EP2761214A1 - Variable gas pressure regulator - Google Patents
Variable gas pressure regulatorInfo
- Publication number
- EP2761214A1 EP2761214A1 EP12827189.7A EP12827189A EP2761214A1 EP 2761214 A1 EP2761214 A1 EP 2761214A1 EP 12827189 A EP12827189 A EP 12827189A EP 2761214 A1 EP2761214 A1 EP 2761214A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- space
- pressure
- control
- regulated
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
Classifications
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D16/00—Control of fluid pressure
- G05D16/20—Control of fluid pressure characterised by the use of electric means
- G05D16/2006—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means
- G05D16/2013—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means
- G05D16/2026—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means with a plurality of throttling means
- G05D16/2033—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means with a plurality of throttling means the plurality of throttling means being arranged in series
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D16/00—Control of fluid pressure
- G05D16/20—Control of fluid pressure characterised by the use of electric means
- G05D16/2093—Control of fluid pressure characterised by the use of electric means with combination of electric and non-electric auxiliary power
- G05D16/2095—Control of fluid pressure characterised by the use of electric means with combination of electric and non-electric auxiliary power using membranes within the main valve
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/30—Hydrogen technology
- Y02E60/32—Hydrogen storage
Definitions
- the present invention relates to an improved variable pressure regulator for controlling, for example, the gas pressure supplied to an engine using gaseous fuels.
- the gas is compressed natural gas (CNG) .
- An on-demand regulator has a control member 5 controlling throttling valve head 6 acted upon by diaphragm 7 responsive to the differential pressure across diaphragm 7 acting in a first direction and a spring 8 providing a force loading acting in the opposite direction, the spring force acting so as to normally open throttling valve 1 when the pressure in regulated space 3 is low.
- a control member 5 controlling throttling valve head 6 acted upon by diaphragm 7 responsive to the differential pressure across diaphragm 7 acting in a first direction and a spring 8 providing a force loading acting in the opposite direction, the spring force acting so as to normally open throttling valve 1 when the pressure in regulated space 3 is low.
- a control member 5 controlling throttling valve head 6 acted upon by diaphragm 7 responsive to the differential pressure across diaphragm 7 acting in a first direction and a spring 8 providing a force loading acting in the opposite direction, the spring force acting so as to normally open throttling valve 1 when the pressure in regulated
- Throttling valve 1 when there is no source of high-pressure gas present at inlet port 2, throttling valve 1 is normally open in this condition. Throttling valve 1 closes when the forces generated by the pressure in regulated space 3 exceed a certain pre-determined level of pressure defined by the pre-load of spring 8.
- the spring force also changes as spring 8 is compressed or relaxed as throttling valve head 6 moves to a different position of equilibrium as the gas flow changes in response to differing demands of regulated gas flow.
- This change in force is due to the inherent and characteristic stiffness of spring 8 where the spring force varies with the position of valve head 6. Therefore, the regulated pressure tends to vary with the flow rate rather than stay constant for a given nominal spring setting.
- a reducing pressure characteristic with increasing flow as measured at the destination of the gas flow is exacerbated by the pressure drop across the exit port and its extensions on the way to the destination where the regulated pressure may be typically measured.
- a serious flaw of such a regulator is that there is typically a large pressure force acting across diaphragm 7.
- gas may escape across diaphragm 7, creating a potential fire hazard as it escapes through reference port 9 of Figure 1.
- reference port 9 might be connected to the inlet manifold of an engine in an application using CNG as a fuel. Otherwise, it may be connected to the atmosphere. Any gas leaking from reference port 9 and passing to the intake manifold of an engine represents additional fuel that may force higher combustion temperatures that can be destructive to an engine, particularly if detonation is induced before the control system can either correct this condition or elicit a response from the human operator of such an engine using an electronic warning system.
- throttling valve 1 tends to open in response to the rupture of diaphragm 7 due to the changed equilibrium of forces acting on control member 5, allowing the regulated pressure to rise about the nominal regulated value, sometimes to a dangerous level where the operation of a safety relief valve is necessary to dump high pressure gas to the atmosphere.
- CNG gases are vented to the atmosphere they represent an undesirable emission of a gas contributing to the well-known greenhouse effect in the atmosphere.
- the operation of the gas metering system and the engine management system may be compromised under such conditions, resulting in the shutdown of an engine and its subject vehicle, often in an inconvenient location and strategic situation in a busy traffic system. In an extreme case, a severe fire hazard may exist if regulations have not been complied with.
