MXPA97003862A - Three eta gas pressure regulator - Google Patents

Abstract

The present invention relates to a supplemental pressure regulator that can be used with single-stage or multi-stage pressure regulators. It can also be conveniently used with a novel two-stage balanced pressure regulator to form a three-stage vacuum demand pressure regulation system, which can be used to regulate the pressure of compressed gases used as fuel in engines, such as the natural gas used in vehicles activated with natural gas. The pressure regulator of the present is a regulator with a low slip, a low set point change, a low pressure drop, low drop, with a high flow, compact and strong, which is suitable for both OEM and be used in the market later. It is particularly useful in applications for single-engine, twin-engine and double-fuel engines.

Description

THREE-STAGE GAS PRESSURE REGULATOR DESCRIPTION OF THE INVENTION The present invention relates to a novel pressure regulator, which is particularly useful as part of a vacuum demand pressure regulation system used to control and regulate the pressure of propane or compressed natural gas in engines supplied with these fuels. It can be used as a supplementary pressure regulator with conventional single-stage or multi-stage pressure regulators, or as the third stage of a novel three-stage pressure regulator. It has become common to use so-called alternative fuels, such as propane or natural gas, in internal combustion engines. Vehicles that are manufactured to operate on a primary fuel such as gasoline can be converted to operate with one of two or more alternate sources of fuel, such as propane or natural gas. In some conversions, the operator has the ability to interrupt between the fuel sources that depend on the availability and price of these fuels. While vehicles are converted to run on these alternate fuels in most cases they have been manufactured with storage tanks for gasoline, pumps to move gasoline from the tank to the engine, and carburetors or fuel injectors to introduce the fuel and the required amount of air for combustion in the engine, it is generally necessary to add to the vehicle being converted the components required to store the alternate fuel and to move it in the required quantities and at the desired pressure for the vehicle engine. Gaseous fuels such as propane and natural gas as alternative fuels are generally stored in pressurized cylinders in which the gas is compressed into a manageable volume. Increasing the pressure to the highest level that can be safely handled by a pressurized storage cylinder increases the amount of fuel that can be stored in this cylinder, and extends the distance the vehicle can be driven before refueling . The typical storage cylinder pressure varies from 2000 to 5000 pounds / inch2. While the pressure inside the storage cylinder in most cases provides the necessary force to move the fuel to the engine, the internal combustion engines can not operate at the high pressures found in the storage cylinder. The gas pressure should be reduced to a level at which the engine can be operated safely, and maintained at a relatively constant reduced pressure to ensure efficient operation of the engine. In addition, it is often desired to provide a vacuum demand fuel system for such vehicles, in which the fuel is introduced to the engine in substantially the same pressure as the combustion air, In such a system, the fuel is not forced into the fuel. engine by a pump or by pressure; it is attracted to the engine by a reduction in the pressure of the combustion air when this air is attracted to the engine. In such a system, it is important to ensure that the relative pressures of air and fuel remain constant to ensure the proper proportion of air and fuel in the engine. Consequently, the fuel pressure should be regulated when it is reduced to minimize the effect of these factors affecting the outlet pressure of the pressure regulation system, and to ensure that the pressure of the fuel entering the engine is constant even when the pressure in the storage cylinder is reduced. At the same time, the regulation of the pressure should allow as much fuel as possible to remove it from the storage cylinder, and thus allow the pressure in the storage cylinder to fall as close as possible to the operating pressure of the engine, while still providing the force required to move the gaseous fuel through the pressure regulation system and into the engine. Conventional pressure regulators having one or more stages over which the regulated gas pressure is reduced and have been used for a long time to reduce the pressure and regulate the flow of the compressed gases are well known. Some of these conventional pressure regulators such as pressure balanced regulators are well known. These typically use various spring arrangements, diaphragms and machine parts to balance the pressure and fluid flow over the various stages of the regulator. For example, U.S. Patent No. 2,794,321 issued June 4, 1957, granted to F.J. Warner et al, discloses a single-stage fuel pressure regulator, which will be useful for reducing and regulating the pressure of fuels such as propane to be used as fuel in an internal combustion engine. Some pressure regulators, such as those commonly used in compressed gas tanks, such as oxygen or acetylene, are designed to allow the operator to adjust the decrease in pressure through each stage. Others, such as those typically used in fuel supply systems, are pre-adjusted and do not allow for any adjustment, or only a "fine tuning" of the outlet pressure by the operator, although more extensive adjustments can be made by personnel from authorized service. The pressure regulators of the prior art suffer from a number of disadvantages that the supplementary pressure regulator of the present invention seeks to overcome. One of the main problems associated with the pressure regulators of the prior art is referred to as the "decrease", that is, the degree of uncertainty about the outlet pressure of the regulator. This degree of uncertainty is a function of the rate of fuel flow and the pressure in the storage cylinder. The "decrease" can create problems in the proper operation of an engine, due for example, to the fuel injectors commonly used in modern vehicles with which it is intended to operate at a constant fuel pressure, and the typical venturi mixer. Carburation requires that the fuel pressure be corresponding with the air pressure to ensure proper control of the fuel-air mixture. The previously proposed solutions to these problems include the use of temperature and pressure transmitters to detect variations in temperature and fuel pressure, and make appropriate adjustments for the operation of the engine. The present invention attempts to overcome or reduce the problem of "decrease" without requiring adjustments to the operation of the engine. Another problem is the "displacement", the increase in pressure inside the regulator, and the downstream of the regulator, when the injector is turned off or the closing solenoid is closed by the carbureted motors, ie it is intended to cut off the fuel supply to the engine. This is sometimes referred to as a pressure rise with a zero flow rate, and is caused by the imperfect sealing of the regulator components including the fuel shut-off solenoid. While displacement can be reduced by increasing the sealing forces within the regulator, such an increase often requires modifications to the regulator structure, not only when applying these larger forces but also to balance them, to ensure that the regulator can be easily open when the fuel supply to the engine starts again. Associated with the rise of the zero flow rate pressure is the leakage of fuel from the regulator to the atmosphere. Another problem with the regulators of the prior art is the change of the established point, mainly the degree of uncertainty about the variation of the outlet pressure of the regulator, due to changes in the requirements of the operating temperature, or the fuel of the engine or the air flow. Changing the set point can create problems in the proper operation of the engine, for example, when the venturi carburetor mixer requires that the fuel pressure be corresponding with the air pressure to ensure proper control of the fuel-air mixture. . The fuel flow from a storage cylinder to a pressure regulator is typically controlled by a solenoid controlled valve that can be mounted on the same regulator and can be opened by the vehicle operator just before the ignition system of the vehicle. motor is off. The solenoid-controlled valve typically opens against the pressure of the storage cylinder, and when it opens, fuel flows through the regulator to the engine. In the prior art regulator assemblies, it may take several seconds for the full fuel flow to be available for the engine fuel injector, and for the desired operating pressure in the fuel injector to be reached. Unless the vehicle operator waits for this interval before closing the ignition, the vehicle may not start properly, or may not start. In the spring diaphragm-based regulators of the prior art, the outlet pressure is a function of a large number of variables including the outlet pressure to the regulator, the output flow rate, the characteristics and properties of the diaphragm, which include its area and extension, the reference pressure, the area and configuration of the hole, the area and configuration of the pin, the spring rate and the operating temperature. Changes in these variables result in fluctuations in pressure and output, and require that the output pressure of such regulators be set at a level higher than the optimum level to ensure that there is a positive fuel flow at all times in the engine. This can result in operating inefficiencies and greater than the necessary emission levels. In addition, while the regulator can be set to provide optimum idle conditions, the effect of these variables can cause delays in the return of the regulator to optimum conditions after extending the high-speed operation, typically leading to stopping the engine. Conventional vacuum pressure pressure regulation systems are extremely sensitive to change to the reference pressure, particularly under idle conditions. Minor variations in the reference pressure, unless it responds quickly, can cause an error in the reference pressure at the regulator with respect to the air inlet pressure to the engine. This reference pressure error can cause the venturi carburetor mixer to react poorly because they are not corresponding in air pressure and fuel. It can also lead to the interruption of the supply of fuel to the engine and possible stopping of the engine. So that it is an object of the present invention to provide an improved pressure regulator which is adapted to provide a rapid response and maximum sensitivity to change in the inlet pressure and which minimizes fluctuations in the outlet pressure. It is also an object of the present invention to provide an improved pressure regulator adapted to open quickly even against the high pressures of the storage cylinder, thus allowing the regulator to reach operating pressures almost immediately. Another object of the present invention is to provide a pressure regulation system necessary to make effective the operation of the fuel pressure supply system, and thus allowing a larger operation of the vehicle before reloading. The present invention provides a supplemental pressure regulator that can be used with single-stage or multi-stage pressure regulators. It can also be conveniently used with a novel pressure regulator balanced by two stages to form a three-stage vacuum demand pressure regulation system that can be used to regulate the pressure of the compressed gases used as fuels in the engines, such as natural gas used in vehicles activated with natural gas. The pressure regulator of the present invention is a low displacement regulator, with a low set point change, a low pressure decrease, with a low decrease, with a high, compact and strong flow, which is suitable both for OEM as for later use in the market. It is particularly useful in mono-, bi-motor and dual motor applications. The improved supplemental pressure regulator of the present invention minimizes the effect of several of the factors that affect the stability of the outlet pressure of the regulator by providing an optimum balance of several of the