US20110175009A1 - Fluid regulator - Google Patents

Fluid regulator Download PDF

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Publication number
US20110175009A1
US20110175009A1 US13/119,593 US200913119593A US2011175009A1 US 20110175009 A1 US20110175009 A1 US 20110175009A1 US 200913119593 A US200913119593 A US 200913119593A US 2011175009 A1 US2011175009 A1 US 2011175009A1
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United States
Prior art keywords
fluid
valve
fluid pressure
regulating unit
pressure regulating
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Abandoned
Application number
US13/119,593
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English (en)
Inventor
Soeren Kristoffersen
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Isomatic AS
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Isomatic AS
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Assigned to ISOMATIC A/S reassignment ISOMATIC A/S ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: Kristoffersen, Soeren
Publication of US20110175009A1 publication Critical patent/US20110175009A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/30—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces specially adapted for pressure containers
    • F16K1/307—Additional means used in combination with the main valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/06—Check valves with guided rigid valve members with guided stems
    • F16K15/063—Check valves with guided rigid valve members with guided stems the valve being loaded by a spring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/044—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with more than one spring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/06—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with special arrangements for adjusting the opening pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
    • F16K31/1221—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston one side of the piston being spring-loaded
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
    • F16K31/1223—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston one side of the piston being acted upon by the circulating fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
    • F16K31/1226—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston the fluid circulating through the piston
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D16/00—Control of fluid pressure
    • G05D16/04—Control of fluid pressure without auxiliary power
    • G05D16/10—Control of fluid pressure without auxiliary power the sensing element being a piston or plunger
    • G05D16/103—Control of fluid pressure without auxiliary power the sensing element being a piston or plunger the sensing element placed between the inlet and outlet
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7758—Pilot or servo controlled
    • Y10T137/7762—Fluid pressure type
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7781—With separate connected fluid reactor surface
    • Y10T137/7835—Valve seating in direction of flow
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7781—With separate connected fluid reactor surface
    • Y10T137/7835—Valve seating in direction of flow
    • Y10T137/7836—Flexible diaphragm or bellows reactor
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7904—Reciprocating valves
    • Y10T137/7905—Plural biasing means

Definitions

  • the invention relates to a fluid pressure regulating unit, comprising a fluid inlet port, a fluid outlet port, a valve means and a main valve biasing means, wherein said main valve biasing means biases said valve means in the direction of a first position.
  • Fluid regulators as such are well known in the state of the art. They are used to reduce the pressure of a fluid, entering the fluid regulator on a high pressure side, to a lower pressure level on the fluid outlet side. Preferably, the pressure on the fluid outlet side will be essentially constant.
  • Such pressure regulating units are used, for example, for pressurized gas bottles (pressure cylinders), where the pressure of the gas inside the bottle of up to 300 bars (or even higher) has to be reduced to a lower pressure level of usually 3-10 bars, which can be handled better. In some applications, however, a reduced pressure on a level around 40-50 bars is desired.
  • fire extinguishers and/or fire extinguishing systems fire fighting systems
  • fire fighting systems can be portable, mobile (built into a vehicle, for example) or stationary (built into a building, for example).
  • the supply of a fire extinguishing agent with a usually changing pressure level during use has to be reduced to lower pressure level with a preferably constant pressure.
  • the fire extinguishing agent with the reduced pressure level can hence be expelled by an appropriate nozzle, for example.
  • the fluid not only gases are possible. Also, liquids (like liquid CO 2 , for example), supercritical fluids (where no distinction between the liquid and the gaseous phase is possible any more), and mixtures of liquids, supercritical fluids and/or gases are possible. Also, the fluid can even contain a certain percentage of solids (smoke and/or suspensions, for example).
  • in-line constructions For improving the pressure output characteristics and reducing the vibration problems, so called “in-line” constructions have been proposed.
  • in-line constructions the number of directional changes of the fluid flowing through the pressure regulator is reduced. Furthermore, the number of moving parts can usually be reduced with in-line constructions. Therefore, in-line pressure regulators usually show less vibrations and a more constant, less fluctuating fluid output pressure.
