CA2268861A1

CA2268861A1 - Anti hammer pilot operated valves having remote pilot for use in refuelling, domestic mains water, refrigeration applications

Info

Publication number: CA2268861A1
Application number: CA002268861A
Authority: CA
Inventors: Trevor Thomas Esplin; Patricia Anne Esplin; Walter George Morrison; Jean Morrison
Original assignee: Individual
Current assignee: Individual
Priority date: 1996-10-08
Filing date: 1997-10-08
Publication date: 1998-04-30
Also published as: EP0931231A4; EP0931231A1; WO1998017935A1

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

WO 98/f 7935 PCTIAU97100674 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 andlor a momentary low pressure shock wave in the fluid downstream of the valve. This invention also has particular relevance to those applications which require high flow rates, remote triggering, where nil electric 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 appropriate 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 andlor the pressure of the fluid that the valve is controlling. In one of its many and varied forms, this invention includes a single signal latching system for activating and deactivating the triggering device. In another form includes a vibration sensing triggering 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 during 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 irrigation systems. It has the ability to provide high flow rates, remote triggering with or without the need of any electric power while providing a long term reliability by being able to perform consistently within its design criteria. The invention can also be used for the control of various fluids such as in the fuel systems for motor vehicles, for marine use, for aeronautical and aerospace applications. Its domestic, commercial and industrial applications can cover the control of air, gas, water and a wide variety of different volatile and toxic fluids.
SUBSTiTLJTE SH~ET tRULE Z6) WO 98117935 PCTJAU97JOOb74 BACKGROUND OF THE INVENTION
The type of solenoid valves which can be found in washing machines and dishwashers require a continual electrical current to maintain their operational state.
When energised, the solenoid valve opens an orifice passageway in the centre of the diaphragm. As the diaphragm has another, but smaller orifice, the action of the solenoid allows the fluid pressure to open the primary diaphragm the fluid flow valve and commence the fluid flow. When the electrical current is terminated, the solenoid valve closes the orifice passageway and as further fluid flows through the smaller orifice and builds up pressure on that side, the increase of the fluid pressure closes the primary diaphragm valve which then terminates the fluid flow.
The design of these solenoid valves locate their internal inlet orifice axially surrounding 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 inletloutlet side of the diaphragm exceeds the pressure on the other side and the primary 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 inledoutlet side of the diaphragm and thus the primary 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 current 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 electrical current to remain open, their diaphragms are located directly in the fluid flow path which not only causes flow restriction, but also encourages erosion wear to the soft valve seal. They are not particularly satisfactory when used for irrigation or main water supply line applications especially when the water contains a degree of impurities in the form of solids.
In those situations, these units are required to remain open for long periods 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 electric 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 primary 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 trigger system which may only require a single momentary pulse of electrical charge to change its operational state, can provide a closing mechanism which greatly reduces water hammer, can SU85TITUTE SH~~T (RULE 26) ........~_.._...._..___...._.. ........._......,..~..'.-..~,-~y~......_......,..__.._... ~.. .....~, ........ ......._........ ~. ~ ...._._ . .. . .. _....

provide a remotely controlled valve system which has a low internal pressure loss with high flow rate, can eliminate the need for a spring to help close the primary 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 description of the operation of a standard diaphragm solenoid valve will show how this current invention differs in design and concept.
The base component of a standard electrically operated solenoid valve is constructed such that fluid passes from the inlet passageway into the inlet chamber which contains within its centre a smaller diameter, axially located primary valve seat within which is located an outlet orifice which leads to an outlet passageway. Onto the valve seat the sealing section of the diaphragm valve, which is the primary 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 within the chamber above in 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 orifice below the diaphragm, plus the effect of any spring above the diaphragm, creates a condition whereby the diaphragm closes expeditiously with a slamming motion. The volume area of the inlet orifice and passageways and the volume of the chamber above the diaphragm becomes highly pressurised 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 prior 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 main supply line to the appliance from the tap remains pressurised when the appliance is turned off and therefore requires a suitably heavy duty flexible hose to withstand the -mains pressure over a considerable period of time. With this method, the risk of flooding is present should the flexible hose experience a rupture type failure.

