas, under constant pressure at one end, which it had a perforated lid over the other. The system was designed to simulate the situation under which the end of the system is at low pressure away from the entrance. With the Threshold Speed of the valve fixed at approximately 64,000 BTUs (67.52 MJ) for natural gas (or 50 SCFH (1,416 m3 / h)), the valve under test interrupted flow when a 0.125 inch (0.32 cm) orifice was drilled. of diameter in the lid. When a Threshold Speed of approximately 128,000 BTUs (135.04 MJ) was set for natural gas (or 100 SCFH (2.83 m3 / h)), the valve was closed by drilling a 0.1719 inch (0.44 cm) diameter hole in the cap. Since the pressure in the system is higher at the inlet than at its final end, when a hole is drilled near the inlet, for example within the first 10 feet (3.05 m) approximately, the valve typically closes being the smaller hole, for example, when it is half the size of the hole drilled at the far end. Having the possibility of P888 to fix the valve in a precise Threshold Speed, the valve of the present is able to detect both small and large leaks without confusing the first with interruptions of the pilot light, or the large ones with the ignition of all the devices, that is, a situation of maximum consumption. Although the present invention has been described in detail, it must be taken into account that it is not limited to the specific modalities illustrated and explained. The present invention contemplates that the modalities that have not been described or illustrated are within its scope, that its scope is exclusively delimited by the appended Claims.

P888

Claims (31)