- a further limitation of the conventional on-demand regulator is that the pressure setting is relatively fixed by virtue of the relatively fixed spring force acting on the diaphragm. It is convenient for an engine running on CNG for the pressure of the gas supplied to gas metering injectors to be variable so that, for example, a low pressure may be set by the engine control system at engine idle and a high pressure be set at full engine load. The metering accuracy of a gas injector may be better optimised by such an arrangement whilst potentially allowing for a better matching of the gas flow relative to the airflow of the engine.
- a further disadvantage of the conventional regulator defined in Figure 1 is the fact that throttling valve 1 is normally open when the gas pressure in inlet 2 is low.
- throttling valve 1 is normally open when the gas pressure in inlet 2 is low.
- a gas supply at high pressure is suddenly applied to inlet 2 by an external valve upstream of inlet 2 and this tends to result in the regulated pressure in regulated space 3 temporarily exceeding the normal regulated pressure.
- This is due to the relatively slow response of the assembly as it acts to close throttling valve 1 in response to the rapidly rising gas pressure at inlet 2. This tends to result in high stresses on throttling valve 1 , on control member 5 and on diaphragm 7.
- variable gas pressure regulator for regulating the pressure of a gas supplied from a high pressure gas supply to a user.
- the variable gas pressure regulator comprises: a. a body provided with an inlet and an outlet; b. a control space and a regulated space, the regulated space being fluidly connected to the outlet and being separated from the control space by a diaphragm; c. a throttling valve operable to regulate fluid flow between the inlet and the outlet; d. a control member associated with the diaphragm to move in response to movements of the diaphragm, the control member being movable to operate the throttling valve; and e. a lock-off valve associated with the control member and located in a fluid flow path between the throttling valve and the regulated space, wherein the lock-off valve stops flow of fluid from the inlet to the regulated space when the throttling valve is closed.
- variable gas pressure regulator also comprises a first electronically activated valve for controlling flow of fluid from the inlet to the control space and a second electronically activated valve for controlling flow of fluid from the control space to the regulated space.
- variable gas pressure regulator further comprises a spring mechanism which acts on the diaphragm to move the control member against the pressure force of the fluid in the control space when the pressure in the control space equals the pressure in the regulated space, whereby the throttling valve and the lock-off valve are urged to their respective closed positions.
- variable gas pressure regulator further comprises a high-pressure solenoid which is actuated to open or close the first electronically actuated valve and a low- pressure solenoid which is actuated to open or close the second electronically actuated valve.
- the first electronically actuated valve or its associated fluid passage has a cross-sectional fluid flow area that is at least 10 times bigger than the cross-sectional fluid flow area of the second
- the present variable gas pressure regulator can comprise a heating gallery through which a heating fluid can circulate close to the throttling valve to prevent the freezing of the gas pressure regulator.
- variable gas pressure regulator can comprise an electrical heating element located close to the throttling valve to prevent freezing of the gas pressure regulator fluid.
- the throttling valve comprises at least one component made of a metallic material.
- the lock-off valve comprises a resilient seal for sealing a fluid passage between inlet and the regulated space.
- a method for operating a variable gas pressure regulator comprising an inlet, an outlet, a control space and a regulated space which is fluidly connected to the outlet and separated by a diaphragm from the control space.
- the method comprises: a. increasing the pressure in the control space by periodically actuating a first electronically activated valve to open fluid flow between the inlet and the control space thereby moving the diaphragm and a control member associated with the diaphragm to open a throttling valve and a lock-off valve which are associated with the control member to open fluid flow between said inlet and said outlet; and b.
- the lock-off valve In its closed position, the lock-off valve further stops the flow of fluid from the inlet to the regulated space when the throttling valve is closed.
- the fluid flow rate through the throttling valve and through the lock-off valve is determined by the position of the control member.
- the second electronically activated valve opens when the pressure in the control space exceeds a predetermined limit to allow fluid flow from the control space to the regulated space.
- Figure 1 illustrates a conventional on demand pressure regulator.
- Figure 2 shows a schematic illustration of the preferred embodiment of a variable gas pressure regulator comprising a throttling valve and a lock-off valve for regulating the pressure at the outlet wherein the throttling valve and the lock-off valve are illustrated in their closed position.
- Figure 3 shows a schematic illustration of the same preferred embodiment of a variable gas pressure regulator shown in Figure 2 but also showing the outlet connected to a delivery duct and with the throttling valve and the lock-off valve illustrated in their open position.
