EP0918966A1 - Outlet pressure limiting valve - Google Patents

Outlet pressure limiting valve

Info

Publication number
EP0918966A1
EP0918966A1 EP97934391A EP97934391A EP0918966A1 EP 0918966 A1 EP0918966 A1 EP 0918966A1 EP 97934391 A EP97934391 A EP 97934391A EP 97934391 A EP97934391 A EP 97934391A EP 0918966 A1 EP0918966 A1 EP 0918966A1
Authority
EP
European Patent Office
Prior art keywords
fluid flow
valve according
pressure controlling
fluid
controlling valve
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Withdrawn
Application number
EP97934391A
Other languages
German (de)
French (fr)
Inventor
Trevor Thomas Esplin
Patricia Anne Esplin
Walter George Morrison
Jean Morrison
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Australian Water Products Pty Ltd
Original Assignee
Australian Water Products Pty Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from AUPO1724A external-priority patent/AUPO172496A0/en
Priority claimed from AUPO4708A external-priority patent/AUPO470897A0/en
Application filed by Australian Water Products Pty Ltd filed Critical Australian Water Products Pty Ltd
Publication of EP0918966A1 publication Critical patent/EP0918966A1/en
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • F16K17/048—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 combined with other safety valves, or with pressure control devices
    • 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
    • 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
    • F16K17/065—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 with differential piston
    • 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
    • F16K17/28—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only
    • F16K17/30—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only 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
    • F16K37/00—Special means in or on valves or other cut-off apparatus for indicating or recording operation thereof, or for enabling an alarm to be given
    • F16K37/0008—Mechanical means
    • 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
    • G05D16/0402—Control of fluid pressure without auxiliary power with two or more controllers mounted in series
    • 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
    • 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
    • G05D16/106—Sleeve-like sensing elements; Sensing elements surrounded by the flow path