SUBSTITUTE SHEET (RULE z6) WO 98/17935 PCTlAU97/00674 By way of example, one embodiment of the present invention can be described in the following manner.
The base of the standard solenoid valve can remain the same design as described above except that the fluid passes through the unit in the reverse direction. Thus the fluid inlet passageway 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 trigger passageway leads from the pressure chamber located above the valve piston member. A trigger passageway leads from 1 S the pressure chamber to a trigger valve mechanism and then progresses as the trigger outlet passageway and outflows into the main fluid flow downstream of the fluid inlet passageway valve seat.
Located in the trigger passageway is a trigger valve seat or trigger valve mechanism.
Altemativeiy, the trigger passageway can lead to a trigger chamber which contains the trigger valve mechanism. This trigger can be manually, electrically or mechanically operated. The trigger valve can be described as a soft valve seal which lowers onto, and raises form, the trigger valve seat which surrounds the trigger outlet passageway. This trigger outlet passageway can lead to the main fluid outlet passageway. The trigger outlet passageway can include more than 2~ one outlet orifice. The size of the pressure chamber inlet passageway and the trigger outlet passageway are of a larger diameter than the pressure chamber inlet passageway. When the trigger 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 rising from the inlet fluid passageway valve seat and, as a result, the valve member opens by rising from the inlet fluid passageway valve seat. When the trigger 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 necessarily need a spring 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 SU8ST1TUTE SH~~T (RULE Zfi) _.. ._.__..._ _..._ _.".. t ,r ~ ~ , _ _ . __.. .

WO 98!17935 PCTlAU97/00674 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, pressurises the supply pipeline.
This design greatly reduces the effect referred to as water hammer.
The trigger can be further defined as using the same principle as the standard solenoid whereby a continual electrical current opens the valve and a termination of the current closes the valve. It can also be arranged whereby two solenoids are set at about ninety degrees to each other and are arranged to have a latching arrangement whereby an electrical pulse to one raises the trigger 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 position. It should be noted that this is a single pulse on, single pulse off operation and can be also achieved with other layouts of trigger combinations. Axially aligned solenoids with sliding trigger 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 irrigation control systems.
The trigger mechanism can be arranged to provide a severe restricting function 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 trigger 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 trigger can be used which can include a handle system with a cam mechanism above the moveable piston which can provide a variable 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 trigger 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 periods while doing so without the need for outside power consumption.
While this invention was originally 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 -surrounding the storage device become hotter. While not all LPG containers require an SUBSTITUTE SH~~T (RULE 26) Automatic Fill Limiting (AFL) valve to be installed, those that do are normally covered by fairly strict 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 integrity 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 trigger 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 experience the high static pressure experienced 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 experience the higher static fluid pressures they are far less likely to fracture or rupture. Therefore, in those instances where the trigger passageway is located within the flexible hose, should a small leak in the trigger 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 contributing further -to the danger of the situation. in normal form or with the dual latching system, a shut-off signal SUBSTZTL1TE SHEET (RULE 26~
..... ...... ... T ... .... ~ ~ .. .....

WO 98117935 PCTlAU97/00674 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 security alarm system whereby the incorrect 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 security 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 mechanism for restoring normal operation may require accessing the interior of the fuel tank which would mean the abrupt end to a joy-ride type theft as time and the services of qualified personnel are required to restore the full i 5 operation of the fuel supply.
As with the example for washing machines as described above, a similar device could be connected to garden hoses whereby the trigger 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 trigger passageway valve is connected to a float which will respond to the water level in the cistern by closing the trigger valve passageway. In order to ensure a positive shut-off from the trigger 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 current eighty per cent fill systems enjoy a number of operational problems which detract from the benefits they are trying to offer.
The majority of these systems place a float operated trigger and shut-off valve as one unit into SUBSTITUTE SHEET (RULE 2fi) the LPG container. These current systems unnecessarily add to the cost and are not as effective as this embodiment of the invention which splits the trigger mechanism from the filling shut-off and provides a method of pressure filling with no atmospheric 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 primary 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 f ping 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 1 S the trigger 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. During the filling process, the fluid flowing into the valve assembly devices pressure chamber is allowed to flow relatively unrestricted through the trigger passageway, through the mating connection, through the mating connection passageway and through the flotation valve into the LPG container. When the flotation valve is restricted to the point that the flow of fluid entering 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 trigger passageway. Valve one would be located within the trigger 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 trigger passageway valves are open. Valve two is located in the other end of the trigger passageway within the trigger passageway connection. This is a normally closed valve which is only opened after the trigger passageway connection makes a sealing contact with the mating connector on the LPG container valve. Valve three is a normally closed valve located within the mating connector which only opens after the trigger 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 mechanism between the moveable piston and the connection end. This greatly reduces the discharge during the disconnection process and adds to the overall safety of the filling process.
Unless the filling station equipment mechanism is correctly installed onto an LPG container which is less than eighty percent full, the fuel flow will not be able to be initiated.