- Like components are referred to in the disclosure by the same reference numbers, though not shown in Figure 3.
- the disclosed variable pressure regulator is capable of achieving a variable pressure at the outlet by actuating a high-pressure solenoid and a low-pressure solenoid which are operable to control the pressure in a control space relative to a regulated space.
- the variable pressure regulator is used for controlling the gas pressure supplied to an engine using gaseous fuels.
- the gas is preferably compressed natural gas (CNG), but it can be any other gaseous fuel such as hydrogen, propane, ethane, butane, methane, and mixtures thereof.
- CNG compressed natural gas
- the operation of the present variable pressure regulator will now be described for regulating the pressure of a gas that is delivered from a gas supply to a user that can be, for example, a gaseous fuelled engine.
- a person skilled in this technology will easily recognize that such a variable pressure regulator can be used for other gaseous fluids and at a wide range of pressures.
- a method of regulation is provided whereby the spring force of a conventional regulator is replaced on one side of diaphragm 12 by a force generated by the pressure in control space 10 acting to oppose the regulating pressure force acting on the other side of diaphragm 12, said other side of the diaphragm being responsive to the pressure in regulated space 11.
- the pressure in control space 10 replaces the force provided by the spring of a conventional regulator, substantially reducing the pressure difference between one side of the diaphragm and the other.
- the pressure in control space 10 substantially defines the regulated pressure setting whilst substantially reducing the forces acting to rupture diaphragm 12.
- spring 13 acting to produce a force tending to normally close throttling valve 14 acting in parallel with and in the same direction as the gas forces on throttling valve 14, tending to act together to close throttling valve 14 and opposing the pressure forces in control space 10 relative to the pressure forces in regulated space 11.
- spring 13 provides a relatively low force and has low stiffness.
- the disclosed variable pressure regulator creates the reference pressure in control space 10 using both a high-pressure "HP" solenoid 16 connected to control flow between high-pressure inlet 15 and control space 10 in a first aspect, and a low- pressure "LP" solenoid 17 connected to control flow between control space 10 and regulated space 1 1 in a second aspect, both solenoids being actuated in order to control the pressure in control space 10 relative to regulated space 11 , using the following means: a) directing gas from high pressure supply 15 to first high pressure HP solenoid 16 that is normally closed to gas flow, preventing the flow of HP gas to the communicating control space 10 downstream of HP solenoid 16; b) periodically opening HP solenoid 16 to admit a discrete mass of gas from HP supply 15 to control space 10; c) monitoring the resulting regulated pressure in regulated space 1 1 or its extensions so as to ensure that a certain specified reference pressure is achieved in regulated space 11 or its extensions by comparing the resulting regulated pressure with a pre-determined reference pressure set by controller 30
- Valve port 41 is normally open when no current is flowing continuously in solenoid coil 42, said gas flow allowing substantial equilibrium in pressure to occur between control space 10 and regulated space 11 while the HP solenoid 16 is closed to flow for an extended period, thereby allowing spring 13 to lift control member 18 and close lock- off valve 37 when there is a low level of current in coil 42 and correspondingly lower magnetic flux linking armature 43 and magnetic pole 45, or when there is no source of electrical power providing current to the said coil 42. Meanwhile, spring 35 and the throttling pressure forces acting on throttling valve 14 press the throttling valve against valve seat 32.
- regulator 19 is defined that has low net forces acting across diaphragm 12 that controls throttling valve 14 interposed between inlet 15 and regulated space 1 1, the opening of throttling valve 14 being responsive to the relative pressures in control space 10 and regulated space 1 1, together with the action of spring 35 acting in such a direction as to urge closure of throttling valve 14.
- control member 18 is high and the mechanical stiffness is low, allowing for high responsiveness to any change in the equilibrium of control member 18, particularly due to pressure changes in regulated space 11 or control space 10.
- regulated pressure may be
- regulator 19 is intrinsically safe because the rupture of diaphragm 12 does not result in the leakage of gas to the exterior of regulator 19.
- throttling valve 14 will always close in response to this condition by virtue of the substantial equilibrium of the pressure forces thereby established across diaphragm 12 upon the opening of valve port 41 of LP solenoid 17 to allow gas flow between control space 10 and regulated space 1 1.
- HP solenoid 16 allows a significant overpressure to be supplied on the supply side of the regulator without the uncontrolled release of gas under such conditions.
