US3809111A - Pressure reduction valve - Google Patents

Pressure reduction valve Download PDF

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Publication number
US3809111A
US3809111A US16033571A US3809111A US 3809111 A US3809111 A US 3809111A US 16033571 A US16033571 A US 16033571A US 3809111 A US3809111 A US 3809111A
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United States
Prior art keywords
piston
pressure
outlet
inlet
channels
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Expired - Lifetime
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English (en)
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A Olsson
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Individual
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Individual
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Filing date
Publication date
Priority claimed from SE09592/70A external-priority patent/SE355657B/xx
Priority claimed from SE03727/71A external-priority patent/SE366103B/xx
Application filed by Individual filed Critical Individual
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Publication of US3809111A publication Critical patent/US3809111A/en
Anticipated expiration legal-status Critical
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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
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/20—Excess-flow valves
    • F16K17/22—Excess-flow valves actuated by the difference of pressure between two places in the flow line
    • F16K17/24—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member
    • 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
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D7/00—Control of flow
    • G05D7/01—Control of flow without auxiliary power
    • G05D7/0126—Control of flow without auxiliary power the sensing element being a piston or plunger associated with one or more springs
    • G05D7/0133—Control of flow without auxiliary power the sensing element being a piston or plunger associated with one or more springs within the flow-path
    • 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
    • Y10T137/7784—Responsive to change in rate of fluid flow
    • Y10T137/7787—Expansible chamber subject to differential pressures
    • Y10T137/7791—Pressures across flow line 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
    • 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
    • Y10T137/7793—With opening bias [e.g., pressure regulator]
    • Y10T137/7796—Senses inlet pressure
    • 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]
    • Y10T137/7859—Single head, plural ports in parallel
    • Y10T137/786—Concentric ports
    • 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]
    • Y10T137/7859—Single head, plural ports in parallel
    • Y10T137/7861—Annular head
    • 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]
    • Y10T137/7866—Plural seating
    • Y10T137/7867—Sequential