SUBST1TUTF SH~~T (RULE 2~y ..~.~.._,~ t _ ..

In another embodiment of this invention there is an Automatic Fill Limiting (AFL) valve which eliminates the problems which are associated with the majority of AFL
valves currently 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 trigger register for terminating the inlet flow can be instigated by the fluid level indicator in that when the 80% fill is achieved and the fluid level indicator opens an electrical trigger circuit, the trigger passageway solenoid is de-energised and the fill is terminated.
In another embodiment of this current 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 electric solenoid for opening the trigger passageway valve and a pressure sensitive switch which is located downstream of the trigger passageway valve seat. This fluid flow valve system is normally Located on the high pressure line between the drier mechanism 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 primarv_ valve seat and the non-return 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 electric solenoid will be terminated which will close the secondary valve which will cause the primary 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 in 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 arranged 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 current invention this valuing system can be installed between the town supply of water and water conditioning equipment such as water filters, reverse osmosis units, hot water systems, chiliers 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 SUBST1TUT~ SH~ET (RULE 2b) atmosphere. experiences 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 experience are the dynamic flow pressures of the water and the unit can be designed such that a flow restriction occurs within the unit which prevents any build up of dynamic flow pressure within 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 trigger passageway valve, one line which takes the fluid discharged from the trigger passageway valve back to the fluid supply Iine 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 trigger passageway pipe can be located within the discharge trigger passageway pipe so as to give the appearance of only two pipes going to, or coming from, this valuing system. In this manner, should the high pressure trigger 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 trigger valve, a trigger valve inlet passageway, a trigger valve outlet passageway and a main outlet passageway and spout. For this above counter-top outlet spout, the trigger valve inlet passageway can be contained within the trigger 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 trigger 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 trigger 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 arranged such that an increase of water pressure allows the cold water trigger valve to open and thus opens the primary cold water control valve and discharge to atmosphere thereby reducing the pressure within the hot water tank. Also, they can be arranged so that when the temperature sensing trigger valve opens it opens not only the primary sensing valve but also opens the primary 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 SU85TtTUTE SHEET (RULE 2b) ____ __~.._... __,...~._.,r t _ 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.
BRIEF DESCRIPTION OF THE DRAWINGS
Preferred 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 hut 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 I3 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).
Surrounding the fluid inlet passageway valve seat is the outlet passageway ( 110) which leads to SU85TtTUTE SHEET tRULF 26) the outlet orifice ( l 0).
Attaching to the base assembly is the top assembly which makes a sealing contact at the outer housing ( 1 i 1 ). 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 ( 1 I ) 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 1 ~ 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 ( I S) where a non-return 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 {2I ) a non return valve (not shown) can be mounted. Leading form the pressure chamber is a trigger passageway ( I 7) which contains a trigger mechanism devices (not shown). The extended periphery ( 1 I2) of the turbulence shield is arranged 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 towers the pressure of the dynamic fluid flow pressure between the valve member arid 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 SU8ST1TUTE SH~ET (RULE 2fi~
._~..~.__,~ , ..