Definitions

  • fluid is often required to be delivered at a particular flow rate at a maximum set pressure regardless of the dynamic or static supply pressure of the fluid.
  • pressure regulators are normally required to be installed in order to provide the particular fluid flow requirements for these specific applications.
  • normal fluid regulators are too expensive diaphragm type regulators, the units are bulky and do not provide any method of indicating the presents of a system failure.
  • This invention relates particularly to providing an inexpensive method for the control of fluids for certain domestic and commercial uses, whereby the amount of fluid that flows through the device and the pressure of that fluid is required to be kept within certain defined limits regardless of the supply systems pressure
  • One particular application for this invention relates to the flow of water from a town water supply or similar, into water conditioning apparatus such as water filtration devices and reverse osmosis units as well as commercial or domestic hot water heaters. It has been found that for the cartridge type filters which are the plumbed in, under sink variety, for the plumbed in reverse osmosis units and for the hot water cylinder type capacity heaters, the uncontrolled or unmonitored connection to a town water supply can introduce a variety of unwanted complications to the end user of the devices which can range from the annoying to the down ⁇ ght dangerous.
  • the current invention seeks to overcome these problems by providing a simple method of monitoring the line pressure and conditioning the quantity of water which is allowed to pass through these units as well as limiting the maximum pressure which these units will experience
  • the current unit is able to provide a maximum pressure to these various water conditioning apparatus types while preventing any shock load of water hammer from passing into the units This is achieved while still providing a single or dual non-return valve check function within the unit
  • a Fluid Flow and Pressure Controlling Valve composing, a body section which has an inlet end which contains an inlet o ⁇ fice and an outlet end which contains an outlet orifice, which are separated by an interconnecting passageway
  • the interconnecting passageway comprises an arrangement of at least two boreholes which are in a stepped relationship with each other wherein the outlet side borehole is of a larger or major diameter compared to the smaller or minor diameter inlet side and the central axes of both of the different diameter boreholes are axially aligned
  • an inlet passageway connects the inlet o ⁇ fice at the inlet end at the smaller diameter of the interconnecting passageway, within the arrangement of stepped boreholes is located a stepped piston which makes a sliding and sealing contact with both internal surfaces of the major and minor diameters of the stepped boreholes, between the inlet side of the larger diameter of the stepped piston and the outlet side of the end of the smaller diameter of the stepped borehole is formed a controlling chamber
  • a valve seat component Preferably the flow controlling chamber and the stepped boreholes are cylindrical in shape
  • the inlet end contains a screwed attachment for connecting to other fluid transport mechanisms
  • the outside of the body section is basically cylmdncal in shape
  • a bleed hole in the body section which leads from the controlling chamber to the outside of the said body section
  • a sealing device which can totally block the movement of fluids from the pressure chamber flowing through the exit o ⁇ fice to the outside of the body section
  • a sealing device which can totally block the movement of fluids from the pressure chamber flowing through the exit o ⁇ fice to the outside of the body section
  • two sealing grooves Preferably located on either side of the exit o ⁇ fice of the bleed hole on the surface of the body section are two sealing grooves which are axially aligned with the central axis of the body section
  • a safety ⁇ ng is positioned such that it
  • the fluid termination pin is positioned so that it my come into contact with the valve seat component on the stepped piston
  • the valve seat component is made up of a cylindrical recess which surrounds the inlet side of the flow control passageway at the inlet side of the smaller diameter of the stepped piston into which is positioned a valve seat O-nng.
  • the stepped piston is biased towards the inlet end of the body.
  • the biasing means is a sp ⁇ ng
  • the sp ⁇ ng is a conical compression sp ⁇ ng whereby the rate of compression of the sp ⁇ ng vanes as the sp ⁇ ng moves through its range of compression
  • an increase of fluid pressure on the outlet side of the stepped piston above the combined pressure of the fluid and the pressure of the biasing means on the inlet side of the stepped piston causes the stepped piston to move towards the inlet side of the body section.
  • the fluid termination pin comes into engaging contact with the valve seat component
  • the valve shaft which can protrude proud from either end of the flow control passageway
  • the valve shaft contains a vaive seat O- ⁇ ng which can make a sealing contact with the valve seat component
  • the valve shaft is biased away from the valve seat component
  • the biasing means is a sp ⁇ ng
  • an increase of fluid pressure on the outlet side of the stepped piston above the pressure of fluid combined with the pressure of the biasing means on the inlet side of the stepped piston causes the stepped piston to move towards the inlet side of the body section
  • the valve shaft comes into an interfe ⁇ ng contact with an inlet stop component
  • the valve shaft comes into an interfe ⁇ ng contact with the inlet stop component and the stepped piston continues to move towards the inlet side of the body section, the va
  • the outlet end of the valve shaft comes into interfe ⁇ ng contact with an outlet stop component
  • the outlet end of the valve shaft's interfering contact with the outlet stop component ensures that the seal between the valve seat O- ⁇ ng and the valve seat component is broken
  • this device can be installed between a town water supply and a water conditioning apparatus in order to limit the maximum static water pressure expe ⁇ enced by such an apparatus
  • the valve mechanism can be determined to have failed
  • the body section has an external step whereby the outer diameters of the two sealing grooves are of different sizes
  • the internal section of the safety ⁇ ng has two stepped diameters which allows the safety ring to make a sealing contact with each of the sealing O
  • the stepped sections provide a stop position for the safety ⁇ ng
  • any substantial build up of fluid pressure in the bleed tube causes the safety nng to move away from the stop position
  • the indicator on the body section is revealed
  • a Fluid Flow and Pressure Controlling Valve ( 101 ) composes a body section ( 102) which has an inlet end (103) which contains an inlet o ⁇ fice ( 104) and an outlet end ( 105) which contains an outlet orifice ( 106) which are separated by an interconnecting passageway ( 107)