Definitions

  • the valve contains a plurality of elongated relatively UNITED STATES PATENTS narrow by-pass-channels between the inlet and the 7 outlet, which by-pass-channels are so shaped and arigfs l ggg ranged that they are opened or closed, respectively, 2 918 082 12/1959 Garran....
  • the present invention refers to such pressure reduction valves which are used both for reducing the presv sure in a feeder line, for instance to a tapping place provided with a control valve so that a suitable pressure is obtained at this tapping place, and for securing an even volume of medium stream.
  • the invention has for its purpose essentially independently of the pressure in the feeder line to make sure a given limited maximum amount of streaming medium per unit of time to the consumption apparatus, which may in turn be controlled by the proper control valve of the consumption apparatus.
  • One purpose of the present invention therefore is to remedy the noice and rumbling disturbances from a pressure reduction valve of the type mentioned above.
  • the invention thereby is based upon the knowledge about that pressure reduction by laminar movement in channels with a relatively great length and small diameter will give an essentially smaller disturbing noice.
  • valve arrangement In order that one shall create the above mentioned maximum volume of moving medium per unit of time, independent of the feeder pressure, however, the valve arrangement must comprise means for variation of the movement resistance. It is technically difficult and unpractical to make this by variation of the length and/or the diameter of a channel for the moving medium, which would otherwise be able to give the desired result.
  • This invention instead is based upon that one should use a plurality of channels connectable in parallel to each other, similarily as a plurality of resistors connectable in parallel are used for controlling electric current.
  • the parallel connection In order to cause a correct control of the type intended, however, the parallel connection must take place as a function of the real drop of pressure over the resistances for the current medium and therefore be substantially independent of the feeder pressure, which corresponds to the relations in an electric constant current circuit.
  • the invention therefore further is based upon the knowledge that a valve influenced by pressure from both sides, that means influenced on its one side by the input pressure and on its other side by the output pressure, and which is further biassed by a spring in a direction counter-acting the action of the input pressure, will at variation of any of the said pressure components displace itself in-axially direction to a position, dependent upon the difference in pressure, and that this displacement of position, which is thus substantially independent of the absolute valve of the input pressure may be used for adjustment of the resistance against moving medium.
  • the invention thus refers to an arrangement in pressure reduction valve for a medium moving under pressure and intended to be connected in the conduit between .the source of the medium under pressure and a valve controlled tapping place.
  • the valve has an inlet and an outlet and is provided with means for execution of a variable resistance for the moving medium substantially independent of the pressure drop over the valve.
  • the valve contains a run, arranged inside of a valve housing, one end of which being in connection with the inlet: to the valve and the other end being in connection with the outlet from the valve.
  • a piston is arranged. axially displaceable in the run, so that the piston will be subjected on its one side for the action of the inlet pressure and on its other side be subjected to the action of the outlet pressure.
  • the piston further is biassed by a spring against the action of the inlet pressure, so that it will always tend to assume a position, where the action of the inlet pressure is annulated by the action of the sum of the outlet pressure and the resilient spring pressure.
  • the valve further contains a plurality of elongated rather narrow by pass-channels between the inlet and the outlet of the valve, which are so shaped and arranged that they are opened and closed dependent upon the position of the piston in the run, so that a progressively increasing number of by-pass-channels is opened and the effective resistance against movement of the valve decreases, when the valve is displaced in a direction onto the outlet and vice versa.
  • FIG. 1 shows a longitudinal section through a valve according to the invention
  • FIG. 2 is a cross-section through the valve according to FIG. 1 along the point dashed line in this Figure.
  • FIG. 3 shows an electrical and logical circuit to the arrangement according to FIGS. 1 and 2.
  • FIG. 4 shows a modification of the arrangement according to FIG. 1 and FIG. 2, in which the channels are arranged in the piston instead of, as in the arrangement according to FIGS. 1 and 2, in the valve housing.
  • FIGS. 5 and 6 finally show a couple of more developed forms. of execution of the arrangement according to the invention.
  • the valve arrangement shown in FIGS. 1 and 2 contains a cylindrical valve housing 1 with inlet end 2 and outlet end 3.
  • a cylindrical main passage or run 4 is arranged, which is in some suitable way at its one end connected to the inlet 2 and at its other end to the outlet 3.
  • the run may in the way, shown in the drawing, be of uniform cross-section, but it is also understood that the valve should be capable of being attached to tubing and the like and that for this purpose the run and its connection means may require to be made with different diameters.
  • a cylindrical piston 5 is arranged, which is biassed by means of a pressure spring 6 in a direction onto the inlet 2.
  • the spring in this case is introduced between a spring seat at the end of the piston 5 and a ring near the outlet 3 of the valve, but it may also act as a traction spring and be provided on the other side of the piston.
  • This spring 6 will be further described below.