regulator components. The plug assembly of the supplemental pressure of the present invention is balanced to eliminate the effect of the inlet pressure, which is one of the aspects that most significantly contributes to the entire decrease. The use of a balanced regulator in the present invention allows a much smaller regulator to achieve the desired level of decrease. Regulators generally smaller have a faster response and are, in general, cheaper to manufacture than large regulators that perform the same function. The supplemental pressure regulator of the present invention provides a transient response to fluctuations in the inlet pressure. The supplemental pressure regulator of the present invention comprises a substantially hollow body having a substantially diaphragm pressure device fitted therein. The body conveniently comprises two body members having abutting abutting edges, which can be held together by any conventional means to form the regulating body. The diaphragm can conveniently be held in place between the abutting edges of the two body members. The proportion of the surface area of the diaphragm in the interior volume of the regulator is substantially higher than that commonly found in the pressure regulators of the prior art. One side of the diaphragm is exposed by means of a reference gate at a generally constant reference pressure, which may be an atmospheric pressure, or in the case of turbocharged engines, there may be a pressure at the point where air and fuel mix. The other side of the diaphragm is exposed by means of an inlet gate to a gas flow at a regulated pressure which is intended to be relatively constant with respect to the reference pressure, and in the case of the preferred embodiment, it is intended that is substantially equal to this reference pressure. Mounted on the regulator body are the closing solenoid elements to open and close the flow of the pressurized gas from the regulator inlet to the regulator body, and the solenoid elements of idle and start to allow the flow of fuel from the input of the regulator to the engine during the start and idle conditions. A pressure regulation plug assembly is arranged between the gas inlet in the regulator and the regulator body to control the flow of gas through the regulator, and is connected to the diaphragm to form a pressure regulation assembly inside. of the regulator body. The closing solenoid elements can be integrally constructed with the pressure regulating pin assembly to ensure complete closing of the regulator when the regulating fuel supply is closed and to provide an efficient space and compact assembly. The regulated pressure side of the diaphragm is in fluid communication with the engine to which the regulated pressure fuel pressure is directed. While the engine is in operation, the fuel inlet to the engine is generally at a lower pressure than the regulated pressure inside the regulator body, due to the movement of the combustion air to the engine, passing this fuel inlet. In a preferred embodiment of the present invention, the reference pressure is the pressure of the air supply source (which may be atmospheric or turbocharged) and the fuel pressure at the outlet of the regulator is intended to be substantially equal to the reference pressure. In operation of the engine, the combustion air is attracted or forced to the engine, and the flow of air through the inlet venturi causes a lower pressure in the throat of the venturi that causes the regulated pressure gas to flow from the regulator to the motor. The diaphragm is reinforced by at least one support plate mounted centrally on one side of the diaphragm, preferably the regulated side. The support plate is pivotally connected to the valve assembly of the plug which regulates the gas flow through the plug hole in the regulator chamber. When the regulated pressure varies from the reference pressure, the diaphragm moves next to the lower pressure of the regulator. This movement causes the pin valve assembly to move within the hole in the pin, and change the size of this hole and the speed at which the pressurized gas flows to the regulated side of the regulator body. This change in velocity or flow rate will restore the pressure balance of the regulator body. A second support plate may be provided on the reference pressure side of the diaphragm. The configuration of the plug and pin hole can be changed to provide the most efficient flow of pressurized gas around the plug assembly and through the plug hole. While one or two support plates are used to reinforce the central area of the diaphragm and to provide an element for connecting the diaphragm to the pin assembly, it will be understood that the support plates should be sufficiently smaller in diameter than the diaphragm for allow proper movement of the diaphragm inside the regulating body. Several of the components of the supplementary regulator of the present invention have novel designs that allow the regulator to achieve the objects of the invention. The novel plug assembly of the present invention employs an all-metal plug in its preferred embodiment to minimize fluctuations at the set point of the regulator and change at the same point, i.e., the outlet pressure previously determined due to the variations at the operating temperatures and the air flow velocities of the engine and the engine fuel. In addition, it incorporates an integral solenoid to seal the pin hole during zero flow conditions. The plug assembly can be connected to the diaphragm by means of a plastic or lightweight die-cast lever, thus providing a high ratio of the plug to the diaphragm force, which in the case of the preferred embodiment can be in the range of approximately 6: 1. The lever can be connected to the plug by means of a suitable pivot, such as a sliding gasket loaded by spring. The plug assembly can be connected to the diaphragm by means of a low friction block, a low mass material such as Zytel, which allows a relatively easy lateral movement of the diaphragm with respect to the lever. The diaphragm support plates can be conveniently formed from aluminum blanks and can thus be substantially thinner than those used for regulators of the prior art. The ability to use a relatively thin support plate is achieved through the use of a diaphragm stop ring on the inner side of the regulator body, and by incorporating suitable pivot elements such as a spring-loaded sliding joint between the stem of the plug and pin pin. The stop ring is in contact with the back plate and the support, the diaphragm of the regulator in its most extreme or full slip position, which generally occurs when the engine is loaded with fuel with the primary fuel source, such as gasoline. In this situation, there is a complete vacuum of the venturi applied to the diaphragm, but no fuel flows into the regulator body to replace the air removed by the vacuum. The diaphragm and the support plate move the regulated side of the regulator and are in contact with the stop ring that limits the displacement of the diaphragm while only minimally reducing the volume of the regulator body. In the event of an overpressure in the regulator, which may occur in the event of premature ignition of the engine or by a rapid closing of the throttle valve, the spring-loaded sliding joint between the plug stem and the pivot allows the Diaphragm in the bottom comes out against the lower cover, thus significantly reducing the requirement of the resistance of the diaphragm lever and the support plates. The diaphragm cavity and cover plate can be designed to incorporate an appropriate safety factor over the normal operating pressure inside the regulator that is typically close to 25 psig. The supplemental pressure regulator of the present invention provides a closing solenoid assembly, which includes a solenoid piston, which is an integral part of the three stage plug arrangement. The solenoid piston provides a guide for the pin when in the open position and seals the hole in the pin against the gas flow when in the closed position. This novel arrangement allows the use of an ampere-turn coil, as explained below, when the return spring of the pin provides a force opposite to the pressing force that is applied to the solenoid piston seal. The solenoid piston is thus arranged that when the solenoid is activated and the solenoid piston is open, no force is applied to the pin, which is maintained in a balanced position by the opposing forces of gas pressure and regulator springs of the plug assembly. When the solenoid is deactivated, the force of the springs forces the solenoid down against the pin, forcing contact with the hole, and thus stopping the flow of fuel through the pin hole. Once the solenoid closes the pin hole, the pressure acting on the pin in the open position is relieved, and the regulator spring provides a force, with the closing force of the solenoid, and the open direction of the solenoid, reducing thus the magnetic force required to open the solenoid. In some applications of the pressure regulator, a closing solenoid assembly may not be required, and a plug may be used to close the socket cavity and provide pin support. The supplemental pressure regulator of the present invention may incorporate an adjustable orifice, sometimes referred to as a power valve, to regulate the flow of fuel through the outlet of the regulator. The power valve can conveniently use a threaded shaft by means of which a valve disc can be moved from top to bottom either manually or by means of a properly activated motor, inside the power valve to adjust the size of the valve. output of the regulator. The supplemental pressure regulator of the present invention may also incorporate a vacuum solenoid assembly and a start solenoid assembly, each of which may be supplied with a fuel directly from the input of the supplemental regulator of the present invention. by means of a perforation or other opening of the plug cavity. Each of the idle solenoid or starting solenoid assemblies may substantially contain the same solenoids. Both the holes of the idle and start up can be machined in the body of the regulator to minimize the cost of production. further, both solenoid cavities are designated for an identical solenoid core tube that is used in all solenoid applications through the regulator. This core tube consists of a magnetic flange and a stop, and a non-magnetic sleeve. All three parts, ie, the stop, the flange and the sleeve are jointly welded together to provide a substantially hermetic seal to the gas capable of supporting at least four times the maximum operating pressure normally found in the regulator under normal service. In some embodiments of the invention, it may not be necessary to use the idle solenoid or start solenoid, or any of them. When either or both solenoids are not required, the orifice can be sealed with a suitable plug, thus allowing the use of a standardized regulator body for a variety of applications. While the improved supplemental pressure regulator of the present invention can be used in association with conventional single-stage or multi-stage pressure regulators, it can be more effectively used with the novel two-stage pressure regulators disclosed in co-pending patent application No. 2,131,108. The novel two-stage regulator disclosed in this application provides a first and second stage designed to minimize the mass of the dynamic components to provide the fastest response for changes in operating conditions in the regulator. Each of the two stages employs two opposite winding springs to minimize the spring constant and the height of the required spring tower. All components of the first dynamic stage, with the exception of the plug, can be constructed of aluminum, or other light weight materials that have an appropriate strength and thermal conductivity properties. A roller diaphragm is used in each of the first and second stages to maintain a constant effective area throughout the range of motion of the diaphragm. Such a diaphragm has a longer durability, and allows a greater manufacturing tolerance, than a flat diaphragm, and a large extension eliminates the hysteresis effect of the flat diaphragms. A diaphragm of this configuration has an exceptionally long operating life and good performance in cold weather and durability. In this regulator, the spring tower of the first stage is sealed from the environment and referenced in the pressure in the second stage.

