ANTI HAMMER PILOT OPERATED VALVES HAVING REMOTE PILOT FOR USE IN REFUELLING, DOMESTIC MAINS WATER, REFRIGERATION APPLICATIONS

Abstract: A pilot operated valve having an inlet passageway (8) surrounded by an annular seat (6) surrounded by an outlet passageway (110) respectively. The main valve member (7) having turbulence shield (11) of greater diameter than the external diameter of the seat (113) and deflector plate (34). Turbulence shield (11) slows the descent of the valve during closing and prevents water hammer. Pressure chamber inlet (37 or 14) may have a check valve (15 or 21 respectively). Trigger passageway (17) is remotely operated depending on the application. For example a latching solenoid arrangement (figs. 3 to 7), float (figs. 10 and 11), handle or pressure balanced piston (fig. 15). The latching arrangement involves two solenoids with interacting armatures. As a refuelling valve trigger passageway (17) has a first pilot valve at a distal end opened upon coupling to the destination tank to vent the pilot chamber (12) and open main valve (7). A float comprises a second pilot valve which closes the trigger passageway prior to disengagement of the coupling to trigger the closing ot the main valve (6). A third manually operated pilot valve may be located on the main valve body. As a faucet valve (fgs. 12 to 14) the main valve resides under the counter and the pilot above. In one such arrangement the passageway (17) is concentric with the outlet (10), in another the pressure chamber inlet (14) and trigger (17) passageways are concentric. The pressure chamber (12) and outlet (10) may be concentric and in line (fig. 12).

Description: ANTI HAMMER PILOT OPERATED VALVES HAVING REMOTE PILOT FOR USE IN REFUELLING, DOMESTIC MAINS WATER, REFRIGERATION APPLICATIONS The original intention of this invention was to directly address several of the problems associated with conventional type diaphragm solenoid valves which are currently available on the market today This invention has particular application to those situations which require silent operation with a soft closing of the shut-off device without producing the annoying effect sometimes known in water type applications as "water hammer " Water hammer occurs where the sudden closing of a valve produces a momentary high pressure shock wave to the fluid upstream of the valve and/or a momentary low pressure shock wave m the fluid downstream of the valve This invention also has particular relevance to those applications which require high flow rates, remote triggering, where nil electnc power consumption is needed while the fluid is either flowing or when the fluid flow has been terminated and where a long service life is desired It also encompasses those applications where continually energised solenoids are not appropπate and where the activation of the mechanism to change the operational state of the valve rely on nothing more than the design of the valve and/or the pressure of the fluid that the valve is controlling In one of its many and vaπed forms, this invention includes a single signal latching system for activating and deactivating the tπggeπng device In another form includes a vibration sensing tπggenng latch device which will terminate the flow of a volatile fluid such as Natural Gas or Liquid Petroleum Gas (LPG) in either its liquid or gaseous state should an unsafe condition such as an earthquake above a predetermined magnitude occur It also includes within the scope of this invention a novel system, for preventing storage devices like LPG tanks or cylinders from being filled above a predetermined quantity, for protecting air conditioning systems and the like which may be charged with potentially volatile or toxic refrigerants in that when a minor leak occurs the system, the valve remains closed and isolates part of the refrigeration pipe work and stops further refrigerant from escaping regardless of whether the compressor is energised or not, or duπng a major leak by closing and isolating part of the refrigeration pipe work to stops further refrigerant from escaping regardless of the operational state of the air conditioner's compressor The applications for this invention are too numerous to mention here, but include "pulse valves" which are used in the operation for the control of liquids for dishwashers, washing machines, garden hoses and water treatment systems as well as new style of domestic taps, toilet cisterns, mains water applications as well as lrngation systems It has the ability to provide high flow rates, remote tπggeπng with or without the need of any electric power while providing a long term reliability by being able to perform consistently within its design cπteria The invention can also be used for the control of vaπous fluids such as in the fuel systems for motor vehicles, for maπne use, for aeronautical and aerospace applications Its domestic, commercial and industπal applications can cover the control of air, gas, water and a wide variety of different volatile and toxic fluids SUBSTITUTE SHEET RULE 25 BACKGROUND OF THE INVENTION The type of solenoid valves which can be found washing machines and dishwashers require a continual electπcal cuπent to maintain their operational state When energised, the solenoid valve opens an oπfice passageway in the centre of the diaphragm As the diaphragm has another, but smaller oπfice, the action of the solenoid allows the fluid pressure to open the pπmary diaphragm the fluid flow valve and commence the fluid flow When the electπcal current is terminated, the solenoid valve closes the oπfice passageway and as further fluid flows through the smaller oπfice and builds up pressure on that side, the increase of the fluid pressure closes the pπmary diaphragm valve which then terminates the fluid flow The design of these solenoid valves locate their internal inlet oπfice axially suπoundmg their valve seat outlet orifice such that both are located on the same side of the diaphragm Thus when the solenoid is energised, the fluid pressure acting on the inlet/outlet side of the diaphragm exceeds the pressure on the other side and the pπmary valve opens When the solenoid is de- energised, the solenoid valve is closed and the pressure on the area behind the diaphragm exceeds the pressure on the smaller area on the inlet/outlet side of the diaphragm and thus the pπmary valve closes As this shut-off operates suddenly and as the diaphragm centre slams forcibly into its valve seat, the effect thus produced is often the cause of what is referred to as water hammer These cuπent types of solenoid valves are designed to spend most of their life closed and are occasionally opened For the above mentioned applications, they are normally fairly satisfactory However as they require a continual electπcal current to remain open, their diaphragms are located directly in the fluid flow path which not only causes flow restπction, but also encourages erosion wear to the soft valve seal They are not particularly satisfactory when used for lrngation or main water supply line applications especially when the water contains a degree of impuπties in the form of solids In those situations, these units are required to remain open for long penods of time, must be able to pass fluid freely and must have a long, service free life Current solenoids also have an unpredictable failure state in that if the diaphragm were to fail, the valve could remain open or shut but, if the electnc solenoid was to fail, the valve closes or remained closed The present invention addresses these shortcomings and can provide a solenoid valve system which can utilise a high lift pπmary valve, can provide a valve sealing system which includes a shield to reduce the fluid flow erosion wear of the soft valve seal, can provide a tπgger system which may only require a single momentary pulse of electπcal charge to change its operational state, can provide a closing mechanism which greatly reduces water hammer, can SUBSTTTUTE SHEET RULE 26 provide a remotely controlled valve system which has a low internal pressure loss with high flow rate, can eliminate the need for a spπng to help close the pπmary valve and by having the ability to fail in the as-is state or condition This is achieved by eliminating the traditional diaphragm normally used in solenoid valves and replacing it with a piston operated valve mechanism and by having the fluid flow in a reverse direction when compared to the fluid flow of normal diaphragm solenoid valves The following descπption of the operation of a standard diaphragm solenoid valve will show how this cuπent invention differs in design and concept The base component of a standard electπcally operated solenoid valve is constructed such that fluid passes from the inlet passageway into the inlet chamber which contains withm its centre a smaller diameter, axially located pπmary valve seat within which is located an outlet oπfice which leads to an outlet passageway Onto the valve seat the sealing section of the diaphragm valve, which is the pπmary valve, comes to rest when the solenoid valve, the secondary valve, is closed A small hole in the diaphragm is positioned outside the valve seat area This allows the inlet fluid under pressure to enter into the chamber above, or on the other side of, the diaphragm The solenoid secondary valve is designed to control the pressure withm the chamber above m relation to the pressure of the fluid on the inlet side of the solenoid By energising the solenoid, fluid is allowed to escape from this upper area at a faster rate than it is coming in and, as a result, the diaphragm valve opens When the solenoid valve closes, the pressure within this chamber above builds up and this forces the diaphragm to close This pressure build up above the diaphragm, combined with the suction effect produced by the movement of the fluid flow in the outlet oπfice below the diaphragm, plus the effect of any spπng above the diaphragm, creates a condition whereby the diaphragm closes expeditiously with a slamming motion The volume area of the mlet onfice and passageways and the volume of the chamber above the diaphragm becomes highly pressuπsed as the diaphragm closes This pressure build up then back feeds down the supply line Of course the degree of the pressure build up will be dependent on the pressure and the quantity of the fluid flowing through the valve at the time immediately pπor to closure At the same time the fluid pressure on the outlet side of the diaphragm valve suddenly drops at the moment of closure thus creating a negative pressure wave in the outlet pipe Both of these effects result in an unnecessary loads being placed upon the plumbing pipelines As well, the mam supply line to the appliance from the tap remains pressuπsed when the appliance is turned off and therefore requires a suitably heavy duty flexible hose to withstand the mains pressure over a considerable peπod of time With this method, the πsk of flooding is present should the flexible hose expeπence a rupture type failure By way of example, one embodiment of the present invention can be descnbed in the following manner The base of the standard solenoid valve can remain the same design as descnbed above except that the fluid passes through the unit in the reverse direction Thus the fluid inlet passagewav leads to, and ends at, the fluid inlet passageway valve seat Above this fluid inlet passageway valve seat is a moveable valve seal This is supported by a moveable piston member which moves substantially along the central axis of the end of the fluid inlet passageway This valve piston member is located within a valve piston chamber, the diameter of which is larger than the diameter of the fluid inlet passageway valve seat sealing diameter There is a pressure chamber inlet passageway leading from the fluid inlet passageway to the pressure chamber located above the valve piston member A tngger passageway leads from the pressure chamber located above the valve piston member A tπgger passageway leads from the pressure chamber to a tπgger valve mechanism and then progresses as the tπgger outlet passageway and outflows into the main fluid flow downstream of the fluid inlet passageway valve seat Located m the tπgger passageway is a tngger valve seat or tngger valve mechanism Alternatively, the tπgger passageway can lead to a trigger chamber which