- Inlet port 15 is connected to a source of high pressure gas and a high pressure bleed port 20 allows gas to communicate with valve head 21 normally sealing high pressure port 22 of high pressure solenoid 16.
- coil 23 of HP solenoid 16 is energised by current flow, armature 24 is attracted towards pole 25 due to the linkage of magnetic flux created by the electrical current in coil 23, the attractive magnetic force overcoming both the force of spring 26 and the gas pressure across valve head 21 that normally holds valve head 21 in sealing relationship with the seat of port 22, thereby opening port 22 and allowing gas to flow from inlet 15 through bleed port 20 and past open port 22, and ultimately into control space 10 through duct 27.
- pressure transducer 28 may be connected to delivery duct 38 communicating with regulated space 11.
- a controller 30 monitoring the pressure in regulated space 1 1 or its extensions can curtail the current in coil 23, resulting in port 22 closing by virtue of the forces in spring 26, aided by pressure forces on valve head 21 tending to increase the sealing of port 22.
- throttling valve 14 The regulation provided by throttling valve 14 occurs as follows.
- control member 18 and pushrod 31 move further towards closure of throttling valve 14, thereby defining a defined regulated pressure in regulated space 1 1 and in exit port 29 and its extensions in delivery duct 38 illustrated in Figure 3.
- FIG. 2 it is an aspect of this regulator to provide a secondary lock-off valve 37 in the path between throttling valve 14 and regulated space 11 comprising of a bore 39 through which grooved valve head 40 is in cooperation with control member 18 and is in sealable relationship with bore 39 due to seal 26 in the groove of valve head 40.
- Lock-off valve 37 is primarily controlled by the action of LP solenoid 17 and HP solenoid 16 which control the relative pressure difference between control space 10 and regulated space 11 , together with the forces from the spring 13 to determine the axial position of the control member 18.
- control unit 30 acts to shut down the flow of gas from regulator 19 to switch to the position shown in Figure 2, the current in coil 42 of LP solenoid 17 is reduced or turned off completely, allowing the combined force of spring 44 and the pressure forces across port 41 acting on valve member 46 to open port 41, allowing gas to flow from control space 10 to regulated space 11 , thereby allowing substantial equilibrium in pressure across diaphragm 12.
- This substantial equilibrium in pressure and the combined action of spring 13 and the throttling pressure forces across throttling valve 14 and valve head 40 act to close lock-off valve 37 and force valve head 40 into sealed relationship with bore 39 by virtue of seal 26.
- Lock-off valve 37 has a flexible seal 26 that will reduce leakage into regulated space 11 when regulator 19 is shut down by control unit 30. Also, lock-off valve 37 may allow the regulation of the gas flow when the flow rate is extremely small and where main throttling valve 14 may have high enough leakage when closed to preclude effective regulation at such a low rate of gas flow.
- throttling valve 14 may be a fully metallic valve to promote precise flow characteristics and good heat transfer from a heating fluid in heating gallery 47, said flow being conveniently circulated from a fluid flow associated with an operating engine providing waste heat to a circulated fluid in heating gallery 47.
- an electrical heating element as an adjunct to or in addition to the heated fluid circulated in the heating gallery 47.
- the arrangement of a valve carrier 48 surrounding the throttling valve 14 promotes good heat transfer to valve seat 32 and intermediate duct 36 so as to prevent the formation of ice as the gas flow is throttled across throttling valve 14 and drops in temperature due to its expansion into intermediate space 36. This arrangement also avoids extreme cooling of flexible seal 26, which might be otherwise susceptible to hardening at extremely low temperatures.
- LP solenoid 17 of this regulator is also intrinsically a safety relief valve controlling the relief of excessive gas pressure between control space 10 and regulated space 11.
- the relief pressure is determined in this case by the pressure acting across port 41 acting on valve member 46 in parallel to the force of spring 44 and opposing the electromagnetic force of attraction between armature 43 and magnetic pole piece 45.
- this electromagnetic force may be programmed by a predetermined level of current in coil 42, said current defining a predetermined electromagnetic force on armature 43 and a characteristic relief pressure.
- This electromagnetic force may be conveniently selected by automatic controls and calibration methods for different engine applications with differing relief pressure settings, for example.
- valve port 41 of LP solenoid 17 relative to valve port 22 of HP solenoid 16 is important.
- the ratio of said sizes measured by the nominal cross sectional area limiting the gas flow in each port is to be constrained to a ratio of 10: 1 or more. That is, the cross-sectional area limiting the flow of gas through valve port 41 is to be at least 10 times that of valve port 22 when both ports are fully open.