Each stage of the first and second stages includes a novel pin assembly designed to eliminate potential leak paths. The construction of each stage of the first and second stages of this particular regulator are substantially identical, with the exception of the arrangement of the particular plug seal used, and the details of the construction of the spring tower. A circular or captured 0-ring gasket can be used for the seal of the second stage plug, since the seal is exposed to a maximum pressure of approximately 170 psig. The spring tower of the second stage may contain a pressure adjustment screw, which allows adjustment of the pressure in the second stage, and thereby the outlet pressure of the first two stages of this regulator. The pressure regulator of the aforementioned copending application may be provided with a pressure relief valve intended to operate in the event of a failure of the first stage of the regulator. The pressure relief valve ("PRV") is provided between the first and second stages and consists of a low mass raft, a PRV spring and a PRV tower. Once the previously determined pressure in the PRV is reached, and the piston moves and is forced towards the wide opening, providing an immediate relief of the pressure.

The two-stage regulator provides the fluid passages that control the temperature to control the temperature of the regulated gas and to compensate for the loss of heat when the gas expands. The supplementary regulator of the present invention provides compensation for fluctuating gas temperatures through the use of an optional power valve. The two-stage regulator disclosed in the aforementioned co-pending application requires only minor modifications to be used with the pressure regulator of the present invention and is the basis of the three-stage regulator design. The regulator body requires some minor modifications of the machining. The most significant modification is that the exit passage is left undrilled and a new outlet and a front seal bushing of the circular package is added to the left front. Also, the locations of the original mounting screw on the left front are not used for a long time; Instead of mounting the threads they are added to the front seal bushing. The arrangement for an optional refrigerant solenoid can be added to the back front; This requires additional drilling and a plug in an appropriate location on the regulator body. The springs of the first and second stages can be replaced with springs of lesser force in order to produce the required first and second stage pressure of 60-170 psig and 23-26 psig, respectively, for use in association with the regulator of additional pressure of the present invention. The supplemental pressure regulator of the present invention when used with the two-stage regulator provides a three-stage regulator that is much more compact than the regulators of the prior art. In operation, pressurized gas, which can be stored at a pressure of 150 psig up to 5000 psig, passes through a preliminary pressure regulation system, which may be disclosed in the aforementioned patent application. The gas pressure is reduced to the regulated pressure within a relatively narrow range, which can typically be from about 21 to 28, or more preferably from 23-26, psig (or such other pressure as may be selected and maintained by selections). of appropriate spring regimes). The natural gas or other fuel flows at this reduced pressure in the passages connecting the pressure regulator of the present invention, and as long as the closing solenoid is open, it can flow therefrom through the plug hole towards the interior of the regulator body. If the closing solenoid closes, it can flow through the boot supply passage to the start and run solenoid assemblies. The interface between the preliminary pressure regulating system and the pressure regulator of the present invention can be designed to ensure the most efficient movement of the gas between the two regulators. Under normal operating conditions, when the gas begins to flow the solenoid opens and allows the plug assembly to move, opening the hole in the plug. To ensure a quick opening of the plug, elements can be provided to allow the flow of gas directly to the regulator body to assist in the opening of the plug, by balancing the pressure on either side of the plug and to provide a flow of fuel Positive pressure to the motor. Under starting or idling conditions, the fuel flow to the engine is low, and sudden variations or pulsations in the reference pressure can cause a temporary closure of the pin hole. Accordingly, the optional separate idle start and idle mounts are provided to accommodate these circumstances. The starter assembly includes an electrically controlled solenoid that opens to allow fuel to flow directly to the engine at the start in the supplemental pressure regulator. To ensure an adequate supply of fuel to the engine under all operating conditions, and without taking into account the nature of the first pressure regulator, the pressure regulator of the present invention can be arranged to provide the idle fuel flow. positive to the motor to ensure proper operation of the motor under idle conditions. The idle circuit uses a solenoid assembly to provide the elements to provide a mechanically adjustable, constant and safe positive fuel flow to the engine under idle conditions. When this circuit is also the source of the pressure of the second stage, its output is also immune to instantaneous changes in the output of three stages or reference pressures. BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a top view partly in section of the pressure regulator body of the present invention, shown in the preferred embodiment as the third stage of the three stage pressure regulator. Figure 2 is a perspective view of the external surface of the pressure regulator body of the present invention. Figure 3 is a top perspective view of the pressure regulator body of the present invention shown in Figure 2. Figure 4 is a perspective view of the internal surface of the pressure regulator body of the present invention. Figure 5 is a perspective view of the inner surface of the lower cover of the pressure regulator of the present invention. Figure 6 is a sectional view taken along line 6-6 of Figure 1. Figure 7 is a sectional view of the power valve assembly taken along line 7-7 of the Figure 1. Figure 8 is a sectional view of the idle solenoid assembly and a start solenoid assembly, taken along line 8-8 of Figure 1. Figures 9A and 9B are plan views. and facing, respectively, the pin lever used in the pin assembly of the present invention. Figures 10A and 10B are plan and sectional views, respectively of the sliding coupling used in the plug assembly of the present invention. Figure 11 is a sectional view of the supplemental pressure regulator of the present invention in a preferred embodiment, as a third stage of a three-stage pressure regulation system, taken along the line generally corresponding to line 6 -6 in Figure 1.