contains the trigger valve mechanism This tπgger can be manually, electrically or mechanically operated The tπgger valve can be descnbed as a soft valve seal which lowers onto, and raises form, the tπgger valve seat which suπounds the tngger outlet passageway This tngger outlet passageway can lead to the main fluid outlet passageway The tπgger outlet passageway can include more than one outlet oπfice The size of the pressure chamber inlet passageway and the tngger outlet passageway are of a larger diameter than the pressure chamber inlet passageway When the tngger valve is open, the dynamic fluid pressure above the valve piston member is less than that below it around the valve seat and, as a result, the valve member opens by nsing from the inlet fluid passageway valve seat and, as a result, the valve member opens by nsing from the inlet fluid passageway valve seat When the tπgger valve is closed, the fluid pressure above the valve piston member increases and, as the diameter of the piston is greater than the sealing diameter of the fluid inlet passageway valve seat, the value member descends and forms a seal with the fluid inlet passageway valve seat The advantages of using a piston instead of a diaphragm are that a much higher life is achievable, the fluid pressure required to lift the valve is less, the piston does not necessaπly need a spπng to close it, the valve can remain open when the fluid flow is terminated elsewhere in the system and the high lift piston helps reduce erosion wear to the soft sealing section of the valve by reducing the dynamic fluid flow pressure under the valve Also as the pressure build-up area of the piston is far smaller than the area above the equivalent solenoid diaphragm, this results in a more gentle closure of the main valve To enhance this further and, as the fluid flow is reversed to the normal solenoid base unit, the pressure which builds up under the valve as it closes in a more gentle and progressive manner which, in turn, pressuπses the supply pipeline This design greatly reduces the effect refeπed to as water hammer The tπgger can be further defined as using the same pnnciple as the standard solenoid whereby a continual electncal cuπent opens the valve and a termination of the current closes the valve It can also be aπanged whereby two solenoids are set at about ninety degrees to each other and are arranged to have a latching aπangement whereby an electncal pulse to one raises the tπgger valve from its valve seat and latches with the other which holds it open The energising of the other solenoid unlatches it from the first and allows the first to return to its closed positton It should be noted that this is a single pulse on, single pulse off operation and can be also achieved with other layouts of tπgger combinations Axially aligned solenoids with sliding tπgger between them or rotary solenoids with a cam system are other alternatives This type of "single shot" pulse on, pulse off, system is particularly applicable to solar powered lrngation control systems The tπgger mechanism can be aπanged to provide a severe restricting funcUon whereby an intermediate position between full on and full off which allows the moveable piston to close the main valve while allowing a small fluid flow through the tπgger outlet passageway The amount of fluid flowing from the pressure chamber would, in this case, be less than the amount of fluid able to flow into the pressure chamber A manual tngger can be used which can include a handle system with a cam mechanism above the moveable piston which can provide a vanable positioning of the moveable piston in order to produce a range of proportional openings for varying the maximum amount of fluid flow This can be incorporated into the tngger shut-off device so as to allow the fluid pressure to finally shut the valve This would help prolong the soft valve seal life as it could not be closed with excessive force This embodiment of the current invention enhances the prospects of manual and remotely controlled shut-off devices which are required to remain open for extended peπods while doing so without the need for outside power consumption While this invention was onginally developed for control of domestic and commercial water applications, it was found that it could be adapted for the following tasks very effectively LPG tanks and cylinders, by the nature of the fluid which they contain, must be considered to be full when they are filled to a maximum of eighty percent of their total volume In this manner, a safety volume remains which allows for the fluid to expand should the ambient conditions suπounding the storage device become hotter While not all LPG containers require an SUBSTTTUTE SHEET (RULE 26) Automattc Fill Limiting (AFL) valve to be installed, those that do are normally covered by fairly stπct regulations due to the environment which surrounds the storage device This is nowhere more evident than in automotive or other internal combustion engine type applications where the overfilling of such storage devices is very imprudent The current operational status of AFL valves when surveyed in field tests indicate that many of the units are unreliable, in that they consistently terminate the filling operation at a point other than eighty percent full or that they appear to have no effect on the filling operation at all For those LPG containers which are not required by regulations to contain an AFL valve and which are currently being filled by decanting or weight fill methods, an inexpensive and effective AFL valve could greatly enhance user safety This current invention also addresses the safety valve which is associated with the LPG containers in that it can provide a dual flow discharge to relieve the increasing internal pressure which these valves are intended to address This dual flow function provides a second higher discharge rate should the structural lntegπty of the container be compromised by an abnormally rapid build up of internal pressure DISCLOSURE OF THE INVENTION According to one embodiment of the present invention, there is a valve assembly device incorporated into the flexible home system which supplies water to a dishwasher or washing machine The valve assembly device is connected to and located near the laundry or kitchen machine supply taps A very small diameter hose leads from the pressure chamber of the device and can be located within the flexible leading from the device to the machine Inside the machine is a smaller than normal button solenoid which has been designed to control the very small flow from the tngger passageway With this system, the supply water pressure is contained just below the tap when the valve assembly device is in its off position When it is on, the flexible hose to the appliance does not expeπence the high static pressure expenenced by existing washing machine hoses due to the pressure loss across the valve assembly device and because the machine end of the flexible hose is always open top the atmosphere As these flexible hoses are not allowed to expeπence the higher static fluid pressures they are far less likely to fracture or rupture Therefore, in those instances where the tngger passageway is located within the flexible hose, should a small leak in the tπgger passageway occur, the liquid would find its way into the bowl and not cause a flood on the floor The device also has applications for fuel shut-off protection within motor vehicles, aircraft, boats etc , where the valve assembly device is located at, or inside, the fuel tank or cell Thus when the fuel shut-off is in the off condition, the fuel is positively contained within the tank The advantages of this safety system can be appreciated in a crash type situation where broken fuel lines are prevented from disgorging fuel from the tank thereby contπbuting further to the danger of the situation In normal form or with the dual latching system, a shut-off signal SUBSTTTUTE SHEET (RULE 26) to the for the fuel shut-off system could be connected to sensors in the vehicle, such as the air- bag deployment system, so that when a crash is detected the fuel supply is terminated at the fuel tank This system could also be connected to vehicles secuπty alarm system whereby the mcoπect disarming of the alarms deactivation process would ensure that the vehicles engine was starved of fuel This fuel shut-off device can also be connected to an apparatus such as a pocket pager or mobile telephone whereby, by accessing a certain secunty code and transmitting it to the vehicle, the fuel supply can be terminated or partially terminated This would prevent the vehicle from proceeding further under its own power or would act as a partial fuel cut-off by preventing the engine from consuming more than a limited volume and thus prevent the vehicle from reaching a pre-determined speed The reset mechamsm for restoπng normal operation may require accessing the inteπor of the fuel tank which would mean the abrupt end to a joy-πde type theft as time and the services of qualified personnel are required to restore the full operation of the fuel supply As with the example for washing machines as descnbed above, a similar device could be connected to garden hoses whereby the tπgger valve is at the hose outlet while the valve assembly device is at the garden tap end When in the off condition, the garden hose does not have to try to maintain the force of mains pressure which, in time, damages and weakens the hose The maximum flow rate can be adjusted in the valve assembly device which can also incorporate a manual shut-off latching device In another embodiment of this invention, there is a mechanism for providing a fast fill for the water tanks usually associated with toilet cisterns Due to the high lift and high flow rate performance with quite shut-off from this valve system, the filling protocol can be push the button, flush and fill or it could be push the button, fill and flush The advantage of the second fill protocol is that, if the cistern flush valve were to leak, water would not be wasted as the cistern would not keep topping itself up as it only fills after the flush button is activated For both of the above protocol styles, the tngger passageway valve is connected to a float which will respond to the water level in the cistern by closing the tngger valve passageway In order to ensure a positive shut-off from the tπgger valve, the float has a shield encircling its lower portion such that as the cistern fills to a certain pre-determined point, the shield rapidly fills with water and causes the float to lift rapidly and smoothly Another embodiment of this invention is to provide an effective eighty per cent shut-off for filling applications for LP gas containers and the like The cuπent eighty per cent fill systems enjoy a number of operational problems which detract from the benefits they are trying to offer The majonty of these systems place a float operated tπgger and shut-off valve as one unit into SUBSTTTUTE SHEET (RULE 26) the LPG container These cuπent systems unnecessary add to the cost and are not as effective as this embodiment of the invention which splits the tngger mechamsm from the filling shut-off and provides a method of pressure filling with no atmosphenc release of gas or a more traditional decanting fill by the use of an inexpensive filling tool In this case the valve assembly device, which now forms part of the filling station equipment mechanism, contains the pπmary shut-off moveable piston and pressure chamber as well as incorporating part of the trigger passageway By keeping this mechanism external and separate from the LPG container, the amount of mechanism required to be installed within the LPG containers has been reduced It will be understood that as the filling station equipment mechanisms will be in far smaller quantities than the LPG container valves, the overall costs for this system are kept to a minimum The filling valve on the LPG container has, in addition to the normal features such as the on/off valve, the safety valve and the filling and/or outlet connections, a mating connection with the tπgger passageway from the valve assembly device which will now form part of the filling station equipment This mating connection has a passageway which leads into the LPG container to a pre-determined height and, at the end of