  • the interconnecting passageway comp ⁇ ses an arrangement of at least two boreholes which are in a stepped relationship with each other wherein the outlet side borehole ( 108) is of a larger or major diameter when compared to the smaller or minor diameter inlet side (109) and the central axes of both of the different diameter boreholes are axially aligned
  • An inlet passageway ( 1 10) connects the inlet o ⁇ fice at the inlet end of the smaller diameter of the interconnecting passageway
  • a stepped piston ( 1 1 1 ) which makes a sliding and sealing contact with both internal surfaces of the major and minor diameters of the stepped boreholes at ( 1 12) and ( 113)
  • the stepped sections provide a stop position ( 129) for the safety ring.
  • an indicator ( 130) present on the body section whereby when the safety' ring is in its stop position, the indicator is concealed. Any substantial build up of fluid pressure in the bleed tube causes the safety ring to move away from the stop position due to the different diameters of the sealing O- ⁇ ngs and the indicator is revealed.
  • a safety ring stop ( 131 ) attached to the external surface of the body section to limit the amount of travel of the safety ring when the indicator is exposed.
  • the valve mechanism can be determined to have failed.
  • a stepped projection ( 132) on the external part of the body section wherein when the safety ⁇ ng comes to rest in a home position it is prevented from any further longitudinal movement and it effectively prevents fluid in the bleed hole from communicating freely with the atmosphere.
  • a controlling ingress orifice ( 133) Located within the inlet passageway is a controlling ingress orifice ( 133) which limits the amount of fluid flowing through the device.
  • the controlling ingress orifice is the smallest in diameter and effectively limits the dynamic flow of fluid through the device by controlling the flow of fluid flowing into the device.
  • Contained within the inlet passageway is located a non-return valve (134).
  • a fluid termination pin ( 135) is located within the inlet passageway and projects into the smaller diameter of the stepped borehole.
  • the fluid termination pin has an internal passageway ( 136) which allows fluid to flow from the inlet passageway to the minor diameter of the stepped borehole and the fluid termination pin is axially aligned with the central axis of the biasing means.
  • the fluid termination pin is positioned so that it may come into contact with the valve seat component on the stepped piston.
  • the stepped piston is biased towards the outlet end of the body by means is a spring ( 137).
  • a spring 137
  • the stepped piston moves towards the inlet side of the body section.
  • the fluid termination pin comes into engaging contact with the valve seat component as is shown below the centre line in the figure.
  • Contained within the flow control passageway is a non return valve (138).
  • the section of stepped piston above the centre line shows the open position with the non-return valve in an open position as would be the case if fluid were flowing through the device.
  • the outlet has a screwed attachment ( 139) for attaching to further fluid transport mechanisms.
  • the flow control passageway is stepped and has within its length at least two different size diameters (201) and (202).
  • the flow control passageway valve shaft (203) which can protrude proud from either end of the flow control passageway.
  • the valve shaft contains a valve seat 0-ring (204) which can make a sealing contact with the valve seat component.
  • the valve shaft is biased away from the valve seat component by a sp ⁇ ng (205).
  • An increase of fluid pressure on the outlet side of the stepped piston above the pressure of fluid combined with the pressure of the biasing means on the inlet side of the stepped piston causes the stepped piston to move towards the inlet side of the body section.
  • the valve shaft comes into an interfering contact with an inlet stop component (206).
  • valve shaft's valve seat O-ring makes a sealing contact with the valve seat component (207).
  • a restriction orifice (208) On the outlet side of the stepped piston's flow control passageway is a restriction orifice (208) through which projects the outlet end of the valve shaft.
  • This device can be installed between a town water supply and a water conditioning apparatus in order to limit the maximum static water pressure experienced by such an apparatus.
  • a Fluid Flow and Pressure Controlling Valve (301 ) composes a body section (302) which has an inlet end (303) which contains an inlet o ⁇ fice (304) and an outlet end (305) which contains an outlet orifice (306) which are separated by an interconnecting passageway (307).
  • the interconnecting passageway comprises an arrangement of at least two boreholes which are in a stepped relationship with each other wherein the outlet side borehole (308) is of a larger or major diameter when compared to the smaller or minor diameter inlet side (309) and the central axes of both of the different diameter boreholes are axially aligned.
  • An inlet passageway (310) connects the inlet orifice at the inlet end of the smaller diameter of the interconnecting passageway.
  • a stepped piston (31 1 ) which makes a sliding and sealing contact with both internal surfaces of the major and minor diameters of the stepped boreholes at (312) and (313).
  • a controlling chamber (314) whose volume varies according to the position of the stepped piston within the stepped boreholes.
  • an intermediate borehole (315) can be included for ease of manufacture.
  • a retaining means 316 which limits the amount of travel of the stepped piston in a direction away from the miet end
  • a communicating passageway 318 which is positioned between passageways (310) and (317) Alternatively, the communicating passageway may be located within the non-return valve
  • the inlet end of the body section contains a screwed attachment (320) for connecting to other fluid transport mechanisms
  • a bleed hole 321
  • a sealing device which can totally block the movement of fluids from the pressure chamber flowing through the exit o ⁇ fice to the outside of the body section Located on either side of the exit orifice

Abstract

A main water supply safety valve to provide a maximum pressure to a water conditioning apparatus while preventing any shock load of water hammer from passing into the apparatus while still providing a single or dual check valve. When pressure acting on outlet side (306) of stepped piston (311) exceeds the force of spring (337) and pressure acting on the inlet side (304) of piston (311), the piston moves to shut off flow. The valve also has check valves (338 and 334) and a stepped ring (325) which moves to expose ring (330) to indicate that seals (312 and 313) have leaked or failed. In a different embodiment, the piston (311) has an internal seat (207) at the outlet end of piston bore (317) and a stepped shaft (203) in piston bore (317) biased towards the valve inlet (304). The step shoulder of shaft (203) seals against internal seat (207) when the piston (311) moves towards inlet (304) and a protruding portion of shaft (203) abuts against a stop.