- certain novel gas metering systems may be derived by the advanced functions provided by this regulator. Because the pressure provided by the regulator is variable and controllable electronically, it is possible to replace the complex electromagnetically controlled injectors downstream of the regulator with fixed orifice injectors controlling the flow to the intake of the engine. In this example, the control of the gas pressure as a function of engine variables allows for control of the flow of gas to an engine.
- the fuel flow to the intake manifold of certain large engines may be controlled in response to sensed operating parameters on an engine and by varying the gas pressure using the said regulator the fuel delivery to the engine may be controlled in response to required operating variables.
Landscapes
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Physics & Mathematics (AREA)
- Engineering & Computer Science (AREA)
- Automation & Control Theory (AREA)
- Control Of Fluid Pressure (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU2011903466A AU2011903466A0 (en) | 2011-08-29 | Improvements in Gas Pressure Regulation | |
PCT/CA2012/050595 WO2013029175A1 (en) | 2011-08-29 | 2012-08-28 | Variable gas pressure regulator |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2761214A1 true EP2761214A1 (en) | 2014-08-06 |
EP2761214A4 EP2761214A4 (en) | 2015-08-12 |
Family
ID=47755151
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP12827189.7A Withdrawn EP2761214A4 (en) | 2011-08-29 | 2012-08-28 | Variable gas pressure regulator |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP2761214A4 (en) |
CN (1) | CN103765067B (en) |
IN (1) | IN2014CN02341A (en) |
RU (1) | RU2014110695A (en) |
WO (1) | WO2013029175A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2016120673A1 (en) * | 2015-01-29 | 2016-08-04 | Anand Kumar Jain | A gas regulator having variable pressure means together with excess-flow shut-off means |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EA031600B1 (en) * | 2016-12-08 | 2019-01-31 | Юрий Иванович ДРОБОТЯ | Method for control of a leak-tight vessel filling with a fluid medium |
JP7243960B2 (en) * | 2019-01-11 | 2023-03-22 | Smc株式会社 | solenoid valve system |
CN113513705B (en) * | 2021-05-13 | 2023-02-17 | 重庆凯瑞动力科技有限公司 | High-pressure hydrogen combined bottle mouth valve for vehicle |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4520838A (en) * | 1983-07-01 | 1985-06-04 | The B.F. Goodrich Company | Valve for high pressure fluid container |
US4655246A (en) * | 1983-09-30 | 1987-04-07 | Essex Industries, Inc. | Regulated gas flow control valve |
JP3352147B2 (en) * | 1993-06-08 | 2002-12-03 | 株式会社テージーケー | Pilot type solenoid valve |
CA2131108C (en) * | 1994-08-30 | 2005-06-07 | Stephen A. Carter | Two-stage pressure regulator |
US6467505B1 (en) * | 2000-10-11 | 2002-10-22 | Flowmatrix Inc. | Variable pressure regulated flow controllers |
US7309113B2 (en) * | 2003-11-18 | 2007-12-18 | Dynetek Industries Ltd. | Flow control system for a valve |
US7905252B2 (en) * | 2006-03-20 | 2011-03-15 | Tescom Corporation | Apparatus and methods to dispense fluid from a bank of containers and to refill same |
US20090071548A1 (en) * | 2007-09-14 | 2009-03-19 | Daryll Duane Patterson | Modular in-line fluid regulators |
-
2012
- 2012-08-28 RU RU2014110695/06A patent/RU2014110695A/en not_active Application Discontinuation
- 2012-08-28 EP EP12827189.7A patent/EP2761214A4/en not_active Withdrawn
- 2012-08-28 WO PCT/CA2012/050595 patent/WO2013029175A1/en active Application Filing
- 2012-08-28 CN CN201280041641.0A patent/CN103765067B/en active Active
-
2014
- 2014-03-27 IN IN2341CHN2014 patent/IN2014CN02341A/en unknown
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2016120673A1 (en) * | 2015-01-29 | 2016-08-04 | Anand Kumar Jain | A gas regulator having variable pressure means together with excess-flow shut-off means |
Also Published As
Publication number | Publication date |
---|---|
IN2014CN02341A (en) | 2015-06-19 |
RU2014110695A (en) | 2015-10-10 |
EP2761214A4 (en) | 2015-08-12 |
CN103765067B (en) | 2015-07-15 |
CN103765067A (en) | 2014-04-30 |
WO2013029175A1 (en) | 2013-03-07 |
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