this passageway is a flotation member and flotation valve Duπng the filling process, the fluid flowing into the valve assembly devices pressure chamber is allowed to flow relatively unrestncted through the tngger passageway, through the mating connection, through the mating connection passageway and through the flotation valve into the LPG container When the flotation valve is restncted to the point that the flow of fluid entenng the pressure chamber is greater than the flow leaving it, the increase of pressure exerts a force onto the moveable piston and causes it to close the primary valve To further enhance the field operation of this mechanism, several additional valves can be installed into the tπgger passageway Valve one would be located withm the tngger valve passageway and is designed to latch with the moveable piston such that when the moveable piston approaches its closed position it unlatches and valve one closes The reset for this valve requires an external and manual operation when all the other tπgger passageway valves are open Valve two is located in the other end of the tπgger passageway withm the tπgger passageway connection This is a normally closed valve which is only opened after the tπgger passageway connection makes a sealing contact with the mating connector on the LPG container valve Valve three is a normally closed valve located withm the mating connector which only opens after the tπgger passageway connection makes a sealing contact with the mating connector on the LPG container valve For the above, a manual secondary valve can be installed into the filling station equipment mechamsm between the moveable piston and the connection end This greatly reduces the discharge dunng the disconnection process and adds to the overall safety of the filling process Unless the filling station equipment mechanism is coπectly installed onto an LPG container which is less than eighty percent full, the fuel flow will not be able to be initiated SUBSTTTUTE SHEET (RULE 25) In another embodiment of this invention there is an Automatic Fill Limiting (AFL) valve which eliminates the problems which are associated with the majonty of AFL valves cuπently in use These AFL valves can be incorporated to include the tank supply outlet to the engine as well as the fluid level indicator for the tank In this manner the number of penetrations into the tank can be reduced from three to one In addition, the tπgger register for terminating the inlet flow can be insugated by the fluid level indicator in that when the 80% fill is achieved and the fluid level indicator opens an electπcal tngger circuit, the tngger passageway solenoid is de-energised and the fill is terminated In another embodiment of this cuπent invention the fluid flow valve system can be installed within the plumbing network of an air conditioning system whereby the fluid flow valve system utilises an electnc solenoid for opening the tngger passageway valve and a pressure sensitive switch which is located downstream of the tπgger passageway valve seat This fluid flow valve system is normally located on the high pressure line between the dner mechamsm and the TX valve associated with the evaporator The fluid flow valve system allows the pressure switch to test that the line pressure between the primary valve seat and the nonreturn valve located within the compressor is always within certain limits If when the air conditioning is off, should the pressure drop below the limit of the pressure switch, the solenoid will not be energised when the air conditioner is switched on, thus preventing further fluid from escaping to the atmosphere Should the pressure within the pressure switch drop below the limit of the pressure switch while the air conditioner is operational due to a major leak, the power to the electnc solenoid will be terminated which will close the secondary valve which will cause the pnmary valve within the fluid flow valve system to close and terminate the fluid flow within the pipe network Alternatively, with this particular air conditioning safety system, a non-return valve can be installed on the low pressure line on the evaporator and the pressure sensing switch is attached to this unit In this manner, this safety system is considerably enhanced as a major rupture or failure of the line to the TX valve results in a pressure loss being registered first m this particular area of the system In another embodiment of this invention, the power to the solenoid is provided by the air conditioners thermostat circuit In this way, when the thermostat operates and terminates the power to the compressor clutch, the solenoid is also powered down Thus this circuit can be aπanged so that when the pressure switch removes the power to the solenoid, the power to the compressor clutch relay is also terminated In this way, a minor leak can be detected by allowing the pressure switch to go open circuit when the pressure drops between solenoid and the non-return valve In another embodiment of this cuπent invention this valving system can be installed between the town supply of water and water conditioning equipment such as water filters, reverse osmosis units, hot water systems, chillers and the like In this manner, when the valve is turned off the water conditioning apparatus, whose delivery line can now be normally left open to the SUBSTTTUTE SHEET (RULE 26) atmosphere, expenences no static build up of water pressure and the resultant stresses on the canisters and internal chambers are therefore markedly reduced The only water pressure these units will then expeπence are the dynamic flow pressures of the water and the unit can be designed such that a flow restπction occurs withm the unit which prevents any build up of dynamic flow pressure withm these susceptible chambers The standard water faucet for the delivery of the water from these water filtration units is such that their appearance above the counter is virtually identical with units that are currently sold today The internal and under counter differences are that there are now normally three lines going to the unit, one line which takes high pressure fluid from the pressure chamber to the tπgger passageway valve, one line which takes the fluid discharged from the tngger passageway valve back to the fluid supply line upstream of the water conditioning equipment and the third line takes the conditioned fluid from the fluid conditioning equipment to the discharge spout It should be noted that the higher pressure tπgger passageway pipe can be located within the discharge tπgger passageway pipe so as to give the appearance of only two pipes going to, or coming from, this valving system In this manner, should the high pressure tngger passageway pipe burst the flow of fluid is controlled and remains within the pipe network It merely turns the pulse valve on and fluid is discharged from the spout into a receptacle such as a sink Therefore with this embodiment of the invention there is an above counter-top outlet spout and valve which contains a tngger valve, a tngger valve inlet passageway, a tngger valve outlet passageway and a mam outlet passageway and spout For this above counter-top outlet spout, the tngger valve inlet passageway can be contained within the tngger valve outlet passageway In another embodiment of this invention, it should be noted that this valve system can be utilised as a high flow pressure limiting valve wherein the tngger valve is responsive to the pressure of the fluid downstream of the main valve seat wherein when the pressure of the fluid reaches a predetermined value the tngger passageway closes and the main valve also closes In another embodiment of this invention, it should be noted that this valve system can be installed in the cold water supply line to a hot water unit It can be used in conjunction with another valve system which is connected to a temperature sensing device installed at the top of the hot water tank The two valve systems can be aπanged such that an increase of water pressure allows the cold water tπgger valve to open and thus opens the pπmary cold water control valve and discharge to atmosphere thereby reducing the pressure withm the hot water tank Also, they can be aπanged so that when the temperature sensing tπgger valve opens it opens not only the pnmary sensing valve but also opens the pπmary cold water control valve as well Thus the discharge temperature of fluid from the tank can be controlled and the water will never exceed a predetermined value of say 40° to 60°C In another version of this embodiment, an outlet passageway from the top of the hot water tank proceeds via a non-return valve to the cold water passageway leading into the bottom of the hot water tank Another non-return valve 10 SUBSTTTUTE SHEET (RULE 25) is located near the cold water line. These two non-return valves prevent hot water from flowing into the cold water line and prevent cold water from flowing into the hot water line. Between the two non-return valves is located this pulse valve system. The trigger passageway from the pulse valve leads to a trigger valve which is responsive to a temperature probe located at or near the top of the hot water tank thus when the temperature increases and the temperature probe opens the trigger valve, mixed hot and cold mixed water is released at a temperature range between say 40° to 60°C. In another embodiment of the present invention, this device can be used to provide a power flush for water storage tanks such as cisterns. The water flowing from the outlet passageway can be made to turn an impeller. This impeller is connected to second impeller located within the cisterns outlet orifice which forces the fluid exiting from the cistern to do so in a more forceful manner. It is, of course, understood that this invention relates to the control of all types of fluids and is not limited to only those applications mentioned herein. BRffiF DESCRIPTION OF THE DRAWINGS Prefeπed embodiments of the present invention will now be described by way of example only with reference to the accompanying drawings in which: - Figure 1 shows a sectional side view of one embodiment of an open valve assembly device and with an optional opening limiting device but not with the triggering mechanisms; Figure 2 shows a variation of the valve piston assembly shown in Figure 1. Figure 3 shows a sectional side view of the latching trigger chamber mechanism and Figures 4, 5, 6 and 7 show the four positions of the manual cyclic dual trigger latching mechanism. Figures 8, 9, 10 & 11 show various embodiments of the AFL valve. Figure 12 shows an in-line embodiment of the pulse valve which could be used for washing machines and dishwashers, Figure 13 shows an in- line embodiment of the pulse valve which could be used for water treatment systems while Figure 14 shows the above counter-top outlet spout with the trigger valve inlet passageway contained within the trigger valve outlet passageway for use with the device outlined in Figure 13. Figure 15 shows one embodiment of a high flow pressure limiting valve. Referring to two of the major components of the valve assembly device, Figure 1 details the base assembly (2) and the top assembly (1). The base assembly comprises a fluid inlet orifice (109) which leads via the fluid inlet passageway (9) to the end of the fluid inlet passageway at (8). Encircling the end of the fluid inlet passageway is the fluid inlet passageway valve seat (6). Suπounding the fluid inlet passageway valve seat is the outlet passageway (110) which leads to 1 1 SUBSTTTUTE SHEET (RULE 25) the outlet orifice (10). Attaching to the base assembly is the top assembly which makes a sealing contact at the outer housing (111). Located within the top assembly is the primary valve moveable piston (4) which is axially aligned with the fluid inlet passageway valve seat. The moveable piston is loosely fitted into the cylindrical pressure chamber (5) which is also axially aligned with the axis of the fluid inlet passageway valve seat. Between the moveable piston and the pressure chamber is an 0-ring 47 which is located within a groove located at the top of the moveable piston. The diameter of the pressure chamber is greater than the effective sealing diameter of the fluid inlet passageway valve seat. Above the moveable piston is a mechanical adjustment 48 which is provided