Description

OUTLET PRESSURE LIMITING VALVE
In a variety of different situations, fluid is often required to be delivered at a particular flow rate at a maximum set pressure regardless of the dynamic or static supply pressure of the fluid. In the majority of such cases, pressure regulators are normally required to be installed in order to provide the particular fluid flow requirements for these specific applications However there are occasions when normal fluid regulators are too expensive diaphragm type regulators, the units are bulky and do not provide any method of indicating the presents of a system failure. Current plunger type regulators are also too bulky and rely heavily on a substantial adjustable spπng to provide the level of required protection This invention relates particularly to providing an inexpensive method for the control of fluids for certain domestic and commercial uses, whereby the amount of fluid that flows through the device and the pressure of that fluid is required to be kept within certain defined limits regardless of the supply systems pressure
BACKGROUND OF THE INVENTION
One particular application for this invention relates to the flow of water from a town water supply or similar, into water conditioning apparatus such as water filtration devices and reverse osmosis units as well as commercial or domestic hot water heaters. It has been found that for the cartridge type filters which are the plumbed in, under sink variety, for the plumbed in reverse osmosis units and for the hot water cylinder type capacity heaters, the uncontrolled or unmonitored connection to a town water supply can introduce a variety of unwanted complications to the end user of the devices which can range from the annoying to the down πght dangerous. A variety of water authorities around the world require that once fluid has passed into the various filtration chambers of water conditioning apparatus that an effective method be provided in order to prevent any back feeding of the residual sludge into the drinking water supply line. To accomplish this single or dual check valves are normally installed between the town supply and the filtration cartridges. However, it has been found that providing a set-up of this nature leads to annoying failures whereby mams pressure water is allowed to be vented in an uncontrolled manner thus causing flood type damage to the properties internal areas. This is caused by the fact that when water hammer occurs the housings which encapsulate the various filtration members momentarily become pressurised by the shock wave which caused the water hammer to occur. As the pressure in these housings πses the non-return valves prevent the pressure from being discharged back down the line. Therefore, sustained water hammer in the system can produce pressures to build up within the houses which exceed their designed capabilities. Once these housings or their seals fail, water is vented to the atmosphere in an uncontrolled manner. This normally results in much inconvenience to the householder as well as various insurance claims in order to rectify the resultant damage. The current invention seeks to overcome these problems by providing a simple method of monitoring the line pressure and conditioning the quantity of water which is allowed to pass through these units as well as limiting the maximum pressure which these units will experience
BRIEF DESCRIPTION OF THE INVENTION
It will be noted from the following descπptions that the current unit is able to provide a maximum pressure to these various water conditioning apparatus types while preventing any shock load of water hammer from passing into the units This is achieved while still providing a single or dual non-return valve check function within the unit
The above flow performance requirements are achieved by providing a Fluid Flow and Pressure Controlling Valve composing, a body section which has an inlet end which contains an inlet oπfice and an outlet end which contains an outlet orifice, which are separated by an interconnecting passageway, the interconnecting passageway comprises an arrangement of at least two boreholes which are in a stepped relationship with each other wherein the outlet side borehole is of a larger or major diameter compared to the smaller or minor diameter inlet side and the central axes of both of the different diameter boreholes are axially aligned, an inlet passageway connects the inlet oπfice at the inlet end at the smaller diameter of the interconnecting passageway, within the arrangement of stepped boreholes is located a stepped piston which makes a sliding and sealing contact with both internal surfaces of the major and minor diameters of the stepped boreholes, between the inlet side of the larger diameter of the stepped piston and the outlet side of the end of the smaller diameter of the stepped borehole is formed a controlling chamber whose volume vanes according to the position of the stepped piston within the stepped boreholes, located near the outlet end of the major diameter borehole is a retaining means which limits the amount of travel of the stepped piston in a direction away from the inlet end Preferably located within the length of the stepped piston is a flow control passageway Preferably the flow control passageway is located along the central axis of the stepped piston. Preferably located in the stepped piston in cooperation with the flow control passageway is a valve seat component Preferably the flow controlling chamber and the stepped boreholes are cylindrical in shape Preferably the inlet end contains a screwed attachment for connecting to other fluid transport mechanisms Preferably the outside of the body section is basically cylmdncal in shape Preferably between the sliding and sealing contacts of the major and minor diameters of the stepped piston is a bleed hole in the body section which leads from the controlling chamber to the outside of the said body section Preferably located in conjunction with the bleed hole is a sealing device which can totally block the movement of fluids from the pressure chamber flowing through the exit oπfice to the outside of the body section Preferably located on either side of the exit oπfice of the bleed hole on the surface of the body section are two sealing grooves which are axially aligned with the central axis of the body section Preferably located within each of the sealing grooves is an sealing O-ring Preferably a safety πng is positioned such that it makes a sliding and sealing contact with the O-πngs in the two sealing grooves Preferably there is a stepped projection on the external pan of the body section wherein when the safety πng comes to rest in a home position it is prevented from any further longitudinal movement and it effectively prevents fluid in the bleed hole from communicating freely with the atmosphere Preferably located within the mlet passageway is a controlling ingress oπfice Preferably of all of the vaπous internal fluid passageways within this device, the controlling ingress oπfice is the smallest in diameter and effectively limits the dynamic flow of fluid through the device by controlling the flow of fluid flowing into the device Preferably the flow control passageway is stepped and has within its length at least two different size diameters Preferably contained within the inlet passageway is located an inlet valve seat Preferably contained within the inlet passageway and located on the outlet side of the inlet valve seat is an inlet non-return valve Preferably a fluid termination pin is located within the inlet passageway and projects into the smaller diameter of the stepped borehole Preferably a fluid termination shaft is iocated at the smaller diameter end of the stepped piston and projects into the smaller diameter of the stepped borehole Preferably the fluid termination shaft and the stepped piston are of unitary construction Preferably the fluid termination pin has an internal passageway which allows fluid to flow from the inlet passageway to the minor diameter of the stepped borehole Preferably the fluid termination shaft has an internal passageway which allows fluid to flow from the inlet passageway to the minor diameter of the stepped borehole Preferably the fluid termination pin is axially aligned with the central axis of the biasing means Preferably the fluid termination shaft is axially aligned with the central axis of the biasing means Preferably the fluid termination shaft can make a sealing contact with the inlet valve seat Preferable the fluid termination shaft can make interfeπng contact with the inlet non-return valve which causes it to have a sealing contact with the inlet valve seat. Preferably the fluid termination pin is positioned so that it my come into contact with the valve seat component on the stepped piston Preferably the valve seat component is made up of a cylindrical recess which surrounds the inlet side of the flow control passageway at the inlet side of the smaller diameter of the stepped piston into which is positioned a valve seat O-nng. Preferably the stepped piston is biased towards the inlet end of the body. Preferably the biasing means is a spπng Preferably the spπng is a conical compression spπng whereby the rate of compression of the spπng vanes as the spπng moves through its range of compression Preferably an increase of fluid pressure on the outlet side of the stepped piston above the combined pressure of the fluid and the pressure of the biasing