  • the inlet opening of the channel 7 thus is situated closer to the inlet 2, the inlet opening of the channel 8 a little further displaced away in axial direction from said inlet, and most far into the valve is the inlet opening of the channel 9.
  • the channels 7, 8 and 9 are in some suitable way distributed about the valve housing 1, preferably in a circular distribution with even distances.
  • the inlet openings of the channels 7, 8 and 9 are situated within a range, substantially corresponding to the axial length of the piston 5. In a given position of the piston 5 consequently all of the inlet openings of the channels are covered.
  • the outlet openings of the said channels further are situated in a sufficiently great axial distance from the range of movement of the piston 5 in order that the piston when displaced against action of the spring 6 shall never cover any one of the outlet openings of the channels.
  • the invention is not limited to the use of only three channels. The greater the number of channels are and the narrower they are, the more even will the control he. Nor must the channels be completely contained in the material of the valve housing, but they may be formed by rifles having a suitable cross-section in the walls of the run. Finally they could be given a rather great length, which may take place by the channels starting in progressively increasing axial distances from the inlet 2 and continuing backwardly past the working range of the piston 5.
  • valve even the inlet end and the outlet end of the valve may be continuously connected over a suitable shunt conduit. Also this does not affect the function of the valve.
  • the valve according to the invention may serve for instance independently of the inlet pressure to limit the volume of movement on the outlet side to a predetermined maximum value.
  • the spring 6 suitably is provided with a means not shown in the drawings for adjustment of the spring force dependent upon amongst other things the expected inlet pressure of the medium.
  • FIG. 3 shows an equivalent electrical wireing diagram over the valve arrangement according to FIGS. 1 and 2.
  • the electrical current passes a switch 5' analogous to thepiston 5, which may connect the resistors 7', 8 and 9' step by step in parallel connection.
  • the group of resistors is connected in series in the path of the current, so that the total resistance against current decreases step by step.
  • the other ends of said resistors are connected to the output conductor 3'.
  • FIGS. 5 and 6 The modifications and developments of the above described arrangements according to FIGS. 1 and 2 or FIG. 4, resp., which are shown in FIGS. 5 and 6, have for their purpose to make possible a more exact control, which should further within wide limits allow for the adaption of the control characteristic to the magnitude of the inlet pressure.
  • the arrangements according to FIGS. 5 and 6 further allow for a control of the dynamic controlling properties of the valve, especially so that the reaction speed of the controlling means are limited and thereby also impact loads, so called water impacts are avoided.
  • the constructions according to FIGS. 5 and 6 further will give the constructor a greater freedom when the question is one about providing a desired control characteristic in each separate case.
  • valve housing 1 1 which has been shown as an example in the form of a cylindrical sleeve.
  • valve housing 11 thus there is a cylindrical run 12 which in the end of the arrangement according to FIG. 5 at right turns over into a somewhat wider cylindrical run 12.
  • a ring-formed or cylindrically shellformed piston 13 is arranged in such a way that it will rather well tighten against the inner walls of the run 12.
  • the ring-formed annular piston 13 is axially displaceable to and fro in the run 12.
  • a second cylindrical piston 14 is in turn axially displaceable.
  • the ring-formed piston 13 is supported by a spring 15 at its one end resting against a perforated disk 16, which is provided at its middle part with a hole corresponding to the cylindrical piston 14 so that this cylindrical piston 14 may pass freely through the hole.
  • the disk 16 is kept in place between a recess in the turn over from the narrower piece 12 of the run to the wider piece 12' of said run, on the one hand, and a sleeve 17, on the other hand.
  • a space 18 is limited between the disk 16, the corresponding end of the ring-formed piston. 13, the outer mantle surface of the cylindrical piston 14 and the corresponding wall part of the run 12.
  • the space 18 is in'connection with the outlet side of the valve over a narrow conduit 19, which may be controllable as'to its cross-section.
  • the cylindrical piston 14 is supported over the prolongation 23 by a spring 24, resting on a disk 21, which is kept in place by its outer edge being spanned between the sleeve 17 and a further sleeve 22.
  • the screw spring 24 thus contacts with its one end the outwardly directed flange on the prolongation 23 and with its other end the middle part of the disk 21.
  • a bar 25 is attached to the disk 21, said bar extending into a corresponding hole in the piston 14 so that the spring 24 will get the required guiding in the sideward direction.
  • the cylindrical piston 14 is axially movable substantially in the same way as already described in connection with the ring-formed piston 13.
  • P the pressure from the inlet medium
  • the piston surfaces and the spring forces should be chosen in such a way that a change of the relation P,;,/P,,, will give a stronger reaction with the piston 13 than with the piston 14; in both cases the reaction is measured in the form of the displacement.
  • the state shown in FIG. 5 thereby should correspond to the reaction for a great difference between P and P,,,, for instance caused by a consumption apparatus in which small resistance against movement of medium is. momentarily connected to the output side of a valve according to the invention. Before this took place, the two pistons thus were situated more far at left in the drawing Figure, so that the channels 29, 30, and 31 where covered with their months by the ring-formed piston 13.