  • the object of the present invention lies therefore in providing an improved fluid pressure regulating unit, as compared to fluid pressure regulating units according to the state of the art.
  • a fluid pressure regulating unit comprising a fluid inlet port, a fluid outlet port, a valve means and a main valve biasing means, wherein said main valve biasing means biases said valve means in the direction of a first position, with an auxiliary valve biasing means, wherein said auxiliary valve biasing means biases said valve means in the direction of a second position, being different from said first position.
  • the auxiliary valve biasing means is designed to be relatively weak and/or small as compared to the main valve biasing means. Therefore, the main valve biasing means can usually easily counteract the forces, imposed by the auxiliary valve biasing means, if properly set. It has to be noted that according to usual designs of pressure regulators, a main valve biasing means is already present. Additionally, in usual setups, the main valve biasing means is already designed to have a relatively high strength. Hence, when using presently available main valve biasing means, the forces, imposed by said auxiliary valve biasing means can usually be easily compensated for, e.g.
  • auxiliary valve biasing means should be able to provide a force, being sufficient to securely close the valve means of the fluid pressure regulating unit.
  • fluid liquids, gases, mixtures of fluids and gases and supercritical fluids are in encompassed. It is even possible, that a fluid can contain a certain amount of solid particles (e.g. smoke and/or suspensions).
  • the fluid pressure regulating unit is designed in a way that said first position and said second position are opposing each other, in particular in that said first position corresponds to an open position and said second position corresponds to a closed position of said valve means.
  • the main valve biasing means can easily and effectively compensate for the forces, generated by the auxiliary valve biasing means. In particular, frictional losses or the like can be minimized. If said first position corresponds to an open position and said second position corresponds to a closed position of said valve means, the main valve biasing means usually performs an opening of the pressure regulating unit, while the auxiliary valve biasing means performs the closing of the pressure regulating unit.
  • a fluid pressure operated member can be of an active and/or a passive type.
  • An active fluid pressure operated member can be realized by providing fluid chambers, which can be fluidly connected to external fluid reservoirs (pressurized and/or unpressurized). Using such an active fluid pressure operated member, an actively controllable fluid pressure regulating unit can be provided.
  • a passive fluid pressure operated member can be realized by providing closed chambers, filled with a gas. This way, a gas spring strut like member can be provided.
  • An elastically deformable member can be essentially made of any elastically deformable material, for example out of rubber and the like.
  • a spring e.g. made of metal
  • every form of spring can be used, normally a helical spring shows the best results.
  • valve biasing means in particular said main valve biasing means is adjustable.
  • the fluid pressure regulating unit can be easily adjusted to the intended use.
  • the fluid pressure regulating unit can be changed from an initial delivery adjustment, as set by the manufacturer, to an adjustment, needed for the setup, the fluid pressure regulating unit is used for.
  • the fluid regulating unit is designed in a way that the valve biasing means can be readjusted, e.g. during operation of the unit, when the unit is transferred to a different application and/or when the fluid pressure regulating unit is taken out of the unit and put into another unit.
  • said valve member of said fluid pressure regulating unit comprises a variable fluid flow cross section.
  • an adaptable fluid flux through the fluid pressure regulating unit can be provided.
  • a different fluid flux through the valve means is necessary to sustain a certain pressure level on the fluid outlet side of the fluid pressure regulating unit.
  • valve member comprises an axially movable tubular unit, wherein preferably said tubular unit comprises an inner passage.
  • a very simple setup of the fluid pressure regulating unit can be achieved.
  • the opening of said axially movable tubular unit on one side can be used as a part of the valve seat arrangement, where the variable fluid flow-cross section of the valve member is located.
  • a tubular unit normally relatively huge changes in fluid flow cross section can be achieved with a relatively small axial movement of the tubular unit.
  • the tubular unit can comprise one or several extensions, in particular radial extensions, which can be used as a fluid pressure receiving surface (in particular of the fluid pressure on the fluid outlet side of the fluid pressure regulating unit) and/or as a web for mounting a mechanical spring, for example.
  • extensions in particular radial extensions
  • These effects can be particularly well achieved, if the axially movable tubular unit comprises an inner passage.
  • This inner passage can be used for the fluid, being regulated by fluid pressure regulating unit.