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 variation 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-ring (42). Into the recess (43) fcts a spring (45) which biases the jumper valve away from the moveable piston. The passageway (50) allows fluid to flow to the pressure chamber as previously described.
Figure 3 details one embodiment of the trigger mechanism. The trigger valve ( 16), can be comprised of an electric solenoid {25), a central moveable stem (24), a trigger chamber ( 18), a trigger valve seat ( 19) and a trigger valve mechanism (20) which can come into sealing contact with the trigger valve seat. When the electronic solenoid is energised, the fluid from the trigger passageway ( 17) is allowed to flow through the trigger outlet passageway (23) unhindered.
When the solenoid is not energised, the spring (26) returns the central moveable stem to its rest position and the trigger valve mechanism seals the trigger valve seat. A
second electric solenoid system (28) can be installed so that its central moveable stem (27) has an interfering contact (30) with the first central moveable stem. When the second electric solenoid is energised, the second central moveable stem allows the first central moveable stem to descend and seal the trigger valve seat while latching the second central moveable stem in the retracted position. A single pulse to the first solenoid will open the trigger valve seat seal and allow the second central moveable stem to be biased by the spring (29) to latch under the first central moveable stem and thus keep the trigger 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 trigger 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 trigger 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 various SU8STTTUTE SHEET (RULE Z6) 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 main 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 trigger passageway valve connection system from the Fluid Flow Valve Assembly. This secondary passageway within the cylinders main valve includes a shut-off valve operated by a flotation device which, when installed within the gas cylinder, will allow during a tilling procedure for a termination of the fluid flow through the secondary passageway when the level of the fluid in the cylinder causes the float to rise. The float location is positioned such that the shut-off of the secondary passageway occurs when the cylinder is 80% full.
Therefore, during a filling operation when the Improved Fluid Flow Valve Assembly is connected to the cylinders main valve and the trigger passageway valve connection system is attached to the mounting portion and the cylinder is being tilled, the operation of the shut-oft' of the secondary valve will cause a rise of pressure in the pressure chamber of the Fluid Flow Valve Assembly which will cause the primary valve moveable piston to form a seal with the primary 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, during a filling operation when the shut-off has occurred, the trigger 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 tiom the primary valve seat. Also, if the Fluid Flow Valve Assembly is disconnected from the cylinder valve first, the shut-off has already occurred 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 during this type of decanting procedure, when the float on the secondary passageway encounters the rising fluid level, the secondary valve mechanism shuts and terminates the filling procedure.
In Figure 8 we have one embodiment of the AFL valve whereby the triggering of the fluid flowing into the tank is initiated by the opening of the solenoid valve. In this diagram the electric windings of the solenoid and the mounting fittings for attaching the AFL valve into the cylinder have not been shown. The body assembly ( I ) has an inlet orifice (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 within the pressure chamber is a movable piston (8.) which makes a sliding sealing contact with the internal wail of the pressure chamber. Located down the centre axis of the movable piston is a small diameter SUBSTITUTE SHEET RULE 2fi) ._. ..__._ . . __ _~.~.. T