to vary the opening travel of the moveable piston. Attached to the lower end of the moveable piston is a turbulence shield (11) inside which is located the pliable disc (3). Attached underneath the pliable disc is a flow deflection plate (34) which helps deflect the flow of fluid away from the soft pliable disc. This deflection plate is of such a diameter that it fits within the internal diameter of the fluid inlet passageway valve seat. Protruding from its centre is a centre hub (35) which projects below the level of the end of the fluid inlet passageway even when the moveable piston is in the fully open position. The pressure chamber inlet passageway (14) can lead from the fluid inlet passageway to the pressure chamber emerging at position (15) where a non-retum valve (not shown) can be mounted. Alternatively, the pressure chamber inlet passageway (37) can be located through the centre of the moveable piston, the turbulence shield , the pliable disc, the deflection plate and the centre hub. At its outlet end at position (21) a non- retum valve (not shown) can be mounted. Leading form the pressure chamber is a trigger passageway (17) which contains a trigger mechanism devices (not shown). The extended periphery (112) of the turbulence shield is aπanged such that when the moveable piston is in the closed position, the internal diameter of the extended periphery is greater than the external diameter of the outer edge (113) of the fluid inlet passageway valve seat. In conditions of dynamic fluid pressure flow, these diameters are important. When the trigger mechanism is in the off position, the pressure builds up in the pressure chamber and the moveable piston, due to its larger diameter, is forced to descend towards the fluid inlet passageway valve seat. This increases the pressure in the inlet fluid passageway as the volume flow of the fluid is reduced. This increase of pressure is transmitted to the pressure chamber inlet passageway. However there is a variable which is introduced at this point, namely that as the moveable piston approaches its valve seat, the localised rate of flow of the fluid is greatly increased at position (114) between the valve seat and the moveable piston. This increase in the rate of the fluid flow at the point lowers the pressure of the dynamic fluid flow pressure between the valve member and the valve seat and, as a result, (according to Bernoulli's theorem) a condition is created whereby the dynamic pressure drops and, in this case, this effect helps to accelerate the valve towards the valve seat. The resultant closure can create the effect of "water hammer". To overcome this the extended periphery of the turbulence shield, due to its close proximity to the 12 SUBSTTTUTE SHEET (RULE 26) outer edge of the fluid inlet passageway, causes the fluid passing between the pliable disc and the valve seat to become turbulent and slow down This slow down of the fluid flow increases the dynamic pressure of the fluid flow, thus compressing onto the fluid and slowing down the rate of closure of the moveable piston towards the end of its travel resulting in a silent operation of the valve assembly Figure 2 shows the vaπation embodiment of using a moveable pliable disc shown here as a jumper valve (38) wherein, the jumper valve is located onto the moveable piston via a centrally located bore hole (39) into which the jumper valve stem (41 ) has a sealing fit due to the O-nng (42) Into the recess (43) fits a spnng (45) which biases the jumper valve away from the moveable piston The passageway (50) allows fluid to flow to the pressure chamber as previously descnbed Figure 3 details one embodiment of the tπgger mechanism The tπgger valve (16), can be comprised of an electnc solenoid (25), a central moveable stem (24), a tπgger chamber (18), a tπgger valve seat (19) and a tngger valve mechanism (20) which can come into sealing contact with the tπgger valve seat When the electronic solenoid is energised, the fluid from the trigger passageway (17) is allowed to flow through the tngger outlet passageway (23) unhindered When the solenoid is not energised, the spnng (26) returns the central moveable stem to its rest position and the tπgger valve mechanism seals the tπgger valve seat A second electnc solenoid system (28) can be installed so that its central moveable stem (27) has an interfeπng contact (30) with the first central moveable stem When the second electnc solenoid is energised, the second central moveable stem allows the first central moveable stem to descend and seal the tngger valve seat while latching the second central moveable stem in the retracted position A single pulse to the first solenoid will open the tngger valve seat seal and allow the second central moveable stem to be biased by the spnng (29) to latch under the first central moveable stem and thus keep the tπgger valve seat seal open In this way a simple latching system allows momentary pulses to the first or second solenoids to allow fluid to flow or prevent it The advantages for battery or solar powered systems are obvious Figure 4 details the dual manual latching cam in its central position with the valve trigger closed, while Figure 5 shows the dual manual latching cam opening the valve tπgger and allowing the second central moveable stem to latch underneath it Figure 6 shows the dual manual latching cam in its central position with the tπgger valve open, while Figure 7 shows the dual manual cam unlatching the trigger valve and allowing it to close This Fluid Flow Valve Assembly has particular application for the control of vanous 13 SUBSTTTUTE SHEET (RULE 25) volatile fluids such as LP gas and the like In one form it can be presented as a refilling option for pressure filling LP gas cylinders wherein the Fluid Flow Valve Assembly inlet passageway is connectable to, or part of, the gas supply line while its outlet passageway is connectable to the main valve housing on the cylinder The mam valve housing on the cylinder has been modified such that a secondary passageway is present which has a mounting portion with a venting valve which is compatible to the tπgger passageway valve connection system from the Fluid Flow Valve Assembly This secondary passageway withm the cylinders main valve includes a shut-off valve operated by a flotation device which, when installed within the gas cylinder, will allow duπng a filling procedure for a termination of the fluid flow through the secondary passageway when the level of the fluid m the cylinder causes the float to πse The float location is positioned such that the shut-off of the secondary passageway occurs when the cylinder is 80% full Therefore, duπng a filling operation when the Improved Fluid Flow Valve Assembly is connected to the cylinders mam valve and the tπgger passageway valve connection system is attached to the mounting portion and the cylinder is being filled, the operation ot the shut-off of the secondary valve will cause a rise of pressure in the pressure chamber of the Fluid Flow Valve Assembly which will cause the pnmary valve moveable piston to form a seal with the pπmary valve seat which will then terminate the fluid flow The main advantage of this type of design which includes a valve connection system in the trigger passageway is that if, dunng a filling operation when the shut-off has occuπed, the tπgger passageway is disconnected first, the valve connection system will not allow the pressure to drop in the pressure chamber which will prevent the fluid from flowing from the pnmary valve seat Also, if the Fluid Flow Valve Assembly is disconnected from the cylinder valve first, the shut-off has already occuπed so no gas will vent to the atmosphere Another advantage of this type of design is that a simple attachment device can be installed into the mounting portion which opens the venting valve and allows the cylinder to be filled by normal decanting methods It should be noted that duπng this type of decanting procedure, when the float on the secondary passageway encounters the rising fluid level, the secondary valve mechamsm shuts and terminates the filling procedure In Figure 8 we have one embodiment of the AFL valve whereby the tπggenng of the fluid flowing into the tank is initiated by the opemng of the solenoid valve In this diagram the electnc windings of the solenoid and the mounting fittings for attaching the AFL valve into the cylinder have not been shown The body assembly (1) has an inlet oπfice (2) which leads via the inlet passageway (3) to a main shut-off valve seat (4) which is axially aligned with the central axis of a flow chamber (5) located within the flow chamber and axially aligned with it is a pressure chamber housing (6) which contains a pressure chamber (7) located withm the pressure chamber is a movable piston (8) which makes a sliding sealing contact with the internal wall of the pressure chamber Located down the centre axis of the movable piston is a small diameter 14 SUBSTTTUTE SHEET (RULE 25) oπfice (9) located on the inlet end of the movable piston is a main valve seal ( 10). The pressure chamber housing at its' outlet end makes a sealing contact with the body assembly at ( 11 ) axially aligned with the central axis of the pressure chamber is a tπgger egress passageway (12) which communicates with a trigger passageway (13) which leads to a solenoid chamber (14). Leading from the solenoid chamber is a tπgger outlet passageway (15) which leads to a non-return valve (16) and exits from the body assembly at (17). Surrounding the tπgger outlet passageway is a solenoid valve seat (20) which can make a sealing contact with the solenoid piston seal (21) when the solenoid piston (22) is not being affected by the electro-magnetic force of the solenoid's coil. The main cylinder seal (18) allows for a fluid type seal to be formed between the AFL valve and the LPG container (which is not shown) also present in the body assembly is a main fluid outlet passageway (19) in this particular diagram fluid flows into the body assembly at the inlet orifice and down through the inlet passageway. As the electnc solenoid has been energised and the solenoid piston is in its' open condition there is less pressure in the pressure chamber behind the movable piston than the fluid pressure which is built up in front of the piston, thus the piston has moved to its fully opened state. The fluid which is flowing down the small diameter orifice in the piston is then allowed to flow through the tngger egress passageway to the tngger passageway and through the solenoid chamber then into the trigger outlet passageway at a faster rate than it flows through from the small diameter oπfice. When the main valve is open the main flow of fluid is allowed into the cylinder through the main fluid outlet passageway which leads from the flow chamber. When you compare this diagram with Figure 9 it should be noted that the solenoid piston (22) has returned to its rest position under the influence of the solenoid piston spπng (21). The pressure in the trigger passageway (13) builds up as does the pressure in the pressure chamber (7) which therefore forces the movable piston from the pressure chamber which causes a seal to be made between the main valve seal (10) and the shut-off valve seat (4) This terminates the flow of fluid through the inlet passageway and prevents further filling of the LPG container. It should be noted that in this condition even when the LPG filling tank has been disconnected from the cylinders filling connection, the non-return valve (16) prevents any fluid from flowing down the tngger outlet passageway then into the tngger passageway and then venting into the inlet passageway. This prevents any volume discharge from the AFL valve should the integrity of any of the plumbing connections or components between the inlet orifice and the cylinders filling connection become compromised. There may be also present a hairsbreadth passageway (24) between the outside of the body assembly and the tngger passageway. It should be noted that the sensing of the fluid level within the tank comes from a modified fuel gauge sensing mechanism which opens the electrical circuit to the electnc solenoid when the fluid level is at the 80% full level. There is also a pressure sensing switch in the circuit which closes when a fluid supply pressure above 120 pounds is expeπenced. In