1. CLAIMS 1. A valve consisting of: an outer housing having a chamber extending in the longitudinal direction; the housing has a hole located at one of the ends of the chamber; a rod within the chamber, moving in the longitudinal direction between an open and a closed position, the rod adapted to seal the hole in the closed position; a spring element for pushing the rod in the longitudinal direction away from the hole to the open position; an externally adjustable threaded element that extends through the housing and into the chamber; a retainer for limiting the movement of the rod relative to the hole in the longitudinal direction, the retainer is associated with the threaded element in such a way that turning the threaded element causes a first angled surface on the retainer to move longitudinally relative to the threaded element and laterally in relation to the camera; a second angled surface located on the rod which is pushed by the spring substantially towards the first angled surface, wherein the first and second angled surfaces are adapted to join P888 with each other and slide one with respect to the other substantially along the same plane; and wherein by externally turning the threaded element, the retainer can move longitudinally relative to the threaded element and laterally relative to the chamber, and the location of the first angled surface mentioned can be adjusted and fixed at a predetermined position, where the position of the first angled surface determines the maximum distance of displacement of the rod in the longitudinal direction, wherein the position of the first angled surface helps determine the flow velocity threshold of the valve. The valve of Claim 1, wherein the valve is adapted in such a way that the rotation of the rod relative to the retainer is substantially limited by one or more guides, wherein the first and second angled surfaces are adapted to join one with the other and slip one with respect to the other substantially in only one direction. 3. The valve of Claim 1, wherein the spring element substantially pushes the second angled surface against the first angled surface, such that they are in substantial contact with each other, wherein the turn of the threaded element P888 causes the first angled surface to move laterally relative to the second angled surface causing the rod to move either towards or away from the hole. The valve of claim 1, wherein the threaded element is substantially fixed relative to the housing in all directions except rotationally, wherein at least a portion of the threaded element is substantially located within the chamber, the element threaded having a head which can be accessed from outside the housing, such that the threaded element can be adjusted externally. The valve of Claim 4, wherein a breakable plug is provided to prevent it from being returned to the head of the threaded element once it is adjusted. The valve of Claim 1, wherein the rod is provided with one or more support arms to assist in supporting the rod laterally within the chamber; the support arms being adapted to allow the rod to move freely in the longitudinal direction within the chamber. The valve of Claim 1, wherein one or more spacers are supplied within the chamber P888 for adjusting the tension of the spring element and changing the flow rate threshold of the valve, wherein the one or more spacers are used to adjust the distance in which the spring element is to be compressed to move the rod to the closed position for any maximum distance of displacement of the rod. 8. The valve of Claim 1, wherein the housing is provided with multiple positions in which the threaded element can be placed, wherein each of the positions is located on the housing at a predetermined distance from the hole, wherein when changing the position of the threaded element in In a particular position, the spectrum of flow velocity thresholds can be adjusted. The valve of Claim 8, wherein each of the multiple positions comprises an opening on one side of the housing and a notch on the other side, wherein the threaded element can be inserted through the opening and extended through the chamber to the other side within the notch, wherein the threaded element is retained within the housing in all directions except rotationally and is oriented laterally within the chamber. The valve of Claim 1, wherein the retainer is virtually infinitely variable P888 between the minimum and maximum positions in the threaded element, where the position of the first angled surface can be accurately controlled by the threaded element, where the valve achieves the necessary sensitivity for low pressure applications. 11. A valve consisting of: a body having a chamber and a hole located at one end of the chamber; a rod within the chamber that can move between an open and a closed position and is adapted to seal the hole; a spring element for pushing the rod away from the hole to the open position; and an adjustment mechanism consisting of an externally adjustable element and a movable cam associated therewith, wherein the cam can be moved relative to the externally adjustable element and can be used to establish the maximum distance of travel of the rod relative to the externally adjustable element. to the orifice, where the position of the cam on the externally adjustable element helps determine the flow velocity threshold of the valve. The valve of Claim 11, wherein the externally adjustable element is threaded and extends within the chamber, wherein the cam is associated by threading with the externally adjustable element of such P888 so that when turning the element the cam can be moved longitudinally along the element and laterally inside the chamber. The valve of Claim 12, wherein on top of the cam there is a first angled surface that is adapted to be joined with a second angled surface on the rod, the second angled surface is urged by the spring towards the first angled surface, at where by moving the cam longitudinally along the externally adjustable element in one direction it causes the first and second angled surfaces to slide relative to one another, and the second angled surface to move in a second direction, where the rod it is moved, either towards or away from the hole. The valve of Claim 13, wherein one or more guides are provided to substantially limit the rotation of the rod and / or the cam, wherein the rotation of the rod relative to the cam is substantially restricted, in such a manner that, when the externally adjustable element is rotated and the cam moves longitudinally along the element, the first and second angled surfaces slide one relative to the other, substantially along the same plane and substantially in only one direction . P888 15. The valve of Claim 11, wherein the externally adjustable element is substantially fixed within the chamber except in the rotational direction, wherein turning the externally adjustable element causes the cam associated with it to move longitudinally relative to the to the element and laterally in relation to the camera. 16. A method for adjusting the flow velocity threshold of a gas or fluid flow system containing natural gas, liquid petroleum, or similar materials, under pressure, which involves: installing a valve with a rod and a hole in the fluid flow system, the valve having an adjustment mechanism comprising an externally adjustable element and a movable cam associated therewith; determine the flow velocity threshold, of the fluid flow system; setting the flow rate threshold of the valve by means of adjusting the externally adjustable element and moving the cam in relation to it, wherein the position of the cam relative to the externally adjustable element determines the maximum distance of displacement of the rod with relation to the hole. 17. The method of Claim 16, wherein P888 the step of installing the valve in the fluid flow system comprises the additional step of providing a first angled surface on the cam and a second angled surface on the rod, wherein the first and second angled surfaces are joined to each other, to determine the maximum distance of displacement of the rod relative to the hole. The method of Claim 17, wherein the method includes the additional step of limiting the rotational movement of the rod relative to the cam, wherein the rotational orientation of the first angled surface relative to the second angled surface is maintained substantially constant. The method of Claim 17, wherein the step of fixing the maximum distance of travel of the rod relative to the hole includes turning the externally adjustable member and causing the cam to move longitudinally thereon in a first direction , wherein moving the cam in the first direction causes the first and second angled surfaces to slide in relation to one another, and the rod, which is pushed by the spring towards the cam, moves in a second direction and either towards or away from the hole. 20. The method of Claim 19, wherein P888 The step of setting the flow rate threshold allows the valve to close when the flow rate threshold is exceeded in the system, where the flow rate threshold is exceeded when the pressure differential between the upstream portions and downstream of the system is large enough to cause the rod to overcome the spring pressure by pushing the rod towards the cam and causing the rod to slide towards and against the hole. The method of Claim 16, wherein the step of determining the flow velocity threshold of the fluid flow system comprises the step of determining the maximum consumption velocity of the fluid flow system and adding to the maximum velocity. of consumption a predetermined amount. 22. The method of Claim 21, wherein the predetermined amount that is added to the maximum consumption rate is about 10 percent of the maximum consumption speed. The method of Claim 16, wherein the method comprises the additional step of providing a plurality of positions in the valve and positioning the externally adjustable element in one of the positions, wherein the spectrum of possible thresholds of flow rates is You can adjust in that way. P888 24. The method of Claim 16, wherein the method comprises the additional step of providing a spring that pushes the rod away from the hole to an open position and of providing one or more spacers that can, for any maximum travel distance of the rod, to be used to adjust the tension of the spring, wherein one or more of these spacers can be used to adjust the amount that the spring must be compressed to cause the rod to be moved to a closed position. The method of Claim 16, wherein the method comprises the additional step of selecting a rod having a predetermined length, wherein the length of the rod can be used to adjust a range of possible flow velocity thresholds, which they can be used in the method. 26. A valve that consists of: a body that has a chamber and a hole; a rod within the chamber that moves between an open and a closed position, the rod adapted to seal the hole in the closed position and having a first sliding surface thereon; a spring for pushing the rod away from the hole to the open position; P888 an adjustment mechanism comprising an externally adjustable element and a second sliding surface extending therefrom, wherein the first and second sliding surfaces are adapted to be joined with one another to establish the maximum distance of displacement of the rod relative to to the orifice, wherein the position of the second sliding surface relative to the first sliding surface determines the flow velocity threshold of the valve; and a guide for limiting the rotation of the rod relative to the adjustment mechanism, such that the rotational orientation of the first sliding surface relative to the second sliding surface can be maintained tantially constant. 27. The valve of Claim 26, wherein the first and second sliding surfaces are joined to each other, the sliding surfaces extending tantially along the same angled plane. The valve of Claim 26, wherein the guide is comprised of two or more guide surfaces extended on each side of the first and / or second sliding surfaces, wherein the distance between the two or more guide surfaces is only slightly greater than the width of the first and / or second sliding surfaces, P888 in such a way that the guide surfaces limit the extent to which the first sliding surface and the second sliding surface can rotate with respect to one another. 29. The valve of Claim 28, wherein by limiting the relative rotational movement of the first and second sliding surfaces, the first and second sliding surfaces remain substantially parallel with respect to each other and slide one relative to the other substantially in one direction, substantially at length of the same plane during adjustments. 30. The valve of Claim 26, wherein the support arms extend from the rod outward toward the wall of the chamber to stabilize the rod during adjustments and to assist in supporting the rod during longitudinal movement of the rod. rod in the camera. The valve of Claim 26, wherein the externally adjustable element comprises a threaded shaft extending inside the chamber, wherein a cam having a threaded bore associated with the threaded shaft is provided therein, and wherein the second The sliding surface is located on the cam, in such a way that when turning the externally adjustable element, the cam P888 moves longitudinally along the threaded shaft and causes the second sliding surface to move in one direction, such that the second sliding surface slides relative to the first sliding surface and causes the first sliding surface to move in one direction. second address. P888