orifice (9) located on the inlet end of the movable piston is a main valve seal (IU). 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 trigger egress passageway ( 12) which communicates with a trigger passageway ( 13 ) which leads to a solenoid chamber ( 14). Leading from the solenoid chamber is a trigger outlet passageway ( 15 ) which leads to a non-return valve (16) and exits from the body assembly at (17). Surrounding the trigger 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. 'I he main cylinder seal ( I8) 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 electric 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 I S 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 trigger egress passageway to the trigger passageway and through the solenoid chamber then into the trigger outlet passageway at a faster rate than it flows through from the small diameter orifice. 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 (?2) has returned to its rest position under the influence of the solenoid piston spring (21). The pressure in the trigger passageway ( 13 ) builds up as does the pressure in the pressure chamber 2~ (7) which therefore forces the movable piston from the pressure chamber which causes a seal to be made between the main valve seal ( I O) and the shut-ott~ 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 trigger outlet passageway then into the trigger passageway and then venting into the inlet passageway. This prevents any volume discharge from the AFL valve should tire 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 trigger 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 electric solenoid when the fluid level is at the 8U% full level. There is also a pressure sensing switch in the circuit which closes when a fluid supply pressure above 120_pounds is experienced. In this manner, the till solenoid is only energised when the contents of the tank are below 80°io and when the supply pressure of the SUBSTITUTE SHEET (RULE 26) WO 98117935 PCTlAU97/00674 delivery pump is experienced.
In another embodiment of the present invention it will be seen from Figures 10 and i I
that the major components remain unchanged however there is a different mechanical triggering system which provide an accurate termination of the fluid flow at the required time during the tilling process and, as well, are highly reliable.
In Figure lU fluid flows from the flow chamber into the tank through the main outlet passageway (31 ) past a trigger valve pivot plate (32). 'This trigger 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 opening pin (36) which is attached to the trigger valve pivot plate (32). As the trigger valve pivot plate starts to move the trigger 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 11 by the force of the fluid coming into interfering contact with it. It will be noted in Figure lU that with the position of the trigger valve pivot plate the trigger 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 trigger valve has closed, the main 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 t3uid 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 trigger valve.
In Figure i2 the body (40) contains the inlet orifice passageway (41 ) and the inlet valve seat (42 j. The piston (43) has a primary valve seat seal (44 j and a pressure chamber inlet passageway (45) which extends form the inlet orifice passageway, through the piston to the pressure chamber (46). The pressure chamber is contained within the cylindrical 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 trigger passageway (51 ) which leads to a trigger valve (not shown).

SUBSTTTUTF SHEET (RULE 26) _ _ _ _ _. _w._.,~.~..,~.__e _., . ._ In Figure I3, 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 1 ~ 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 transferred 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 S U B ST1TUT~ S H ~ ~T { R U LE 26 ) modifications, obvious to those skilled in the art, can be made thereto without departing from the scope of the present invention.

SUBSTITUTE SH E~T (RULE 26) ...... .,......T.......~............ T ,.,..... . .. ~

Claims

THE CLAIMS DEFINING THE INVENTION ARE AS FOLLOWS:

1. A fluid flow valve system comprising:
a body assembly, having an inlet for connection to a fluid supply, an inlet passageway leading from the inlet orifice of the inlet to a primary valve seat outlet, a primary valve seat which encircles and is axially aligned with the primary valve seat outlet, an outlet chamber which surrounds encircles and is axially aligned with the axis of the primary valve seat and primary valve seat outlet and which leads from the primary valve seat outlet to an outlet aperture and this body assembly is connectable to a further fluid flow transport mechanism;
a cylindrical pressure chamber which is axially aligned with the axis of the primary valve seat and is located on the outlet side of the said primary valve seat;
located within the pressure chamber and making a sliding and sealing contact with it is a primary valve movable piston which, when moved fully towards the primary valve seat, forms a fluid tight seal with it, wherein the effective sealing area of the primary valve seat is less than the area of the sealing contact of the primary valve movable piston;
a pressure chamber inlet passageway which allows fluid from the inlet passageway to communicate with the fluid in the pressure chamber;
and a trigger 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 primary 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-ring 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 primary 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.

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 orifice which is located within the further fluid flow transport mechanism.

10. A fluid flow valve system according to any of the previous claims wherein, within the body assembly which contains the outlet aperture are two passageways, one is the trigger 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, within the trigger passageway system of the further fluid flow transport mechanism is located a trigger passageway secondary valve.

12. A fluid flow valve system according to any of the previous claims wherein, the end of the trigger passageway further most from the pressure chamber terminates in a trigger passageway connection member which is compatible with a cooperating trigger 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 trigger passageway connection member incorporates a fast connect/disconnect attachment mechanism which is compatible with the cooperating trigger passageway connection portion.

14. A fluid flow valve system according to any of the previous claims wherein, located within the end of the trigger passageway connection member is a trigger 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 trigger passageway valve is held open after the trigger passageway connection member makes a sealing connection with the cooperating trigger 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 trigger passageway and positioned between the pressure chamber and the trigger passageway connector valve is a trigger passageway primary 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 trigger passageways which are closed, the fluid pressure in the pressure chamber is therefore relatively lower and the primary valve movable piston moves away from the primary 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, during those times of dynamic fluid flow when any of the valves in the trigger 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 trigger passageway, an increase of the pressure in the pressure chamber occurs which causes the primary valve movable piston to move away from its fully open position and to form a seal with the primary valve seat.