  • valve member comprises a valve seat with an essentially even surface, in particular a plate like valve seat.
  • a valve seat can be easily and cheaply manufactured.
  • leakage due to imperfections of the valve seat and/or the corresponding valve member can be reduced, because the respective surfaces can be easily and precisely manufactured.
  • unwanted pressure drops, being caused by the valve member can be reduced, since a relatively large fluid flow cross section can be provided (in particular, if the valve member is arranged in a rotationally symmetric manner) and because the necessary redirection of the fluid, flowing through the fluid pressure regulating unit is relatively small.
  • the valve seat can be designed to be changeable. This way, a fluid pressure regulating unit with a very long lifetime can be provided.
  • the fluid pressure regulating unit should be designed in a way that at least one valve biasing means is at least partially in mechanical contact with said tubular unit. This can be achieved, for example, by a direct contact between a mechanical spring and a web of the tubular unit. This way, vibrations due to a play between the valve biasing means and the tubular unit can be reduced. If the (one or several) valve biasing means is in a relatively direct contact with said tubular unit, the pressure output characteristics of the fluid pressure regulating unit can be even further improved.
  • a preferred embodiment of the fluid pressure regulating unit is achieved, if the position of said valve means is essentially independent of the fluid pressure in said fluid inlet port and/or the position of said valve means is at least partially dependent on the fluid pressure in said fluid outlet port.
  • the desired output pressure characteristics of a pressure regulator can be provided.
  • the usually desired pressure output characteristics of a pressure regulator is that the fluid output pressure is constant, independent of the fluid inlet pressure.
  • a slight dependence on the fluid inlet pressure is also desired, because the operator can be provided with a feedback on the amount of still available fluid on the high pressure side of the apparatus, for example.
  • the fluid pressure regulating unit is provided with at least one fluid inlet side pressure balancing means.
  • a fluid inlet side pressure balancing means any device is in encompassed, which at least essentially provides for a fluid output pressure, being essentially independent of the fluid inlet pressure.
  • every balancing means known in the state of the art, can be used.
  • every surface part being fluidly connected to said fluid inlet port and having a surface normal at least partially in parallel to the moving direction of the moving part of said valve means, is balanced by a balancing surface part.
  • the “opposing” surface part is arranged in a way that a (vectorial fractional) second force is generated, when pressure is applied to the fluid inlet port of the fluid pressure regulating unit.
  • the two forces are preferably of the same magnitude and of opposite directions. Therefore, the occurring forces can cancel each other and the resulting net force can be zero.
  • the valve means can be independent of the pressure on the fluid inlet side of the fluid pressure regulating unit.
  • valve member in particular said axially movable tubular unit is designed and arranged with a minimum of surface parts, being fluidly connected to said fluid inlet port and having a surface normal at least partially in parallel to the moving direction of the moving part of said valve means.
  • said axially movable tubular unit can comprise a tapered surface part.
  • the tapered surface part of the movable tubular unit can be particularly arranged on the side, being fluidly connected with the fluid outlet port of the fluid pressure regulating unit. Using tapered surface parts, in particular a highly leak-proof valve seat can be provided for.
  • the adjustment of at least one of said valve biasing means is performed using a biasing thread.
  • a biasing thread With a biasing thread, a relatively large movement (e.g. by the operator of the machinery) can be translated into a small movement of the respective biasing means.
  • the fluid pressure regulating unit can be precisely adjustable.
  • threads are usually self locking.
  • a preferred embodiment can be achieved, if said valve means is in said second position, in particular in a closed position, if that main valve biasing means is in a weakly biased and/or unbiased state.
  • a positive closing of the fluid pressure regulating unit can be easily performed by the auxiliary valve biasing means.
  • the fluid pressure regulating unit is designed and arranged as an in-line regulator unit.
  • the number and amount of redirections of the fluid, flowing through the fluid pressure regulating unit can be minimized, thus yielding an improved pressure output characteristic of the fluid pressure regulating unit.
  • the resulting vibrations can usually be reduced.
  • said fluid pressure regulating unit comprises at least one actuator means.
  • said fluid pressure regulating unit comprises at least one actuator means.