  • the arrangement according to FIG. 6 differs from the arrangement according to FIG. 5 mainly in the following respects:
  • the space 18 is in connection with the outlet side of the valve over a narrow conduit 19
  • the corresponding space 18 in the arrangement according to FIG. 6 is practically in unprevented connection with the outlet side of the valve through a plurality of openings 20 of a suitable form in the disk 16.
  • the piston 14 is supported against the one end of the screw spring 24, the other end of said spring being supported by the middle part of the disk 21, and a bar being arranged in the interior of the screw spring 24, the piston 14 is instead supported in the arrangement according to FIG. 6 against the end of a bellows 26, which is attached at its other end to the middle part of the disk 21.
  • a conduit 27 which may be provided with a control arrangement 28, the interior of the bellows 26 is in connection with the surrounding atmosphere or perhaps with some source of a pressure medium, which is, however, not shown in the drawing, along with suitable sensing or indication means for the pressure in the interior of the bellows.
  • a change of the relation P /P will cause a displacement in one direction or the other one of the ring- .formed piston 13, so that the state of equilibrium is retained according to the equation (1)
  • Analogically the change also causes a displacement in the one direction or the other one of the cylindrical piston 14, so that one will retain one of the following states of equilibrium, viz.
  • An automatically acting pressure reduction valve for controlling the pressure of a moving fluid medium between a pressurized area and a valve controlled tap for such medium in such a way that the pressure at the valve controlled tap will be at least approximately constant, comprising:
  • control means between said inlet and outlet for varying the resistance against movement of the fluid medium in response to the pressure drop across the pressure reduction valve, said control means including: an elongated main passage from said inlet to said outlet,
  • a piston positioned in said main passage for freely sliding axial movement therein, the upstream side of said piston being subjected to inlet pressure and the downstream side thereof being subjected to outlet pressure,
  • the piston being freely movable to a position such that the force of the outlet pressure and the force of the spring equal the force of the inlet pressure
  • a pressure reduction valve according to claim 1, said channels being formed in the housing, the downstream side of said channels opening without obstruction into the outlet, the upstream ends of said channels being staggered in the direction of fluid flow and positioned such that all of them are normally covered by the piston at said initial position, these upstream ends successively being uncovered as the piston moves downstream as the pressure drop across the piston increases, thereby increasing the number of channels through which the fluid passes from the inlet to the outlet until an equilibrium is reached at which the force of the inlet pressure equals the force of the outlet pressure plus the spring force.
  • a pressure reduction valve according to claim 2 in which the channels are of substantially equal length and have the same cross-sectional area and are formed in theouter walls of the valve housing.
  • a pressure reduction valve according to claim 1 said spring means comprising an adjustable spring acting against one end of the piston.
  • a pressure reduction valve according to claim 1, said channels being formed in the piston, all of at least one of the said inlet or outlet ends being opened to the main passage, the other of said inlet or outlet ends being staggered, and said housing including a small cross-sectional area covering the staggered channel ends in said initial position of the piston, and said hous ing including an enlarged cross-sectional area adjacent the small cross-sectional area and positioned such that as the piston moves downstream in response to an increase in the pressure drop across the piston, said staggered channels are successively uncovered, thereby increasing the number of channels through which the fluid passes from the inlet to the outlet until an equilibrium is reached at which the force of the inlet pressure equals the force of the outlet pressure plus the spring force.
  • a pressure reduction valve according to claim 1 in which the piston is formed in two parts including a first piston which is annular in cross-section and a second piston movable in the interior of the first piston,
  • the annular piston being movable against the action of a first spring and provided in given positions to cover the said openings to the channels which are formed in the second interior piston, the latter piston being under the action of a second spring.
  • the interior piston is displaceable through a screen arranged across the main passage, such that a pressure chamber which varies in volume upon displacement of the pistons will be formed between the side surface of the interior piston, the screen, the housing and the end surface of the annular piston, and including a choke channel arranged for releasing the pressure in said pressure chamber.
  • a pressure reduction valve in which a bellows is provided between the downstream end of the interior piston and a screen extending across the main passage, said bellows being filled with a pressure receiving medium and said bellows being in fluid connection with the surroundings via a choke channel.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Safety Valves (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Gas Separation By Absorption (AREA)
  • Control Of Fluid Pressure (AREA)
US16033571 1970-07-10 1971-07-07 Pressure reduction valve Expired - Lifetime US3809111A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE09592/70A SE355657B (fr) 1970-07-10 1970-07-10
SE03727/71A SE366103B (fr) 1971-03-23 1971-03-23