this manner, the fill solenoid is only energised when the contents of the tank are below 80% and when the supply pressure of the 15 SUBSTTTUTE SHEET (RULE 25) delivery pump is expeπenced. In another embodiment of the present invention it will be seen from Figures 10 and 1 1 that the major components remain unchanged however there is a different mechanical tπggeπng system which provide an accurate termination of the fluid flow at the required time duπng the filling process and, as well, are highly reliable. In Figure 10 fluid flows from the flow chamber into the tank through the main outlet passageway (31) past a tπgger valve pivot plate (32). This tngger valve pivot plate is connected to the body and partially rotates around its' pivot (33) when acted upon by the flotation arm (34) which is connected to a flotation member which is not shown. During the filling process the flotation arm which is attached to the body with a flotation arm pivot (35) reacts to the increasing level of fluid in the tank and presses on an opemng pin (36) which is attached to the trigger valve pivot plate (32). As the tngger valve pivot plate starts to move the tngger valve pivot plate projection (37) is introduced to the fluid flow proceeding from the outlet passageway and is powered to its open position shown in Figure 1 1 by the force of the fluid coming into interfeπng contact with it. It will be noted in Figure 10 that with the position of the tngger valve pivot plate the tngger valve (38) is being held open. In Figure 11 the trigger valve pivot plate projection (37) came into interfering contact with the discharge of fluid flowing from the main outlet passageway (31 ) and has moved to its fully opened position. The tngger valve has closed, the mam piston has been partially expelled from the pressure chamber and the main valve has terminated the flow of fluid through the AFL valve. It should be noted that in this condition the trigger valve pivot plate is counter-weighted to remain in this open position until the fluid level in the tank drops and the flotation arm is allowed to come into contact with stud (39) which, as the fluid level drops and as the weight of the flotation arm comes to fully bear in it, will return the trigger valve pivot plate to its rest position. In this condition the trigger valve pivot plate con overcome the spring tension which is trying to close the tπgger valve. In Figure 12 the body (40) contains the inlet orifice passageway (41) and the inlet valve seat (42). The piston (43) has a primary valve seat seal (44) and a pressure chamber inlet passageway (45) which extends form the inlet oπfice passageway, through the piston to the pressure chamber (46). The pressure chamber is contained within the cyhndncal pressure chamber body (47) which has flow passageways (48) which allow fluid to flow from the inlet passageway to the outlet passageway when the primary valve seat is open. The cylindrical pressure chamber body is contained within the outlet portion of the body (49) and passing through the outlet passageway (50) is a tngger passageway (51) which leads to a trigger valve (not shown). 16 SUBSTTTUTE SHEET (RULE 26) In Figure 13, the cylindrical pressure chamber is part of the outlet portion of the body (51) and the main outlet passageway (52) leads to an outlet mechanism (not shown) via the outlet connection (53). The pressure chamber trigger passageway outlet (54) leads to a trigger passageway valve (not shown) via a trigger passageway connection (55) and is contained within the trigger passageway return connection (56). The trigger passageway return connection leads to a trigger passageway return channel (57) which discharges through to the main outlet passageway. Figure 14 details the above counter-top outlet spout with the trigger valve inlet passageway contained within the trigger valve outlet passageway. The above counter-top outlet spout body (58) captures the trigger passageways within the above counter-top outlet body lower section (59). This is achieved by the outlet connection passageway (60) compressing the above counter-top outlet body lower section between the mounting plate (61) by means of the locating nut (62). The larger sealing O-Ring (63) contains the fluid within the trigger passageway return channel (64) which communicates with the trigger passageway return connection (65). The trigger passageway return connection makes a seal at the medium O-Ring (68) and the above counter-top outlet body lower section. Located within the trigger passageway return connection is the trigger passageway connection (66) which is sealed to the above counter-top outlet spout body by the small O-Ring (67). The trigger valve (69) forms an occasional seal between the trigger passageway connection and the trigger passageway return channel. The trigger valve is biased towards the closed position by the spring (70). The trigger valve is opened by the movement of the control handle (71). Figure 15 defines a high flow pressure limiting valve utilising one embodiment of the invention. A body (72) with an inlet orifice (73) which is connectable to a further fluid transport mechanism leads to a valve orifice and valve seat at (75) which leads to an outlet orifice at (74) which is also connectable to a further fluid flow transport mechanism. The movable piston (76) makes a sliding and sealing contact with the pressure chamber (78) which is located within the trigger body (79). The pressure chamber inlet passageway (77) communicates fluid pressure from the valve orifice to the pressure chamber. The trigger passageway (80) leads to a trigger valve seat at (82). An increase of pressure at the outlet orifice is transfeπed to the trigger pressure chamber (81) via the trigger pressure passageway (86) which can cause the trigger piston (85) to compress the trigger piston spring (84) and close the trigger valve which causes a build up of pressure chamber which closes the valve seat. Thus when the outlet orifice pressure drops the trigger valve seat opens and fluid flows from the pressure chamber via the trigger outlet (87) which allows the movable piston to move away from the valve seat as the fluid flows. The trigger piston spring adjuster (83) can vary the opening pressure of the trigger valve. The foregoing describes only some of the embodiments of the present invention and 17 SUBSTTTUTE SH EET (RULE 26) modifications, obvious to those skilled in the art, can be made thereto without departing from the scope of the present invention. 18 SUBSTTTUTE SH EET (RULE 26)

Claims: THE CLAIMS DEFINING THE INVENTION ARE AS FOLLOWS: 1 A fluid flow valve system compπsmg a body assembly, having an inlet for connection to a fluid supply, an inlet passageway leading from the inlet onfice of the inlet to a pπmary valve seat outlet, a pnmary valve seat which encircles and is axially aligned with the pπmary valve seat outlet, an outlet chamber which suπounds encircles and is axially aligned with the axis of the pπmary valve seat and pπmary valve seat outlet and which leads from the pπmary valve seat outlet to an outlet aperture and this body assembly is connectable to a further fluid flow transport mechanism, a cyhndncal pressure chamber which is axially aligned with the axis of the pπmary valve seat and is located on the outlet side of the said pnmary valve seat, located within the pressure chamber and making a sliding and sealing contact with it is a pπmary valve movable piston which, when moved fully towards the pnmary valve seat, forms a fluid tight seal with it, wherein the effective sealing area of the pπmary valve seat is less than the area of the sealing contact of the pπmary valve movable piston, a pressure chamber inlet passageway which allows fluid from the inlet passageway to communicate with the fluid m the pressure chamber, and a tπgger passageway which leads from the pressure chamber to a trigger passageway valve system 2 A fluid flow valve system according to claim 1 wherein, there is at least one outlet flow passageway which leads from the outlet chamber to the outlet aperture wherein part of its axis is substantially parallel to the axis of the pressure chamber 3 A fluid flow valve system according to any of the previous claims wherein the axis of the pressure chamber inlet passageway is positioned and aligned with the central axis of the pπmary valve movable piston 4 A fluid flow valve system according to any of the previous claims wherein, the sliding and sealing contact between the pressure chamber and the movable piston is a U-sealing packing member which is attached to the movable piston 5 A fluid flow valve system according to any of the claims 1 to 3 wherein, the sliding and sealing contact between the pressure chamber and the movable piston is an O-πng which is attached to the movable piston 6 A fluid flow valve system according to any of the previous claims wherein, the body assembly, the inlet for connection to a fluid supply, the pπmary valve seat, the pressure chamber and the movable piston are axially aligned to a common datum 7 A fluid flow valve system according to any of the previous claims wherein, the pressure chamber is located within and held in position by the body assembly 8 A fluid flow valve system according to any of the previous claims wherein, the body assembly is constructed in two sections whereby the second section of the body assembly incorporates an interconnection joining means for the further fluid flow transport mechanism 19 SUBSTTTUTE SHEET (RULE 25) 9 A fluid flow valve system according to any of the previous claims wherein, fluid may pass freely from the outlet aperture to the outlet oπfice which is located withm the further fluid flow transport mechanism 10 A fluid flow valve system according to any of the previous claims wherein, withm the body assembly which contains the outlet aperture are two passageways, one is the tngger passageway which passes through the outlet aperture and the other is the main fluid flow passageway which is the outlet aperture 11 A fluid flow valve system according to any of the previous claims wherein, withm the tπgger passageway system of the further fluid flow transport mechamsm is located a tπgger passageway secondary valve 12 A fluid flow valve system according to any of the previous claims wherein, the end of the tπgger passageway further most from the pressure chamber terminates in a tngger passageway connection member which is compatible with a cooperating tngger passageway connection portion that is an integral part of the trigger passageway system of the further fluid flow transport mechanisms 13 A fluid flow valve system according to claim 12 wherein, the tπgger passageway connection member incorporates a fast connect/disconnect attachment mechanism which is compatible with the cooperating tπgger passageway connection portion 14 A fluid flow valve system according to any of the previous claims wherein, located withm the end of the tπgger passageway connection member is a tπgger passageway connector valve which is biased towards the closed position 15 A fluid flow valve system according to any of the previous claims wherein, the tπgger passageway valve is held open after the tngger passageway connection member makes a sealing connection with the cooperating tngger passageway connector portion of the further fluid flow transport mechanisms 16 A fluid flow valve system according to any of the previous claims wherein, located within the tπgger passageway and positioned between the pressure chamber and the tngger passageway connector valve is a tngger passageway pnmary valve 17 A fluid flow valve system according to any of the previous claims wherein, when there is an increase of fluid pressure in the inlet passageway above a predetermined amount and there are no valves in the tπgger passageways which are closed, the fluid pressure in the pressure chamber is therefore relatively lower and the pnmary valve movable piston moves away from the pπmary valve seat and allows fluid to flow from the inlet to the outlet aperture 18 A fluid flow valve system according to any of the previous claims wherein, duπng those times of dynamic fluid flow when any of the valves in the tπgger passageways are closed or when the rate of fluid flowing into the pressure chamber through the pressure chamber inlet passageway is greater than the rate of fluid flowing