  • This closing of the fluid pressure regulating unit can be performed independent of the fluid pressure at the fluid output port.
  • the functionality of an actuated cut-off valve can be easily incorporated into the fluid pressure regulating unit.
  • pilot pressure applying means are provided, which preferably can be selectively connected to said first fluid port and/or said second fluid port.
  • the actuator of the resulting unit can be switched, using fluid pressures.
  • the switching means can be based on the fluid pressure, mechanical forces, electricity, magnetic forces and the like, for example.
  • Another embodiment of said fluid pressure regulating unit can be achieved, if said pilot pressure applying means can be connected to a respective fluid pressure reservoir via a fluid throughput reducing means.
  • a fluid throughput reducing means can be a throttle or an orifice opening, for example.
  • FIG. 1 is a first embodiment of a pressure regulator with an auxiliary spring
  • FIG. 2 is a second embodiment of a pressure regulator with an auxiliary spring
  • FIG. 3 is a third embodiment of a pressure regulator with an auxiliary spring
  • FIG. 4 is a third embodiment of a fluid pressure regulator
  • FIG. 5 is a fourth embodiment of a fluid pressure regulator.
  • FIG. 1 a schematical cross section through a first possible embodiment of a pressure regulator 1 is depicted.
  • the pressure regulator 1 comprises a casing 2 with a fluid inlet port 3 and a fluid outlet port 4 . Both fluid inlet port 3 and fluid outlet port 4 have an inner thread 5 , so that a corresponding fluid pipe or fluid hose can be threadingly engaged in the respective fluid port 3 , 4 .
  • a valve unit 6 is arranged within the casing 2 of the pressure regulator 1 .
  • the valve unit 6 essentially consists of a valve seat 7 and a valve tube 8 .
  • the valve tube 8 can be moved in an axial direction (as indicated by double-headed arrow A) within the casing 2 of the pressure regulator 1 .
  • the valve tube 8 is designed to have a hollow interior 9 , forming an inner fluid line 9 through the valve tube 8 .
  • the contacting area between valve seat 7 and valve tube 8 forms the valve opening 10 . If the valve tube 8 is in its leftmost position (as drawn in FIG. 1 ), the valve seat 7 and the contacting edge 11 of the valve tube 8 contact each other, thus closing the valve opening 10 . In this position, no fluid flow is permitted between fluid inlet port 3 and fluid outlet port 4 . When the valve tube 8 is moving to the right, however, the contacting edge 11 of the valve tube 8 and the valve seat 7 get out of contact from each other, thus opening the valve opening 10 . Hence, fluid can flow from the fluid inlet port 3 to the fluid outlet port 4 .
  • the valve seat 7 is designed as a flat, circular plate.
  • the valve seat 7 is held in place by several holding bars 12 . Between the holding bars 12 , openings are provided, so that fluid can pass through.
  • the valve tube 8 is designed to have a circular cross section. Consequently, the contacting edge 11 shows a circular cross section.
  • the valve tube 8 comprises tapered edges 13 on the inner side 9 of the valve tube 8 , thus forming sharp contacting edges 11 .
  • the valve seat 7 is made of a slightly deformable material, so that the contacting edges 11 can slightly indentate the valve seat 7 , thus forming a tight fluid seal.
  • the valve tube 8 In a normal working adjustment position (main spring 14 biased), the valve tube 8 is pushed out of contact with the valve seat 7 (thus opening the valve opening 10 ) by means of the main spring 14 .
  • the main spring 14 is supported on its right side (see FIG. 1 ) by a circular web 15 integrally formed with the valve tube 8 .
  • the main spring 14 On the left side, the main spring 14 is supported by a nut 16 .
  • the nut 16 shows an inner thread 17 , which is engaged to a corresponding thread, arranged on the outer side of a collar like extension 23 of the casing 2 .
  • the nut 16 By a turning action of the nut 16 , the nut 16 can be displaced in an axial direction A by means of the thread 17 . Therefore, the biasing force of main spring 14 can be adjusted to the appropriate amount.
  • the nut 16 is designed to have a plurality of openings 22 for insertion of a part of an appropriate tool.