Publications (1)

Publication Number Publication Date
US3809111A true US3809111A (en) 1974-05-07

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Family Applications (1)

Application Number Title Priority Date Filing Date
US16033571 Expired - Lifetime US3809111A (en) 1970-07-10 1971-07-07 Pressure reduction valve

Country Status (6)

Country Link
US (1) US3809111A (fr)
CA (1) CA950793A (fr)
DE (1) DE2134093C3 (fr)
FR (1) FR2101569A5 (fr)
GB (1) GB1351222A (fr)
NO (1) NO131901C (fr)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997009917A1 (fr) * 1995-09-14 1997-03-20 Smartplug Pty. Ltd. Bonde a auto-vidage
US5697351A (en) * 1996-11-12 1997-12-16 Miniature Precision Components, Inc. Positive crankcase ventilation valve for motor vehicle
US20060071088A1 (en) * 2004-10-05 2006-04-06 Paul Adams Fuel cartridge with an environmentally sensitive valve
WO2006051391A1 (fr) * 2004-11-09 2006-05-18 Masco Corporation Of Indiana Dispositif pour la regulation dynamique d'un ecoulement d'eau
US20060236989A1 (en) * 2005-04-22 2006-10-26 Callahan Douglas J Heated pcv system
US20130105007A1 (en) * 2011-10-31 2013-05-02 Korea Aerospace Research Institute Flow control valve
US20140284508A1 (en) * 2013-03-25 2014-09-25 E.H. Price Ltd. Venturi Valve with Hard Stop
US20170234106A1 (en) * 2012-03-21 2017-08-17 Inflow Control AS Flow Control Device
CN110220022A (zh) * 2019-05-13 2019-09-10 芜湖美的厨卫电器制造有限公司 安全阀和热水器
EP3540177A1 (fr) * 2018-03-12 2019-09-18 Inflowcontrol AS Dispositif et procédé de réglage de débit
US12117851B2 (en) * 2021-07-27 2024-10-15 Qtrack Health Systems Private Limited Oxygen pressure regulating device and system

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2658579B1 (fr) * 1990-02-22 1992-04-30 Soudure Autogene Francaise Detendeur.

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US1879197A (en) * 1931-01-12 1932-09-27 Kelvinator Corp Resistor unit for refrigerating apparatus
US2706490A (en) * 1950-01-18 1955-04-19 Nordberg Manufacturing Co Variable retraction valve
US2918082A (en) * 1955-02-21 1959-12-22 Hudson Mfg Co H D Pressure regulating device
US3093155A (en) * 1960-06-20 1963-06-11 Bendix Corp Variable-restriction valve
US3138175A (en) * 1960-11-22 1964-06-23 Futurecraft Corp High pressure modulating valve
US3468341A (en) * 1964-11-19 1969-09-23 Broughton Corp Precision vacuum controller
US3568711A (en) * 1967-06-29 1971-03-09 Maurice Katz Vehicle shock absorbers

Patent Citations (7)

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Publication number Priority date Publication date Assignee Title
US1879197A (en) * 1931-01-12 1932-09-27 Kelvinator Corp Resistor unit for refrigerating apparatus
US2706490A (en) * 1950-01-18 1955-04-19 Nordberg Manufacturing Co Variable retraction valve
US2918082A (en) * 1955-02-21 1959-12-22 Hudson Mfg Co H D Pressure regulating device
US3093155A (en) * 1960-06-20 1963-06-11 Bendix Corp Variable-restriction valve
US3138175A (en) * 1960-11-22 1964-06-23 Futurecraft Corp High pressure modulating valve
US3468341A (en) * 1964-11-19 1969-09-23 Broughton Corp Precision vacuum controller
US3568711A (en) * 1967-06-29 1971-03-09 Maurice Katz Vehicle shock absorbers