from the pressure chamber through the tπgger passageway, an increase of the pressure m the pressure chamber occurs which causes the pnmary valve movable piston to move away from its fully open position and to form a seal with 20 SUBSTTTUTE SHEET (RULE 25) the primary valve seat 19 A fluid flow valve system according to any of the previous claims wherein, one end of the tngger passageway pπmary valve mechanism is a shaft which is of sufficient length to protrude proud of the pressure chamber and slides within a seal which defines and contains that portion of the pressure chamber and tngger passageway 20 A fluid flow valve system according to claim 19 wherein, the end of the tngger passageway pnmary valve mechanism shaft which protrudes proud of the pressure chamber is exposed to the effects of atmosphenc pressure 21 A fluid flow valve system according to either claim 19 or claim 20 wherein, the tngger passageway pπmary valve shaft is biased away from the pressure chamber 22 A fluid flow valve system according to claim 21 wherein, the biasing means is the pressure of the fluid in the pressure chamber 23 A fluid flow valve system according to any of the previous claims wherein, when the tngger passageway pnmary valve shaft is moved to its limit of travel from the pressure chamber, the tπgger passageway pπmary valve is closed 24 A fluid flow valve system according to any of the previous claims wherein, a biasing means is positioned to apply a force to the tπgger passageway pnmary valve shaft in the direction towards the pressure chamber 25 A fluid flow valve system according to any of the claims 21 to 24 wherein, the biasing means is a spring 26 A fluid flow valve system according to claim 24 wherein, the force of the biasing means is insufficient to overcome the effect of the static fluid pressure within the pressure chamber when the static pressure is above a predetermined valve 27 A fluid flow valve system according to claim 26 wherein, the force of the biasing means is sufficient to overcome the effect of the dynamic fluid pressure withm the pressure chamber when fluid is flowing through this fluid flow valve system 28 A fluid flow valve system according to any of the claims 19 to 27 wherein, the end of the tπgger passageway pπmary valve mechanism which is exposed to the effects of atmosphenc pressures of such a length to allow an external force to move the tπgger passageway pπmary valve mechanism to an open position 29 A fluid flow valve system according to any of the previous claims wherein, when the tngger passageway pnmary valve mechanism is moved to its fully open position and when the fluid pressure in the pressure chamber drops sufficiently when compared to the fluid pressure in the inlet passageway to then allow the piston to move to its open position, the tπgger passageway pπmary valve is held open by a latching mechanism cooperating between it and the piston when the force required to move the tngger passageway pnmary valve mechanism to its fully open position is released 30 A fluid flow valve system according to any of the previous claims wherein, when the pressure in the pressure chamber increases and equates to the pressure m the inlet passageway, 21 SUBSTTTUTE SHEET (RULE 25) the primary valve movable piston is forced away from its fully open position and it unlatches the tπgger passageway pnmary valve latching mechanism and allows the tngger passageway pπmary valve to close 31 A fluid flow valve system according to any of the previous claims wherein, regardless of the effectiveness of the closing ability of the other valves located within the tngger passageways, when there is sufficient fluid flow through the fluid flow valve system and the tngger passageway pπmary valve closes, a build up of pressure m the pressure chamber results which is sufficient to produce an effective seal between the pnmary valve movable piston and the pnmary valve seat 32 A fluid flow valve system according to claim 31 wherein, the biasing means is a spπng 33 A fluid flow valve system according to any of the previous claims wherein, the pressure chamber inlet passageway includes a non-return valve which is located so that fluid is prevented from flowing from the pressure chamber to the inlet passageway 34 A fluid flow valve system according to any of the previous claims wherein, a tπgger valve mechanism is located withm the pressure chamber 35 A fluid flow valve system according to any of the claims 1 to 33 wherein, the tπgger passageway leads to a tπgger chamber 36 A fluid flow valve system according to claim 35 wherein, a tngger outlet passageway leads from the tngger chamber to an outlet passageway downstream of the pnmary valve seat 37 A fluid flow valve system according to claim 36 wherein, within the tngger chamber is a tπgger chamber valve seat which suπounds the oπfice leading from the tngger chamber to the tπgger outlet passageway 38 A fluid flow valve system according to claim 37 wherein, the fluid flows from the trigger chamber past the tngger chamber valve seat to the tngger outlet passageway 39 A fluid flow valve system according to claim 37 or 38 wherein, a tngger chamber valve mechamsm is positioned so that it can make a sealing contact with the tngger chamber valve seat 40 A fluid flow valve system according to any of the claims 35 to 39 wherem, the tngger chamber valve mechanism is attached to the central movable stem of an electnc solenoid valve system 41 A fluid flow valve system according to claim 40 wherein, the central movable stem of the electnc solenoid valve system is biased towards the tngger chamber valve seat 42 A fluid flow valve system according to claim 40 or claim 41 wherein, the central movable stem for the tngger chamber valve mechanism comes into interference contact with a second central movable stem of a second electnc solenoid system 43 A fluid flow valve system according to claim 42 wherein, the second central movable stem of the second electnc solenoid system is mounted at or about nght angles to the central movable stem of the electnc solenoid valve system 44 A fluid flow valve system according to claim 42 or claim 43 wherein, the second central 22 SUBSTTTUTE SHEET (RULE 25) movable stem is biased towards the tπgger chamber valve seat 45 A fluid flow valve system according to any of the claims 42 to 44 wherein, the second central movable stem latches under the central movable stem for the electnc solenoid valve system when that electnc solenoid is momentanly energised 46 A fluid flow valve system according to any of the claims 42 to 45 wherein, the central movable stem for the electnc solenoid valve system is allowed to form a sealing contact with the tngger chamber valve seat when the second central movable stem unlatches as and when the electnc solenoid of the second electnc solenoid system is momentanly energised 47 A fluid flow valve system according to any of the claims 42 to 46 wherein, a manual overπde latching system is provided to allow the tngger chamber valve mechamsm, the central movable stem and the second central movable stem to be latched and unlatched externally 48 A fluid flow valve system according to claim 47 wherein, the manual overπde latching system compπses a three position cam system whereby the central position neither interfere with the central movable stem nor the second central movable stem, whereby rotating the three position cam system in one direction unlatches the central movable stem while rotating it in the other direction past the central position, unlatches the central movable stem 49 A fluid flow valve system according to claim 48 wherein, the three position cam system is biased to return to the central position 50 A fluid flow valve system according to claims 41, 44 and 49 wherein, the biasing means are spnngs 51 A fluid flow valve system according to any of the previous claims wherein, the further fluid flow transport mechanism contains a tπgger passageway, a cooperating tπgger passageway connection portion, a mam tπgger passageway, a main fluid passageway valve and a connection aπangement for attaching the further fluid flow transport mechanism to a fluid container 52 A fluid flow valve system according to claim 51 wherein, the further fluid flow transport mechanism contains a pressure responsive valve which is located in the cooperating tngger passageway connection portion 53 A fluid flow valve system according to the claims 51 or 52 wherein, the further fluid flow transport mechanism's pressure responsive valve is biased towards the closed position 54 A fluid flow valve system according to any of the claims 51 to 53 wherein, the further fluid flow transport mechanism's pressure responsive valve can open automatically and be held open when the tπgger passageway connection member is engaged with it 55 A fluid flow valve system according to any of the claims 51 to 54 wherein, the further fluid flow transport mechanism contains a mam shut-off valve m its mam fluid passageway 56 A fluid flow valve system according to any of the claims 51 to 55 wherein, the further fluid flow transport mechanism's main fluid passageway can be utilised as the containers filling passageway and the supply passageway for dehveπng fluid from the container 57 A fluid flow valve system according to any of the claims 51 to 56 wherein, the further fluid flow transport mechamsm contains a liquid filling passageway and liquid filling attachment 23 SUBSTTTUTE SHEET (RULE 25) which is exclusive from the main fluid passageway. 58. A fluid flow valve system according to any of the claims 51 to 57 wherein, the further fluid flow transport mechanism contains a safety valve which will allow fluid to vent from the container when the pressure within the container exceeds a predetermined value. 59. A fluid flow valve system according to any of the claims 51 to 58 wherein, the further fluid flow transport mechanism contains a non-return valve in the liquid filling attachment. 60. A fluid flow valve system according to any of the previous claims wherein, the further fluid flow transport mechamsm contains a trigger chamber located near or at the end of its trigger passageway system. 61. A fluid flow valve system according to either of the claims 60 wherein, the further fluid flow transport mechanism trigger chamber contains a trigger passageway valve. 62. A fluid flow valve system according to any of the previous claims wherein, the further fluid flow transport mechanism flotation valve is attached to a cam system which, when rotated to the closed position, applies to a force to the trigger passageway valve and substantially reduces the fluid flow through the trigger passageway. 63. A fluid flow valve system according to claim 62 wherein, as the cam of the further fluid flow transport mechanism starts to move part of it is introduced into the fluid stream coming from the main filling passageway outlet orifice which causes the cam to be positively rotated to its closed position. 64. A fluid flow valve system according to either of the claims 62 or 63 wherein, the further fluid flow transport mechanism's main filling passageway outlet orifice contains a deflection portion which causes in the fluid stream a shadow area around the cam so that the cam is positively removed from the fluid stream until its rotation cycle reaches a predetermined number of degrees. 65. A fluid flow valve system according to any of the claims 51 to 64 wherein, the further fluid flow transport mechanism's flotation member is mounted in a vertical orientation within a location tube. 66. A fluid flow valve system according to any of the previous claims wherein, the flotation member or the outlet of the trigger passageway are positioned at a point within the fluid container whereby, when the fluid level in the container reaches a predetermined level during the filling process, the fluid state within the trigger passageway changes. 67. A fluid flow valve system according to claim 66 wherein, the change in the fluid state within the trigger passageway is a substantial reduction of the dynamic flow of the fluid within the trigger passageway. 68. A fluid flow valve system according to any of the claims 51 to 59 wherein, during the filling cycle of container, the trigger passageway primary value is held open when fluid can flow through the further fluid flow transport mechanism's trigger passageway. 