Figure 12 is a sectional view of an alternative embodiment of the regulator of the present invention. Figure 13A is a plan view of a preferred diaphragm assembly used in the embodiment of Figure 12. Figure 13B is a plan view of an anti-wrinkle ring used in a preferred diaphragm assembly of the present invention. Figure 13C is a sectional view of a preferred diaphragm assembly that can be used in the embodiment of Figure 12. Figure 14 is a sectional view of a preferred closing solenoid assembly that can be used in the pressure regulator of the present invention. Figure 15A is a partial view of the regulator plant of Figure 12 showing the pressure relief valve, the fuel temperature sensor or detector and a three stage closing solenoid. Figure 15B is a sectional view along the line EE of Figure 15A showing the construction of the pressure relief valve, the fuel temperature sensor or detector and the three stage closing cavity of the regulator of Figure 12. Figure 16B is a plan view of the diaphragm lever assembly of the embodiment of Figure 12. Figure 16C is an end view of the plug coupler used in the preferred diaphragm assembly of Figures 13A and 13C. Figure 17 is a sectional view of another embodiment of the regulator of the present invention taken along the generally corresponding line with line 6-6 in Figure 1. In one of its preferred embodiments, the supplemental pressure regulator of The present invention is used in combination with a balanced two-stage pressure regulator, and can be constructed to receive and support such a pressure regulator. The construction and operation of the supplemental pressure regulator of the present invention will be described with particular reference to this contemplated use, although those skilled in the art will understand that the construction can be modified to accommodate the use to which the supplemental pressure regulator of the present invention can provide and the pressure regulators will be used with it. Shown in Figure 1 is a partially sectional view of the body 1102 of the pressure regulator of the present invention, which is generally designated 1100. In this preferred embodiment of the invention, the regulator body has an upper surface 1116, which can adapted to cooperate with, or be coupled with, a single-stage or multi-stage pressure regulator such as the two-stage pressure regulator shown in co-pending Canadian Patent Application No. 2,131,108. Vertically elevated from the surface 1116 of the regulator body is a mounting surface 1118, in which a plurality of mounting protrusions 1122 are formed, which are adapted to allow securing, for example, of the two-stage pressure regulator. as described above, in the three-stage body, by any conventional suitable element. Formed within the vertical surface 1118 is a fuel inlet gate in the form of a transfer passage 1120 through which the gas to be regulated can pass, from the main pressure regulator into the interior of the pressure regulator supplementary to the present invention. Disposed on the external surface of the regulator body 1102 are a start solenoid tower 1202 and a no-load solenoid tower 1302. In the embodiment of the invention shown in FIG. 1, a start solenoid cavity 1204 is formed in the solenoid tower 1202 and a vacuum solenoid cavity 1304 is formed in the solenoid tower 1302. In addition, there is a closing solenoid tower 1402, in which a closing solenoid cavity 1404 is formed, and a pressure adjustment tower 1406. Also arranged on the surface 1116 of the regulator body is a valve adjusting tower 1502, and an extension of the power valve tower (not shown), which has mounted thereon or integrally assembled therewith, an output of the power valve 1506. In the embodiment shown in Figure 1, The components of the starting solenoid towers, idling and closing, and the pressure adjustment tower can be assembled from the outer surface of the regulator body and fixed to the body by conventional elements. Around the periphery of the body are mounting ears 1106 having openings therein 1108 adapted to receive screws, bolts or the like (not shown). The body 1102 and the lower cover 1104 of the supplemental pressure regulator of the present invention can be made or formed by any conventional means, such as molding or casting, and the openings and cavities formed by conventional machining methods. The body 1102 and the lower cover 1104 as well as the outer components of the solenoid and closing towers can be conveniently made of materials such as metal or plastic. Shown in Figure 2 is the body of the mounting surface of a preferred embodiment of the supplemental pressure regulator of the present invention, generally designated 1102. In this preferred embodiment of the invention, the regulating body has an upper surface 1116, which it can be adapted to cooperate with, or be coupled with a single-stage or multi-stage pressure regulator, such as the two stage pressure regulator shown in the copending patent application mentioned above. Vertically elevated from the surface 1116 of the regulator body is a mounting surface 1118, in which a plurality of mounting protrusions 1122 are formed, which are adapted to allow securing, for example, of the two-stage pressure regulator. as described above, in the three-stage body, by any conventional suitable element. Formed within the vertical surface 1118 is a fuel inlet gate in the form of a transfer passage 1120 through which the gas to be regulated can pass, from the main pressure regulator into the interior of the pressure regulator supplementary to the present invention. Disposed on the external surface of the regulator body 1102 are a start solenoid tower 1202 and a no-load solenoid tower 1302, a closing solenoid tower 1402 and a three-stage pressure adjustment tower 1406. arranged on the upper surface 1116 of the regulator body 1102 is a power valve adjustment tower 1502 and an extension of the power valve tower 1504, which has mounted thereto or integrally assembled therewith, a output of the power valve 1506. In this embodiment of the invention, the starting solenoid cavity 1204 and the no-load solenoid cavity 1304 are formed as in the embodiment of FIG. 1, as a solenoid cavity of three stage closure 1404. The valve adjusting tower 1502 can be formed integrally with the regulator body 1102 and arranged to allow the insertion and mounting of the power valve of the valve. sde the inner side of the regulator body. Around the periphery of the body are mounting ears 1106 having openings therein 1108 adapted to receive screws, bolts or the like (not shown). Referring now to Figure 3, a top perspective view of the regulator body of the present invention shown in Figure 2 is shown. It can be seen in Figure 3 in addition to the components shown in Figure 2, a detector gate of the fuel temperature 1110 adapted to receive a conventional fuel temperature sensing assembly, optional (not shown). This gate can be plugged if the fuel temperature sensing assembly is not used. Also shown in Figure 3 is a fuel supply passage 1206 extending through the regulator body 1102 from the start solenoid cavity 1204 through the idle solenoid cavity 1304 to the solenoid cavity of the solenoid. three-stage closure 1404, and which is adapted to allow the flow of relatively small amounts of fuel from the start solenoid and idle mount assemblies to the three stage closure assembly under the start and idle conditions respectively . As disclosed in relation to Figure 2, a power valve adjustment tower 1502 with an extension of the tower 1506 can be molded integrally with the regulator body 1102. Figure 4 shows the lower side of the regulator body. 1102 of Figure 2 and in particular, shows a flange or circumferential edge 1150 designed to cooperate with the lower cover (shown in Figure 5) to define an internal cavity (as shown in Figure 6) within the regulator body and which, when assembled with the lower cover (shown in Figure 5) engages and retains the edges of the regulating diaphragm (not shown). The regulator body 1102 may have support ribs or rims 1152, which may be integral to reinforce the upper surface 1116 (shown in Figure 2) and a central support rib and a diaphragm stop ring 1154. the supporting ribs 1152 can be used to reinforce the regulator body 1102, depending on the strength of the material used to form the regulator body. A start solenoid passage 1206 extends through the surface 1116 toward the start solenoid cavity (shown in Figure 2) and a vacuum run solenoid passage 1306 passes through the upper surface 1116 to communicate with the starter solenoid 1206. the vacuum solenoid cavity (shown in Figure 2). Mounted within the body are the mounting blocks of the diaphragm lever 1130 adapted to receive a diaphragm lever (shown in Figures 9A and 9B) and are described in detail below. The support ribs 1152, the central support rib of and the diaphragm stop ring 1154 and the diaphragm lever assembly blocks 1130 can be conveniently made integral with the regulator body 1102, and molded or forged as part of the body of regulator. A pin hole 1408 communicates with the closing solenoid cavity, and provides an input element for the gas to be regulated to flow from the closing solenoid assembly 1400 through the pin hole 1408 to the cavity. 