  • the casing 2 of the pressure regulator 1 is designed with an access window 24 for easy manipulation of the nut 16 .
  • the second interior space 19 within the casing 2 of pressure regulator 1 shows ambient pressure. Therefore, sealing rings 21 are provided between first internal space 18 , second internal space 19 and third internal space 20 , respectively.
  • the working cycle of the pressure regulator 1 is as follows:
  • valve tube 8 is in its open position (right side in FIG. 1 ; valve opening 10 is open). Fluid at high pressure enters the fluid inlet port 3 of the pressure regulator 1 . The fluid flows through the first internal space 18 , past the opened valve opening 10 , through the inner fluid line 9 of valve tube 8 into the third internal space 20 . According to an actual fluid flow demand, part of the fluid entering third internal space 20 leaves the casing 2 of the pressure regulator 1 by fluid outlet port 4 . However, in an open position of the valve unit 6 , a positive net fluid flow into the third internal space 20 occurs. Therefore, pressure builds up in the third internal space 20 . With increasing pressure, an increasing force is exerted on the piston surface 25 of the valve tube 8 .
  • the valve opening 10 closes and the pressure within the third internal space 20 remains at its set level. If the pressure inside the third internal space 20 drops again due to fluid, leaving through fluid outlet port 4 , the valve tube 8 will move slightly to the right, thus opening the valve opening 10 slightly. Hence, an equilibrium is achieved, so that the pressure in the third internal space 20 remains constant.
  • auxiliary spring 26 Apart from the pressure, exerted by the fluid within third internal space 20 onto the piston surface 25 of valve tube 8 , an additional force is exerted by means of an auxiliary spring 26 .
  • the auxiliary spring 26 has a small spring constant, when compared to the spring constant of main spring 14 .
  • the main spring 14 may easily compensate for the pressure, exerted by auxiliary spring 26 .
  • the force, exerted by auxiliary spring 26 is sufficient to safely close the valve unit 6 of the pressure regulator 1 . Therefore, no additional valve is needed, although the functionality of a cut-off valve is implemented in the pressure regulator 1 .
  • the closed position of the pressure regulator 1 (main spring 14 unbiased), is also advantageous for shipping the pressure regulator 1 .
  • normal vibrations during transportation of the pressure regulator 1 will not be able to open and close the valve unit 6 repetitively.
  • a wear of the pressure regulator 1 during transportation can be avoided.
  • auxiliary spring 26 can provide for an unambiguous position of the tube 8 . Therefore, one always know in which position the system will start and/or the system was arranged.
  • the axially movable valve tube 8 shows no surface parts within the first internal space 18 (high pressure chamber), which have to be balanced. If a fluid pressure is present in first internal space 18 , every surface of the valve tube 8 , being in contact with the high pressure fluid in first internal space 18 shows a surface normal, being solely perpendicular to the moving direction of the valve tube 8 . Therefore, any pressure within first internal space 18 will neither generate force, urging the valve tube 8 in an open position, nor generate a force, urging the valve tube 8 in a closing direction. Therefore, the high pressure part of pressure regulator 1 is perfectly balanced, even without balancing surfaces.
  • the movable valve tube 8 shows a tapered surface 13 , creating a sharp edge 11 . This way, fluid resistance is reduced, if the valve opening 10 is open. Also, a tight seal can be provided if the valve opening 10 is closed.
  • the tapered part 13 of the valve tube 8 is additionally working as a balancing surface for the respective surface part of the piston surface 25 of the valve tube 8 (both fluidly connected to the fluid outlet port 4 ).
  • the pressure regulator 1 is still dependent on the fluid outlet pressure, because a flange part 27 is provided for the valve tube 8 , showing a cross section, exceeding the cross section of tapered surface parts 13 .
  • the special design of the tapered surface 13 on the inner side 9 of the valve tube 8 in the vicinity of the valve opening 10 insures that the pressure drop of the fluid, flowing through the pressure regulator 1 will essentially occur in a very small area. Therefore, this construction can be less effected by variations in the pressure within first internal space 18 . This is, because the areas, being in contact with the high pressure fluid are extremely small as compared to the areas, being in contact with the low pressure fluid.