69. A fluid flow valve system according to claim 68 wherein, a substantial reduction of the flow of the fluid in the further fluid flow transport mechanism's trigger passageway causes the 24 SUBSTTTUTE SH EET (RULE 26) tngger passageway pπmary valve to close 70 A fluid flow valve system according to any of the previous claims wherein, a pliable sealing disc is located on the pnmary valve seat end of the pnmary valve movable piston 71 A fluid flow valve system according to any of the previous claims wherein, the pressure chamber inlet passageway is positioned and aligned with the central axis of the pπmary valve movable piston 72 A fluid flow valve system according to claim 71 wherein, when the pπmary valve movable piston forms a seal with the pnmary valve seat, the inlet end of the pressure chamber inlet passageway is of sufficient length that it projects into the mlet passageway 73 A fluid flow valve system according to any of the previous claims wherein, there is a flow deflection plate which is attached and located around the centre of the pliable sealing disc and is shaped to assist the fluid flow while deflecting the fluid flow from the pliable sealing disc and reducing erosion wear 74 A fluid flow valve system according to any of the previous claims wherein, the diameter of the pnmary valve movable piston is greater than the diameter of the effective sealing portion of the pπmary valve seat 75 A fluid flow valve system according to any of the previous claims wherein, the closing of the tπgger chamber valve mechanism in conditions of dynamic fluid flow causes an increase of pressure in the pressure chamber which thus forces the pnmary valve movable piston to a position where it produces a seal with the pnmary valve seat 76 A fluid flow valve system according to any of the previous claims wherein, a fluid flow restnction shield is located close to the pπmary valve seat when the pnmary valve movable piston approaches close to the pnmary valve seat when the pnmary valve movable piston approaches close to the pπmary valve seat such that it causes a build up of fluid pressure around the pπmary valve movable piston and this increase of fluid pressure decreases the speed of the closing action 77 A fluid flow valve system according to any of the previous claims wherein, the opening of the tπgger chamber valve mechanism in conditions of dynamic fluid flow causes a decrease of pressure in the pressure chamber which forces the pπmary valve movable piston to deny a seal with, and move away from, the pπmary valve seat 78 A fluid flow valve system according to any of the previous claims wherein, the tngger chamber valve mechanism is activated to move to its closed position when it expeπences vibrations above a predetermined valve 79 A fluid flow valve system according to claim 78 wherein, the vibration sensitive tπgger chamber valve mechanism is able to be reset to its armed position by means of a reset mechanism 80 A fluid flow valve system according to claim 79 wherein, the reset mechanism can be reset to its armed position by a manual ovemde system 81 A fluid flow valve system according to claim 80 wherein, the reset mechamsm can be 25 SUBSTTTUTE SHEET (RULE 26) reset to its armed position by a discrete remotely generated signal 82 A fluid flow valve system according to any of the previous claims wherein, a mechanical adjustment is installed on the pressure chamber side of the primary valve movable piston whereby it can be set to limit the distance the pnmary valve movable piston can travel form its closed position 83 A fluid flow valve system according to claim 82 wherein, the mechanical adjustment is linked with the operation of the tngger chamber valve mechanism 84 A fluid flow valve system according to any of the previous claims wherein, the mechanical adjustment is connected to an operating handle 85 A fluid flow valve system according to any of the previous claims wherein, the tπgger passageway is of sufficient length such that the tngger chamber valve mechanism can be housed within a piece of equipment separate from, and connectable to, the fluid flow valve system and/or the tngger passageway 86 A fluid flow valve system according to any of the previous claims wherein, the downstream end of the tngger passageway includes a valve connection system which remains closed when the valve connection system is not connected to a suitable piece of compatible separate equipment 87 A fluid flow valve system according to any of the previous claims wherein, the valve connection system closes before the fluid tight seal, between the tπgger passageway and the suitable piece of the compatible separate equipment, is broken duπng the disconnection process 88 A fluid flow valve system according to any of the previous claims wherein, a tπgger passageway supplementary valve is installed near the intersection of the tngger passageway and the pressure chamber 89 A fluid flow valve system according to claim 88 wherein, the tπgger passageway supplementary valve is biased towards the closed position 90 A fluid flow valve system according to claim 89 wherein, the biasing means is a spnng 91 A fluid flow valve system according to any of the claims 88 to 90 wherein, the tngger passageway supplementary valve extends past and protrudes proud of the body 92 A fluid flow valve system according to any of the claims 88 to 91 wherein, the tπgger passageway supplementary valve can be latched in its open position by engaging with a portion of the movable piston when it moves to its open position 93 A fluid flow valve system according to any of the claims 88 to 92 wherein, the tπgger passageway supplementary valve includes an indicator which is visible when it has been latched into its open position 94 A fluid flow valve system according to any of the claims 89 to 93 wherein, the tπgger passageway supplementary valve can be opened by manual intervention 95 A fluid flow valve system according to any of the previous claims wherein, the tπgger passageway is located within the passageway leading from the outlet aperture 96 A fluid flow valve system according to any of the previous claims wherein, the axes of 26 SUBSTTTUTE SHEET (RULE 25) the inlet and outlet passageways are approximately aligned and the axis of the pressure chamber is set at an angle of about ninety degrees 97 A fluid flow valve system according to any of the previous claims wherein, the axes of the mlet and outlet passageways are aligned with the axis of the pressure chamber 98 A fluid flow valve system according to claim 97 wherein, the body between the inlet and outlet passageways can be assembled in two portions and employ a joining mechamsm 99 A fluid flow valve system according to any of the previous claims wherein, the end of the outlet pipe, not connected to the outlet oπfice of the fluid flow valve system, is open and at the effect of atmosphenc pressure 100 A fluid flow valve system according to claim 99 wherein, the tngger passageway is located within the outlet pipe 101 A fluid flow valve system according to any of the previous claims wherein, the deflection plate stands proud of the pliable sealing disc and protrudes into the pnmary valve seat orifice to restrict and impede the flow of the fluid dunng the operation when the moveable piston is moving to its closed position 102 A fluid flow valve system according to any of the previous claims wherein, withm the movable piston is a second pressure chamber and withm the second pressure chamber is a second movable piston 103 A fluid flow valve system according to claim 102 wherein, when the pressure in the pressure chamber increases, the movable piston forms a partial seal around the pπmary valve seat 104 A fluid flow valve system according to claim 103 wherein, when the pressure in the second pressure chamber increases, the second movable piston forms a seal with the pπmary valve seat 105 A fluid flow valve system according to any of the previous claims wherein, the further cooperating fluid flow transport mechanism compπses a connection for attaching it to a fluid container, a mam valve for initiating or terminating the flow of fluid through the valve, an outlet aperture which is connectable to further fluid flow transport mechanisms, a tngger passageway height tube which includes a separate passageway to an external compatible tngger passageway connection portion which contains a normally closed valve 106 A fluid flow valve system according to claim 105 wherein, the compatible tngger passageway connection portion normally closed valve is opened after a sealing contact has been made with the tngger passageway connection member 107 A fluid flow valve system according to claim 105 wherein, the compatible tπgger passageway connection portion normally closed valve is opened after a contact has been made with a special decanting tool 108 A fluid flow valve system according to any of the claims 105 to 107 wherein, the further cooperating fluid flow transport mechamsm includes a safety valve device 109 A fluid flow valve system according to any of the claims 105 or 108 wherein, the further 27 SUBSTTTUTE SHEET (RULE 25) cooperating fluid flow transport mechanism includes a float unit incorporated into the trigger a passageway height tube. 110. A fluid flow valve system according to any of the previous claims wherein, the fluid flow transport mechanism float unit restricts the trigger passageway height tube when the fluid level in the fluid container reaches a predetermined height. 111. A fluid flow valve system according to claim 110 wherein, when the further cooperating fluid flow transport mechanism float unit restricts the trigger passageway height tube, an increase of pressure occurs in this height tube during a filling procedure. 112. A fluid flow valve system according to claim 111 wherein, the increase of pressure in the height tube during a filling operation is transfeπed to an increase of pressure in the trigger passageway which unlatches the trigger passageway primary valve and allows it to close. 113. A fluid flow valve system according to any of the previous claims wherein, there is a special splash guard suπounding the end of the trigger passageway height tube. 114. A fluid flow valve system according to any of the previous claims wherein, within the trigger passageway leading from the pressure chamber is an electric solenoid valve. 115. A fluid flow valve system according to claim 114 wherein, a switching mechanism is incorporated into the pick-up for the tanks fuel gauge which closes the switch when the level of the fluid in the tank would allow a filling operation to take place. 116. A fluid flow valve system according to claim 115 wherein, there is a pressure switch in the fluid supply line between the tanks connector portion and the AFL valves' primary valve which is in series with the fuel tanks switching mechanism which closes only when the supply line pressure from the filling bowser is experienced. 117. A fluid flow valve system according to any of the previous claims wherein, the AFL valve and the tanks pick-up for suppling fuel to the engine are incorporated into the same unit. 118. A fluid flow valve system according to any of the previous claims wherein, he AFL valve, the tanks pick-up and the fuel gauge pick-up are incorporated into the one unit. 119. A fluid flow valve system according to any of the previous claims wherein, the fluid flow valve system is installed between a source of water supply and a water conditioning apparatus such as a water filter, reverse osmosis unit, water chiller or hot water service. 120. A fluid flow valve system according to any of the previous claims wherein, the further cooperating fluid flow transport mechanism comprises a dispensing spout with a primary outlet passageway which leads from the water conditioning equipment and is open to atmospheric pressure and also has a trigger passageway which is blocked by a normally closed valve which is connected to a coπesponding release mechanism. 121. A fluid flow valve system according to either of the claims 119 or 120 wherein, the dispensing spout contains a trigger passageway connection from the fluid flow valve system which leads to the trigger passageway valve and the discharge fluid from the trigger passageway valve when the said valve is opened allows fluid to travel through the trigger discharge passageway and to then discharge into the spout. 