1105 in the body of the regulator. An outlet passage 1508 which in the preferred embodiment is a passage through the assembly of the power valve 1500, provides an outlet element for the regulated pressure gas to flow from the pressure regulator to the motor. Within passage 1508 is an index channel of the power valve 1510 which prevents rotation of the flow control disk described in more detail with reference to Figure 7. Figure 5 shows the lower cover 1104 of the regulator controller housing of the present invention, which together with the regulator body 1102 defines a generally circular internal chamber or cavity 1105 shown in Figure 6. Always within the lower cover is a reference pressure passage 1138 communicating between the interior of the controller housing, through the reference pressure ear 1142 defined within the reference pressure gate 1140. Surrounding the periphery of the lower cover are the ears 1106 which are corresponding to those of the regulator body, and which have openings 1108 adapted to receive screws, bolts or other fasteners. In a preferred embodiment of the invention, the reference pressure gate 1140 (ear 1142) is substantially of the same size as the exit passage 1508. Figure 6 shows a sectional view of the regulator of the present invention, taken along of line 6-6 of Figure 1. Shown in Figure 6 is the regulator housing 1100, which consists of the upper body 1102 and the regulator base 1104, joined through bolts or other conventional fasteners 1114, which pass to through the openings 1108 in the ears 1106. Between the adjoining edges of the body 1102 and the base 1104 a gasket 1112 may be provided to maintain a pressure-tight seal in the housing and to provide elements for holding the diaphragm 1680, which together with the package 1112, it is gripped around its circumference by adjoining edges of the body 1102 and the base 1104. As shown in Figure 5, there is a solenoid tower 1402, which has a extension 1406 in it. Within the tower 1402 is a cavity 1404 communicating with the two to three step passage 1120 (shown in Figure 1) and the hole in the three-stage plug 1408. Defining the transition between the cavity 1404 and the hole 1404. three stages 1408 is a collar 1410 configured to receive the pin assembly 1600 as described in more detail below, and to optimize the gas flow between the cavity 1404 and the opening 1408. Mounted on the solenoid tower is an assembly of closing solenoid 1400 consisting of a solenoid-operated piston 1420 having within its upper end, a cavity 1421 adapted to receive and retain a return spring of the piston 1422. The solenoid-operated piston 1420 is adapted to move within the cavity 1404. On the lower surface of the piston 1420 is a circular gasket 1424 or other sealing elements adapted to be coupled with a pressure-tight seal and provide the same with the collar 1410. Within the lower end of the piston is an opening 1426 adapted to receive the upper end of the pin assembly 1600 described in more detail below. The piston 1420 can be operated by a closing solenoid 1430, contained within a solenoid fork 1432. The screw 1434 holds the fork 1432 and the closing solenoid 1430 together, forming the closure assembly 1400 which provides a magnetic flow path from the top to the bottom of the coil. The regulator screw 1434 clamps the fork 1432 with the solenoid piston 1420 and so clams the solenoid coil 1430 and provides a magnetic flux path from the top to the base of the coil. Communicating with the cavity 1404 is the passage 1206 from the vacuum solenoid cavity 1304 and the start solenoid cavity 1204. Contained within the extension of the tower 1406 is a spring cavity 1440 adapted to receive the regulator spring. three-stage 1442, which is adjustably mounted between the three-stage adjusting screw 1444 and the three-stage regulating piston 1443 which is connected to the pin 1636 of the pin assembly 1600. The operating pressure of the regulator can be adjusted by means of a three-stage adjusting screw 1444, which is provided with a circular packing seal 1448 to ensure pressure-tight operation of the adjusting screw 1444. There is the arrangement in the extension of the tower 1406 for a tamper-proof cap 1446, which can be used to avoid an undesired adjustment of the upper pressure. As shown in Figure 6, the pin assembly 1600 is pivotally mounted to the mounting blocks of the pin lever 1130 (shown in Figure 4). The plug assembly 1600 comprises a pin 1620 mounted by a pivot in a pin lever assembly 1630, which is shown in greater detail in Figures 9A and 9B. The mounting of the pin lever is disclosed in detail in Figure 9A. The pin lever assembly 1630 comprises a pin lever 1632 having a transverse pivot arm 1634 adapted to be pivotally mounted to the mounting blocks of the pin lever 1130 (shown in Figure 4) by any conventional means . At one end of the pin lever 1632 is a pin 1636 adapted to mate with a corresponding opening in the three stage regulator piston 1443 (shown in Figure 6). At the other end of the pin arm 1632 is a diaphragm pin 1638 adapted to mate with the sliding coupling 1652 shown in Figures 10A and 10B. On the side of the transverse pivot arm 1634 opposite the pin 1636 is an opening 1640 in the pin arm adapted to engage with the pin 1610, and the openings receiving the bearing 1642 passing through the pin lever 1632 perpendicularly to the opening 1640. Referring again to Figure 6, the plug 1610 has an opening (not shown) at its lower end through which an axle or bearing coupled with the openings 1642 can pass. In this form, the plug is connected by pivoting the pin lever 1630. The distances between the pin 1632 and the center of the pivot arm 134 and between the center of the pivot arm 1634 and the center of rotation of the pin 1610, as well as the spring constants of the three-stage regulator spring 1442 and leaf spring or leaf spring of pin 1672 are selected to ensure that forces extended by spring or spring 1442 and spring 1672 are balanced mutually offset in the center of rotation of the pivot arm 1634. The pin assembly 1600 comprises a pin rod 1612 which is fitted with a pin flange 1610, which is adapted to engage with the annular collar 1410 and the circular packing 1424 when the pin is in a closed position, to provide a substantially pressure-tight seal. At the upper end of the plug 1610 is a plug head 1616 which is slidably disposed within the opening 1426 in the piston 1420. The lower end of the pin rod contains a circular groove 1697 which is used to retain the pin 1696. The plug stem slides in the bearing 1692 and is retained by the spring 1695 and the clamp 1634. The plug assembly 1600 comprises a plug stem 1612 on which a plug flange 1610 is mounted, which it is adapted to mate with annular collar 1410 and circular packing 1424 when the pin is in a closed position, to provide a substantially pressure-tight seal. At the upper end of the plug 1610 is a plug head 1616 which is slidably disposed within the opening 1426 in the piston 1420. The lower end of the plug rod contains a circular groove 1697 which is used to retain the pin 1696 The plug stem slides in the bearing 1692 and is retained by the spring 1695 and the clip 1696. The configuration of the pin 1610 of the corresponding annular collar 1410 and the pin hole can be selected to provide the most efficient gas flow around. from pin 1610 and through plug hole 1408. This ensures that losses of pressures such as gas flows through the regulator can be controlled to the greatest extent possible, and minimize losses that can not be controlled or regulated. The spring-loaded slide joint allows the pin to slide on the pivot bearing 1642 if the force exerted on the pin (by the pivot bearing 1642) in the closing direction exceeds the force of the spring or spring 1673, which acts as an impact absorber for damping the relative movements of the pin assembly 1600 and the diaphragm assembly 1650. This allows the diaphragm support plates to be in contact with the lower cover without exerting high forces on the support plates, coupler or lever in the event that excessive pressure is applied to the three-stage diaphragm (excessive pressure may be applied during an early ignition, a rapid decrease in flow demand or by an installer blowing in the outlet). The use of the sliding joint also reduces the impact load on the seat of the plug when exposed to the above conditions, thus reducing the wear of the seat and the change of the resulting set point associated therewith. Consequently, the incorporation of the sliding joint reduces the change of the established point and allows the support plates, the coupler and the lever of the plug to be lighter, thus improving the transient response. The lower end of the pin lever 1630 engages with the sliding coupling 1652 formed in the upper diaphragm support plate 1650 as shown in Figure 10. A leaf spring 1672 can be mounted to the housing 1102 by means of a screw 1671, forming a cantilever spring assembly. The deviation of the spring in the assembly applies a force to the plug stem 1612, balancing the force imparted by the spring 1442 at the center of rotation provided by the high pressure fuel against the plug 1610. The use of a leaf spring 1672 allows that a larger portion of the force of the regulating spring is applied directly to the base of the plug. A smaller portion of the force of the resulting spring is provided through the spring 1442 as an element for adjusting the pressure. The leaf spring 1672 and the coil spring 1442 work in parallel, and their forces in the pin assembly are additive. When applying the majority of the force directly to the pin, the force to be applied by the spring 1442 is substantially smaller, causing a significant decrease in the forces on the pivots of the lever. So, the hysteresis effect due to the friction of the pivot is greatly reduced compared to the designs that apply only the force of the regulating spring on the lever. In addition, the leaf spring deflects the gas jet (exiting from the pin hole) away from the diaphragm, thereby reducing or eliminating local pressure variations in the diaphragm and reducing any tendency for the diaphragm to tilt. In addition, any waste that can be trapped in the gas stream is also directed away from the diaphragm, thus protecting the diaphragm from the perforation. A preferred form of a power valve assembly 1500 is shown in detail in Figure 7. This assembly provides an adjustable valve for regulating the amount of fuel entering the engine at a desired temperature and pressure. The assembly comprises a power valve tower 1502 and an extension of the power valve tower 1504, each of which can be integrally formed with the upper body section 1102, for example, by casting or molding. Within the tower 1502 is a cavity 1503. Arranged within the cavity 1503 is a flow control disk 1510 axially mounted on a threaded adjusting screw 1512. The flow control disk is pushed into a wrong position by means of a previously loaded spring 1514. The rotation of adjusting screw 1512 causes the flow control disc to move up or down within tower 1502, thus adjusting the size of the opening through which the pressurized fuel You can pass. An end stop screw 1520 prevents the flow control disc 1510 from releasing from the end of the adjusting screw 1512. The cavity 1503 communicates with the NGV 1506 output which can in turn be connected to the motor by means of conventional elements . The end of the threaded shaft contains a circular packing to seal the increase pressure and sits in a tapered bottom hole to eliminate fluctuations. An internal spring prevents the adjustment disc from vibrating and prevents the adjusting screw from being pushed out during the high increase pressure. The rotation of the adjustment disc is