  • the auxiliary spring 26 can put the pressure regulator 1 in a shut off state, if there is no load on the main spring 14 (or on the flange part 38 of valve tube 8 in the pressure regulator 35 , as shown in FIG. 3 ). Hence, the fluid regulator 1 described can work as a shut off valve as well.
  • the flange part 27 could be designed as a membrane for the like.
  • such an alternative design could be used in units of a different design as well.
  • FIG. 2 a second possible embodiment of a pressure regular 28 is shown. Most parts of the present pressure regulator 28 are similar or the same as those used for pressure regulator 1 , as illustrated in FIG. 1 .
  • the presently used valve tube 32 comprises a tapered surface 30 in the vicinity of the valve seat 7 .
  • the tapered surface 30 is presently arranged on the outside of the valve tube 32 , thus facing towards the first internal space 18 , being fluidly connected to the fluid inlet port 3 of pressure regulator 28 .
  • This introduces a force, urging the valve tube 32 into an opening direction, when high pressure is applied to the first internal space 18 .
  • the effective opening force is the vectorial fraction of the pressure force, pointing in the direction of movement of valve tube 32 .
  • the pressure regulator 28 is provided with a balancing section 33 .
  • the fourth internal space 29 is provided, which is fluidly connected to the first internal space 18 by a fluid channel 34 . Facing towards the fourth internal space 29 , the valve tube 32 is provided with a balancing web 31 .
  • the size of the balancing web 31 is chosen in a way that the resulting force, being exerted onto the valve tube 32 when pressure is applied to fluid inlet port 3 (and therefore to first internal space 18 and fourth internal space 29 ) is of the same magnitude as the force generated by the tapered surface 30 .
  • the direction of both forces, however, is opposite to each other. Therefore, both forces cancel each other.
  • the pressure regulator 28 is balanced towards the high pressure side. In other words, the output pressure characteristics of the pressure regulator 28 is independent of the pressure at fluid inlet port 3 .
  • An advantage of the proposed design with the tapered surface 30 on the outside of the valve tube 32 is that the dimensions of the fluid tube 32 can be chosen from a very wide range. This is, because generally speaking an almost arbitrary size of the surface area on the front side of the valve tube 32 (near valve opening 10 ) can be compensated by the counteracting force delivered by the ring like web 31 of valve tube 32 . Thus, a pressure regulator 28 of the design proposed can be used with very high pressures.
  • the thickness of the walls of the valve tube 8 , 32 is normally in the order of one millimetre (pressures in the range from 200 to 300 bars).
  • wall thicknesses for the valve tube 8 , 32 in the area of several millimetres can be easily realized.
  • the design of the pressure regulator 28 can be used for the design of a pilot driven valve 41 , 53 as well (see FIGS. 4 , 5 ).
  • the arrangement of the tapered surface 30 on the outside of valve tube 32 can be used for pilot driven valves 41 , 53 .
  • the tapered surface 30 on the outside of the valve tube 32 can also be used in connection with the pilot driven 37 fluid pressure regulator 35 design, as depicted in FIG. 3 .
  • FIG. 3 another possible embodiment of a pressure regulator 35 is illustrated.
  • the main spring 14 is omitted.
  • a pilot pressure chamber 36 is provided as a replacement for the main spring 14 .
  • the pilot pressure chamber 36 is fluidly connected to a pilot fluid port 37 .
  • a flange part 38 of the valve tube 39 is located on one side of the pilot pressure chamber 36 . Therefore, by applying a pressure to the pilot pressure chamber 36 , an appropriate biasing force can be exerted on the valve tube 39 .
  • the biasing can be changed by varying the pressure, applied to the pilot pressure chamber 36 . It has to be noted that this way an automated change of biasing force can be easily implemented.
  • the medium in the pressure chamber 36 should be compressible.
  • a gas or a liquid/gas mixture with a certain gas contents could be used.
  • a non-compressible fluid could be used.
  • some compressible device should be used, like a compressible gas-filled sphere or a kind of spring operated storage, which can be loaded by a pressure pulse in the biasing fluid.
  • the backside volume 40 is of course at ambient pressure.
  • the pressure regulator 35 resembles the pressure regulator 1 , as shown in FIG. 1 .