means on the inlet side of the stepped piston, causes the stepped piston to move towards the inlet side of the body section. Preferably as the stepped piston moves fully to the inlet side of the body section the fluid termination pin comes into engaging contact with the valve seat component Preferably within the flow control passageway is a valve shaft which can protrude proud from either end of the flow control passageway Preferably the valve shaft contains a vaive seat O-πng which can make a sealing contact with the valve seat component Preferably the valve shaft is biased away from the valve seat component Preferably the biasing means is a spπng Preferably an increase of fluid pressure on the outlet side of the stepped piston above the pressure of fluid combined with the pressure of the biasing means on the inlet side of the stepped piston causes the stepped piston to move towards the inlet side of the body section Preferably when the stepped piston moves towards the inlet side of its limit of travel, the valve shaft comes into an interfeπng contact with an inlet stop component Preferably when the valve shaft comes into an interfeπng contact with the inlet stop component and the stepped piston continues to move towards the inlet side of the body section, the vaive shaft's valve seat O-πng makes a sealing contact with the valve seat component Preferably on the outlet side of the stepped piston's flow control passageway is a restriction oπfice through which projects the outlet end of the valve shaft Preferably, when the fluid pressure on the outlet side of the stepped piston is less than the pressure of the fluid combined with the pressure of the biasing means on the inlet side of the stepped piston causes the stepped piston to move towards the outlet side of the body section. Preferably as the stepped piston moves towards the outlet end of the body section the outlet end of the valve shaft comes into interfeπng contact with an outlet stop component Preferably as the stepped piston arπves at its limit of travel at the outlet end of the of the body section, the outlet end of the valve shaft's interfering contact with the outlet stop component ensures that the seal between the valve seat O-πng and the valve seat component is broken Preferably this device can be installed between a town water supply and a water conditioning apparatus in order to limit the maximum static water pressure expeπenced by such an apparatus Preferably should any fluid discharge occur from the bleed hole when any substantial external manual movement of the safety πng happens which is sufficient enough to expose one of the two sealing O-πngs, the valve mechanism can be determined to have failed Preferably the body section has an external step whereby the outer diameters of the two sealing grooves are of different sizes Preferably the internal section of the safety πng has two stepped diameters which allows the safety ring to make a sealing contact with each of the sealing O-πngs. Preferably and when the safety πng is in its sealing position the stepped sections provide a stop position for the safety πng Preferably there is an indicator present on the body section whereby when the safety πng is in its stop position, the indicator is concealed Preferably any substantial build up of fluid pressure in the bleed tube causes the safety nng to move away from the stop position Preferably when the safety πng moves away from the stop position the indicator on the body section is revealed
DESCRIPTION OF THE DRAWINGS
A fuller explanation can be given by way of reference to the following drawings where Figure 1 and 3 show two preferred embodiments suitable for controlling the supply of water to water filters and other similar water conditioning devices, Figure 2 shows one preferred embodiment suitable for controlling the supply of water to hot water systems and the like It should be noted that these are only two general topics and that the devices do have wider applications however, for simplicity they will be descπbed hereinafter as being applicable for those applications
In Figure 1 , a Fluid Flow and Pressure Controlling Valve ( 101 ) composes a body section ( 102) which has an inlet end (103) which contains an inlet oπfice ( 104) and an outlet end ( 105) which contains an outlet orifice ( 106) which are separated by an interconnecting passageway ( 107) The interconnecting passageway compπses an arrangement of at least two boreholes which are in a stepped relationship with each other wherein the outlet side borehole ( 108) is of a larger or major diameter when compared to the smaller or minor diameter inlet side (109) and the central axes of both of the different diameter boreholes are axially aligned An inlet passageway ( 1 10) connects the inlet oπfice at the inlet end of the smaller diameter of the interconnecting passageway Within the arrangement of stepped boreholes is located a stepped piston ( 1 1 1 ) which makes a sliding and sealing contact with both internal surfaces of the major and minor diameters of the stepped boreholes at ( 1 12) and ( 113) Between the inlet side of the larger diameter of the stepped piston and the outlet side of the end of the smaller diameter of the stepped borehole is formed a controlling chamber ( 1 14) whose volume vanes according to the position of the stepped piston within the stepped boreholes It should be noted that an intermediate borehole (115) can be included for ease of manufacture Located near the outlet end of the major diameter borehole is a retaining means ( 1 16) which limits the amount of travel of the stepped piston m a direction away from the inlet end Located within the length of the stepped piston is a flow control passageway ( 1 17) and is aligned with its central axis Located on the stepped piston in cooperation with the flow control passageway is a valve seat component which in this case is an O-ring ( 1 18) which is positioned within a recess ( 119) on the inlet end of the stepped piston The inlet end of the body section contains a screwed attachment ( 120) for connecting to other fluid transpoπ mechanisms Between the sliding and sealing contacts of the major and minor diameters of the stepped piston is a bleed hole ( 121 ) in the body section which leads from the controlling chamber to the outside of the said body section Located in conjunction with the bleed hole is a sealing device which can totally block the movement of fluids from the pressure chamber flowing through the exit oπfice to the outside of the body section Located on either side of the exit orifice ( 122) of the bleed hole on the surface of the body section are two sealing grooves which are axially aligned with the central axis of the body section and within each is contained an O-πng ( 123) and ( 124) A safety ring ( 125) is positioned such that it makes a sliding and sealing contact with the O-πngs in the two sealing grooves In one preferred embodiment shown here, the body section has an external step (126) whereby the outer diameters of the two sealing grooves are of different sizes The internal section of the safety ring has two matching stepped diameters ( 127) and ( 128) which allow the safety ring to make a sealing contact with each of the sealing O-rings. When the safety ring is in its sealing position the stepped sections provide a stop position ( 129) for the safety ring. There is an indicator ( 130) present on the body section whereby when the safety' ring is in its stop position, the indicator is concealed. Any substantial build up of fluid pressure in the bleed tube causes the safety ring to move away from the stop position due to the different diameters of the sealing O-πngs and the indicator is revealed There is a safety ring stop ( 131 ) attached to the external surface of the body section to limit the amount of travel of the safety ring when the indicator is exposed. In another preferred embodiment wherein the two sealing O-rings are the same size, should any fluid discharge occur from the bleed hole when any substantial external manual movement of the safety ring happens which is sufficient enough to expose one of the two sealing O-πngs, the valve mechanism can be determined to have failed. In this case, there is a stepped projection ( 132) on the external part of the body section wherein when the safety πng comes to rest in a home position it is prevented from any further longitudinal movement and it effectively prevents fluid in the bleed hole from communicating freely with the atmosphere. Located within the inlet passageway is a controlling ingress orifice ( 133) which limits the amount of fluid flowing through the device. It should be noted in one preferred embodiment, of all of the various internal fluid passageways within this device, the controlling ingress orifice is the smallest in diameter and effectively limits the dynamic flow of fluid through the device by controlling the flow of fluid flowing into the device. Contained within the inlet passageway is located a non-return valve (134). A fluid termination pin ( 135) is located within the inlet passageway and projects into the smaller diameter of the stepped borehole. The fluid termination pin has an internal passageway ( 136) which allows fluid to flow from the inlet passageway to the minor diameter of the stepped borehole and the fluid termination pin is axially aligned with the central axis of the biasing means. The fluid termination pin is positioned so that it may come into contact with the valve seat component on the stepped piston. The stepped piston is biased towards the outlet end of the body by means is a spring ( 137). When an increase of fluid pressure on the outlet side of the stepped piston occurs above the combined pressure of the fluid and the pressure of the biasing means on the inlet side of the stepped piston, the stepped piston moves towards the inlet side of the body section. As the stepped piston moves fully to the inlet side of the body section the fluid termination pin comes into engaging contact with the valve seat component as is shown below the centre line in the figure. Contained within the flow control passageway is a non return valve (138). The section of stepped piston above the centre line shows the open position with the non-return valve in an open position as would be the case if fluid were flowing through the device. The outlet has a screwed attachment ( 139) for attaching to further fluid transport mechanisms.