avoided when indexing the slots in the regulator body. This arrangement is easily adaptable in staggered motor operations. With reference now to Figure 8, the start solenoid assembly 1200 and the idle solenoid assembly 1300 are shown. The start solenoid assembly 1200 is mounted above the start solenoid cavity 1204 in the housing 1102. The cavity 1204 is in gaseous communication , by means of the no-load supply passage 1206, with the three-stage closing solenoid cavity 1404, and the no-load solenoid cavity 1304. The start solenoid assembly 1200 can comprise any conventional solenoid 1210 capable of opening the solenoid piston 1212 against the pressures normally found in the regulator. A gas flow passage 1214 is connected to the start solenoid cavity 1204 with the three stage diaphragm cavity 1105. The idle solenoid assembly 1300 is mounted above the no-load solenoid cavity 1304, which is a gaseous communication via a supply passage 1206 with the three-stage closing solenoid cavity 1404 and the starting solenoid cavity 1204. The solenoid assembly of the idle run may comprise any conventional solenoid capable of opening the solenoid piston 1312 against the pressures normally found in the regulator. A gas flow passage 1314 is connected to the no-load solenoid cavity 1304 with the no-load flow adjustment cavity 1316. Arranged within the no-load flow adjustment cavity is an adjusting pin. of the threading idle flow rate 1318. The idle flow rate adjustment cavity 1316 is tapering, becoming progressively narrower in the direction of the internal part of the regulator. The idle flow adjustment pin provides an annular passage of an adjustable size through which the gas can flow. The size of the annular passage can be adjusted by turning the idle flow adjustment pin 1318, which has a threaded arrow to rotate within the threaded portion of the cavity 1316, thereby moving the tapered end portion in or out of the cavity 1316. The idling flow adjustment pin 1318 regulates the idle flow and has an adjustment range of 20.95 SCFH. In another embodiment of the invention, the idle flow adjustment pin 1318 may be replaced by a needle or pin valve to adjust for high or low idle flow rates as required by the engine. The idle flow adjustment pin 1318 consists of a threaded shaft finely connected to a tapered pin that can be tapered at approximately 1.5 degrees per side. A circular packing sleeve is contained in the screw head 1319 to provide a seal. The orifice seat can be machined in the three-stage regulator body to reduce manufacturing costs. In Figure 11, the supplemental pressure regulator of the present invention is shown in a preferred embodiment used as a third stage in conjunction with a pressure regulator balanced by two stages. The spring or spring of the first stage 50o is shown in an exterior view of the plant and comprises a cover of the spring tower 502 having an upper wall 503 and side walls 504. Between the upper wall 503 and the side walls 504 is a projection 506. The construction details of the spring tower are disclosed in the aforementioned pending Canadian patent application. The spring or spring tower of the first stage may contain one or more springs whose spring constants are selected to provide the desired output pressures and prolongs the life of the regulator and its components. The cover of the spring tower 502 is adapted to be mounted on the base 100 by means of the mounting bolts or other fastening mechanisms, not shown. Figure 11 shows a sectional view of the two-stage spring tower 700 and the supplemental pressure regulator of the present invention as shown in Figure 6. The spring tower of the second stage 700 comprises a tower cover of spring 702 having a top surface 703, side walls 704 and a lower flange 705. Between the side walls 704, the upper surface 703 is a projection 706. The pressure within a tow of the second stage referenced in the three-stage outlet pressure, which may be a gate or atmospheric pressure opening in the cover 702, or in some other convenient location. Within the spring of the second stage of the pressure regulator is a plug assembly of the second stage 708. A locking ring 707 is provided to secure the tower assembly of the second spring to the base. Included within the tower assembly of the second spring are the first and second springs 710 and 712 respectively, which, in the preferred embodiment, are in opposite directions. The upper ends of the springs 710 and 712 abut against an adjusting end head 722, thus allowing an adjustment of the force exerted by the springs 710 and 712 against the plug assembly 708. The adjustment screw can be secured against the unauthorized tamper-proof adjustment 724, using any of the known tamper-proof elements. The orifice of this spring tower is larger than the hole corresponding to the outlet chamber to prevent the diaphragm piston from cutting to the diaphragm if the plug fails. The use of two opposite winding springs in the two-stage tower assembly minimizes the height of the tower and the spring constant. By minimizing spring rates by a given tower height, this spring or spring configuration leads to a lower degree of uncertainty in operating pressure ("decrease"). The reverse winding of the springs minimizes the risk that the coils of the adjacent springs will become locked during the movement of the springs. As mentioned above, the presence of a roller convolution provides numerous advantages, including an increase in the longevity of the diaphragm's useful life, allows greater tolerances in the manufacture of the diaphragm. The roller convolution also eliminates the hysteresis effect found otherwise in the planar diaphragm during the operational displacement of the diaphragm. Yet another preferred embodiment can be used in a "cup" style diaphragm (not shown) with a longer convolution instead of a diaphragm with a previously formed convolution. This can be used to minimize variations in the diaphragm area that may otherwise occur with changes in the position of the pin assemblies. As shown in Figure 11, the plug assembly of the second stage consists of a diaphragm 752 generally disposed in a horizontal direction, but having a roller convolution 711 extended upwardly of the diaphragm 752 to provide a modification in the behavior of the diaphragm 752. diaphragm. The diaphragm 752 is mounted on a lower diaphragm stop 758 having a downwardly external edge 713, and a central protrusion 760 extended through the center of the diaphragm 752. The diaphragm is retained in the stop element of the lower diaphragm of a diaphragm 752. diaphragm piston 754, and a locking ring 762. A spring-loaded regulator 764 retained between the locking ring 762 and the external circumference extending upwardly of the upper diaphragm piston 754. The spring-loaded regulator 764 is support against the side wall 704 (of the spring tower (shown in Figure 4) but can travel along the walls during the movement of the second stage plug assembly Mounted within the central protrusion of the diaphragm stop lower is a plug stem 765 which may have a narrow central portion, and a head 766 which is retained in place in the protrusion 760 by a plug retainer 763. In the former The lower section of the plug arrangement of the first stage is a valve plug 770, threadably coupled to the plug stem 765. The valve plug is a molded rubber seal 774. Significantly lower fluid pressures in the pressure chamber of the second stage allow the use of a molded rubber seal with the risk of deformation of the seal that may otherwise occur in the presence of the high fluid pressures most commonly encountered in the first stage pressure chamber desired, a Teflon washer can be added between diaphragm 752 and diaphragm piston 754 to provide improved protection during cold weather. The Teflon washer slowly lowers heat transfer to the diaphragm 752. Alternatively, the diaphragm piston 754 and the lower diaphragm stop 758 can be ceramic coated to provide improved performance in cold weather. In addition, the configuration of the spring tow chamber (at 714) can be altered to provide a "dead gas" trap between the diaphragm 754 and the lower stop 754 to improve cold weather operation. Referring again to Figure 11, fluid under pressure is introduced into the housing through the inlet 103 (shown in Figure 1) and can pass through a filter assembly as described in the above-mentioned copending application. The fluid enters the pressure regulator of the first stage through the inlet gate (not shown) in a plug chamber of the first stage, which is essentially at the same pressure as the gas storage cylinder. The flow passes in a controlled manner through the space between the plug seal of the first stage to the walls of the plug chamber, and then the pressure recovery section of the first stage inside the spring tower of the first stage. The flow of fluid through the first spring tower is regulated by a combined force exerted by the regulator springs and the diaphragm which tends to move the pin assembly in the direction of the open position, considering that the fluid pressure in the pin chamber acts against the diaphragm 552 tending to move the pin to a closed position. The flow of fluid through the chamber of the second stage is regulated by a combined force exerted by the springs 710 and 712 and the diaphragm which tend to move the plug assembly of the second stage in the direction of the open position. The fluid pressure in the pin chamber 180 acting against the diaphragm 752 provides an opposing force that tends to move the plug of the second stage to a closed position. The diaphragm 752 provides a seal against the escape of the fluid through the tow of the second stage and allows a more homogeneous vertical movement of the plug of the second stage between the closed and fully open positions. The lower diaphragm stop 758 defines the upper wall of the upper portion 216 of the exit chamber of the second stage. A flange 717 is provided in the outlet chamber 216 to engage with the outer edge 713, the lower diaphragm stop 758 and thus prevent displacement of the pin assembly of the second stage beyond the set point. The exit chamber of the second stage incorporates a spiral ramp (not shown (to further reduce the fall.The ramp generates high speeds and a more uniform transition in the exit.The ramp can be incorporated into the base when using the techniques of forged that are typically less expensive than machining techniques.The regulated pressure fluid then passes through the outlet