  • a pilot controlled fluid pressure regulator 56 is depicted.
  • the pilot controlled fluid pressure regulator 56 can be considered to be a fluid pressure regulator 1 , as shown in FIG. 1 , in which a pilot control section 59 , comprising an additional closing chamber 57 is provided.
  • the closing chamber 57 is fluidly connected to the first internal space 18 via a feeding line 48 and a connecting line 47 .
  • the fluid flux through the feeding line 48 is limited by a throttle 51 , which can be formed as a part of the feeding line 48 . If the piloting valve 50 is in its closed position (as shown in FIG. 4 ), the pressure in the closing chamber 57 will eventually be the same as the pressure in the first internal space 18 .
  • the pressure of the fluid in closing chamber 57 exerts a force on the flange part 38 of valve tube 8 .
  • This will cause the valve tube 8 to move to the left side, i.e. pushing the valve tube 8 on the valve seat 7 , thus closing the valve unit 6 .
  • the pilot controlled fluid pressure regulator 56 can be safely closed, irrespective of the fluid pressure in third internal space 20 , i.e. irrespective of the fluid pressure at the fluid outlet port 4 .
  • the second internal space 19 lying on the flange part 38 of the valve tube 8 , which is opposite to the closing chamber 57 , is vented to ambient pressure via channel 46 .
  • piloting valve 50 If the piloting valve 50 is switched to its open position, however, a fluid connection is established between connecting line 47 and third internal space 20 via piloting valve 50 and discharge line 49 . Therefore, the pressure in the closing chamber 57 will drop to the pressure level of third internal space 20 . This is, because the influx of fluid is limited by throttle 51 . Because of the falling pressure within closing chamber 57 , the valve tube 8 is now again free to move to the right side, i.e. into the open position of valve unit 6 . Whether this movement will actually take place, or not, depends on the pressure in third internal space 20 . Therefore, the pilot controlled fluid pressure regulator 56 now works as a standard fluid pressure regulator.
  • FIG. 5 is a modification of the pilot controlled fluid pressure regulator 56 , shown in FIG. 4 .
  • the presently shown pilot controlled fluid pressure regulator 58 shows an additional balancing section 33 , which is equivalent to the balancing section 33 of the pressure regulator 28 , shown in FIG. 2 .
  • the fluid pressure regulator 28 shown in FIG. 2
  • a pilot controlled fluid regulator 58 which is fluid pressure regulated (in particular towards the high pressure side of the pilot controlled fluid pressure regulator), can be realised.
  • piloting valve 50 can be designed differently as well.
  • a manual operation of piloting valve 50 is possible.
  • piloting valve 50 can be constructed in a way that intermediary states can be achieved. This can be achieved by providing an intermediary mechanical position of the piloting valve 50 .
  • a proportional valve is possible as well. This could be achieved by a modulated magnetic valve, for example.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Control Of Fluid Pressure (AREA)
  • Safety Valves (AREA)
US13/119,593 2008-09-19 2009-09-17 Fluid regulator Abandoned US20110175009A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP08016555.8A EP2166424B1 (fr) 2008-09-19 2008-09-19 Régulateur de fluides
EP08016555.8 2008-09-19
PCT/DK2009/000208 WO2010031401A1 (fr) 2008-09-19 2009-09-17 Régulateur de fluide

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/DK2009/000208 A-371-Of-International WO2010031401A1 (fr) 2008-09-19 2009-09-17 Régulateur de fluide