19. A fluid flow valve system according to any of the previous claims wherein, one end of the trigger passageway primary 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 trigger passageway.

20. A fluid flow valve system according to claim 19 wherein, the end of the trigger passageway primary valve mechanism shaft which protrudes proud of the pressure chamber is exposed to the effects of atmospheric pressure.

21. A fluid flow valve system according to either claim 19 or claim 20 wherein, the trigger passageway primary 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 trigger passageway primary valve shaft is moved to its limit of travel from the pressure chamber, the trigger passageway primary 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 trigger passageway primary 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 sprang.

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 within 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 trigger passageway primary valve mechanism which is exposed to the effects of atmospheric pressures of such a length to allow an external force to move the trigger passageway primary valve mechanism to an open position.

29. A fluid flow valve system according to any of the previous claims wherein, when the trigger passageway primary 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 trigger passageway primary valve is held open by a latching mechanism cooperating between it and the piston when the force required to move the trigger passageway primary 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 in the inlet passageway, the primary valve movable piston is forced away from its fully open position and it unlatches the trigger passageway primary valve latching mechanism and allows the trigger passageway primary 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 trigger passageways, when there is sufficient fluid flow through the fluid flow valve system and the trigger passageway primary valve closes, a build up of pressure in the pressure chamber results which is sufficient to produce an effective seal between the primary valve movable piston and the primary valve seat.

32. A fluid flow valve system according to claim 31 wherein, the biasing means is a spring.

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 trigger valve mechanism is located within the pressure chamber.

35. A fluid flow valve system according to any of the claims 1 to 33 wherein, the trigger passageway leads to a trigger chamber.

36. A fluid flow valve system according to claim 35 wherein, a trigger outlet passageway leads from the trigger chamber to an outlet passageway downstream of the primary valve seat.

37. A fluid flow valve system according to claim 36 wherein, within the trigger chamber is a trigger chamber valve seat which surrounds the orifice leading from the trigger chamber to the trigger outlet passageway.

38. A fluid flow valve system according to claim 37 wherein, the fluid flows from the trigger chamber past the trigger chamber valve seat to the trigger outlet passageway.

39. A fluid flow valve system according to claim 37 or 38 wherein, a trigger chamber valve mechanism is positioned so that it can make a sealing contact with the trigger chamber valve seat.

40. A fluid flow valve system according to any of the claims 35 to 39 wherein, the trigger chamber valve mechanism is attached to the central movable stem of an electric solenoid valve system.

41. A fluid flow valve system according to claim 40 wherein, the central movable stem of the electric solenoid valve system is biased towards the trigger chamber valve seat.

42. A fluid flow valve system according to claim 40 or claim 41 wherein, the central movable stem for the trigger chamber valve mechanism comes into interference contact with a second central movable stem of a second electric solenoid system.

43. A fluid flow valve system according to claim 42 wherein, the second central movable stem of the second electric solenoid system is mounted at or about right angles to the central movable stem of the electric solenoid valve system.

44. A fluid flow valve system according to claim 42 or claim 43 wherein, the second central movable stem is biased towards the trigger 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 electric solenoid valve system when that electric solenoid is momentarily energised.

46. A fluid flow valve system according to any of the claims 42 to 45 wherein, the central movable stem for the electric solenoid valve system is allowed to form a sealing contact with the trigger chamber valve seat when the second central movable stem unlatches as and when the electric solenoid of the second electric solenoid system is momentarily energised.

47. A fluid flow valve system according to any of the claims 42 to 46 wherein, a manual override latching system is provided to allow the trigger chamber valve mechanism, 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 override latching system comprises 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 springs.