passageway 156 communicating with the outlet gate 106 shown in (Figure 1). A removable endcap 780 is provided to enclose the lower portion of the pin chamber of the second stage 180. A circular package or O-ring 782 is provided to form a seal between the base of the regulator 100 and the end cap of the second stage 780. The Figure 12 shows a sectional view of a second embodiment of the regulator of the present invention, taken from the line that is generally corresponding to line 6-6 shown in Figure 12 is the assembled regulator housing 2100, which consists of a body 2102 and a regulator base cover 2104. Each of the regulator body 2102 and the base cover 2104 are generally arc-shaped and can be conveniently fabricated of plastic or other lightweight material, in view of the relatively encountered pressures within the regulator. Each of the regulator body 2102 and base cover 2104 may have centrally disposed spines 2114 and 2115 centrally disposed, respectively, which serve to reinforce the regulator body and which act as a support and stop for the 2700 diaphragm assembly The regulator body 2102 may be provided with upstanding support members 2103, which may be molded or integrally formed with the regulator body 2104 and which are adapted to support a primary or two-stage regulator. The support members 2103 are adapted to hold the primary regulator (not shown) in a position substantially perpendicular to the mounting surface 21128 to ensure that the connection is substantially pressure-tight between the two regulators. Between the adjoining edges of the body 2102 and the base cover 2104, a gasket 2112 is provided to maintain the pressure-tight seal in the housing, and provide the elements for holding the outer edges of the diaphragm 2680, which together with the package 2112, is clamped around its circumference by the adjoining edges of the body 2102 and the base cover 2104. In a preferred embodiment of the invention, the diaphragm 2680 and the package 2112 can be integrally molded in one piece for reduce the number of parts in the assembly and the time required for the assembly of the pressure regulator of the present invention. Each of the upper body 2102 and the base cover 2104 have external edges adapted to fit snugly against the corresponding outer edge of the other shape of a substantially pressure-tight seal Around the circumference of each upper body 2102 and a cover of base 2104 are the circumferential flanges 2106 and 2107, respectively, which are adapted to receive a fastening band or other means for jointly holding the regulator body 2102 and the base cover 2102 in an air-tight manner. The regulator body 2102 includes a solenoid tower 2402 generally circular in cross section with an outwardly extending extension 2406 as can also be seen, for example in Figure 15A. The solenoid tower 2402 is adapted to receive the solenoid assembly 2400 and the regulator spring assembly 2440 as described in more detail below. Within the solenoid tower 2402 is a cavity 2406 which provides an input to the regulator of the present invention that communicates in a mode with the output 1120 of the primary regulator (as shown in Figure 16), and the pin hole. 2408. Defining the transition between the cavity 2404 and the pin hole 2408 is a collar 2410, configured to receive the pin assembly 2600 as described in more detail below, and to optimize the flow of gas between the cavity and the hole of plug 2408. As will be described in more detail in the reference of Figure 14, the regulator of the present invention that is provided is a lock solenoid assembly 24000, which comprises a solenoid operated piston 2420, having inside its upper end, a cavity 2421 adapted to receive and retain a piston return spring 2422. The solenoid-operated piston 2420 adapted to move within the cavity 2404. In FIG. The lower surface of the piston 2420 is a circular gasket 2424 or other sealing element adapted to engage and provide a pressure-tight seal with the collar 2410. Within the lower end of the piston is an axial opening 24 adapted to receive the upper end of the piston. pin 1600 assembly described in more detail below. The piston 2420 can be operated by a closing solenoid 2430 contained with a solenoid fork. The regulating screw 2434 attaches to the fork 2432 in the solenoid piston 2420 and thus attaches to the solenoid coil 2430 and provides a magnetic fluid path from the top to the bottom of the coil. Communicating with the cavity 2406 is a fuel supply passage 2206 from the idle solenoid cavity 2304 and the start solenoid cavity 2204. The lower section of the pin hole 2408 is defined and configured by an insert 2412 which can be made of metal to provide a durable surface on which the gas can flow, and which can be retained in the regulator body 2102 by threads other conventional means .. The arrangement of such insert elements maintains the durable surface for retention required to define the pin hole, while allowing most of the rest of the regulator to be made with lightweight, low cost materials. The insertion element 2412 and the pin assembly 2600 are configured to provide the desired characteristics to the gas flow through the regulator, as described in more detail below. Within the extension of tower 2406, there is a regulator spring assembly 2440 comprising the regulator spring 2442 having spring or spring caps 2443 at each of its ends. The regulator spring 2442 is disposed between the regulator piston 2446 and a pin 2636 mounted on the pin assembly 2600. The spring caps 2443 are respectively engaged with the regulator piston 2446 and the pin 1636. The regulator piston 2446 is arranged within the spring cavity 2438 and held by a regulator spring 242 against the adjusting screw 2450. The adjusting screw 2450 is received threadably at the upper end of the cavity 2438; its position within this cavity can be adjusted by turning the screw to move it up or down inside the cavity 2438. The operating pressure of the regulator can be adjusted by adjusting screw 2450, which is provided with a circular packing seal 2448 to ensure the pressure-tight operation of the adjuster screw 2450. A tamper-resistant plug 2452 can be used in the extension of tower 2406 to avoid undesired adjustment of the upper pressure. As shown in Figure 12, the pin assembly 2600 is a pin 2610 pivotally mounted on a pin lever assembly 2630, which is shown in detail in Figures 16A and 16B. The plug 2610 is shown more clearly in Figure 14, and comprises a plug rod 2612 that fuses smoothly into the plug base 2614, which is adapted to interact with the insertion element 2412. A solenoid piston 2420 has a seal 2424 circular packing which provides a substantially pressure-tight seal between the solenoid piston 2420 and the collar 2410 when the pin is in a closed position. At the upper end of the plug 2610 is a pin head 2616 which is slidably disposed within the opening 2426 in the solenoid piston 2420. Below the pin base 2614 is a lower pin 2616 to which it is clamped the pin support pin 2618, which rests on the pin lever assembly 2630, and is supported thereby as described in more detail below. The configurations of the pin 2610 of the corresponding annular collar 2410 and the pin hole insertion element 2412 can be selected to provide a more efficient gas flow around the pin 2610 and through the pin hole 2408. This ensures that the losses of Pressure when the gas flows through the regulator can be controlled to the maximum extent possible, and minimizes any of the pressure losses that can not be controlled and regulated. The pin lever assembly 2630 is disclosed in detail in Figures 16A and 16B. The pin lever assembly 2630 comprises a pin lever 2632 which has to be pivoted d adjacent to one end on a mounting pin 2634. At this end of the lever 2632 is a support pin 2636 adapted to be engaged with a corresponding opening in the spring cap 2443. Mounted on the other end of the pin arm 2632 is a coupling pin 2637 adapted to engage with the slide coupling 2652 shown in Figures 16B and 16C. As shown in Figures 16A and 16B, the pin support lever has a mounting thereon on the side of the pin guide assembly 2638 that is adapted to support the pin support pin 2618, which is supported by the mounting pin guide 2638. As shown in greater detail in Figure 14, a pin guide assembly 2638 includes side supports 2640, a central arrow 2642, a spring support 2644, and a spring 26. Mounted at the base of the arrow 2642 are the spring hooks 2648. The corresponding spring hooks 2650 are retained at the base of the solenoid tower 2402 at any of the large pin holes 2408 by the insert member. Mounted between the corresponding pairs of spring clips 2648 are the pin support springs 2652. The distances between the pin 2636 and the center of the pivot lever pin 26 and between the center of the pivot arm 2634 and the center 2618 of the assembly of the pin, as well as the spring constants of the regulating spring 2442, the pin support springs 2652 and the spring or spring 2646 are selected to ensure that the force exerted by the springs 2442, 2646 and 2652 balances the force exerted by the springs. the high pressure fuel against the plug 2610. The spring 2646 pushes up against the pin assembly 2610 and normally holds the pin assembly 2610 away from the pin lever assembly 2630 and allows the lever assembly to continue to move downward yet after the base of pin 2614 is completely supported on the insert 2412, and pin hole 2408 is completely closed. This allows the diaphragm support plates to be in contact with the lower cover without exerting superior forces on the support, coupler or lever plates in the event that excessive pressure is applied to the three stage diaphragm. Such excessive pressure can be applied during an anticipated ignition, a rapid decrease in the flow demand, or by an installer that blows in the outlet. This allows the use of lighter materials in the construction of lever assembly 2630. The use of spring 2646 also reduces the impact of being loaded on the plug seal when exposed to the above conditions, thereby reducing seat wear and change of the resulting established point associated with them. The incorporation of the spring 2646 reduces the change of the set point and allows the support plates and pin lever assembly to be lighter, thus improving the instantaneous response of the regulator. The lower end of the pin lever 2632 engages with a sliding coupling 2652 formed in the upper diaphragm support lever 2704 and operates in the same manner as the sliding coupling