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US14/466,045 Division US9739387B2 (en) 2008-09-19 2014-08-22 Fluid regulator

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US20110175009A1 true US20110175009A1 (en) 2011-07-21

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US13/119,593 Abandoned US20110175009A1 (en) 2008-09-19 2009-09-17 Fluid regulator
US14/466,045 Active US9739387B2 (en) 2008-09-19 2014-08-22 Fluid regulator

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US (2) US20110175009A1 (fr)
EP (1) EP2166424B1 (fr)
CN (1) CN102160012B (fr)
AU (1) AU2009295049B2 (fr)
BR (1) BRPI0918811B1 (fr)
DK (1) DK2166424T3 (fr)
WO (1) WO2010031401A1 (fr)

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US10161526B2 (en) * 2016-01-04 2018-12-25 Hyundai Motor Company Valve for controlling coolant flow and fuel cell cooling system using the same
CN109312867A (zh) * 2016-06-21 2019-02-05 喜开理株式会社 流体控制阀及流体控制阀制造方法
US20190301624A1 (en) * 2018-03-29 2019-10-03 Hamilton Sundstrand Corporation Valve with segmented spring guide assembly
WO2020208483A1 (fr) 2019-04-08 2020-10-15 Netafim Ltd Vanne réductrice de pression avec mécanisme d'arrêt
US20210165431A1 (en) * 2019-11-29 2021-06-03 Mico, Inc. Reverse modulation valve assembly including deadband state
CN113685565A (zh) * 2021-10-26 2021-11-23 徐州盛安化工科技有限公司 一种适用于呋喃树脂的储存设备及其存储方法
US11193427B2 (en) * 2018-04-27 2021-12-07 Hamilton Sundstrand Corporation Passive active poppet-type bleed valves
US11293462B2 (en) * 2016-02-09 2022-04-05 National Oilwell Varco, L.P. Pilot close vent valve
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Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10753479B2 (en) 2016-01-04 2020-08-25 Hyundai Motor Company Valve for controlling coolant flow and fuel cell cooling system using the same
US10161526B2 (en) * 2016-01-04 2018-12-25 Hyundai Motor Company Valve for controlling coolant flow and fuel cell cooling system using the same
US11293462B2 (en) * 2016-02-09 2022-04-05 National Oilwell Varco, L.P. Pilot close vent valve
US11118690B2 (en) 2016-06-21 2021-09-14 Ckd Corporation Fluid control valve and fluid control valve manufacturing method
JPWO2017221877A1 (ja) * 2016-06-21 2019-04-11 Ckd株式会社 流体制御弁、及び流体制御弁製造方法
TWI740968B (zh) * 2016-06-21 2021-10-01 日商Ｃｋｄ股份有限公司 流體控制閥製造方法
CN109312867A (zh) * 2016-06-21 2019-02-05 喜开理株式会社 流体控制阀及流体控制阀制造方法
US10753493B2 (en) * 2018-03-29 2020-08-25 Hamilton Sunstrand Corporation Valve with segmented spring guide assembly
US20190301624A1 (en) * 2018-03-29 2019-10-03 Hamilton Sundstrand Corporation Valve with segmented spring guide assembly
US11193427B2 (en) * 2018-04-27 2021-12-07 Hamilton Sundstrand Corporation Passive active poppet-type bleed valves
US11674452B2 (en) * 2018-04-27 2023-06-13 Hamilton Sundstrand Corporation Passive active poppet-type bleed valves
WO2020208483A1 (fr) 2019-04-08 2020-10-15 Netafim Ltd Vanne réductrice de pression avec mécanisme d'arrêt
US20210165431A1 (en) * 2019-11-29 2021-06-03 Mico, Inc. Reverse modulation valve assembly including deadband state
US11609585B2 (en) * 2019-11-29 2023-03-21 Zf Off-Highway Solutions Minnesota Inc. Reverse modulation valve assembly including deadband state
JP7453017B2 (ja) 2020-02-25 2024-03-19 アズビル株式会社 弁機構
CN113685565A (zh) * 2021-10-26 2021-11-23 徐州盛安化工科技有限公司 一种适用于呋喃树脂的储存设备及其存储方法

Also Published As

Publication number Publication date
BRPI0918811A2 (pt) 2015-12-01
US20140360599A1 (en) 2014-12-11
DK2166424T3 (en) 2017-09-18
EP2166424B1 (fr) 2017-06-07
WO2010031401A1 (fr) 2010-03-25
CN102160012A (zh) 2011-08-17
BRPI0918811B1 (pt) 2019-06-18
CN102160012B (zh) 2014-08-27
AU2009295049A1 (en) 2010-03-25
US9739387B2 (en) 2017-08-22
AU2009295049B2 (en) 2013-10-03
EP2166424A1 (fr) 2010-03-24

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