28 SUBSTTTUTE SH EET (RULE 26) 122 A fluid flow valve system according to any of the claims 119 to 121 wherein, the tngger passageway leads to the tngger passageway valve which is located withm the dispensing spout mechamsm and the discharged fluid from the tngger discharge passageway returns to the bodies outlet onfice before the water conditioning system 123 A fluid flow valve system according to claim 122 wherein, the tngger passageway is located withm the tngger passageway discharge line 124 A fluid flow valve system according to any of the previous claims wherein, the fluid flow valve system is installed to monitor the cold water inlet line to a hot water service such that an increase of pressure within the cold water line above a predetermined value causes the tπgger passageway valve to open which allows the excess pressure to vent into a discharge passageway 125 A fluid flow valve system according to any of the previous claims wherein, the fluid flow valve system is installed at or near the top of a hot water tank and is aπanged such that the tπgger passageway valve is connected to a temperature responsive mechanism which when a pre-determined temperature is reached the tπgger passageway valve opens 126 A fluid flow valve system according to claim 125 wherein, the temperature responsive mechanism is also connected to a tngger passageway valve from a cold water inlet fluid flow valve system such that when the temperature responsive mechanism opens both tπgger passageway valves, both hot and cold water mixes and flows through the discharge line 127 A fluid flow valve system according to any of the previous claims wherein, a cylinder liner surrounds the movable piston and forms a seal between itself and the cylindncal pressure chamber 128 A fluid flow valve system according to any of the previous claims wherein, a cylinder liner is located into the cylindrical pressure chamber by a locating means 129 A fluid flow valve system according to any of the previous claims wherein, the cylindncal pressure chamber is located into the body assembly by a locating means 130 A fluid flow valve system according, to either of the claims 128 or 129 wherein, the locating means is a reduction of the aperture size of the component locating either the cylinder liner or the cylindncal pressure chamber 131 A fluid flow valve system according to claim 130 wherein, the locating means is positioned to maintain a predetermined distance between either the cylinder liner or the cylindncal pressure chamber from the pπmary valve seat 132 A fluid flow valve system according to any of the previous claims wherein, the fluid flow valve system is installed between the air conditioner's dπer and the evaporator's TX valve 133 A fluid flow valve system according to claim 132 wherein, the inlet and outlet connections are compatible with the connections of the air conditioning system and can be installed by insertion between existing connections 134 A fluid flow valve system according to any of the previous claims wherein, a pressure switch is located between the pnmary valve seat and the outlet onfice and commumcates with the outlet chamber 135 A fluid flow valve system according to any of the claims 1 to 133 wherein, the pressure switch is located m the low pressure return line from the evaporator to the compressor 136 A fluid flow valve system according to any of the previous claims wherein, the pressure switch is located in a compatible adaptor which is inserted within the connectors of the low pressure return line from the evaporator to the compressor 137 A fluid flow valve system according to any of the previous claims wherein, the compatible adaptor incorporates a non-return valve 138 A fluid flow valve system according to any of the previous claims wherein, the pressure switch is wared in seπes with the electnc solenoid such that when the pressure switch contacts close due to an increase of fluid pressure within the system the electnc solenoid will operate when sufficient voltage is supplied to its circuit 139 A fluid flow valve system according to any of the previous claims wherein, one electnc wire from the electric solenoid is earthed while the other electnc wire is connected to the supply side of the air conditioner's electnc thermostat 140 A fluid flow valve system according to any of the previous claims wherein, when the fluid pressure around the pressure switch drops below, or is below, the pressure responsive setting of the pressure switch, the pressure switch opens and the electnc cuπent to the electnc solenoid is terminated and the solenoid valve closes 141 A fluid flow valve system according to any of the previous claims wherein, when the pressure switch is open, the compressor will not operate 142 A fluid flow valve shut-off system compnsing a body assembly, having an mlet for connection to a fluid supply, an inlet passageway leading from the mlet onfice of the inlet to a pnmary valve seat outlet, a pπmary valve seat which encircles and is axially aligned with the pnmary valve seat outlet, an outlet chamber which suπounds encircles and is axially aligned with the axis of the pπmary valve seat and pnmary valve seat outlet and which leads from the pnmary valve seat outlet to an outlet aperture and this body assembly is connectable within the plumbing network of an air conditioning system and is located between the dner and TX valve, a pressure chamber which is axially aligned with the axis of the pnmary valve seat and is located on the outlet side of the said pπmary valve seat, a pressure chamber inlet passageway which allows fluid from the mlet passageway to communicate with the fluid in the pressure chamber, a tπgger passageway which leads from the pressure chamber to the outlet side of the pπmary valve seat and includes a tngger passageway valve system, an electnc solenoid which, when energised, opens the tngger passageway valve system and a pressure sensing switch which is located in the low pressure line leading from the evaporator to the compressor and which is wired in senes with the electnc solenoid 143 A fluid flow valve shut-off system according to claim 142 wherein the pressure sensing switch is located on a compatible adaptor which includes a non-return valve 30 SUBSTTTUTE SHEET (RULE 26) 144 A fluid flow valve shut-off system according to any of the claims 142 to 143 wherein when the pressure switch is open, the compressor will not operate 145 A fluid dispensing spout mechanism compπsing an above counter-top outlet spout body which contains a main fluid flow passageway which leads from a main fluid flow passageway connection to a spout mechanism, a tngger valve mechamsm which can make and break a seal with the tngger passageway valve seat which is located between the tngger passageway connection and the tπgger passageway return connection by means of an operational handle, an above counter-top outlet body lower section which is located between the above counter-top outlet spout body and the mounting plate 146 A fluid dispensing spout mechanism according to claim 145 wherein, there is a seal formed between the above counter-top outlet spout body and the above counter-top outlet body lower section suπounding the tngger passageway return channel 147 A fluid dispensing spout mechamsm according to any of the claims 145 or 146 wherein, the tngger passageway return connection forms a seal with the above counter-top outlet body lower section at the tπgger passageway return channel 148 A fluid dispensing spout mechanism according to any of the claims 145 or 147 wherein, the tπgger passageway connection forms a seal with the above counter-top outlet spout body at the tπgger passageway leading to the tπgger passageway valve seat 149 A fluid dispensing spout mechanism according to any of the claims 145 or 148 wherein, the tπgger passageway is located within the tπgger passageway return channel 150 A fluid dispensing spout mechanism compπsing an above counter-top outlet spout body which contains more than one main fluid flow passageway such passageway's which leads from diffeπng temperature devices to the spout mechanism, a tngger valve mechanism which can make and break a seal with the tngger passageway valve seat which is located between the tπgger passageway connection and the tngger passageway return connection by means of an operational handle, and as the operating handle selects one of the main fluid flow passageways a secondary mam fluid flow passageway valve is opened before the tπgger passageway valve is opened 151 A fluid flow valve system according to any of the previous claims wherein, an outlet passageway from the top of a hot water tank proceeds via a non-return valve to the cold water passageway leading into the bottom of the hot water tank where another non-return valve is located near the cold water line so these two non-return valves prevent hot water from flowing into the cold water line and prevent cold water from flowing into the hot water line and between the two non-return valves is located this fluid flow valve system 152 A fluid flow valve system according to claim 151 wherein, the tπgger passageway from the pulse valve leads to a tπgger valve which is responsive to a temperature probe located at or near the top of the hot water tank 153 A fluid flow valve system according to claim 151 or 152 wherein, when the temperature 31 SUBSTTTUTE SHEET (RULE 26) increases above a predetermined valve the temperature probe opens the tπgger valve and allows mixed hot and cold mixed water to be released to the atmosphere 154 A fluid flow valve system according to claim 153 wherein, the predetermined temperature is approximately between 95 °C to 98°C 155 A fluid flow valve system according to any of the previous claims wherein, the tπgger passageway valve is connected to tπgger piston which moves within a tπgger pressure chamber such that when the tπgger piston moves to its limit of travel away from the tngger valve, the tπgger valve closes 156 A fluid flow valve system according to claim 155 wherein, a tπgger pressure passageway communicates between the tngger pressure chamber and the outlet side of the pπmary valve 157 A fluid flow valve system according to any of the claims 155 to 156 wherein, the end of the tπgger piston furthermost from the tπgger passageway valve expenences the effects of atmosphenc pressure 158 A fluid flow valve system according to any of the claims 155 to 157 wherein, the tngger piston is biased towards the tngger passageway valve 159 A fluid flow valve system according to claim 158 wherein, the biasing means is a spnng 160 A fluid flow valve system according to claim 159 wherein, the tension of the spnng is adjustable 161 A fluid flow valve system according to any of the claims 155 to 160 wherein, as the increasing pressure in the tngger pressure chamber overcomes the biasing means the tngger passageway valve closes 162 A fluid flow valve system according to any of the claims 1 to 131 wherein, the tngger passageway valve can be closed by a float 163 A fluid flow valve system according to claim 162 wherein, the float encircles the outlet passageway 164 A fluid flow valve system according to any of the claims 162 to 163 wherein, the fluid flow valve system is mounted within a storage tank 165 A fluid flow valve system according to claim 164 wherein, the storage tank is a cistern 166 A fluid flow valve system according to any of the claims 162 to 165 wherein, the fluid flowing from the outlet passageway turns an impeller 167 A fluid flow valve system according to claim 166 wherein, the impeller is connected to a second impeller which is located in the tanks outlet passageway 168 A fluid flow valve system according to claim 167 wherein, when fluid flows from the outlet passageway and turns the impeller, the second impeller forces the fluid in the tank through the tanks outlet passageway 32 SUBSTTTUTE SHEET (RULE 25)

Inventors: ESPLIN PATRICIA ANNE, ESPLIN TREVOR THOMAS, MORRISON JEAN, MORRISON WALTER GEORGE, ESPLIN, PATRICIA, ANNE, ESPLIN, TREVOR, THOMAS, MORRISON, JEAN, MORRISON, WALTER, GEORGE
Applicants: ESPLIN PATRICIA ANNE, ESPLIN TREVOR THOMAS, MORRISON JEAN, MORRISON WALTER GEORGE, ESPLIN, PATRICIA, ANNE, ESPLIN, TREVOR, THOMAS, MORRISON, JEAN, MORRISON, WALTER, GEORGE
Application year: 1997
Main classification: F16K47
IPC codes: B67D5, F16K31, F17C13