In Figure 2, the flow control passageway is stepped and has within its length at least two different size diameters (201) and (202). The flow control passageway valve shaft (203) which can protrude proud from either end of the flow control passageway. The valve shaft contains a valve seat 0-ring (204) which can make a sealing contact with the valve seat component. The valve shaft is biased away from the valve seat component by a spπng (205). An increase of fluid pressure on the outlet side of the stepped piston above the pressure of fluid combined with the pressure of the biasing means on the inlet side of the stepped piston causes the stepped piston to move towards the inlet side of the body section. When the stepped piston moves towards the inlet side of its limit of travel, the valve shaft comes into an interfering contact with an inlet stop component (206). When the valve shaft comes into an interfering contact with the inlet stop component and the stepped piston continues to move towards the inlet side of the body section, the valve shaft's valve seat O-ring makes a sealing contact with the valve seat component (207). On the outlet side of the stepped piston's flow control passageway is a restriction orifice (208) through which projects the outlet end of the valve shaft. When the fluid pressure on the outlet side of the stepped piston is less than the pressure of the fluid combined with the pressure of the biasing means on the inlet side of the stepped piston causes the stepped piston to move towards the outlet side of the body section. As the stepped piston moves towards the outlet end of the body section the outlet end of the valve shaft comes into interfeπng contact with an outlet stop component (209). As the stepped piston arrives at its limit of travel at the outlet end of the of the body section, the outlet end of the valve shaft's interfering contact with the outlet stop component ensures that the seal between the valve seat O-ring and the valve seat component is broken as is shown above the centre line. This device can be installed between a town water supply and a water conditioning apparatus in order to limit the maximum static water pressure experienced by such an apparatus.
In Figure 3, a Fluid Flow and Pressure Controlling Valve (301 ) composes a body section (302) which has an inlet end (303) which contains an inlet oπfice (304) and an outlet end (305) which contains an outlet orifice (306) which are separated by an interconnecting passageway (307). The interconnecting passageway comprises an arrangement of at least two boreholes which are in a stepped relationship with each other wherein the outlet side borehole (308) is of a larger or major diameter when compared to the smaller or minor diameter inlet side (309) and the central axes of both of the different diameter boreholes are axially aligned. An inlet passageway (310) connects the inlet orifice at the inlet end of the smaller diameter of the interconnecting passageway. Within the arrangement of stepped boreholes is located a stepped piston (31 1 ) which makes a sliding and sealing contact with both internal surfaces of the major and minor diameters of the stepped boreholes at (312) and (313). Between the inlet side of the larger diameter of the stepped piston and the outlet side of the end of the smaller diameter of the stepped borehole is formed a controlling chamber (314) whose volume varies according to the position of the stepped piston within the stepped boreholes. It should be noted that an intermediate borehole (315) can be included for ease of manufacture. Located near the outlet end of the major diameter borehole is a retaining means (316) which limits the amount of travel of the stepped piston in a direction away from the miet end A flow control passagewav (317) and is axially aligned with the central axis of the stepped piston and may be located within its length Located on the inlet side of the stepped piston is a communicating passageway (318) which is positioned between passageways (310) and (317) Alternatively, the communicating passageway may be located within the non-return valve The inlet end of the body section contains a screwed attachment (320) for connecting to other fluid transport mechanisms Between the sliding and sealing contacts of the major and minor diameters of the stepped piston is a bleed hole (321 ) in the body section which leads from the controlling chamber to the outside of the said body section Located in conjunction with the bleed hole is a sealing device which can totally block the movement of fluids from the pressure chamber flowing through the exit oπfice to the outside of the body section Located on either side of the exit orifice (322) of the bleed hole on the surface of the body section are two sealing grooves which are axially aligned with the central axis of the body section and within each is contained an O-πng (323) and (324) A safety πng (325) is positioned such that it makes a sliding and sealing contact with the O-nngs in the two sealing grooves In one preferred embodiment shown here, the body section has an external step (326) whereby the outer diameters of the two sealing grooves are of different sizes The internal section of the safety ring has two matching stepped diameters (327) and (328) which allow the safety ring to make a sealing contact with each of the sealing O-πngs When the safety nng is in its sealing position the stepped sections provide a stop position (329) for the safety ring There is an indicator (330) present on the body section whereby when the safety πng is in its stop position, the indicator is concealed Any substantial build up of fluid pressure in the bleed tube causes the safety πng to move away from the stop position due to the different diameters of the sealing O-πngs and the indicator is revealed There is a safety πng stop (331 ) attached to the external surface of the body section to limit the amount of travel of the safety πng when the indicator is exposed In another preferred embodiment wherein the two sealing O-nngs are the same size, should any fluid discharge occur from the bleed hole when any substantial external manual movement of the safety πng happens which is sufficient enough to expose one of the two sealing O-πngs, the valve mechanism can be determined to have failed In this case, there is a stepped projection (332) on the external part of the body section wherein when the safety' πng comes to rest in a home position it is prevented from any further longitudinal movement and it effectively prevents fluid in the bleed hole from communicating freely with the atmosphere Located within the inlet passageway is a controlling ingress oπfice (333) which limits the amount of fluid flowing through the device It should be noted in one preferred embodiment, of all of the vaπous internal fluid passageways within this device, the controlling ingress oπfice is the smallest in diameter and effectively limits the dynamic flow of fluid through the device by controlling the flow of fluid flowing into the device Contained within the inlet passageway is located a non-return valve (334) A fluid termination shaft (335) is located within the inlet passageway and projects towards the inlet passageway nonreturn valve The fluid termination shaft has an internal passageway (336) The fluid termination shaft is positioned so that it may come into contact with the inlet passageway non-return valve The stepped piston is biased towards the outlet end of the body by means is a spπng (337) When an increase of fluid pressure on the outlet side of the larger diameter stepped piston occurs above the combined pressure of the fluid and the pressure of the biasing means on the inlet side of the smaller diameter of the stepped piston and the fluid pressure on the inlet side of the inlet passageway non-return valve, the stepped piston moves towards the inlet side of the body section As the stepped piston moves fully to the inlet side of the body section the fluid termination shaft comes into engaging contact with the inlet passageway non-return valve and forces it to its closed position as is shown below the centre line in the figure Contained within the flow control passageway of the movable piston is a second non return valve (338) The section of stepped piston above the centre line shows the open position with the non-return valve in an open position as would be the case if fluid were flowing through the device The outlet has a screwed attachment (339) for attaching to further fluid transport mechanisms