51. A fluid flow valve system according to any of the previous claims wherein, the further fluid flow transport mechanism contains a trigger passageway, a cooperating trigger passageway connection portion, a main trigger passageway, a main fluid passageway valve and a connection arrangement 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 trigger 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 trigger 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 main shut-off valve in its main 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 far delivering 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 mechanism contains a liquid filling passageway and liquid filling attachment 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 mechanism 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 trigger passageway primary 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 primary valve seat end of the primary 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 primary valve movable piston.

72. A fluid flow valve system according to claim 71 wherein, when the primary valve movable piston forms a seal with the primary valve seat, the inlet end of the pressure chamber inlet passageway is of sufficient length that it projects into the inlet 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 primary valve movable piston is greater than the diameter of the effective sealing portion of the primary valve seat.

75. A fluid flow valve system according to any of the previous claims wherein, the closing of the trigger chamber valve mechanism in conditions of dynamic fluid flow causes an increase of pressure in the pressure chamber which thus forces the primary valve movable piston to a position where it produces a seal with the primary valve seat.

76. A fluid flow valve system according to any of the previous claims wherein, a fluid flow restriction shield is located close to the primary valve seat when the primary valve movable piston approaches close to the primary valve seat when the primary valve movable piston approaches close to the primary valve seat such that it causes a build up of fluid pressure around the primary 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 trigger chamber valve mechanism in conditions of dynamic fluid flow causes a decrease of pressure in the pressure chamber which forces the primary valve movable piston to deny a seal with, and move away from, the primary valve seat.

78. A fluid flow valve system according to any of the previous claims wherein, the trigger chamber valve mechanism is activated to move to its closed position when it experiences vibrations above a predetermined valve.

79. A fluid flow valve system according to claim 78 wherein, the vibration sensitive trigger 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 override system.

81. A fluid flow valve system according to claim 80 wherein, the reset mechanism can be 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 primary 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 trigger 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 trigger passageway is of sufficient length such that the trigger chamber valve mechanism can be housed within a piece of equipment separate from, and connectable to, the fluid flow valve system and/or the trigger passageway.

86. A fluid flow valve system according to any of the previous claims wherein, the downstream end of the trigger 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 trigger passageway and the suitable piece of the compatible separate equipment, is broken during the disconnection process.

88. A fluid flow valve system according to any of the previous claims wherein, a trigger passageway supplementary valve is installed near the intersection of the trigger passageway and the pressure chamber.

89. A fluid flow valve system according to claim 88 wherein, the trigger 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 spring.

91. A fluid flow valve system according to any of the claims 88 to 90 wherein, the trigger 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 trigger 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 trigger 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 trigger passageway supplementary valve can be opened by manual intervention.

95. A fluid flow valve system according to any of the previous claims wherein, the trigger 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 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 inlet 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 mechanism.

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 orifice of the fluid flow valve system, is open and at the effect of atmospheric pressure.

100. A fluid flow valve system according to claim 99 wherein, the trigger 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 primary valve seat orifice to restrict and impede the flow of the fluid during 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, within the movable piston is a second pressure chamber and within 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 primary 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 primary valve seat.

105. A fluid flow valve system according to any of the previous claims wherein, the further cooperating fluid flow transport mechanism comprises a connection for attaching it to a fluid container, a main 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 trigger passageway height tube which includes a separate passageway to an external compatible trigger passageway connection portion which contains a normally closed valve.

106. A fluid flow valve system according to claim 105 wherein, the compatible trigger passageway connection portion normally closed valve is opened after a sealing contact has been made with the trigger passageway connection member.

107. A fluid flow valve system according to claim 105 wherein, the compatible trigger 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 mechanism includes a safety valve device.

109. A fluid flow valve system according to any of the claims 105 or 108 wherein. the further 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 III wherein, the increase of pressure in the height tube during a filling operation is transferred 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 surrounding 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 corresponding release mechanism.

121. A fluid flow valve system according to either of the claims 119 or I20 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.

122. A fluid flow valve system according to any of the claims 119 to 121 wherein, the trigger passageway leads to the trigger passageway valve which is located within the dispensing spout mechanism and the discharged fluid from the trigger discharge passageway returns to the bodies outlet orifice before the water conditioning system.