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997009917A1 (fr) * 1995-09-14 1997-03-20 Smartplug Pty. Ltd. Bonde a auto-vidage
US5697351A (en) * 1996-11-12 1997-12-16 Miniature Precision Components, Inc. Positive crankcase ventilation valve for motor vehicle
US20060071088A1 (en) * 2004-10-05 2006-04-06 Paul Adams Fuel cartridge with an environmentally sensitive valve
WO2006041857A2 (fr) * 2004-10-05 2006-04-20 Societe Bic Cartouche de carburant munie d'un robinet sensible a l'environnement
WO2006041857A3 (fr) * 2004-10-05 2006-05-18 Bic Soc Cartouche de carburant munie d'un robinet sensible a l'environnement
US20070207354A1 (en) * 2004-10-05 2007-09-06 Societe Bic Fuel Cartridge with an Environmentally Sensitive Valve
US7726344B2 (en) 2004-11-09 2010-06-01 Masco Device for dynamic control of a water flow
WO2006051391A1 (fr) * 2004-11-09 2006-05-18 Masco Corporation Of Indiana Dispositif pour la regulation dynamique d'un ecoulement d'eau
US20070289643A1 (en) * 2004-11-09 2007-12-20 Masco Corporation Of Indiana Device for dynamic control of a water flow
US20060236989A1 (en) * 2005-04-22 2006-10-26 Callahan Douglas J Heated pcv system
US7316226B2 (en) 2005-04-22 2008-01-08 Miniature Precision Components, Inc. Heated PCV system
US20130105007A1 (en) * 2011-10-31 2013-05-02 Korea Aerospace Research Institute Flow control valve
US9092032B2 (en) * 2011-10-31 2015-07-28 Korea Aerospace Research Institute Flow control valve
US10260312B2 (en) * 2012-03-21 2019-04-16 Inflowcontrol As Flow control device
US20170234106A1 (en) * 2012-03-21 2017-08-17 Inflow Control AS Flow Control Device
US20140284508A1 (en) * 2013-03-25 2014-09-25 E.H. Price Ltd. Venturi Valve with Hard Stop
EP3540177A1 (fr) * 2018-03-12 2019-09-18 Inflowcontrol AS Dispositif et procédé de réglage de débit
WO2019175078A1 (fr) * 2018-03-12 2019-09-19 Inflowcontrol As Dispositif et procédé de régulation de débit
CN111954747A (zh) * 2018-03-12 2020-11-17 英孚罗控制股份有限公司 流控制装置和方法
CN111954747B (zh) * 2018-03-12 2022-09-30 英孚罗控制股份有限公司 流控制装置和方法
EP3765707B1 (fr) 2018-03-12 2023-04-12 Inflowcontrol AS Dispositif et procédé de réglage de débit
EP4215718A1 (fr) * 2018-03-12 2023-07-26 Inflowcontrol AS Dispositif et procédé de régulation de débit
CN110220022A (zh) * 2019-05-13 2019-09-10 芜湖美的厨卫电器制造有限公司 安全阀和热水器
CN110220022B (zh) * 2019-05-13 2023-08-25 芜湖美的厨卫电器制造有限公司 安全阀和热水器
US12117851B2 (en) * 2021-07-27 2024-10-15 Qtrack Health Systems Private Limited Oxygen pressure regulating device and system

Also Published As

Publication number Publication date
CA950793A (en) 1974-07-09
NO131901C (fr) 1975-08-20
FR2101569A5 (fr) 1972-03-31
DE2134093A1 (de) 1972-01-20
DE2134093C3 (de) 1973-11-08
NO131901B (fr) 1975-05-12
DE2134093B2 (de) 1973-04-19
GB1351222A (en) 1974-04-24

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