Claims

THE CLAIMS DEFINING THE INVENTION ARE AS FOLLOWS:
1 A Fluid Flow and Pressure Controlling Valve compπsing, a body section which has an inlet end which contains an inlet oπfice and an outlet end which contains an outlet oπfice, which are separated by an interconnecting passageway, the interconnecting passageway composes an arrangement of at least two boreholes which are in a stepped relationship with each other wherein the outlet side borehole is of a larger or major diameter compared to the smaller or minor diameter inlet side and the central axes of both of the different diameter boreholes are axially aligned, an inlet passageway connects the inlet orifice at the inlet end to the smaller diameter of the interconnecting passageway, within the arrangement of stepped boreholes is located a stepped piston which makes a sliding and sealing contact with both internal surfaces of the major and minor diameters of the stepped boreholes, between the inlet side of the larger diameter of the stepped piston and the outlet side of the end of the smaller diameter of the stepped borehole is formed a controlling chamber whose volume varies according to the position of the stepped piston within the stepped boreholes, located near the outlet end of the major diameter borehole is a retaining means which limits the amount of travel of the stepped piston in a direction away from the inlet end
2 A Fluid Flow and Pressure Controlling Valve according to claim 1 wherein, a flow control passageway is axially aligned with the central axis of the stepped piston
3 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, the flow control passageway is located within the length of the stepped piston 4 A Fluid Flow and Pressure Controlling Valve according to anv of the previous claims wherein, located in the stepped piston in cooperation with the flow control passageway is a valve seat component
5 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, the flow controlling chamber and the stepped boreholes are cy ndπcal in shape 6 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, the inlet end contains a screwed attachment for connecting to other fluid transport mechanisms
7 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, the outside of the body section is basically cylindπcal in shape 8 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, between the sliding and sealing contacts of the major and minor diameters of the stepped piston is a bleed hole in the body section which leads from the controlling chamber to the outside of the said body section 9 A Fluid Flow and Pressure Controlling Valve according to anv of the previous claims wherein, located in conjunction with the bleed hole is a sealing device which can totally block the movement of fluids from the pressure chamber flowing through the exit oπfice to the outside of the body section
10 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein located on either side of the exit oπfice of the bleed hole on the surface of the body section are two sealing grooves which are axially aligned with the central axis of the body section
1 1 A Fluid Flow and Pressure Controlling Valve according to claim 10 wherein, located within each of the sealing grooves is an sealing O-πng 12 A Fluid Flow and Pressure Controlling Valve according to either of the claims 10 or 1 1 wherein, a safety ring is positioned such that it makes a sliding and sealing contact with the O-πngs in the two sealing grooves
13 A Fluid Flow and Pressure Controlling Valve according to any of the claims 10 to 12 wherein, there is a stepped projection on the external part of the body section wherein when the safety ong comes to rest in a home position it is prevented from any further longitudinal movement and it effectively prevents fluid in the bleed hole from communicating freely with the atmosphere
14 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein located withm the inlet passageway is a controlling ingress oπfice 15 A Fluid Flow and Pressure Controlling Valve according to claim 14 wherein, of all of the vaπous internal fluid passageways within this device, the controlling ingress oofice is the smallest in diameter and effectively limits the dynamic flow of fluid through the device by restricting the flow of fluid flowing into the device
16 A Fluid Flow and Pressure Controlling Valve according to any of the claims 1 to 15 wherein the flow control passageway is stepped and has within its length at least two different size diameters
17 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, contained within the mlet passageway is an inlet valve seat
18 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, contained withm the mlet passageway and located on the outlet side of the mlet valve seat is an inlet non-return valve
19 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, a fluid termination pin is located near the mlet passageway and projects into the smaller diameter of the stepped borehole 20 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, a fluid termination shaft is located at the smaller diameter end of the stepped piston and projects into the smaller diameter of the stepped borehole
21 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein the fluid termination shaft and the stepped piston are of unitary construction
22. A Fluid Flow and Pressure Controlling Valve according to claim 19 wherein, the fluid termination pin has an internal passageway which allows fluid to flow from the inlet passageway to the minor diameter of the stepped borehole.
23. A Fluid Flow and Pressure Controlling Valve according to claim 20 wherein, the fluid termination shaft has an internal passageway which allows fluid to flow from the inlet passageway to the minor diameter of the stepped borehole.
24. A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, the fluid termination pin is axially aligned with the central axis of the biasing means.
25. A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, the fluid termination shaft is axially aligned with the central axis of the biasing means.
26. A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, the fluid termination shaft can make a sealing contact with the inlet valve seat.
27. A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, the fluid termination shaft can make interfering contact with the inlet non-return valve which causes it to have a sealing contact with the inlet valve seat.
28. A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, the fluid termination pin is positioned so that it my come into contact with the valve seat component on the stepped piston. 29. A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, the valve seat component is made up of a cylindrical recess which suπounds the inlet side of the flow control passageway at the inlet side of the smaller diameter of the stepped piston into which is positioned a valve seat O-ring.
30. A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, the stepped piston is biased towards the outlet end of the body.
31. A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, the biasing means is a spring.
32. A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, the spring is a conical compression spring whereby the rate of compression of the spring varies as the spring moves through its range of compression.
33. A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, an increase of fluid pressure on the outlet side of the stepped piston above the combined pressure of the fluid and the pressure of the biasing means on the inlet side of the stepped piston, causes the stepped piston to move towards the inlet side of the body section. 34. A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, as the stepped piston moves fully to the inlet side of the body section the fluid termination pin comes into engaging contact with the valve seat component. 35. A Fluid Flow and Pressure Controlling Valve according to any of the claims 1 to 15 wherein, within the flow control passageway is a valve shaft which can protrude proud from either end of the flow control passagewav
36 A Fluid Flow and Pressure Controlling Valve according to claim 35 wherein, the valve shaft contains a valve seat O-πng which can make a sealing contact with the valve seat component 37 A Fluid Flow and Pressure Controlling Valve according to any of the claims 35 to 36 wherein, the valve shaft is biased away from the valve seat component
38 A Fluid Flow and Pressure Controlling Valve according to claim 37 wherein, the biasing means is a spπng
39 A Fluid Flow and Pressure Controlling Valve according to any of the claims 35 to 38 wherein, an increase of fluid pressure on the outlet side of the stepped piston above the pressure of fluid combined with the pressure of the biasing means on the inlet side of the stepped piston causes the stepped piston to move towards the inlet side of the body section
40 A Fluid Flow and Pressure Controlling Valve according to any of the claims 35 to 39 wherein, when the stepped piston moves towards the inlet side of its limit of travel, the valve shaft comes into an interfering contact with an inlet stop component
41 A Fluid Flow and Pressure Controlling Valve according to any of the claims 35 to 40 wherein, when the vaive shaft comes into an interfeπng contact with the inlet stop component and the stepped piston continues to move towards the mlet side of the body section, the valve shaft's valve seat O-πng makes a sealing contact with the valve seat component 42 A Fluid Flow and Pressure Controlling Valve according to any of the claims 35 to 41 wherein, on the outlet side of the stepped piston's flow control passageway is a restπction oπfice through which projects the outlet end of the valve shaft
43 A Fluid Flow and Pressure Controlling Valve according to any of the claims 35 to 42 wherein, when the fluid pressure on the outlet side of the stepped piston is less than the pressure of the fluid combined with the pressure of the biasing means on the inlet side of the stepped piston causes the stepped piston to move towards the outlet side of the body section
44 A Fluid Flow and Pressure Controlling Valve according to any of the claims 35 to 43 wherein, as the stepped piston moves towards the outlet end of the body section the outlet end of the valve shaft comes into interfeπng contact with an outlet stop component 45 A Fluid Flow and Pressure Controlling Valve according to any of the claims 35 to 44 wherein, as the stepped piston arπves at its limit of travel at the outlet end of the of the body section, the outlet end of the valve shaft's interfering contact with the outlet stop component ensures that the seal between the valve seat O-πng and the valve seat component is broken
46 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, this device can be installed between a town water supply and a water conditioning apparatus in order to limit the maximum static water pressure expeπenced by such an apparatus
47 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, should any fluid discharge occur from the bleed hole when any substantial external manual movement of the safety πng happens which is sufficient enough to expose one of the two sealing O-πngs, the valve mechanism can be determined to have failed
48 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, the body section has an external step whereby the outer diameters of the two sealing grooves are of different sizes
49 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, the internal section of the safety πng has two stepped diameters which allow the safety ring to make a sealing contact with each of the sealing O-πngs
50 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, when the safety ring is in its sealing position the stepped sections provide a stop position for the safety πng
51 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, there is an indicator present on the body section whereby when the safety πng is in its stop position, the indicator is concealed 52 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, any substantial build up of fluid pressure in the bleed tube causes the safety πng to move away from the stop position
53 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, when the safety ring moves away from the stop position the indicator on the body section is revealed
54 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, there is a safety πng stop attached to the external surface of the body section to limit the amount of travel of the safety πng when the indicator is exposed
55 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, when the safety πng moves away from the stop position and the indicator on the body section is revealed, a sever restπction to the fluid flow occurs
56 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, the inlet end non-return valve contains a communicating passageway which allows fluid to flow through it to the flow control passageway located within the termination shaft 57 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, at the inlet end of the inlet non-return valve is located an o-nng which can make a sealing contact with the inlet valve seat
58 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, upstream of the inlet oπfice is a secondary shut-off valve 59 A Fluid Flow and Pressure Controlling Valve according to any of the previous claims wherein, the secondary shut-off valve is a ball valve
EP97934391A 1996-08-19 1997-08-19 Outlet pressure limiting valve Withdrawn EP0918966A1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
AUPO1724/96 1996-08-19
AUPO1724A AUPO172496A0 (en) 1996-08-19 1996-08-19 An improved fluid flow control valve
AUPO4708/97 1997-01-20
AUPO4708A AUPO470897A0 (en) 1997-01-20 1997-01-20 Improved fluid control valves
PCT/AU1997/000526 WO1998008012A1 (en) 1996-08-19 1997-08-19 Outlet pressure limiting valve