123. A fluid flow valve system according to claim 122 wherein, the trigger passageway is located within the trigger 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 trigger 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 arranged such that the trigger passageway valve is connected to a temperature responsive mechanism which when a pre-determined temperature is reached the trigger passageway valve opens.

126. A fluid flow valve system according to claim 125 wherein, the temperature responsive mechanism is also connected to a trigger passageway valve from a cold water inlet fluid flow valve system such that when the temperature responsive mechanism opens both trigger 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 cylindrical 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 cylindrical 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 cylindrical 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 cylindrical pressure chamber from the primary 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 drier 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 primary valve seat and the outlet orifice and communicates 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 in 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 wired in series with the electric solenoid such that when the pressure switch contacts close due to an increase of fluid pressure within the system the electric 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 electric wire from the electric solenoid is earthed while the other electric wire is connected to the supply side of the air conditioner's electric 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 electric current to the electric 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 comprising:
a body assembly, having an inlet for connection to a fluid supply, an inlet passageway leading from the inlet orifice of the inlet to a primary valve seat outlet, a primary valve seat which encircles and is axially aligned with the primary valve seat outlet, an outlet chamber which surrounds encircles and is axially aligned with the axis of the primary valve seat and primary valve seat outlet and which leads from the primary 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 drier and TX valve, a pressure chamber which is axially aligned with the axis of the primary valve seat and is located on the outlet side of the said primary valve seat;
a pressure chamber inlet passageway which allows fluid from the inlet passageway to communicate with the fluid in the pressure chamber;
a trigger passageway which leads from the pressure chamber to the outlet side of the primary valve seat and includes a trigger passageway valve system;
an electric solenoid which, when energised, opens the trigger 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 series with the electric 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.

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 comprising:
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 trigger valve mechanism which can make and break a seal with the trigger passageway valve seat which is located between the trigger passageway connection and the trigger 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 surrounding the trigger passageway return channel.

147. A fluid dispensing spout mechanism according to any of the claims 145 or 146 wherein, the trigger passageway return connection forms a seal with the above counter-top outlet body lower section at the trigger passageway return channel.

148. A fluid dispensing spout mechanism according to any of the claims 145 or 147 wherein, the trigger passageway connection forms a seal with the above counter-top outlet spout body at the trigger passageway leading to the trigger passageway valve seat.

149. A fluid dispensing spout mechanism according to any of the claims 145 or 148 wherein, the trigger passageway is located within the trigger passageway return channel.

150. A fluid dispensing spout mechanism comprising:
an above counter-top outlet spout body which contains more than one main fluid flow passageway such passageway's which leads from differing temperature devices to the spout mechanism, a trigger valve mechanism which can make and break a seal with the trigger passageway valve seat which is located between the trigger passageway connection and the trigger passageway return connection by means of an operational handle, and as the operating handle selects one of the main fluid flow passageways a secondary main fluid flow passageway valve is opened before the trigger 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 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.

153. A fluid flow valve system according to claim 151 or 152 wherein, when the temperature increases above a predetermined valve the temperature probe opens the trigger 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 trigger passageway valve is connected to trigger piston which moves within a trigger pressure chamber such that when the trigger piston moves to its limit of travel away from the trigger valve, the trigger valve closes.

156. A fluid flow valve system according to claim 155 wherein, a trigger pressure passageway communicates between the trigger pressure chamber and the outlet side of the primary valve.

157. A fluid flow valve system according to any of the claims 155 to 156 wherein, the end of the trigger piston furthermost from the trigger passageway valve experiences the effects of atmospheric pressure.

158. A fluid flow valve system according to any of the claims 155 to 157 wherein, the trigger piston is biased towards the trigger passageway valve.

159. A fluid flow valve system according to claim 158 wherein, the biasing means is a spring.

160. A fluid flow valve system according to claim 159 wherein, the tension of the spring is adjustable.

161. A fluid flow valve system according to any of the claims 155 to 160 wherein, as the increasing pressure in the trigger pressure chamber overcomes the biasing means the trigger passageway valve closes.

162. A fluid flow valve system according to any of the claims 1 to 131 wherein, the trigger 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.