shown in Figure 10. The use of pin springs 2652 allows that the largest portion of the force of the regulating spring is applied directly to the base of the plug 2610. A smaller portion of the force of the resulting spring is provided through the regulator spring 2442 as an element for adjusting the acting pressure up on the plug. The springs 2652 and 2446 work in parallel, and their forces in the pin assembly are additive. When it is the case of the embodiment of Figure 6, when applying the majority of the force directly to the pin so that the force to be applied by the spring 2442 is substantially lower than that applied by conventional pressure regulators, originating significantly lower forces on the lever pivots. So the effect of hysteresis due to pivot friction is greatly reduced compared to designs that apply only the spring force resulting in the lever. Figure 14 shows a sectional view of the solenoid tower of Figure 12 taken at the angles in the section view of Figure 12. As shown in Figure 14, the pin assembly 2600 is supported not only by the pin lever assembly 2630, but also by springs 2652 that engage over the spring mounting hooks 2648 and 2650. So the downward force of the gas flowing through pin hole 2408 can be balanced against the rising forces provided by the springs 2652 and the regulator spring 2442. A preferred and alternating power valve assembly 2500 is shown in detail in Figures 15A and 15B. This assembly provides an adjustment valve to regulate the amount of fuel entering the engine at full power, and to ensure that the turbulence of the outflow has all flow rates. The power valve assembly 2500 is mounted on a power valve tower 2503 and the extension of the power valve tower 2504, which can be formed integrally with the upper body section 2102, for example, by molding or casting. Within the tower 2503 is generally a cylindrical cavity 2503. The cavity 2503 communicates with the outlet NGV 2506 which can in turn be connected to the motor by conventional means. Arranged within the cavity 2503, perpendicular to the longitudinal axis of the cap is a flow control disk 2510 axially mounted on a threaded adjusting screw 2512 shown in the drawings. The flow control disc is pushed to the more closed position by means of a preloaded spring 2514. The upper end of the adjusting screw 2512 is exposed through the upper end of the power valve assembly and can be rotated to cause the Flow control disk moves up and down into tower 2502, thus adjusting the size of the opening through which the pressurized fuel can pass. An end stop screw 25 prevents the flow control disc 2510 from loosening from the end of the adjusting screw 2512. The end of the threaded shaft contains a circular packing to seal the increasing or pushing pressures and settle in the tapered base hole, to eliminate fluctuations. An internal spring prevents the adjustment disc from oscillating and prevents the adjusting screw from being pushed during the high thrust pressure. The rotation of the adjustment disc is avoided when indexing the slots in the regulator body. This arrangement is easily adaptable in staggered motor operation (more details and number needed in the drawings). A sectional view of the solenoid tower 2402 and a pin hole 2408 with the collar insert 2410 are shown in Figure 15B. Figure 15B shows the spring mounting hooks 2650 in which the springs Pin holder 2652 are mounted. Also in Figure 15B there is shown a temperature sensing gate 2800, which has a thermal resistance 2801 mounted thereon, with the end detecting the temperature of the thermal resistance extended in the cavity 2408 of the pressure regulator. Also in Figures 15A and 15B there is shown the supply passage 2306 which is connected to the vacuum solenoid cavity 2304 and the three stage closing solenoid cavity 24 and the start solenoid cavity 2404. In one way similar to that of the embodiment of Figure 8, a gas flow passage is connected to the no-load solenoid cavity in the idle solenoid tower 2302 with the no-load flow adjustment cavity 2316 At the end of the idle feed supply passage 2306 is a no-load flow adjusting cavity 2316. Arranged within the no-load flow adjusting cavity 2316 is a flow adjustment regulator of idling (not shown in Figure 15B but is similar to that shown in Figure 8). The vacuum flow flow adjustment cavity 2316 is tapered becoming progressively narrower in the direction of the internal part of the regulator. As shown in Figure 8, the idle flow adjustment pin 1318 (Figure 8) has a similarly tapered end 1320 (in Figure 8) that is disposed within the vacuum flow adjustment cavity. to provide an annular passage of adjustable size through which the gas can flow. The size of the annular passage of the embodiment of Figure 1 can be adjusted by rotating the idle flow rate adjusting pin 2318, which has a threaded arrow to rotate within the threaded portion of the cavity 2316, thereby moving the portion of tapered end in or out of cavity 1316. Figures 13A, 13B and 13C show a particularly preferred diaphragm assembly that can be used in the modes of the regulator shown in Figure 12. The diaphragm assembly 2700 comprises a diaphragm 2701 which can be made from any of the conventional materials whose outer edges are securely held between the regulator body 2102 and the base or bottom cover 2104 (as shown in Figure 12) and includes a molded integral package. Above the diaphragm is a diaphragm support plate to which the slide coupling 2652 is mounted as shown in Figure 12. Below the diaphragm is a diaphragm spring 2706 and an anti-wrinkle ring 2704, the diaphragm spring and the anti-wrinkle ring 2712 are joined together by rivets 2714 or other lightweight fasteners that pass through the diaphragm 2702 but still allow a substantial separation between the upper and lower portions. bottom of the regulator cavity. The diaphragm spring 2706 may comprise three or more projections extending outward from the central hub and adapted to support the anti-wrinkle ring in the manner described below. The support plate 2704 can be a relatively light weight piece of metal or plastic, shaped with spokes and with an external continuous circumference to keep the weight of the support plate as low as possible while keeping the central portion of the diaphragm 2702 relatively flat and parallel with the central axis of the regulator body. Similarly the anti-wrinkle ring 2712 has a circular outer ring 2710 of a larger diameter than that of the support lacquer 2704 which is mounted on raised pins 2716 at the end of the spring lugs 2706. The outer ring raises the edges of the diaphragm above the height of the central portion of the diaphragm in the normal or balanced position of the regulator. If the pressure of the upper portion of the cavity 2105 falls below the reference pressure in the lower portion of the cavity, the central portion of the diaphragm will move upwards to compensate for these pressure differences. The novel construction of the diaphragm of the present invention maintains the diaphragm flat and improves the operation of the regulator. While in many cases it will be preferred to operate the regulator in a balanced position, to minimize the gas outlet pressure, there are circumstances in which the regulator can be operated in an unbalanced position to ensure that there is a positive outlet pressure. small from the regulator to the engine. In Figure 17 the pressure regulator of Figure 12 adapted to ensure a positive outlet pressure from the regulator is shown. Mounted on the lower cover of the pressure regulator is a spring tower assembly 2800 comprising a sleeve 2802 mounted on the lower cover and held in place by a nut 2804. Within the sleeve 2802 are the springs wound in opposite fashion 2806 and 2808 retained between the spring plates 2810 and 2812. The spring plate is fastened to the diaphragm assembly 2700 by the rivets 2714, while the spring plate 2810 is retained within the sleeve 2802 and abuts against a spring adjusting disc 2814, which is threadedly received in the sleeve 2802. Turning the spring adjusting disc 2814 increases or decreases the force of the spring applied against the diaphragm assembly 2700. A tamper-proof cap 2816 may be provided at the end of sleeve 2802, circular gaskets 2828 and 2820 seal the regulator against the effects of ambient pressure.

Claims (5)

1. NOVELTY OF THE INVENTION Having described the invention as above, we consider what is contained in the following: CLAIMS 1. A pressure regulator comprising: a housing consisting of a first housing member and a second housing member; a diaphragm disposed within said housing between said first and second housing members, said diaphragm and said first housing member defining a first chamber within said housing, and said diaphragm and said second housing member defining a second chamber within said housing. said housing: wherein said pressure regulator further comprises: a lever assembly pivotally mounted on said first housing member, said lever assembly comprising a lever arm having first and second ends, the first end of said arm lever is connected in an articulated manner with said diaphragm; Valve elements located in said first housing member for regulating the flow or fluid in said housing, said valve elements comprising a pin assembly pivotally mounted on said lever and disposed within the opening in said first housing member; and spring elements mounted on said first housing member coupled to the second end of said lever arm and acting to urge said valve elements to the open position. A pressure regulator according to claim 1, adapted to regulate and control the fluid flow under pressure in a motor, wherein: said first housing member has an input gate adapted to communicate with a fluid source of high pressure and said second housing member has a reference gate adapted to communicate with a source of the reference pressure; and wherein said valve elements further comprise a valve seat adapted to cooperate with said plug assembly for interrupting the flow of fluid from said inlet gate in said first chamber when the flow of fluid in said motor is not required. 3. The pressure regulator of claim 1, wherein said first chamber and said second chamber are of a substantially equal volume. 4. The pressure regulator of claim 5, wherein said inlet gate and said outlet gate are of a substantially equal size. The pressure regulator of claim 1, wherein said valve elements further include elements adapted to retain said plug assembly in said closed position.