Publications (1)

Publication Number Publication Date
EP0918966A1 true EP0918966A1 (en) 1999-06-02

Family

ID=25645244

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97934391A Withdrawn EP0918966A1 (en) 1996-08-19 1997-08-19 Outlet pressure limiting valve

Country Status (3)

Country Link
EP (1) EP0918966A1 (en)
CA (1) CA2264067A1 (en)
WO (1) WO1998008012A1 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7182896B2 (en) 2002-03-19 2007-02-27 Jsp Corporation Composite foamed polypropylene resin molding and method of producing same
CN106246097A (en) * 2016-11-01 2016-12-21 山东中瑞工程机械有限公司 The top connection device of down-the-hole air hammer
CN106246098A (en) * 2016-11-01 2016-12-21 山东中瑞工程机械有限公司 There is the inner casing formula down-the-hole air hammer being automatically adjusted capacity function

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5996632A (en) * 1998-12-14 1999-12-07 Aeroquip Corporation Pressure relief adapter
FR2818727B1 (en) * 2000-12-21 2004-12-17 Taema OPENING AMPLIFICATION VALVE AND PRESSURE REGULATOR PROVIDED WITH SUCH A VALVE
EP1509714B1 (en) 2002-05-06 2008-04-02 Walter George Morrison Pressure control valve
CN100390523C (en) * 2004-03-25 2008-05-28 上海交通大学 Small thrust straight pushing type dwell check valve under condition of ultrahigh pressure environment
US7213611B2 (en) * 2004-12-15 2007-05-08 Eaton Corporation Valve assembly
GB0428167D0 (en) * 2004-12-23 2005-01-26 Evolve Paintball Ltd Gas Pressure Regulator
FR2883621B1 (en) * 2005-03-25 2008-09-26 Staubli Faverges Sca OVERPRESSURE PROTECTION DEVICE AND CONNECTION SUBASSEMBLY HAVING APPLICATION
US8097156B2 (en) 2005-07-20 2012-01-17 3M Innovative Properties Company Fluid filtration system
KR101667065B1 (en) 2008-09-16 2016-10-24 쓰리엠 이노베이티브 프로퍼티즈 컴파니 Filter cartridge and system using linear actuation
DE102011106265A1 (en) * 2011-05-12 2012-11-15 Honeywell Technologies Sarl Device for handling a liquid medium
ITMI20121186A1 (en) * 2012-07-06 2014-01-07 Bome S R L PRESSURE CONTROL VALVE
JP2016181085A (en) * 2015-03-24 2016-10-13 兼工業株式会社 Proportioning pressure reducing valve for city water
CN107676326A (en) * 2017-11-23 2018-02-09 王雅莲 Automatically the overflow valve calibrated
CN107676327A (en) * 2017-11-23 2018-02-09 王雅莲 Automatically the adjustable overflow valve calibrated
CN112682547B (en) * 2021-01-18 2023-04-11 中国电子科技集团公司第二十九研究所 Self-adaptive pressure relief and liquid containing device of penetrating liquid cooling case of electronic equipment

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3848631A (en) * 1970-10-26 1974-11-19 Draft Systems Beer keg protective device
US3995656A (en) * 1972-02-15 1976-12-07 Lif-O-Gen, Inc. High pressure gas regulator
US3890999A (en) * 1972-12-15 1975-06-24 Eugene D Moskow Fluid pressure regulator
JPS568781B2 (en) * 1974-05-07 1981-02-25
US4412702A (en) * 1981-05-21 1983-11-01 The Bendix Corporation Fluid pressure proportioning valve and plug member therefor
US4561465A (en) * 1983-09-06 1985-12-31 Aeroquip Corporation Axial flow pressure regulator
US4655246A (en) * 1983-09-30 1987-04-07 Essex Industries, Inc. Regulated gas flow control valve
NO154239C (en) * 1984-04-12 1986-08-13 Bryne Mek Verksted As TURNING VALVE.
AU602199B2 (en) * 1987-03-20 1990-10-04 Gsa Industries (Aust.) Pty Ltd Pressure control valve
FR2628229A1 (en) * 1988-03-04 1989-09-08 Peugeot Flow regulator for viscous material - includes mobile piston in chamber with bias spring controlling flow e.g. for mastic

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9808012A1 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7182896B2 (en) 2002-03-19 2007-02-27 Jsp Corporation Composite foamed polypropylene resin molding and method of producing same
CN106246097A (en) * 2016-11-01 2016-12-21 山东中瑞工程机械有限公司 The top connection device of down-the-hole air hammer
CN106246098A (en) * 2016-11-01 2016-12-21 山东中瑞工程机械有限公司 There is the inner casing formula down-the-hole air hammer being automatically adjusted capacity function

Also Published As

Publication number Publication date
CA2264067A1 (en) 1998-02-26
WO1998008012A1 (en) 1998-02-26

Similar Documents

Publication Publication Date Title
EP0918966A1 (en) Outlet pressure limiting valve
US6374852B1 (en) Leak arresting valve
AU2004239252B2 (en) Excess flow shutoff
US6513545B2 (en) Safety valve with adjustable maximum flow shut off mechanism
EP1672259B1 (en) Safety valve assembly
CA2298377A1 (en) Fluid flow valve with variable flow rate
US3583431A (en) Pressure relief valve
CN113906246A (en) Check valve
CA2360706A1 (en) Pressure relief valve
US20160153572A1 (en) Non chattering pressure relief valve
WO2008021963A2 (en) Hydraulic system safety shut off valve
EP4089315A1 (en) Multi-function three-stage pressure regulator
US3389796A (en) Balanced pressure relief valve
US4159025A (en) Back flow preventer valve
CN105247260B (en) Main stage straight-through type pressure control cartridge valve
US3621872A (en) Safety valve
CA2138946A1 (en) Pressure Relief Valve
US4625756A (en) Pilot operated relief valve
US5391209A (en) Method for controlling overpressurization in a gas line
AU3763497A (en) Outlet pressure limiting valve
US4343328A (en) Flow sensing check valve
US5425396A (en) Water pressure level control valve
US20020078993A1 (en) Valve with wider opening and pressure regulator equipped with such a valve
US3709241A (en) Fill limiter, check and safety valve
AU775408B2 (en) Outlet pressure limiting valve

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19990319

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20020301